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2015/5/29
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Tielong ShenDepartment of Engineering and Applied Sciences Sophia University, Tokyo, Japan
Applications of Real-time Optimization Algorithm in Modeling and Control of Automotive Powertrains
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On going projects at Sophia
Real-time Optimization (RHC)
> Case Study I: Combustion Engine Control
> Case Study II: Energy Management of HEVs
> Case Study III: Real-time D-Optimization
Future Challenges
Outline
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Issues and Facility at SOPHIA
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Projects
Advanced control technologies for the next generation of combustion engines,‘05~, Toyota.
Energy management strategy with traffic information ‘11 ~,Nissan
Optimization algorithm for ECU Calibration, ‘12~,Hitachi
Engine efficiency improvement by transient control with dynamical boundary control KAKENHI(B), ‘14 ~
Model-based transient control of combustion engines, KAKENHI(B), No. 23360186), ‘11-’13
Development of high efficiency engines, JST JKC Project, ’13~
Industrial projects
National projects
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Issues (engine)
-- CPS-based engine management-- Real-time optimization -- Probability-constrained optimal control-- Statistical method for boundary detection-- Stochastic logical control of Residual Gas Fraction-- Knock probability control with likelihood estimation-- Cycle-to-cycle behavior -- Extremal seeking-- D-optimization for calibration
Background: Transient and Hardwar in Loop
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-- Controller model + Real Engine-- ECU + Engine Model
Model
Sensors
Actuators
ECU
-- ECU Calibration based on Engine Model
To get engine physics right, engine-in-the-loop system is effective Real-time operating is always in Transient operation. Controller calibration at static modes does not satisfies real-world.
Engine-in-The-Loop System
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MicroAutoBoX II
dSPACE DS1006AD-Phoenix (A&D)
In Motion/Car Maker
Individual Fuel (P/D), SA, VVTin, VVTex,Throttle
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1
Real-time Optimization (RHC)
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Model-based Optimal Control Model of system dynamics under control
Cost function along trajectories
Optimization problem with dynamical constraint
Subject to
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Area: Functional
Control Constraint
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Pontryagin’s Maximum Principle
Cost function
Lev Semenovich Pontryagin1908-1988
Constraint condition
If is the solution, then
Hamiltonian
Real-time Optimization: Receding Horizon control
Reference
Control Period
Output
Area: Functional
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Discretization of the optimality condition (N-steps )
Find:
Numerical Solver: Iterative Algorithm
C/GMRES Algorithm, by T. Ohtsuka
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CASE Study 1:Torque Control of Gasoline Engine
Thanks to M. Kang (Candidate PhD)
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Motivation:Transient Behavior
ThrottleOpening
Rotational Speed
Air flow
Exhaust Gas
Cylinder
Intake valve Ehxaust Valve
Intake Manifold
u y
Input OutputIntake AirDyanmics
RotationalDynamics
ManifoldPressure
t/s12Fuel cut Restarting
14.7
14.7
14.7
Port inj.Direct inj.
0
0
0
t/s12
t/s5
t/s0
0 t/s
throttle opening
engine speed
A/F
5 10 15 20 25 30 35 40
5 10 15 20 25 30 35 40
1500/6
3000/12
13
16
14.7
Fuel Cutting
Fuel Path Switching
Start-up
Throttle Opening
Intake path, fuel path and mechanical dynamics cause transient phenomenon
Transient behavior presents imbalance of mass, thermal energy, etc.
With uncertainties such as nonlinearity, stochastic properties, etc, due to the stochastic characteristics in combustion event.
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Transient Behavior in Combustion Events
−300 −200 −100 0 100 200 3000
10
20
30
40
50
60
Crank angle (degree)
In−cy
linde
r Pre
ssure
(bar
)
Constant Load Mode: Load=76Nm, Average Cycle=3
t=3.0s, 828rpmt=4.0s, 1046rpmt=4.5s, 1337rpmt=5.0s, 1482rpm
0 1 2 3 4 5 6 7
x 10−4
0
10
20
30
40
50
60
Volume of Cylinder (m 3)
In−
cylin
der P
ress
ure
(bar
)
Constant Load Mode: Load=76Nm, Average Cycle=3
t=3.0s, 828rpmt=4.0s, 1046rpmt=4.5s, 1337rpmt=5.0s, 1482rpm
0 5 10 15
5
10
Engi
ne T
hrot
tle
Constant Load Mode: Load=76Nm, Average Cycle=3
0 5 10 1522
23
24
SA
0 5 10 15500
1000
1500
2000
Engi
ne s
peed
(RPM
)
0 5 10 155
10
15
20
Time (s)
CA50
(deg
ree)
Transient response of CA50
Transient response of in-cylinder pressure
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Physics and Control-oriented Model
Air Inlet Path
Dynamics
Fuel Inj. Path
Dynamics
Compr.
