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HRSG pressure part strength calculation
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Page of 1 of 23
Project no. 06745 TAG no. -
Plant Job No : 06B103
Customer /final customer Purpose
Revision A 2006-12-17
No. Date Prepared Approved
Hangzhou BoilerGroup Co.Ltd.
Technical specification
Hariza 9E HRSG
FOR APPROVAL
模块4强度计算书Pressure Parts Strength Calculations-Module 4 (IBR)
DWG. No.:06745JS2(7)
Calculation Criterion:Indian Boiler Act 1923,and Regulations 1950 up to Amendment22nd.Feb.2005
1 st issue
Text
No. PAGE
1 32 33 54 65 86 9
1 132 143 19
Drawn Checked Reviewed ApprovedDate Date Date Date
INTERMEDIATE HEADER 1~3 OF HP ECON1/IP ECON (RIGHT)
OUTLET AND INLET HEADER OF HP ECON1 INTERMEDIATE HEADER 1~3 OF HP ECON1OUTLET AND INLET HEADER OF HP ECON1/IP ECONINTERMEDIATE HEADER 1~3 OF HP ECON1/IP ECON (LEFT)
LP EVAP
NOTE:
HP ECON1 AND IP ECONCOIL OF HP ECON1 AND IP ECON
COIL OF LP EVAPOUTLET AND INLET HEADER OF LP EVAPLP EVAP MANIFOLD
06745JS2(7)
CONTENTSDESIGNATION
Hangzhou BoilerGroup Co.,Ltd
PRESSURE PARTS STRENGTHCALCULATIONS-MODULE 4#
1.THIS CALCULATION BASED ON THE PRESSURE PARTS CAL.06745JS2(4)(ASME)REV:A,CHECK THE MAIN PRESSUERING PARTS AS PER IBR(ACT 1923 ,AND REGULATIONS 1950UP TO AMENDMENT 22ND FEB,2005).
2.MARGIN FOR CORROSION IN THIS CALCULATION TAKE 0mm FOR COIL AND HEADER.
page 2 of 23
custormary metric
1. COIL OF HP ECON1 AND IP ECONDWG.NO.:745147-1-0 Coil Calculation IBR-338(a)(Eqn87)
1.1 Design Pressure of HPECON1 DP psi 1290 8.89
Design Pressure of IPECON 700 4.83
1.2 Design Temperature t ℉ 700 371.111.3 Material Of tube SA210 A-11.4 Outer Diameter of Tube Do in 1.5 38.1
1.5 Actual Thickness of Row1-19 tn in 0.105 2.667
1.6 Allowable Stress of Row 1-19 ft psi ASME Ⅱ,PART D TABLE 1A,P12 15600 107.56
1.7 C in 0 00.03 0.75
1.8 Corrosion C' in 0
1.9 Caculation Thickness ofHP ECON1 Tcal in (Dp*Do)/(2*ft+Dp)+C 0.060 1.51
Caculation Thickness of IPECON 0.062 1.59
1.10 Min Required Thickness ofHP ECON1 Tmin in Tcal+C' 0.060
Min Required Thickness ofIP ECON 0.062
06745JS2(7)
Caculation of Headers and coils
The principle of selecting allowable stress is same as HP SHTR2, allowance stress value in ASME codeSec Ⅱ Part D is more conservation.
Selected According to IBR338(a), Dp≤1000psi,C=0.75;Dp>1000psi,C=0
CONCLUSION:The thickness provided are greater than the value required by IBR,so the designis safe.
VALUE
Hangzhou Boiler GroupCo.,Ltd
PRESSURE PARTS STRENGTHCALCULATIONS-HP ECON/ IP ECON
No. NAME SIGN UNITS FORMULA AND CALCULATION
page 3 of 23
2.OUTLET AND INLET HEADER OF HP ECON1 DWG.NO.:745148-8-0 & 745148-9-0
2.1 Header Shell Calculation IBR-342(Eqn72)2.1.1 Design Pressure DP psi 1290psi+25ft water column 13012.1.2 Design Temperature t ℉ max{inle=395;outlet=475} 4752.1.3 Material Of Header SA106 B2.1.4 Outer Diameter of Header Do in 8" 8.625 219.12.1.5 Inside Diameter of Header D in 7.19 182.58
2.1.6 Nominal Thickness ofHeader Tn in Sch 120 0.719 18.26
2.1.7 Allowable Stress fs psi ASME Ⅱ,PART D TABLE 1A,P12 17100
2.1.8 Efficiency EP 3.72 94.52d 1.5 38.1E IBR-215:(P-d)/P 0.597
2.1.9 Allowable Deviation ofThickness a % 12.5
2.1.10 Corrision C in 02.1.11 Effective Thichness Te in Te=Tn*(1-a%) 0.6292.1.12 Calculation Thickness Tcal in (Dp*D)/(2*fs*E-Dp)+0.03 0.5192.1.13 Min Required Thickness Tmin in Tcal+C 0.5192.1.14 Working Pressure W.P. psi 2*fs*E(Te-0.03-C)/(D+Te-0.03-C) 1571
2.2 Header End Plate Calculation IBR-340(89A)
2.2.1 Material Of End Plate SA516 Gr.702.2.2 Inside Diameter of Header D in 7.19 182.55
2.2.3 Nominal Thickness of EndPlate Tn in 1 25.4
2.2.4 Allowable Stress UnderDesign Temperature fp psi ASME Ⅱ,PART D TABLE 1A,P16 20000 137.90
2.2.5 Ratio C Selected 0.04 12.2.6 Ratio K Selected According to IBR-342 0.19 0.192.2.7 Corrosion C' in 0 02.2.8 Actual Thickness T in Tn-C' 1 25.42.2.9 Working Pressure W.P. psi fp*(T-C)2/(D2*K) 1878 13.0
CONCLUSION:The working pressure provided are greater than the value required by IBR,so thedesign is safe.
