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Hongtao WANG王宏涛
浙江大学应用力学所
玉泉校区教12-223
Email htwzjueducn
Mechanics of Materials(甲)I
Chapter 2 Tension and Compression
Axial tension compression and the internal force and
stresses on both cross section and inclined section
Mechanical behavior of materials subjected to tension
and compression as well as Hookersquos law
Deformation and strain energy under axial tension and
compression stress concentration
Statistically indeterminate problems with tension and
compression (including thermal stress and assembly
stress)
21 Axial Tension and Compression
21 Axial Tension and Compression
Force feature
The resultant force of the external forces must be along the axis of the member
21 Axial Tension and Compression
Deformation feature
The member will be elongated or shortened along its axis
Which one is uniaxial tension
21 Axial Tension and Compression
F FBefore tension
After tension
(A)
(B)
Plane Cross-section Assumption
Plane cross-section assumption
If the cross section is plane at first it still remains plane
after deformed and perpendicular to the axial line
21 Axial Tension and Compression
F Fl0
l
Along the axial direction
Elongation
Strain
21 Axial Tension and Compression
Perpendicular to the axial direction
Elongation
Strain
l0
l
d d0
对同一种材料为常数称之为泊松比(Poissonrsquos ratio)
Poissonrsquos ratio
Simeacuteon Denis Poisson (21 June 1781 ndash
25 April 1840) was a French
mathematician geometer and physicist
21 Axial Tension and Compression
Cross-section
Before tension
After tension
d1
d2
d01
d02
1205761 =1198891minus 1198890111988901
1205762 =1198892minus 1198890211988902
1205760 =119897 minus 11989701198970
Tensile strain
1205921 = minus12057611205760
1205922 = minus12057621205760
Poissonrsquos ratio
Poissonrsquos Ratio
Estimate the value of Poissonrsquos ratio
Material property Poissonrsquos ratio
l0
l
d d0Poissonrsquos ratio
109Pa无量纲
Poissonrsquos ratio
Can Poissonrsquos ratio be negative
What is the Poissonrsquos ratio for non-compressible material
Range for Poissonrsquos ratio
22 Internal force amp Stress under Axial Tension amp Compression
PP
m
m
Internal force on cross section
Three steps
1 Cut
2 Replace with Resultant force and resultant moment
3 Equilibrium equations
F1
F3
F2
Fn
F1 FR
F3M
0
0
F
M
Review Cross-sectional Method
Internal force amp Stress Axial Tension amp Compression
PP
m
m
Sign convention for resultant force
N axial forceP
m
m
SIGN CONVENSION
N gt 0 ( tension ) N lt 0 ( compression )
P2P1
m
m
P3 PP
m
m
If a bar is subjected to external forces P1 P1 hellip Pn and
ngt2 then N=N(x)
Axial force diagram (轴力图)
Axial force diagram (轴力图)
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Chapter 2 Tension and Compression
Axial tension compression and the internal force and
stresses on both cross section and inclined section
Mechanical behavior of materials subjected to tension
and compression as well as Hookersquos law
Deformation and strain energy under axial tension and
compression stress concentration
Statistically indeterminate problems with tension and
compression (including thermal stress and assembly
stress)
21 Axial Tension and Compression
21 Axial Tension and Compression
Force feature
The resultant force of the external forces must be along the axis of the member
21 Axial Tension and Compression
Deformation feature
The member will be elongated or shortened along its axis
Which one is uniaxial tension
21 Axial Tension and Compression
F FBefore tension
After tension
(A)
(B)
Plane Cross-section Assumption
Plane cross-section assumption
If the cross section is plane at first it still remains plane
after deformed and perpendicular to the axial line
21 Axial Tension and Compression
F Fl0
l
Along the axial direction
Elongation
Strain
21 Axial Tension and Compression
Perpendicular to the axial direction
Elongation
Strain
l0
l
d d0
对同一种材料为常数称之为泊松比(Poissonrsquos ratio)
Poissonrsquos ratio
Simeacuteon Denis Poisson (21 June 1781 ndash
25 April 1840) was a French
mathematician geometer and physicist
21 Axial Tension and Compression
Cross-section
Before tension
After tension
d1
d2
d01
d02
1205761 =1198891minus 1198890111988901
1205762 =1198892minus 1198890211988902
1205760 =119897 minus 11989701198970
Tensile strain
1205921 = minus12057611205760
1205922 = minus12057621205760
Poissonrsquos ratio
Poissonrsquos Ratio
Estimate the value of Poissonrsquos ratio
Material property Poissonrsquos ratio
l0
l
d d0Poissonrsquos ratio
109Pa无量纲
Poissonrsquos ratio
Can Poissonrsquos ratio be negative
What is the Poissonrsquos ratio for non-compressible material
Range for Poissonrsquos ratio
22 Internal force amp Stress under Axial Tension amp Compression
PP
m
m
Internal force on cross section
Three steps
1 Cut
2 Replace with Resultant force and resultant moment
3 Equilibrium equations
F1
F3
F2
Fn
F1 FR
F3M
0
0
F
M
Review Cross-sectional Method
Internal force amp Stress Axial Tension amp Compression
PP
m
m
Sign convention for resultant force
N axial forceP
m
m
SIGN CONVENSION