&
Comb.
Torque
Gener.
Proc.
Crankshaft
Rotational
Dynamics
Speed
Throtle
Fuel Inj.
Air
Fuel Torque
Σ
Spark
Air Inlet Path
Dynamics
Fuel Inj. Path
Dynamics
Compr.
&
Comb.
Torque
Gener.
Proc.
Crankshaft
Rotational
Dynamics
Speed
Throtle
Fuel Inj.
Air
Fuel Torque
Σ
Spark
Air path dynamics(MVM)
Rotation speed dynamics
Torque Generation Model (Static)
Mean-value Transient Model
Mean value : 0.0047 g/s Variance : 0.6935
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subject toa) Dynamic equations
b) Torque output equation
c) Necessary constraints
Control objective
Real-time Optimization: Torque Tracking
Torque Tracking
0
50
100
150
Eng
ine
Tor
que[
Nm
]
0
5
10
15
Thr
ottl
e[de
g]
0
1000
2000
3000
Eng
ine
Spe
ed[r
pm]
0 10 20 30 40 50 60 70 80 90 100
-20
0
20
40
Time[s]
Tra
ckin
g E
rror
[Nm
]
SetPointOriginalImproved
Original Improved
neActl
Original Improved
40
60
80
Original RHC parameters:
Predictive time: 0.3sControl period: 0.01sPredictive period: 0.01sPredictive steps: 30
Improved RHC parameters:
Predictive time: 1sControl period: 0.01sPredictive period: 0.01sPredictive steps: 30Integral Gain: 0.6
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1000
1500
2000
2500
Eng
ine
Spe
ed[r
pm]
0
5
10
15
Thr
ottl
e[de
g]
40
60
80
100
Loa
d[N
m]
0 20 40 60 80 100 120 140 160 180 200-300
-200
-100
0
100
200
300
Time [s]
Tra
ckin
g E
rror
[rpm
]
SetPoint ne(PID) ne(MPC)
(PID) (MPC)
l
PID MPC
Tracking error Mean value variance
PID 0.21543 1460.6545
MPC 0.045444 1038.7143
Experiment (Speed Tracking)
Comparison between PID control and RHC control (Enlarged figure)
1500
1600
1700
1800
1900
Eng
ine
Spe
ed [rp
m]
5
6
7
Thr
ottle[
deg]
30
40
50
60
Loa
d[N
m]
45 50 55 60-100
-50
0
50
Time [s]
Tra
ckin
g Err
or[r
pm]
1200
1400
1600
1800
2000
Eng
ine
Spe
ed [rp
m]
0
5
10
15
Thr
ottle[
deg]
40
60
80
100
Loa
d[N
m]
120 125 130 135 140 145
-200
-100
0
100
200
Time [s]
Tra
ckin
g Err
or[r
pm]
SetPoint
ne(PID)
ne(MPC)
(PID)
(MPC)
l
PID
MPC
SetPoint
ne(PID)
ne(MPC)
(PID)
(MPC)
l
PID
MPC
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Driving cycle tests
0
50
100
150
Veh
icle
Spe
ed
Veh.Spd.Ref [Km/h]
Veh.Spd.Actl [Km/h]
0
100
200
300
Eng
ine
Tor
que
d [Nm]
e Actl [Nm]
1000
2000
3000
Eng
ine
Spe
ed
n
e Actl [rpm]
0
20
40
60
80
Drive
r.In
puts &
Thr
ottle
Acc [deg]
Brk [%]
Thr.Actl[deg]
0 50 100 150 200 250 300 350 400 450 500-40
-20
0
20
40
Time [s]
Tra
ckin
g Err
or
Error[Nm]
0
100
200
0
10
20
Tracking error Mean value:
-0.0783 Nm Variance:
23.9715
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CASE Study II:Energy Management for HEVs
Thanks to Dr. J. Zhang, Shunichi Hara(M.S.)
2015/5/29
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Energy Management Problem
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VehiclePowertrainEnergy Manag.