The principle of selecting allowable stress is the same as HP SHTR2, allowance stress value in ASMEcode Sec Ⅱ Part D is more conservative.
CONCLUSION:The thickness & working pressure provided are greater than the value required byIBR,so the design is safe.
page 4 of 23
2.3 According to IBR-279
ASME opening reinforcement cal.meet the requirements. 2.3.1 Material of nozzle SA106 B2.3.2 Nozzle Specification 6"Sch 802.3.3 Outside Diameter of
Nozzle do in 6.625 168.32.3.4 Nominal Thickness tn in 0.432 10.972.3.5 Inside Diameter of Nozzle dn in 5.761
2.3.6 Actual Thickness ofHeader Shell ts in 0.719
2.3.7 Allowable Stress ofHeader fs psi ASME Ⅱ,PART D TABLE 1A,P12 17100
2.3.8 Allowable Stress of Nozzle fn psi ASME Ⅱ,PART D TABLE 1A,P12 171002.3.9 fn/fs 1.000
2.3.10 Efficiency of Header E
The openings is larger than the Max.Uncompensated Holes should betreated as no opening after self-reinforcement. Therefore the Weldefficiency is taken as 1 .
1
2.3.11 Equivalent Thickness ofHeader Shell es in IBR-270(Eqn72)
(Dp*D)/(2*fs*E-Dp)+0.03+C 0.314
2.3.12 Efficiency of Nozzle E' 1
2.3.13 Equivalent Thickness ofNozzle en in IBR-270(Eqn72)
(Dp*dn)/(2*fn*E'-Dp)+0.03+C 0.258
2.3.14 2.5 Nominal Thickness ofShell 2.5ts in 1.798
2.3.15 2.5 Thickness of Nozzle 2.5tn in 1.080
2.3.16 Efficient CompensationHeight b in min{2.5ts,2.5tn} 1.080
b' in 02.3.17 Height of Fillet Weld Cw1 in 0.394 102.3.18 Height of Fillet Weld Cw2 in 0.000
2.3.19 Total Transverse SectionArea of Fillet Weld Cw in2 (Cw1)2fn/fs+(Cw2)2fn/fs 0.155
2.3.20 ts+3in 3.7192.3.21 dn/2 2.881
2.3.22 Efficient CompensationWidth Ci Ci in MAX{ts+3in,dn/2} 3.719
2.3.23 Area Required X in2 dn*es 1.810
2.3.24 Area Compensation Y in2 2(tn-en)b*fn/fs+2tn*b'*fn/fs+2(ts-es)Ci+Cw 3.542
CONCLUSION: Y>X, so the opening of reinforcement meets the requirements of IBR.
Opening Reinforcement Calculation
page 5 of 23
page 6 of 23
3.INTERMEDIATE HEADER 1~3 OF HP ECON1DWG.NO.:745148-12-0
3.1 Header Shell Calculation IBR-342(Eqn72)3.1.1 Design Pressure DP psi 1290psi+95ft water column 13313.1.2 Design Temperature t ℉ 4753.1.3 Material Of Header SA106 B3.1.4 Outer Diameter of Header Do in 4" 4.5 114.33.1.5 Inside Diameter of Header D in 3.15 80.06
3.1.6 Nominal Thickness ofHeader Tn in XXS 0.674 17.12
3.1.7 Allowable Stress fs psi ASME Ⅱ,PART D TABLE 1A,P12 171003.1.8 Efficiency E
a 1.87 47.575b 1.374 34.91d 1.5 38.1
b/a 0.7340.600
E IBR-215:FIG-14 0.385
3.1.9 Allowable Deviation ofThickness a % 12.5
3.1.10 Corrision C in 03.1.11 Effective Thichness Te in Te=Tn*(1-a%) 0.5903.1.12 Calculation Thickness Tcal in (Dp*D)/(2*fs*E-Dp)+0.03 0.3843.1.13 Min Required Thickness Tmin in Tcal+C 0.383.1.14 Working Pressure W.P. psi 2*fs*E(Te-0.03-C)/(D+Te-0.03-C) 1986
3.2 Header End Plate Calculation IBR-340(89A)
3.2.1 Material Of End Plate SA516 Gr.703.2.2 Inside Diameter of Header D in 3.15 80.06
3.2.3 Nominal Thickness of EndPlate Tn in 0.5 12.7
3.2.4 Allowable Stress UnderDesign Temperature fp psi ASME Ⅱ,PART D TABLE 1A,P16 20000 137.90
3.2.5 Ratio C Selected 0.04 13.2.6 Ratio K Selected According to IBR-342 0.19 0.193.2.7 Corrosion C' in 0 0
(2a-d)/2a
CONCLUSION:The thickness & working pressure provided are greater than the value required byIBR,so the design is safe.