N gt 0 ( tension ) N lt 0 ( compression )
P2P1
m
m
P3 PP
m
m
If a bar is subjected to external forces P1 P1 hellip Pn and
ngt2 then N=N(x)
Axial force diagram (轴力图)
Axial force diagram (轴力图)
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
21 Axial Tension and Compression
21 Axial Tension and Compression
Force feature
The resultant force of the external forces must be along the axis of the member
21 Axial Tension and Compression
Deformation feature
The member will be elongated or shortened along its axis
Which one is uniaxial tension
21 Axial Tension and Compression
F FBefore tension
After tension
(A)
(B)
Plane Cross-section Assumption
Plane cross-section assumption
If the cross section is plane at first it still remains plane
after deformed and perpendicular to the axial line
21 Axial Tension and Compression
F Fl0
l
Along the axial direction
Elongation
Strain
21 Axial Tension and Compression
Perpendicular to the axial direction
Elongation
Strain
l0
l
d d0
对同一种材料为常数称之为泊松比(Poissonrsquos ratio)
Poissonrsquos ratio
Simeacuteon Denis Poisson (21 June 1781 ndash
25 April 1840) was a French
mathematician geometer and physicist
21 Axial Tension and Compression
Cross-section
Before tension
After tension
d1
d2
d01
d02
1205761 =1198891minus 1198890111988901
1205762 =1198892minus 1198890211988902
1205760 =119897 minus 11989701198970
Tensile strain
1205921 = minus12057611205760
1205922 = minus12057621205760
Poissonrsquos ratio
Poissonrsquos Ratio
Estimate the value of Poissonrsquos ratio
Material property Poissonrsquos ratio
l0
l
d d0Poissonrsquos ratio
109Pa无量纲
Poissonrsquos ratio
Can Poissonrsquos ratio be negative
What is the Poissonrsquos ratio for non-compressible material
Range for Poissonrsquos ratio
22 Internal force amp Stress under Axial Tension amp Compression
PP
m
m
Internal force on cross section
Three steps
1 Cut
2 Replace with Resultant force and resultant moment
3 Equilibrium equations
F1
F3
F2
Fn
F1 FR
F3M
0
0
F
M
Review Cross-sectional Method
Internal force amp Stress Axial Tension amp Compression
PP
m
m
Sign convention for resultant force
N axial forceP
m
m
SIGN CONVENSION
N gt 0 ( tension ) N lt 0 ( compression )
P2P1
m
m
P3 PP
m
m
If a bar is subjected to external forces P1 P1 hellip Pn and
ngt2 then N=N(x)
Axial force diagram (轴力图)
Axial force diagram (轴力图)
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
21 Axial Tension and Compression
Force feature
The resultant force of the external forces must be along the axis of the member
21 Axial Tension and Compression
Deformation feature
The member will be elongated or shortened along its axis
Which one is uniaxial tension
21 Axial Tension and Compression
F FBefore tension
After tension
(A)
(B)
Plane Cross-section Assumption
Plane cross-section assumption
If the cross section is plane at first it still remains plane
after deformed and perpendicular to the axial line
21 Axial Tension and Compression
F Fl0
l
Along the axial direction
Elongation
Strain
21 Axial Tension and Compression
Perpendicular to the axial direction
Elongation
Strain
l0
l
d d0
对同一种材料为常数称之为泊松比(Poissonrsquos ratio)
Poissonrsquos ratio
Simeacuteon Denis Poisson (21 June 1781 ndash
25 April 1840) was a French
mathematician geometer and physicist
21 Axial Tension and Compression
Cross-section
Before tension
After tension
d1
d2
d01
d02
1205761 =1198891minus 1198890111988901
1205762 =1198892minus 1198890211988902
1205760 =119897 minus 11989701198970
Tensile strain
1205921 = minus12057611205760
1205922 = minus12057621205760
Poissonrsquos ratio
Poissonrsquos Ratio
Estimate the value of Poissonrsquos ratio
Material property Poissonrsquos ratio
l0
l
d d0Poissonrsquos ratio
109Pa无量纲
Poissonrsquos ratio
Can Poissonrsquos ratio be negative
What is the Poissonrsquos ratio for non-compressible material
Range for Poissonrsquos ratio
22 Internal force amp Stress under Axial Tension amp Compression
PP
m
m
Internal force on cross section
Three steps
1 Cut
2 Replace with Resultant force and resultant moment
3 Equilibrium equations
F1
F3
F2
Fn
F1 FR
F3M
0
0
F
M
Review Cross-sectional Method
Internal force amp Stress Axial Tension amp Compression
PP
m
m
Sign convention for resultant force
N axial forceP
m
m
SIGN CONVENSION
N gt 0 ( tension ) N lt 0 ( compression )
P2P1
m
m
P3 PP
m
m
If a bar is subjected to external forces P1 P1 hellip Pn and
ngt2 then N=N(x)
Axial force diagram (轴力图)
Axial force diagram (轴力图)
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Force feature
The resultant force of the external forces must be along the axis of the member
21 Axial Tension and Compression
Deformation feature
The member will be elongated or shortened along its axis
Which one is uniaxial tension
21 Axial Tension and Compression
F FBefore tension
After tension
(A)
(B)
Plane Cross-section Assumption
Plane cross-section assumption
If the cross section is plane at first it still remains plane
after deformed and perpendicular to the axial line
21 Axial Tension and Compression
F Fl0
l
Along the axial direction
