simulating diesel engine transients
TRANSCRIPT
AUTOMOTIVE RESEARCH CENTER
SIMULATING DIESEL ENGINE TRANSIENTS
Zoran S. Filipi, Guoqing Zhang, Stephen Riley and Dennis N. Assanis
W. E. Lay Automotive Laboratory
Automotive Research Center
The University of Michigan
ARC Conference on
Critical Technologies for Modeling & Simulation of Ground Vehicles
June 3 - 4, 1997.
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ACKNOWLEDGMENTS
Arvind Atreya, Claus Borgnakke, David Dowling, Scott Fiveland, Steven Hoffman, Samuel Homsy, Xiaoliu Liu, Fadi Kanafani, Kevin Morrison, Donald Patterson, Michalis Syrimis, Deanna Winton
The authors also appreciate the technical collaboration with Dr. Nabil Hakim, Mr. Jim Hoelzer, Mr. Craig Savonen, and Mr. Tim Prochnau of Detroit Diesel Corporation, an industrial member of the ARC.
Professor Naeim Henein and other members of the ARC research team at Wayne State University for making experimental results measured on the Deutz single- cylinder engine available for model validation purposes.
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MOTIVATION
Need to evaluate and optimize advanced turbocharged diesel systems through the use of simulation models.
Predictive diesel system model crucial for mobility and fuel economy studies of the ground vehicle.
Single-cylinder transient diesel engine module needed as a basic building block for the complex, multi-cylinder engine system simulation.
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OBJECTIVES
Develop a high-fidelity diesel engine cylinder module.
Provide capability for simulation of the transient engine operation on the crank-angle basis.
Integrate in-cylinder modules to create a multi-cylinder engine simulation in a flexible, easily reconfigurable, graphical software environment.
Validate the multi-cylinder engine transient performance predictions against measurements.
Integrate the multi-cylinder engine model with the ancillary components to generate the engine system simulation.
Integrate the engine system with the driveline and the vehicle dynamics model.
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MODELING APPROACH
Extend the non-linear, phenomenological steady-state diesel engine cycle simulation to include engine dynamics on the crank-angle basis .
Include an instantaneous torque model as a necessary prerequisite for yielding accurate predictions of the cyclic fluctuations of the crank shaft angular velocity.
Instantaneous torque, and hence crankshaft speed fluctuate in response to the cyclic nature of the gas pressure force and the slider-crank kinematics - this is accentuated for single-cylinder engine operation. Hence, the approach to modeling is to:
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Features of the Non-Linear, Quasi-Steady Diesel Engine Model
Parent simulation: Assanis and Heywood (1986)
The system of interest is the instantaneous contents of a cylinder. The system is open to the transfer of mass, enthalpy, and energy in the form of work and heat.
Phenomenological combustion model - Watson (1980)
Convective heat transfer model is based on turbulent flow in pipes. Radiative heat transfer is added during combustion.
Characteristic velocity and length scales are obtained from an “energy cascade” turbulent flow model.
Quasi-steady, adiabatic, one-dimensional flow equations are used to predict mass flows past the intake and exhaust valves.
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Behavior of cycle process sub-models during transients
A series of steady-state calculations performed for different operating conditions likely to occur during a transient sequence
Parametric study #1: The effect of engine speed on cycle parameters
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300 350 400 450
600 rpm1200 rpm1800 rpm
CRANK ANGLE [deg]
RA
TE
OF
HE
AT
RE
LEA
SE
[1/s]
Rate of HR
PRESSURE
P inlet = 1.0 bar, mfuel/cyc
= 0.085 g TE
MP
ER
AT
UR
E [K
]
GASTEMPERATURE
a)
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0 80 160 240 320 400 480
600 rpm1200 rpm1800 rpm
CRANK ANGLE [deg]
Rate of HT
TURBULENCEINTENSITY
P inlet = 1.0 barm
fuel/cyc= 0.085 g
b)
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Behavior of cycle process sub-models during transients - cont.
Parametric study #2: The effect of the boost pressure on cycle parameters
-40
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300 350 400 450
Pim=2.3 barPim=1.65 barPim=1.0 bar
CRANK ANGLE [deg]
PRESSURE
1200 rpm
Φ = 0.57
Rate of HR
b)
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400
0 40 80 120 160 200 240
Pim=2.3 barPim=1.65 barPim=1.0 bar
INLE
T M
AS
S F
LOW
[g/s
]
CRANK ANGLE [deg]a)
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Single-Cylinder Engine Dynamic System
ENGINE CYCLE
SIMULATION
OPERATORCOMMAND
FUEL SYSTEM
AMBIENT CONDITIONS
Ωe Ωe
Ω - rotational speedτ - torque
FRICTION MODEL
τb
EXTERNAL LOAD
ENGINE DYNAMICS
τL-
+ Ωe
τe
τF-+
Ωe
Key inputs to the cycle simulation: the operator command, the fueling rate and the ambient conditions.
Key input to the engine dynamics model: Brake torque from the cycle model and the external load imposed by the dynamometer or the vehicle.
Design parameters needed: masses of the engine moving parts, polar moments of inertia of the engine and the load.
Key output parameter: the instantaneous value of the angular shaft velocity, which is a necessary input for computing overall cycle parameters, including the engine torque, at the next instant in time.