page 7 of 23
3.2.8 Actual Thickness T in Tn-C' 0.5 12.73.2.9 Working Pressure W.P. psi fp*(T-C)2/(D2*K) 2242 15.5
CONCLUSION:The working pressure provided are greater than the value required by IBR,so thedesign is safe.
page 8 of 23
4.OUTLET AND INLET HEADER OF HP ECON1/IP ECON
4.1 Header Shell Calculation IBR-342(Eqn72)4.1.1 Design Pressure DP psi 1290psi+25ft water column 13014.1.2 Design Temperature t ℉ 5004.1.3 Material Of Header SA106 B4.1.4 Outer Diameter of Header Do in 8" 8.625 219.14.1.5 Inside Diameter of Header D in 7.19 182.58
4.1.6 Nominal Thickness ofHeader Tn in Sch 120 0.719 18.26
4.1.7 Allowable Stress fs psi ASME Ⅱ,PART D TABLE 1A,P12 171004.1.8 Efficiency E
P 3.60 91.4d 1.5 38.1E IBR-215:(P-d)/P 0.583
4.1.9 Allowable Deviation ofThickness a % 12.5
4.1.10 Corrision C in 04.1.11 Effective Thichness Te in Te=Tn*(1-a%) 0.6294.1.12 Calculation Thickness Tcal in (Dp*D)/(2*fs*E-Dp)+0.03 -7.1574.1.13 Min Required Thickness Tmin in Tcal+C -7.164.1.14 Working Pressure W.P. psi 2*fs*E(Te-0.03-C)/(D+Te-0.03-C) 1535
4.2 Header End Plate Calculation IBR-340(89A)
4.3 According to IBR-279
ASME opening reinforcement cal.meet the requirements. 4.3.1 Material of nozzle SA106 B4.3.2 Nozzle Specification 3"Sch 404.3.3 Outside Diameter of
Nozzle do in 3.5 88.94.3.4 Nominal Thickness tn in 0.216 5.494.3.5 Inside Diameter of Nozzle dn in 3.068
CONCLUSION:The thickness & working pressure provided are greater than the value required byIBR,so the design is safe.
The material and size of end plate is same as outlet and inlet header of HP ECON1, andthe allowance stress is same ,so the calculation is same as the end plate of outlet and inletheader of HP ECON1.
Opening Reinforcement CalculationOpening Reinforcement Calculation of Nozzle 6" Sch80 is same as outlet and inlet headerof OF HP ECON1,here is calculation about 3" Sch40.
DWG.NO.:745148-10-0 & 745148-11-0
page 9 of 23
4.3.6 Actual Thickness ofHeader Shell ts in 0.719
4.3.7 Allowable Stress ofHeader fs psi ASME Ⅱ,PART D TABLE 1A,P12 17100
4.3.8 Allowable Stress of Nozzle fn psi ASME Ⅱ,PART D TABLE 1A,P12 171004.3.9 fn/fs 1.000
4.3.10 Efficiency of Header E
The openings is larger than the Max.Uncompensated Holes should betreated as no opening after self-reinforcement. Therefore the Weldefficiency is taken as 1 .
1
4.3.11 Equivalent Thickness ofHeader Shell es in IBR-270(Eqn72)
(Dp*D)/(2*fs*E-Dp)+0.03+C 0.314
4.3.12 Efficiency of Nozzle E' 1
4.3.13 Equivalent Thickness ofNozzle en in IBR-270(Eqn72)
(Dp*dn)/(2*fn*E'-Dp)+0.03+C 0.151
4.3.14 2.5 Nominal Thickness ofShell 2.5ts in 1.798
4.3.15 2.5 Thickness of Nozzle 2.5tn in 0.540
4.3.16 Efficient CompensationHeight b in min{2.5ts,2.5tn} 0.540
b' in 04.3.17 Height of Fillet Weld Cw1 in 0.394 104.3.18 Height of Fillet Weld Cw2 in 0.000
4.3.19 Total Transverse SectionArea of Fillet Weld Cw in2 (Cw1)2fn/fs+(Cw2)2fn/fs 0.155
4.3.20 ts+3in 3.7194.3.21 dn/2 1.534
4.3.22 Efficient CompensationWidth Ci Ci in MAX{ts+3in,dn/2} 3.719
4.3.23 Area Required X in2 dn*es 0.964
4.3.24 Area Compensation Y in2 2(tn-en)b*fn/fs+2tn*b'*fn/fs+2(ts-es)Ci+Cw 3.236
4.4 Blocker Plate Calculation4.4.1 Material Of Blocker Plate SA516 Gr.704.4.2 Inside Diameter of Header D in 7.19 182.55
4.4.3 Nominal Thickness of EndPlate Tn in 1.260 32
4.4.4 Allowable Stress UnderDesign Temperature fp psi ASME Ⅱ,PART D TABLE 1A,P16 20000 137.90
4.4.5 Ratio C Selected 0.04 14.4.6 Ratio K Selected According to IBR-342 0.28 0.284.4.7 Corrosion C' in 0 04.4.8 Actual Thickness T in Tn-C' 1.260 324.4.9 Working Pressure W.P. psi fp*(T-C)2/(D2*K) 2058 14.2
CONCLUSION: Y>X, so the opening of reinforcement meets the requirements of IBR.