Elongation
Strain
21 Axial Tension and Compression
Perpendicular to the axial direction
Elongation
Strain
l0
l
d d0
对同一种材料为常数称之为泊松比(Poissonrsquos ratio)
Poissonrsquos ratio
Simeacuteon Denis Poisson (21 June 1781 ndash
25 April 1840) was a French
mathematician geometer and physicist
21 Axial Tension and Compression
Cross-section
Before tension
After tension
d1
d2
d01
d02
1205761 =1198891minus 1198890111988901
1205762 =1198892minus 1198890211988902
1205760 =119897 minus 11989701198970
Tensile strain
1205921 = minus12057611205760
1205922 = minus12057621205760
Poissonrsquos ratio
Poissonrsquos Ratio
Estimate the value of Poissonrsquos ratio
Material property Poissonrsquos ratio
l0
l
d d0Poissonrsquos ratio
109Pa无量纲
Poissonrsquos ratio
Can Poissonrsquos ratio be negative
What is the Poissonrsquos ratio for non-compressible material
Range for Poissonrsquos ratio
22 Internal force amp Stress under Axial Tension amp Compression
PP
m
m
Internal force on cross section
Three steps
1 Cut
2 Replace with Resultant force and resultant moment
3 Equilibrium equations
F1
F3
F2
Fn
F1 FR
F3M
0
0
F
M
Review Cross-sectional Method
Internal force amp Stress Axial Tension amp Compression
PP
m
m
Sign convention for resultant force
N axial forceP
m
m
SIGN CONVENSION
N gt 0 ( tension ) N lt 0 ( compression )
P2P1
m
m
P3 PP
m
m
If a bar is subjected to external forces P1 P1 hellip Pn and
ngt2 then N=N(x)
Axial force diagram (轴力图)
Axial force diagram (轴力图)
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Which one is uniaxial tension
21 Axial Tension and Compression
F FBefore tension
After tension
(A)
(B)
Plane Cross-section Assumption
Plane cross-section assumption
If the cross section is plane at first it still remains plane
after deformed and perpendicular to the axial line
21 Axial Tension and Compression
F Fl0
l
Along the axial direction
Elongation
Strain
21 Axial Tension and Compression
Perpendicular to the axial direction
Elongation
Strain
l0
l
d d0
对同一种材料为常数称之为泊松比(Poissonrsquos ratio)
Poissonrsquos ratio
Simeacuteon Denis Poisson (21 June 1781 ndash
25 April 1840) was a French
mathematician geometer and physicist
21 Axial Tension and Compression
Cross-section
Before tension
After tension
d1
d2
d01
d02
1205761 =1198891minus 1198890111988901
1205762 =1198892minus 1198890211988902
1205760 =119897 minus 11989701198970
Tensile strain
1205921 = minus12057611205760
1205922 = minus12057621205760
Poissonrsquos ratio
Poissonrsquos Ratio
Estimate the value of Poissonrsquos ratio
Material property Poissonrsquos ratio
l0
l
d d0Poissonrsquos ratio
109Pa无量纲
Poissonrsquos ratio
Can Poissonrsquos ratio be negative
What is the Poissonrsquos ratio for non-compressible material
Range for Poissonrsquos ratio
22 Internal force amp Stress under Axial Tension amp Compression
PP
m
m
Internal force on cross section
Three steps
1 Cut
2 Replace with Resultant force and resultant moment
3 Equilibrium equations
F1
F3
F2
Fn
F1 FR
F3M
0
0
F
M
Review Cross-sectional Method
Internal force amp Stress Axial Tension amp Compression
PP
m
m
Sign convention for resultant force
N axial forceP
m
m
SIGN CONVENSION
N gt 0 ( tension ) N lt 0 ( compression )
P2P1
m
m
P3 PP
m
m
If a bar is subjected to external forces P1 P1 hellip Pn and
ngt2 then N=N(x)
Axial force diagram (轴力图)
Axial force diagram (轴力图)
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
21 Axial Tension and Compression
F FBefore tension
After tension
(A)
(B)
Plane Cross-section Assumption
Plane cross-section assumption
If the cross section is plane at first it still remains plane
after deformed and perpendicular to the axial line
21 Axial Tension and Compression
F Fl0
l
Along the axial direction
Elongation
Strain
21 Axial Tension and Compression
Perpendicular to the axial direction
Elongation
Strain
l0
l
d d0
对同一种材料为常数称之为泊松比(Poissonrsquos ratio)
Poissonrsquos ratio
Simeacuteon Denis Poisson (21 June 1781 ndash
25 April 1840) was a French
mathematician geometer and physicist
21 Axial Tension and Compression
Cross-section
Before tension
After tension
d1
d2
d01
d02
1205761 =1198891minus 1198890111988901
1205762 =1198892minus 1198890211988902
1205760 =119897 minus 11989701198970
Tensile strain
1205921 = minus12057611205760
1205922 = minus12057621205760
Poissonrsquos ratio
Poissonrsquos Ratio
Estimate the value of Poissonrsquos ratio
Material property Poissonrsquos ratio
l0
l
d d0Poissonrsquos ratio
109Pa无量纲
Poissonrsquos ratio
Can Poissonrsquos ratio be negative
What is the Poissonrsquos ratio for non-compressible material
Range for Poissonrsquos ratio
22 Internal force amp Stress under Axial Tension amp Compression
PP
m
m
Internal force on cross section
Three steps
1 Cut
2 Replace with Resultant force and resultant moment
3 Equilibrium equations
F1
F3
F2
Fn
F1 FR
F3M
0
0
F
M
Review Cross-sectional Method
Internal force amp Stress Axial Tension amp Compression
PP
m
m
Sign convention for resultant force
N axial forceP
m
m
SIGN CONVENSION
N gt 0 ( tension ) N lt 0 ( compression )
P2P1
m
m
P3 PP
m
m