SpeedWheels TorqueRequest
Environment
Demand Decision
Energy Management Problem
Off-line (Here-and-Now)
Goal of Energy Management: Minimizing Consumption
Total power must satisfies the demanded power by driver
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3
VPower-train
Energy Manage
ment
速度
Power Demand
Slope
--Off-line optimization--Fuel or Equivalent Consumption--Prior Route Information
Rule-based and Optimization
Rule-based approachHigh efficiency operating point of each power deviceunder the constraint of total power demand
Optimization-based Approach
Prior Information
Brief Review
Rule-based Approach
Optimization-based Approach[A] Dynamical Programming
Off‐line optimization (DP, Stochastic DP, Pontriyagin’s Principle)Global optimal solution regarding to a priori known driving cycle
Ref. O. Sundstrom, et al,Oil&Gas ST, V65,2010; S. Moura, et al., IEEE CST, V19,2011
Based on efficiency property of the devicesRef. L. Serrao, S. Onori, G. Rizzoni, ASME JDSMC, Vol133, 2011
[B] ECMS( Equivalent Consumption Minimization Strategy)Ref. G. Rizzoni, IFAC Workshop EPCSM, 2012, C.Musardo et al., EJC, V11, 2005
[C] Real-time Optimization
Look‐ahead optimal control, Receding Horizon ControlRef. H.Borhan et al., IEEE CST, V20,2012
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Modeling
Input
engine torque
motor torque
発 generator torque
braking torque
Output
Speed
バッ
燃料 Fuel Consumption
power balancing
state Variable:control input:
external constraint:
Dynamical Model in Nonlinear State Equation Form
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Real-time Optimization
Constraint of power split by driver-demand has been embedded
Simulations Validation with GT‐Simulator provided by JSAE‐SICE benchmark problem
Standard city driving cycle
Driving cycle with part of highway driving
Regular Driving
Jam Driving
slope θ=0;ωemax=4000[rpm], ωgmin=2000[rpm];SoC(0)=0.9;
T=5[s], δτ=0.01[s];
(δτ:Control Period)
Thanks to IDAJ for supporting GT-SUIT
*Parameter from Y. Yasui, JSAE‐SICE Benchmark Problem 2
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Engine-in-The-Loop HEV
Motor-Battery-Driveline-V
Standard city driving cycle (regular driving)
Acceleration performance is weak due to the limitation of the engine power when the emergency mode is activated
Alpha‐speed
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Standard city driving cycle (Jam driving)
Comparisons (regular driving)
by the proposed control scheme by the benchmark example control scheme
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Receding Horizon Control Algorithm
Example Algorithm
FinalSoC[‐]
Fuel Consumption[g]
Sd[%]FinalSoC[‐]
FuelConsumption[g]
Sd[%]
Standard CityDriving
Regular 0.4942 398.95 92.7 0.5203 570.5
100Jam 0.4858 496.78 96.5 0.5066 909.6
Driving with Highway 0.4709 567.7 91.8 0.5087 764.8
Testing Results on GT‐SUIT
Realtimeness Testing on dSPACE
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CASE Study III:Real-time D-Optimization
Thanks to Mitsuru Toyoda (Mater Course)
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Model: linearity
Parameter Identification
Solution
Model Identification: Least-Squares Estimation
Plant
Model
LSE
With the estimation
Experiment Design: D-Optimization
Statistical property
Expectation
Variance
D-Optimality
Wald(1943), Kiefer, Wolfowita (1959).
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Fisher information matrix
D-Optimization: Find optimal input for identification
D-Optimalityto reject covariance of estimated parameter, design optimal input signal in the
sense of
Plant
Discretization
Real-time D-optinization)
Example: Linear Second-order System
With constraint
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2015/5/29 日立報告資料 43
0 0.5 1 1.5 2 2.5 3 3.5 4 4.5 50
1
2
3
t(k)
a1(k)
a1
0 0.5 1 1.5 2 2.5 3 3.5 4 4.5 5-2
-1.5
-1
-0.5
0
t(k)
a2(k)
a2(k)
0 0.5 1 1.5 2 2.5 3 3.5 4 4.5 5-10
-5
0
5x 10
-4
b2(k)
b1
0 0.5 1 1.5 2 2.5 3 3.5 4 4.5 5-50
0
50
t(k)u(k)
u(k)
0 0.5 1 1.5 2 2.5 3 3.5 4 4.5 50
5
10
t(k)
y(k)
y(k)
0 0.5 1 1.5 2 2.5 3 3.5 4 4.5 5-0.2
-0.1
0
0.1
0.2
t(k)
y(k)−y(k)
y(k) − y(k)
Concluding Remarks
Stochastic property
Model-free control strategy
Real-time Optimization with constraint
Multi-core ECU
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Palazzo Imperiale
Tokyo Bay, Pacifico
Sophia University
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