CONCLUSION:The working pressure provided are greater than the value required by IBR,so thedesign is safe.
page 10 of 23
5.INTERMEDIATE HEADER 1~3 OF HP ECON1/IP ECON (LEFT)DWG.NO.:745148-13-0
5.1 Header Shell Calculation IBR-342(Eqn72)5.1.1 Design Pressure DP psi 1290psi+95ft water column 13315.1.2 Design Temperature t ℉ 4755.1.3 Material Of Header SA106 B5.1.4 Outer Diameter of Header Do in 4" 4.5 114.35.1.5 Inside Diameter of Header D in 3.152 80.06
5.1.6 Nominal Thickness ofHeader Tn in XXS 0.674 17.12
5.1.7 Allowable Stress fs psi ASME Ⅱ,PART D TABLE 1A,P12 171005.1.8 Efficiency E
a 1.86 47.285b 1.374 34.9d 1.5 38.1
b/a 0.7380.597
E IBR-215:FIG-14 0.405
5.1.9 Allowable Deviation ofThickness a % 12.5
5.1.10 Corrision C in 05.1.11 Effective Thichness Te in Te=Tn*(1-a%) 0.5905.1.12 Calculation Thickness Tcal (Dp*D)/(2*fs*E-Dp)+0.03 0.3655.1.13 Min Required Thickness Tmin in Tcal+C 0.3655.1.14 Working Pressure W.P. psi 2*fs*E(Te-0.03-C)/(D+Te-0.03-C) 2089
5.2 Header End Plate Calculation IBR-340(89A)
(2a-d)/2a
CONCLUSION:The thickness & working pressure provided are greater than the value required byIBR,so the design is safe.
The material and size of end plate is same as intermediate header 1~3 of HP ECON1,and the allowance stress is same ,so the calculation is same as the end plate of outlet andinlet header of HP ECON1.
page 11 of 23
6.INTERMEDIATE HEADER 1~3 OF HP ECON1/IP ECON (RIGHT)DWG.NO.:745148-14-0
6.1 Header Shell Calculation IBR-342(Eqn72)6.1.1 Design Pressure DP psi 700psi+95ft water column 7416.1.2 Design Temperature t ℉ 5006.1.3 Material Of Header SA106 B6.1.4 Outer Diameter of Header Do in 4" 4.5 114.36.1.5 Inside Diameter of Header D in 3.83 97.18
6.1.6 Nominal Thickness ofHeader Tn in Sch 80 0.337 8.56
6.1.7 Allowable Stress fs psi ASME Ⅱ,PART D TABLE 1A,P12 171006.1.8 Efficiency E
a 1.85 46.89b 1.374 34.9d 1.5 38.1
b/a 0.7440.594
E IBR-215:FIG-14 0.408
6.1.9 Allowable Deviation ofThickness a % 12.5
6.1.10 Corrision C in 06.1.11 Effective Thichness Te in Te=Tn*(1-a%) 0.2956.1.12 Calculation Thickness Tcal in (Dp*D)/(2*fs*E-Dp)+0.03 0.2456.1.13 Min Required Thickness Tmin in Tcal+C 0.2456.1.14 Working Pressure W.P. psi 2*fs*E(Te-0.03-C)/(D+Te-0.03-C) 903
6.2 Header End Plate Calculation IBR-340(89A)
6.2.1 Material Of End Plate SA516 Gr.706.2.2 Inside Diameter of Header D in 3.83 97.18
6.2.3 Nominal Thickness of EndPlate Tn in 0.5 12.7
6.2.4 Allowable Stress UnderDesign Temperature fp psi ASME Ⅱ,PART D TABLE 1A,P16 20000 137.90
6.2.5 Ratio C Selected 0.04 16.2.6 Ratio K Selected According to IBR-342 0.19 0.19
(2a-d)/2a
CONCLUSION:The thickness & working pressure provided are greater than the value required byIBR,so the design is safe.
page 12 of 23
6.2.7 Corrosion C' in 0 06.2.8 Actual Thickness T in Tn-C' 0.5 12.76.2.9 Working Pressure W.P. psi fp*(T-C)2/(D2*K) 1522 10.5
CONCLUSION:The working pressure provided are greater than the value required by IBR,so thedesign is safe.