If a bar is subjected to external forces P1 P1 hellip Pn and
ngt2 then N=N(x)
Axial force diagram (轴力图)
Axial force diagram (轴力图)
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Plane cross-section assumption
If the cross section is plane at first it still remains plane
after deformed and perpendicular to the axial line
21 Axial Tension and Compression
F Fl0
l
Along the axial direction
Elongation
Strain
21 Axial Tension and Compression
Perpendicular to the axial direction
Elongation
Strain
l0
l
d d0
对同一种材料为常数称之为泊松比(Poissonrsquos ratio)
Poissonrsquos ratio
Simeacuteon Denis Poisson (21 June 1781 ndash
25 April 1840) was a French
mathematician geometer and physicist
21 Axial Tension and Compression
Cross-section
Before tension
After tension
d1
d2
d01
d02
1205761 =1198891minus 1198890111988901
1205762 =1198892minus 1198890211988902
1205760 =119897 minus 11989701198970
Tensile strain
1205921 = minus12057611205760
1205922 = minus12057621205760
Poissonrsquos ratio
Poissonrsquos Ratio
Estimate the value of Poissonrsquos ratio
Material property Poissonrsquos ratio
l0
l
d d0Poissonrsquos ratio
109Pa无量纲
Poissonrsquos ratio
Can Poissonrsquos ratio be negative
What is the Poissonrsquos ratio for non-compressible material
Range for Poissonrsquos ratio
22 Internal force amp Stress under Axial Tension amp Compression
PP
m
m
Internal force on cross section
Three steps
1 Cut
2 Replace with Resultant force and resultant moment
3 Equilibrium equations
F1
F3
F2
Fn
F1 FR
F3M
0
0
F
M
Review Cross-sectional Method
Internal force amp Stress Axial Tension amp Compression
PP
m
m
Sign convention for resultant force
N axial forceP
m
m
SIGN CONVENSION
N gt 0 ( tension ) N lt 0 ( compression )
P2P1
m
m
P3 PP
m
m
If a bar is subjected to external forces P1 P1 hellip Pn and
ngt2 then N=N(x)
Axial force diagram (轴力图)
Axial force diagram (轴力图)
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
21 Axial Tension and Compression
F Fl0
l
Along the axial direction
Elongation
Strain
21 Axial Tension and Compression
Perpendicular to the axial direction
Elongation
Strain
l0
l
d d0
对同一种材料为常数称之为泊松比(Poissonrsquos ratio)
Poissonrsquos ratio
Simeacuteon Denis Poisson (21 June 1781 ndash
25 April 1840) was a French
mathematician geometer and physicist
21 Axial Tension and Compression
Cross-section
Before tension
After tension
d1
d2
d01
d02
1205761 =1198891minus 1198890111988901
1205762 =1198892minus 1198890211988902
1205760 =119897 minus 11989701198970
Tensile strain
1205921 = minus12057611205760
1205922 = minus12057621205760
Poissonrsquos ratio
Poissonrsquos Ratio
Estimate the value of Poissonrsquos ratio
Material property Poissonrsquos ratio
l0
l
d d0Poissonrsquos ratio
109Pa无量纲
Poissonrsquos ratio
Can Poissonrsquos ratio be negative
What is the Poissonrsquos ratio for non-compressible material
Range for Poissonrsquos ratio
22 Internal force amp Stress under Axial Tension amp Compression
PP
m
m
Internal force on cross section
Three steps
1 Cut
2 Replace with Resultant force and resultant moment
3 Equilibrium equations
F1
F3
F2
Fn
F1 FR
F3M
0
0
F
M
Review Cross-sectional Method
Internal force amp Stress Axial Tension amp Compression
PP
m
m
Sign convention for resultant force
N axial forceP
m
m
SIGN CONVENSION
N gt 0 ( tension ) N lt 0 ( compression )
P2P1
m
m
P3 PP
m
m
If a bar is subjected to external forces P1 P1 hellip Pn and
ngt2 then N=N(x)
Axial force diagram (轴力图)
Axial force diagram (轴力图)
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
21 Axial Tension and Compression
Perpendicular to the axial direction
Elongation
Strain
l0
l
d d0
对同一种材料为常数称之为泊松比(Poissonrsquos ratio)
Poissonrsquos ratio
Simeacuteon Denis Poisson (21 June 1781 ndash
25 April 1840) was a French
mathematician geometer and physicist
21 Axial Tension and Compression
Cross-section
Before tension
After tension
d1
d2
d01
d02
1205761 =1198891minus 1198890111988901
1205762 =1198892minus 1198890211988902
1205760 =119897 minus 11989701198970
Tensile strain
1205921 = minus12057611205760
1205922 = minus12057621205760
Poissonrsquos ratio
Poissonrsquos Ratio
Estimate the value of Poissonrsquos ratio
Material property Poissonrsquos ratio
l0
l
d d0Poissonrsquos ratio
109Pa无量纲
Poissonrsquos ratio
Can Poissonrsquos ratio be negative
What is the Poissonrsquos ratio for non-compressible material
Range for Poissonrsquos ratio
22 Internal force amp Stress under Axial Tension amp Compression
PP
m
m
Internal force on cross section
Three steps
1 Cut
2 Replace with Resultant force and resultant moment
3 Equilibrium equations
F1
F3
F2
Fn
F1 FR
F3M
0
0
F
M
Review Cross-sectional Method
Internal force amp Stress Axial Tension amp Compression
PP
m
m
Sign convention for resultant force
N axial forceP
m
m
SIGN CONVENSION
N gt 0 ( tension ) N lt 0 ( compression )
P2P1
m
m
P3 PP
m
m
If a bar is subjected to external forces P1 P1 hellip Pn and
ngt2 then N=N(x)
Axial force diagram (轴力图)
Axial force diagram (轴力图)
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
21 Axial Tension and Compression