page 13 of 23
custormary metric
DWG.NO.:745127-1-0 Coil Calculation IBR-338(a)(Eqn87)
1.1 Design Pressure DP psi 155 1.071.2 Design Temperature t ℉ 700 371.111.3 Material Of tube SA210 A-11.4 Outer Diameter of Tube Do in 2 50.81.5 Actual Thickness tn in 0.105 2.6671.6 Allowable Stress ft psi ASME Ⅱ,PART D TABLE 1A,P12 15600 107.56
1.7 C in Selected According to IBR338(a) 0.030 0.751.8 Corrosion C' in 01.9 Caculation Thickness Tcal in (Dp*Do)/(2*ft+Dp)+C 0.039 1.001.10 Min Required Thickness Tmin in Tcal+C' 0.039
Hangzhou Boiler GroupCo.,Ltd
PRESSURE PARTS STRENGTHCALCULATIONS-LP EVAP
06745JS2(7)
No. NAME SIGN UNITS FORMULA AND CALCULATIONVALUE
Caculation of Headers and coils1. COIL OF LP EVAP
The principle of selecting allowable stress is same as HP SHTR2, allowance stress value in ASME codeSec Ⅱ Part D is more conservation.
CONCLUSION:The thickness provided are greater than the value required by IBR,so the designis safe.
page 13 of 23
2.OUTLET AND INLET HEADER OF LP EVAPDWG.NO.:745148-1-0,745148-2-0,745148-3-0,745148-5-0,745148-6-0,745148-7-0
2.1 Header Shell Calculation IBR-342(Eqn72)
2.1.1 Design Pressure DP psi based on inlet header(lower):155psi+95ft water column 196
2.1.2 Design Temperature t ℉ 4202.1.3 Material Of Header SA106 B2.1.4 Outer Diameter of Header Do in 10" 10.75 2732.1.5 Inside Diameter of Header D in 9.56 242.82
2.1.6 Nominal Thickness ofHeader Tn in Sch 80 0.594 15.09
2.1.7 Allowable Stress fs psi ASME Ⅱ,PART D TABLE 1A,P12 17100
2.1.8 Efficiency Ea 2.31 58.77b 2.626 66.7d 2.0 50.8
b/a 1.1350.568
E IBR-215:FIG-14 0.480
2.1.9 Allowable Deviation ofThickness a % 12.5
2.1.10 Corrision C in 02.1.11 Effective Thichness Te in Te=Tn*(1-a%) 0.5202.1.12 Calculation Thickness Tcal in (Dp*D)/(2*fs*E-Dp)+0.03 0.1462.1.13 Min Required Thickness Tmin in Tcal+C 0.1462.1.14 Working Pressure W.P. psi 2*fs*E(Te-0.03-C)/(D+Te-0.03-C) 800
2.2 Header End Plate Calculation IBR-340(89A)
2.2.1 Material Of End Plate SA516 Gr.702.2.2 Inside Diameter of Header D in 9.56 242.87
2.2.3 Nominal Thickness of EndPlate Tn in 0.5 12.7
Header size: Outlet 2-3:10" Sch120,others:10" Sch80, design temperature is same , so thecalculation is based on the header of 10" Sch80 .
The principle of selecting allowable stress is the same as HP SHTR2, allowance stress value in ASMEcode Sec Ⅱ Part D is more conservation.
(2a-d)/2a
CONCLUSION:The thickness & working pressure provided are greater than the value required byIBR,so the design is safe.
page 14 of 23
2.2.4 Allowable Stress UnderDesign Temperature fp psi ASME Ⅱ,PART D TABLE 1A,P16 20000 137.90
2.2.5 Ratio C Selected 0.04 12.2.6 Ratio K Selected According to IBR-342 0.19 0.192.2.7 Corrosion C' in 0 02.2.8 Actual Thickness T in Tn-C' 0.5 12.72.2.9 Working Pressure W.P. psi fp*(T-C)2/(D2*K) 244 1.7
2.3 According to IBR-279Nozzle of outlet 1
ASME opening reinforcement cal.meet the requirements. 2.3.1 Material of nozzle SA106 B2.3.2 Nozzle Specification 6"Sch 402.3.3 Outside Diameter of
Nozzle do in 6.625 2732.3.4 Nominal Thickness tn in 0.28 7.112.3.5 Inside Diameter of Nozzle dn in 6.065
2.3.6 Actual Thickness ofHeader Shell ts in 0.594
2.3.7 Allowable Stress ofHeader fs psi ASME Ⅱ,PART D TABLE 1A,P12 17100
2.3.8 Allowable Stress of Nozzle fn psi ASME Ⅱ,PART D TABLE 1A,P12 171002.3.9 fn/fs 1.000
2.3.10 Efficiency of Header E
The openings is larger than the Max.Uncompensated Holes should betreated as no opening after self-reinforcement. Therefore the Weldefficiency is taken as 1 .
1
2.3.11 Equivalent Thickness ofHeader Shell es in IBR-270(Eqn72)
(Dp*D)/(2*fs*E-Dp)+0.03+C 0.085
2.3.12 Efficiency of Nozzle E' 1
2.3.13 Equivalent Thickness ofNozzle en in IBR-270(Eqn72)
(Dp*dn)/(2*fn*E'-Dp)+0.03+C 0.065
2.3.14 2.5 Nominal Thickness ofShell 2.5ts in 1.485
2.3.15 2.5 Thickness of Nozzle 2.5tn in 0.700
2.3.16 Efficient CompensationHeight b in min{2.5ts,2.5tn} 0.700
b' in 02.3.17 Height of Fillet Weld Cw1 in 0.394 102.3.18 Height of Fillet Weld Cw2 in 0.000
2.3.19 Total Transverse SectionArea of Fillet Weld Cw in2 (Cw1)2fn/fs+(Cw2)2fn/fs 0.155
CONCLUSION:The working pressure provided are greater than the value required by IBR,so thedesign is safe.
Opening Reinforcement Calculation
page 15 of 23
2.3.20 ts+3in 3.5942.3.21 dn/2 3.033
2.3.22 Efficient CompensationWidth Ci Ci in MAX{ts+3in,dn/2} 3.594
2.3.23 Area Required X in2 dn*es 0.516
2.3.24 Area Compensation Y in2 2(tn-en)b*fn/fs+2tn*b'*fn/fs+2(ts-es)Ci+Cw 4.114
2.4 According to IBR-279Nozzle of inlet 1 and 2
ASME opening reinforcement cal.meet the requirements. 2.4.1 Material of nozzle SA106 B2.4.2 Nozzle Specification 5"Sch 402.4.3 Outside Diameter of
Nozzle do in 5.563 141.32.4.4 Nominal Thickness tn in 0.258 6.552.4.5 Inside Diameter of Nozzle dn in 5.047
2.4.6 Actual Thickness ofHeader Shell ts in 0.594
2.4.7 Allowable Stress ofHeader fs psi ASME Ⅱ,PART D TABLE 1A,P12 17100
2.4.8 Allowable Stress of Nozzle fn psi ASME Ⅱ,PART D TABLE 1A,P12 171002.4.9 fn/fs 1.000
2.4.10 Efficiency of Header E
The openings is larger than the Max.Uncompensated Holes should betreated as no opening after self-reinforcement. Therefore the Weldefficiency is taken as 1 .
1
2.4.11 Equivalent Thickness ofHeader Shell es in IBR-270(Eqn72)
(Dp*D)/(2*fs*E-Dp)+0.03+C 0.085
2.4.12 Efficiency of Nozzle E' 1
2.4.13 Equivalent Thickness ofNozzle en in IBR-270(Eqn72)
(Dp*dn)/(2*fn*E'-Dp)+0.03+C 0.059
2.4.14 2.5 Nominal Thickness ofShell 2.5ts in 1.485
2.4.15 2.5 Thickness of Nozzle 2.5tn in 0.645
2.4.16 Efficient CompensationHeight b in min{2.5ts,2.5tn} 0.645
b' in 02.4.17 Height of Fillet Weld Cw1 in 0.394 102.4.18 Height of Fillet Weld Cw2 in 0.000
2.4.19 Total Transverse SectionArea of Fillet Weld Cw in2 (Cw1)2fn/fs+(Cw2)2fn/fs 0.155
CONCLUSION: Y>X, so the opening of reinforcement meets the requirements of IBR.
Opening Reinforcement Calculation
page 16 of 23
2.4.20 ts+3in 3.5942.4.21 dn/2 2.524
2.4.22 Efficient CompensationWidth Ci Ci in MAX{ts+3in,dn/2} 3.594
2.4.23 Area Required X in2 dn*es 0.430
2.4.24 Area Compensation Y in2 2(tn-en)b*fn/fs+2tn*b'*fn/fs+2(ts-es)Ci+Cw 4.069
2.5 According to IBR-279Nozzle of inlet 3
ASME opening reinforcement cal.meet the requirements. 2.5.1 Material of nozzle SA106 B2.5.2 Nozzle Specification 4"Sch 402.5.3 Outside Diameter of
Nozzle do in 4.5 114.32.5.4 Nominal Thickness tn in 0.237 6.022.5.5 Inside Diameter of Nozzle dn in 4.026
2.5.6 Actual Thickness ofHeader Shell ts in 0.594
2.5.7 Allowable Stress ofHeader fs psi ASME Ⅱ,PART D TABLE 1A,P12 17100
2.5.8 Allowable Stress of Nozzle fn psi ASME Ⅱ,PART D TABLE 1A,P12 171002.5.9 fn/fs 1.000
2.5.10 Efficiency of Header E
The openings is larger than the Max.Uncompensated Holes should betreated as no opening after self-reinforcement. Therefore the Weldefficiency is taken as 1 .