Cross-section
Before tension
After tension
d1
d2
d01
d02
1205761 =1198891minus 1198890111988901
1205762 =1198892minus 1198890211988902
1205760 =119897 minus 11989701198970
Tensile strain
1205921 = minus12057611205760
1205922 = minus12057621205760
Poissonrsquos ratio
Poissonrsquos Ratio
Estimate the value of Poissonrsquos ratio
Material property Poissonrsquos ratio
l0
l
d d0Poissonrsquos ratio
109Pa无量纲
Poissonrsquos ratio
Can Poissonrsquos ratio be negative
What is the Poissonrsquos ratio for non-compressible material
Range for Poissonrsquos ratio
22 Internal force amp Stress under Axial Tension amp Compression
PP
m
m
Internal force on cross section
Three steps
1 Cut
2 Replace with Resultant force and resultant moment
3 Equilibrium equations
F1
F3
F2
Fn
F1 FR
F3M
0
0
F
M
Review Cross-sectional Method
Internal force amp Stress Axial Tension amp Compression
PP
m
m
Sign convention for resultant force
N axial forceP
m
m
SIGN CONVENSION
N gt 0 ( tension ) N lt 0 ( compression )
P2P1
m
m
P3 PP
m
m
If a bar is subjected to external forces P1 P1 hellip Pn and
ngt2 then N=N(x)
Axial force diagram (轴力图)
Axial force diagram (轴力图)
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Poissonrsquos Ratio
Estimate the value of Poissonrsquos ratio
Material property Poissonrsquos ratio
l0
l
d d0Poissonrsquos ratio
109Pa无量纲
Poissonrsquos ratio
Can Poissonrsquos ratio be negative
What is the Poissonrsquos ratio for non-compressible material
Range for Poissonrsquos ratio
22 Internal force amp Stress under Axial Tension amp Compression
PP
m
m
Internal force on cross section
Three steps
1 Cut
2 Replace with Resultant force and resultant moment
3 Equilibrium equations
F1
F3
F2
Fn
F1 FR
F3M
0
0
F
M
Review Cross-sectional Method
Internal force amp Stress Axial Tension amp Compression
PP
m
m
Sign convention for resultant force
N axial forceP
m
m
SIGN CONVENSION
N gt 0 ( tension ) N lt 0 ( compression )
P2P1
m
m
P3 PP
m
m
If a bar is subjected to external forces P1 P1 hellip Pn and
ngt2 then N=N(x)
Axial force diagram (轴力图)
Axial force diagram (轴力图)
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Material property Poissonrsquos ratio
l0
l
d d0Poissonrsquos ratio
109Pa无量纲
Poissonrsquos ratio
Can Poissonrsquos ratio be negative
What is the Poissonrsquos ratio for non-compressible material
Range for Poissonrsquos ratio
22 Internal force amp Stress under Axial Tension amp Compression
PP
m
m
Internal force on cross section
Three steps
1 Cut
2 Replace with Resultant force and resultant moment
3 Equilibrium equations
F1
F3
F2
Fn
F1 FR
F3M
0
0
F
M
Review Cross-sectional Method
Internal force amp Stress Axial Tension amp Compression
PP
m
m
Sign convention for resultant force
N axial forceP
m
m
SIGN CONVENSION
N gt 0 ( tension ) N lt 0 ( compression )
P2P1
m
m
P3 PP
m
m
If a bar is subjected to external forces P1 P1 hellip Pn and
ngt2 then N=N(x)
Axial force diagram (轴力图)
Axial force diagram (轴力图)
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Poissonrsquos ratio
Can Poissonrsquos ratio be negative
What is the Poissonrsquos ratio for non-compressible material
Range for Poissonrsquos ratio
22 Internal force amp Stress under Axial Tension amp Compression
PP
m
m
Internal force on cross section
Three steps
1 Cut
2 Replace with Resultant force and resultant moment
3 Equilibrium equations
F1
F3
F2
Fn
F1 FR
F3M
0
0
F
M
Review Cross-sectional Method
Internal force amp Stress Axial Tension amp Compression
PP
m
m
Sign convention for resultant force
N axial forceP
m
m
SIGN CONVENSION
N gt 0 ( tension ) N lt 0 ( compression )
P2P1
m
m
P3 PP
m
m
If a bar is subjected to external forces P1 P1 hellip Pn and
ngt2 then N=N(x)
Axial force diagram (轴力图)
Axial force diagram (轴力图)
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
22 Internal force amp Stress under Axial Tension amp Compression
PP
m
m
Internal force on cross section
Three steps
1 Cut
2 Replace with Resultant force and resultant moment
3 Equilibrium equations
F1
F3
F2
Fn
F1 FR
F3M
0
0
F
M
Review Cross-sectional Method
Internal force amp Stress Axial Tension amp Compression
PP
m
m
Sign convention for resultant force
N axial forceP
m
m
SIGN CONVENSION
N gt 0 ( tension ) N lt 0 ( compression )
P2P1
m
m
P3 PP
m
m
If a bar is subjected to external forces P1 P1 hellip Pn and
ngt2 then N=N(x)
Axial force diagram (轴力图)
Axial force diagram (轴力图)
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Three steps
1 Cut
2 Replace with Resultant force and resultant moment
3 Equilibrium equations
F1
F3
F2
Fn
F1 FR
F3M
0
0
F
M
Review Cross-sectional Method
Internal force amp Stress Axial Tension amp Compression
PP
m
m
Sign convention for resultant force
N axial forceP
m
m
SIGN CONVENSION
N gt 0 ( tension ) N lt 0 ( compression )
P2P1
m
m
P3 PP
m
m
If a bar is subjected to external forces P1 P1 hellip Pn and
ngt2 then N=N(x)
Axial force diagram (轴力图)
Axial force diagram (轴力图)
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Internal force amp Stress Axial Tension amp Compression
PP
m
m
Sign convention for resultant force