1
2.5.11 Equivalent Thickness ofHeader Shell es in IBR-270(Eqn72)
(Dp*D)/(2*fs*E-Dp)+0.03+C 0.085
2.5.12 Efficiency of Nozzle E' 1
2.5.13 Equivalent Thickness ofNozzle en in IBR-270(Eqn72)
(Dp*dn)/(2*fn*E'-Dp)+0.03+C 0.053
2.5.14 2.5 Nominal Thickness ofShell 2.5ts in 1.485
2.5.15 2.5 Thickness of Nozzle 2.5tn in 0.593
2.5.16 Efficient CompensationHeight b in min{2.5ts,2.5tn} 0.593
b' in 02.5.17 Height of Fillet Weld Cw1 in 0.394 102.5.18 Height of Fillet Weld Cw2 in 0.000
2.5.19 Total Transverse SectionArea of Fillet Weld Cw in2 (Cw1)2fn/fs+(Cw2)2fn/fs 0.155
CONCLUSION: Y>X, so the opening of reinforcement meets the requirements of IBR.
Opening Reinforcement Calculation
page 17 of 23
2.5.20 ts+3in 3.5942.5.21 dn/2 2.013
2.5.22 Efficient CompensationWidth Ci Ci in MAX{ts+3in,dn/2} 3.594
2.5.23 Area Required X in2 dn*es 0.343
2.5.24 Area Compensation Y in2 2(tn-en)b*fn/fs+2tn*b'*fn/fs+2(ts-es)Ci+Cw 4.031
CONCLUSION: Y>X, so the opening of reinforcement meets the requirements of IBR.
page 18 of 23
3.LP EVAP MANIFOLDDWG.NO.:745148-4-0
3.1 Header Shell Calculation IBR-342(Eqn72)3.1.1 Design Pressure DP psi 155psi+95ft water column 1963.1.2 Design Temperature t ℉ 4203.1.3 Material Of Header SA106 B3.1.4 Outer Diameter of Header Do in 10" 10.75 2733.1.5 Inside Diameter of Header D in 9.56 242.82
3.1.6 Nominal Thickness ofHeader Tn in Sch 80 0.594 15.09
3.1.7 Allowable Stress fs psi ASME Ⅱ,PART D TABLE 1A,P12 171003.1.8 Efficiency E 1
3.1.9 Allowable Deviation ofThickness a % 12.5
3.1.10 Corrision C in 03.1.11 Effective Thichness Te in Te=Tn*(1-a%) 0.5203.1.12 Calculation Thickness Tcal in (Dp*D)/(2*fs*E-Dp)+0.03 0.0853.1.13 Min Required Thickness Tmin in Tcal+C 0.0853.1.14 Working Pressure W.P. psi 2*fs*E(Te-0.03-C)/(D+Te-0.03-C) 1666
3.2 Header End Plate Calculation IBR-340(89A)The calculation of end plate is same as outlet and inlet header.
3.3 According to IBR-279Nozzle N1 and N2
ASME opening reinforcement cal.meet the requirements. 3.3.1 Material of nozzle SA106 B3.3.2 Nozzle Specification 5"Sch 403.3.3 Outside Diameter of
Nozzle do in 5.563 141.33.3.4 Nominal Thickness tn in 0.258 6.553.3.5 Inside Diameter of Nozzle dn in 5.047
3.3.6 Actual Thickness ofHeader Shell ts in 0.594
3.3.7 Allowable Stress ofHeader fs psi ASME Ⅱ,PART D TABLE 1A,P12 17100
3.3.8 Allowable Stress of Nozzle fn psi ASME Ⅱ,PART D TABLE 1A,P12 171003.3.9 fn/fs 1.000
All the openings which are larger than the Max. permissible opening should be treated asno opening after self-reinforcement. Therefore the Weld efficiency is taken as 1 .
CONCLUSION:The thickness & working pressure provided are greater than the value required byIBR,so the design is safe.
Opening Reinforcement Calculation
page 19 of 23
3.3.10 Efficiency of Header E
The openings is larger than the Max.Uncompensated Holes should betreated as no opening after self-reinforcement. Therefore the Weldefficiency is taken as 1 .
1
3.3.11 Equivalent Thickness ofHeader Shell es in IBR-270(Eqn72)
(Dp*D)/(2*fs*E-Dp)+0.03+C 0.085
3.3.12 Efficiency of Nozzle E' 1
3.3.13 Equivalent Thickness ofNozzle en in IBR-270(Eqn72)
(Dp*dn)/(2*fn*E'-Dp)+0.03+C 0.059
3.3.14 2.5 Nominal Thickness ofShell 2.5ts in 1.485
3.3.15 2.5 Thickness of Nozzle 2.5tn in 0.645
3.3.16 Efficient CompensationHeight b in min{2.5ts,2.5tn} 0.645
b' in 03.3.17 Height of Fillet Weld Cw1 in 0.394 103.3.18 Height of Fillet Weld Cw2 in 0.000
3.3.19 Total Transverse SectionArea of Fillet Weld Cw in2 (Cw1)2fn/fs+(Cw2)2fn/fs 0.155
3.3.20 ts+3in 3.5943.3.21 dn/2 2.524
3.3.22 Efficient CompensationWidth Ci Ci in MAX{ts+3in,dn/2} 3.594
3.3.23 Area Required X in2 dn*es 0.430
3.3.24 Area Compensation Y in2 2(tn-en)b*fn/fs+2tn*b'*fn/fs+2(ts-es)Ci+Cw 4.069
3.4 According to IBR-279Nozzle N3
ASME opening reinforcement cal.meet the requirements. 3.4.1 Material of nozzle SA106 B3.4.2 Nozzle Specification 4"Sch 403.4.3 Outside Diameter of
Nozzle do in 4.5 114.33.4.4 Nominal Thickness tn in 0.237 6.023.4.5 Inside Diameter of Nozzle dn in 4.026
3.4.6 Actual Thickness ofHeader Shell ts in 0.594
3.4.7 Allowable Stress ofHeader fs psi ASME Ⅱ,PART D TABLE 1A,P12 17100
3.4.8 Allowable Stress of Nozzle fn psi ASME Ⅱ,PART D TABLE 1A,P12 171003.4.9 fn/fs 1.000
CONCLUSION: Y>X, so the opening of reinforcement meets the requirements of IBR.
Opening Reinforcement Calculation
page 20 of 23
3.4.10 Efficiency of Header E
The openings is larger than the Max.Uncompensated Holes should betreated as no opening after self-reinforcement. Therefore the Weldefficiency is taken as 1 .
1
3.4.11 Equivalent Thickness ofHeader Shell es in IBR-270(Eqn72)
(Dp*D)/(2*fs*E-Dp)+0.03+C 0.085
3.4.12 Efficiency of Nozzle E' 1
3.4.13 Equivalent Thickness ofNozzle en in IBR-270(Eqn72)
(Dp*dn)/(2*fn*E'-Dp)+0.03+C 0.053
3.4.14 2.5 Nominal Thickness ofShell 2.5ts in 1.485
3.4.15 2.5 Thickness of Nozzle 2.5tn in 0.593
3.4.16 Efficient CompensationHeight b in min{2.5ts,2.5tn} 0.593
b' in 03.4.17 Height of Fillet Weld Cw1 in 0.394 103.4.18 Height of Fillet Weld Cw2 in 0.000
3.4.19 Total Transverse SectionArea of Fillet Weld Cw in2 (Cw1)2fn/fs+(Cw2)2fn/fs 0.155
3.4.20 ts+3in 3.5943.4.21 dn/2 2.013
3.4.22 Efficient CompensationWidth Ci Ci in MAX{ts+3in,dn/2} 3.594
3.4.23 Area Required X in2 dn*es 0.343
3.4.24 Area Compensation Y in2 2(tn-en)b*fn/fs+2tn*b'*fn/fs+2(ts-es)Ci+Cw 4.031
3.5 According to IBR-279Nozzle DC
ASME opening reinforcement cal.meet the requirements. 3.5.1 Material of nozzle SA106 B3.5.2 Nozzle Specification 8"Sch 803.5.3 Outside Diameter of
Nozzle do in 8.625 219.13.5.4 Nominal Thickness tn in 0.5 12.73.5.5 Inside Diameter of Nozzle dn in 7.625
3.5.6 Actual Thickness ofHeader Shell ts in 0.594
3.5.7 Allowable Stress ofHeader fs psi ASME Ⅱ,PART D TABLE 1A,P12 17100
3.5.8 Allowable Stress of Nozzle fn psi ASME Ⅱ,PART D TABLE 1A,P12 171003.5.9 fn/fs 1.000
CONCLUSION: Y>X, so the opening of reinforcement meets the requirements of IBR.
Opening Reinforcement Calculation
page 21 of 23
3.5.10 Efficiency of Header E
The openings is larger than the Max.Uncompensated Holes should betreated as no opening after self-reinforcement. Therefore the Weldefficiency is taken as 1 .
1
3.5.11 Equivalent Thickness ofHeader Shell es in IBR-270(Eqn72)
(Dp*D)/(2*fs*E-Dp)+0.03+C 0.085
3.5.12 Efficiency of Nozzle E' 1
3.5.13 Equivalent Thickness ofNozzle en in IBR-270(Eqn72)
(Dp*dn)/(2*fn*E'-Dp)+0.03+C 0.074
3.5.14 2.5 Nominal Thickness ofShell 2.5ts in 1.485
3.5.15 2.5 Thickness of Nozzle 2.5tn in 1.250
3.5.16 Efficient CompensationHeight b in min{2.5ts,2.5tn} 1.250
b' in 03.5.17 Height of Fillet Weld Cw1 in 0.394 103.5.18 Height of Fillet Weld Cw2 in 0.000
3.5.19 Total Transverse SectionArea of Fillet Weld Cw in2 (Cw1)2fn/fs+(Cw2)2fn/fs 0.155
3.5.20 ts+3in 3.5943.5.21 dn/2 3.813
3.5.22 Efficient CompensationWidth Ci Ci in MAX{ts+3in,dn/2} 3.813
3.5.23 Area Required X in2 dn*es 0.649
3.5.24 Area Compensation Y in2 2(tn-en)b*fn/fs+2tn*b'*fn/fs+2(ts-es)Ci+Cw 5.100
CONCLUSION: Y>X, so the opening of reinforcement meets the requirements of IBR.
page 22 of 23
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