N axial forceP
m
m
SIGN CONVENSION
N gt 0 ( tension ) N lt 0 ( compression )
P2P1
m
m
P3 PP
m
m
If a bar is subjected to external forces P1 P1 hellip Pn and
ngt2 then N=N(x)
Axial force diagram (轴力图)
Axial force diagram (轴力图)
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
P2P1
m
m
P3 PP
m
m
If a bar is subjected to external forces P1 P1 hellip Pn and
ngt2 then N=N(x)
Axial force diagram (轴力图)
Axial force diagram (轴力图)
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Problem A bar is subjected to the force system as shown in the following Fig Plot the axial force diagram of the bar
P1=2kNP2=3kN
P3=1kNA BC
N2P1 =2kNP2 =3kN
AC
A BC2kN
1kN
Axial force diagram
sumX=0 N1-P1=0
sumX=0 N2+P2-P1=0
1
1
2
2
P1=2kN
A
N1
1
1N1=P1=2kN
N2=P1-P2= -1kN
Example 21
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
P1=2kNP2=3kN
P3=1kNA BC
1
1
2
2
Is there a more simple way to obtain the axial force on 2-2
section
Example 21
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
P A
C
m
m
C
m
m
p
m
Pp
A
0 0
lim limmA A
Pp p
A
normal stress
shear stress
Review Stress
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
PP
m
m
PN
22 Stress on cross section
Uniform stress distribution But why
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
PN
A
N dA
A
N dA A N
A
+ (tension stress)
- (compression stress)
Unit Pa=Nm2
1MPa=106Nm2
22 Stress on Cross Section
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Uniform stress distribution Advantage
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Uniform stress distribution Advantage
Assumption Same cross-section area
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Uniform stress distribution Advantage
Every part of the material has the same efficiency
Good for equal-life design
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
( )( )
( )
N xx
A x
1 Bar with varying cross-sections
Fixed PA(x)
2 Bar with varying axial force
Fixed Pp(x)
Axial force diagram
Stress on Cross Section
Is this correct
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Stress on Cross Section
Is this correct ( )( )
( )
N xx
A x
Correct Good approximation Poor approximation
N N N
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Stress on Cross Section
Real stress at point P is
A(x)
N
Approximate stress at point P is a NA(x)
P
Compare and a
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Comparison
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Saint-Venantrsquos Principle for axial tensioncompression
The difference between the
effects of two different but
statically equivalent loads
becomes very small at
sufficiently large distances
from load
Adheacutemar Jean Claude Barreacute de Saint-Venant (August 23
1797 Villiers-en-Biegravere Seine-et-Marne ndash January 1886)
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Example 22
Given F=20kN calculate the stress in rod AB
and CB The cross-section of rod AB is a circle
with diameter of 20mm while it is a square
(15times15mm)for rod BC
F
A
B
C
0yF
kN3281 NF
Solution
1 Calculate the axial force
kN202 NF
0xF
45deg
045cos 21 NN FF
045sin1 FFN
1
2F
B
F
1NF
2NF x
y
45deg
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Example 22
kN3281 NF kN202 NF
2 Calculate the stress
MPa90Pa1090
10204
10328
6
62
3
1
11
A
FN
MPa89Pa1089
1015
1020
6
62
3
2
22
A
FN
F
A
B
C
45deg
1
2F
B
F
1NF
2NF x
y
45deg
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
22 Internal force amp Stress under Axial Tension amp Compression
PP
k
k
Internal force on inclined section
It is observed from experiments that during tensile or
compressive loading a bar may break along inclined
section instead of cross-section
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
P
A Normal stress on cross section
PPk
k
k
k
P P
k
k
PP
p
Internal Force on Inclined Section
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
k
k
P P
k
k
PP
p
cos
AA
P P
cos cosP P P
pA A A
2cos cosp
sin 2sin
2p
Internal Force on Inclined Section
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Internal Force on Inclined Section
k
k
P P
2cos cosp
sin 2sin
2p
Discussion
1 If =0 takes the greatest value
2 If =45ordm takes the greatest value
max
max2
3 If =90ordmmax max 0
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
23 Hookersquos Law
F Fl0
l
Review
External load Material response
F
Global
Local
k 包含了材料和几何尺寸所有的性质
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
23 Hookersquos Law
宏观物理量
载荷F
几何
微观物理量
弹性模量E 是材料属性
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Material property Elastic Modulus
l0
l
d d0
109Pa无量纲
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
23 Hookersquos Law
Robert Hooke FRS (hʊk 28 July [OS 18 July]
1635 ndash 3 March 1703) was an English natural
philosopher architect and polymath
The linear relation between
stress and strain for a bar in a
simple tension or compression
is expressed by = Ee
E is defined as modulus of
elasticity
Note Hookersquos law is a first-order approximation
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Example 23
C
Plot the enlargement sketch of the small deformation
Accurate method to plot diagram of deformation the arc line as shown in the figure
CCrsquo is the REAL displacement
Determine deformation Li of each rod as shown in Fig l
Approximate method to plot the diagram of deformation the tangent of the arc line shown in the figure
CCrsquorsquo is the APPROXIMATE displacement
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Example 23
C
A B
C
L1 L2
P1L
2L
C
Determine the displacement of Point C
What is the error
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Example 23
The length of bar AB is 2m the area 200mm2 The
area of AC is 250mm2 E=200GPa F=10kN Determine
the displacement of A
0yFkN202sin1 FFFN
Solution 1 Calculate axial force AB is taken as 1
while AC 2 At point A
kN32173cos12 FFF NN
0xF 0cos 21 NN FF
0sin1 FFN
2 Calculate the deformation of two bars
1mmm1011020010200
21020 3
69
3
11
111
AE
lFl N
A
F
1NF
2NF x
y
300
mm60m10601025010200
7321103217 3
69
3
22
222
AE
lFl N
AB tensed by
AC compressed by
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Example 23
3 Calculate displacement at A
A
F
1NF
2NF x
y
300
1mm11
111
AE
lFl N
mm6022
222
AE
lFl N
A
A
1A2A
A
A
1A2A
mm111 lAA
mm6022 lAA
mm602 lx
mm039303912
30tan30sin
21433
llAAAAy
mm13
039360 2222
yxAA
3A
4A
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Example 23
i ii
N ll l
EA
Changes in lengths of nonuniform bars - bar consisting of several prismatic segments
Fixed PA(x)
Fixed Pp(x)
Bars with continuously varying loads or dimensions
ii
iii
AE
lNll
ii
i
Nll l
EA
( )( )
( )
N xx
A x
( )d
( )L
N x xl
EA x
( )d( )
( )
N x xd l
EA x
dx
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Example 23
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
24 Strain Energy
Strain energy
The energy which is stored within an deformable body due to its deformation
The strain energy of a straight bar under tension
P
l
Δl
EA
Pll
Δl
P
P
Δl
dP1
dΔl1
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
24 Strain Energy
0 0
1d d
2
l l EA lW P l l P l
l
Δl
P
P
Δl
P
dΔl
The work of external force = strain energy
l
lEA
EA
lPlPWU
2
)(
22
1 22
The strain energy density
EE
Al
lP
V
Uu
22
1
2
122
2 ee
Notes
Unit Jm3
dW=Pdl
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
能量原理
应变能 =应变能密度的体积积分=外力对边界做的功
偶然必然数学上有无类似的定理
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
观察
F
l
Δl系统应变能对作用在该点的力的偏导数等于力作用点沿力作用方向的位移
这种方法叫能量法EA
lFV
2
2
e
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
能量法求位移
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Calculate the displacement of A
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Difference
Axial force can be obtained from
equilibrium equationsAxial force can NOT be obtained from
equilibrium equations
Statistically determinate problem Statistically indeterminate problem
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
25 Statistically Indeterminate Structures
约束反力不能由平衡方程求得
静不定度(次)数约束反力多于
独立平衡方程的数
独立平衡方程数平面任意力系
3个平衡方程平面共点力系
2个平衡方程
平面平行力系2个平衡方程 共线力系1个平衡方程
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
25 Statistically Indeterminate Structures
Compatibility equation
(geometric equation kinematic
equation consistent deformation
equation)
of unknown axial forces gt of equilibrium equations
Equilibrium equation
Constitutive equation
Compatibility equation
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Example 25
1 Equilibrium equation
Solution
210 NNx FFF
FFFF NNy 31 cos20
2 Geometric equation
cos321 lll
3 Constitutive relation
cos
11
EA
lFl N
EA
lFl N 33
4 Complementary equation
coscos
31
EA
lF
EA
lF NN
2
31 cosNN FF
5 Solving equilibrium amp complementary equation
3
2
21cos21
cos
FFF NN 33
cos21
FFN
1l 2l
3l
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Example 25
A bar-AB subjected to axial external force P is rigidly fixed at two
ends Area of cross-section is AElastic modulus is ETry to
determine the support reaction
(1)equilibrium equation
00 PRRY BA
(2) Deformation geometric
relationship
lll CBAC
(b)
Solution
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
25 Statistically Indeterminate Structures
EA
aRl
EA
a2Rl
BCB
AAC
(4) Complementary equation
EA
aR
EA
a2R BA
BA RR2
3
P2R
3
PR BA
(c)
(5) solving equilibrium equation amp
complementary equation
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Example 25
3 bars are made of the same materials Area of AB is
200mm2 area of AC 300 mm2 and area of AD 400 mm2
F=30kN Determine the axial force of each bar
3
2lll ADAB
(1) Equilibrium equation
0 xF0
32
0
1 30cos30cos NNN FFF
FFFF NNy 0
3
0
1 30sin30sin0
that is 1323 321 NNN FFF
2231 FFF NN
(2) Compatibility equation
Solution (0) Assuming the length of bar AB is l
lengths of AB amp AD are therefore
F
30A
B
C30
D
1
2
3
F
A x
y1NF
2NF
3NF
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Example 25
1323 321 NNN FFF
2231 FFF NN
Compatibility equation
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
The components of the
displacement at A are projected to
each bar
cossin1 xyl
xl 2
cossin3 xyl
cos2 213 lll
Deformation relation
213 3 lll
Substituting them into constitutive relation
2
2
1
1
3
3 3
3
2
3
2
EA
lF
EA
lF
EA
lF NNN
322 213 NNN FFF We obtain
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Example 25
F
30A
B
C30
D
1
2
3
x
y
F
A
1NF
2NF
3NF
x
y
A
Ax
y
1323 321 NNN FFF
2231 FFF NN
322 213 NNN FFF
From ①②③ we obtain
kN6343
23 FFN
MPa6863
MPa8262
kN048232 FFN
(tension)
MPa1271
kN4253
221
FFN
(tension)
(compression)
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Method and Steps
Equilibrium equations
Geometric equationmdashcompatibility equation of
deformation
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving statically indeterminate problems
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
Source of Stress
Is there any stress if NO external load
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
2010年10月26日沪杭高铁开通时速最高可达4166公里
1979年台风ldquo泰培rdquo时速306公里这是地球纪录上最强的热带气旋飞机的起飞速度300kmh
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
沪杭高铁轨道(无砟轨道)
无缝钢轨(404根小钢轨焊接形成一条完全无缝隙的ldquo大钢条rdquo长202公里)
轨道板
填充层(厚2-4厘米和Ⅱ型板一样宽水泥乳化沥青砂浆它的作用是缓冲力道调平)
底座板
滑动层(5毫米左右厚其实是两层布加一层膜)
五层结构
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
26 Thermal Stress
The bar-AB is shown in figure Try to
determine the thermal stress after increasing
T
(1)Equilibrium equationSolution
(2)Geometric equation
T Rl l
(3)Physical relation
lTlT
(4)Complementary equation
EA
RllT
EA
RllR
TEAR TEA
R
0RR0X BA RRRSo BA
Thermal stress Stresses due to temperature change
No thermal stress in statistically determined structure
Thermal stress exists in statistically indetermined structure with partial or total
deformation constrained
(5)Solving complementary equation amp
equilibrium equation
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
26 Thermal Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including thermal item)
Physical equation mdash Constitutive law (including thermal
item)
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving thermal stress problems
Tl T l
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
26 Thermal Stress
Materials and dimensions of rod 1and2 are all
the same as shown in the figure If temperature
of the structure changes from T1 to T2
determine the thermal internal forces of each
rod(linear thermal expansion coefficient of
each rod i T= T2 -T1)
C
A
B D
1 2
3
A1
1L2L
3L
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Geometric equation
Solution Equilibrium equations
1 2sin sin 0X N N
0coscos 321 NNNY
cos31 LL
ii
ii
iii LT
AE
LNL
Physical equation
A
N1
N3
N2
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
26 Thermal Stress
C
A
B D
1 2
3
A1
1L2L
3L
Complementary equation
cos)( 33
33
3311
11
11 LTAE
LNLT
AE
LN
Solving equilibrium equations and the
complementary equation we get
cos21
)cos(
3311
3
2
311121
AEAE
TAENN
cos21
cos)cos(2
3311
3
2
31113
AEAE
TAEN
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
26 Thermal Stress
aa
aa
N1
N2
The upper and lower ends of a ladder-like steel shaft are fixed
at temperature T1=5 as shown in the figure Areas of the
upper and lower segments are 1=cm2 and 2=cm2
respectively When its temperature reaches T2=25
determine the temperature stress of each rod(Linear thermal
expansion coefficient = 125times10 -6 1oCElastic Modulus
E=200GPa)
Geometric equation
Solution Equilibrium equation
021 NNY
0 NT LLL
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
26 Thermal Stress
Physical equation
Solving equilibrium equations and the
complementary equation we get kN 33321 NN
Complementary equation 2
2
1
1 2EA
aN
EA
aNLTaL NT
2
2
1
12EA
N
EA
NT
Temperature stresses
MPa 7661
11
A
N MPa 333
2
22
A
N
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
27 Assembly Stress
Assembly stress Stresses due to manufacturing error
No Assembly stress in statistically determined structure
Assembly stress exists in statistically indetermined structure with manufacturing error
A
B C
1 2
A
B C
1 2
D
A1
3
Compatible
Incompatible
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
27 Assembly Stress
Geometric equation
Solution Equilibrium equations
0sinsin 21 NNX
0coscos 321 NNNY
13 cos)( LL
The dimension error of rod 3 is as shown in the figure
Determine the assemble internal force of each rod
A
B C
1 2
D
A1
3
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
27 Assembly Stress
cos)(33
33
11
11
AE
LN
AE
LN
Physical equation and complementary equation
Solving equilibrium equations and
the complementary equation we get
cos21
cos
3311
3
2
11
3
21AEAE
AE
LNN
cos21
cos2
3311
3
3
11
3
3AEAE
AE
LN
d
A1
N1
N2
N3
A
A13L
2L1L
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End
27 Assembly Stress
Equilibrium equations
Geometric equationmdashcompatibility equation of deformation
(including manufacturing error)
Physical equation mdash Constitutive law
Complementary equationfrom geometric equation and
physical equation
Solving equilibrium equations and the complementary
equation
Method and steps for solving assembly stress problems
The End