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Instantaneous Engine Torque
rF p p
Bpres cyl atm= − ⋅( )
2
4
Π
vF m m ainer pg rcr= − + ⋅( )
a R
R
= + +−
+
+−
ω λ λλ
ω λλ
22 4
2 2 3 2
2 2 1 2
2
1
11
cos(cos sin )
( sin )
˙ sincos
( sin )
/
/
Θ Θ ΘΘ
Θ ΘΘ
r r rF F Fpstn pres iner= +
r rC Fpstn= (
cos)
1
β
r rT Fpstn= +
(sin( )
cos)
Θ ββ
TORQUE T R= ⋅
R = Stroke/2; L - connecting rod length; λ = R/L;Θ - crankshaft angular position and β - angle of swing of the connecting rod
R
β
Θ
CFpstn
N
T
Fpres
L
The pressure force:
The inertial force:
while the linear acceleration of reciprocating components is:
The resultant force on the piston:
The torque on the shaft:
Force in the directionof the connecting rod:
The tangential force on the crank journal:
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0 5 10 15 20 25 30
ENGINE: Deutz F1L 210 D
ENGINE MOMENT OF INERTIA: 0.386 kgm2
FUEL/CYCLE: 40 mm3
EXTERNAL LOAD: 0 Nm
MEASURED
PREDICTED
EN
GIN
E
SP
EE
D
[rpm
]
ENGINE CYCLE NUMBER
ValidationComparison of predicted and measured crankshaft speed fluctuations during engine free acceleration
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Overall Transient Model Behavior- cont.Predicted crankshaft speed fluctuations during an
elementary engine transient.
Both the amplitudes and the periods of cyclic fluctuations gradually decrease as the mean engine speed increases.
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0.0 0.5 1.0 1.5 2.0 2.5 3.0
SINGLE CYLINDER CI ENGINEBore = 0.13 m, Stroke = 0.16 m
MOMENT OF INERTIA = 1.4 kgm2EXTERNAL LOAD = 0 Nm
EN
GIN
E S
PE
ED
[rp
m]
MA
SS
OF
FU
EL/C
YC
LE [g]
TIME [s]
enginespeed
fuel per cycle
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Overall Transient Model Behavior- cont.Predicted single-cylinder cyclic torque fluctuations
during an elementary engine transient.
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SINGLE CYLINDER CI ENGINEBore = 0.13 m, Stroke = 0.16 mENGINE SPEED: 900 - 2160 rpmEXTERNAL LOAD: 0 Nm
EN
GIN
E T
OR
QU
E [
Nm
]
CRANK ANGLE [deg]
2160 rpmhigh idle
900 rpmno load
900 rpm100 % fuel
2160 rpm100 % fuel
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Multi-Cylinder Engine Simulation Assembled in SIMULINK
In-cylinder diesel engine code converted to FORTRAN-MEX file with appropriate external links in order to be able to generate a multi-cylinder simulation in SIMULINK and test the newly developed models.
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experimentsimulation
Cylinder
Pressure
(bar)
Crank Angle (deg)
Experimental Validation
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RPM - PREDICTEDRPM - MEASUREDEXTERNAL LOAD
BOOST PRESS.
Engine
Speed
(rpm
);
External
Load
(N
m)
Intake
Manifold
Pressure
(KPa)
Time (s)
VALIDATION
OF
SUB-MODELS
VALIDATION
OF THE
ENGINE
RESPONSE
Pressure Transducers / Heat Flux Probesin all Cylinders
Three-Component Force Transducer for Engine Vibrations Studies
The Engine: DDC-60 Six-Cylinder, Turbocharged, Intercooled, Direct Injection Diesel
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In-Cylinder Module in the Context ofthe Flexible Powertrain Simulation
The UM in-cylinder model embedded in the multi-cylinder engine block.
Flexible Powertrain Simulation developed in SIMULINK by the University of Wisconsin team.
• HIERARCHICAL
• INTERACTIVE
• CHOICE OF SUB-MODELS
• EASILY RECONFIGURABLE
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HILL CLIMBING
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-0.05
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0 2 4 6 8 10
VEHICLE
SPEED
(mph)
VEHICLE
ACCELERATION
(g’s)
TIME (s)
M916A1 SEMI, Gross Curb Weight 126,000 lb
ax
v
x
5
10
15
0 2 4 6 8 10
WHEEL
VERTICAL
LOAD
(lb*1000)
TIME (s)
M916A1 SEMIGross Curb Weight 126,000 lb
FRONT
FRONT REAR
REAR
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HILL CLIMBING - cont.
FRONTWHEELS SLIPPING
1.2
1.4
1.6
1.8
2
2.2
2.4
2.6
2.8
0 2 4 6 8 10
WHEEL
SPEED
(rev/s)
TIME (s)
M916A1 SEMIGross Curb Weight 126,000 lb
FRONT
REAR
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0 2 4 6 8 10
WHEEL
LONG.
FORCE
(lbf)
M916A1 SEMIGross Curb Weight 126,000 lb
FRONT
REAR
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HILL CLIMBING
0.08
0.1
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0.14
0.16
0.18
0.2
0.22
0 1 2 3 4 5 6 7 8
FU
EL
INJE
CT
ED
(g/
cycl
e)
TIME (s)
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2200
0 1 2 3 4 5 6 7 8
EN
GIN
E S
PE
ED
(rp
m)
TIME (s)
Fuel System Response Engine Speed Response
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0 1 2 3 4 5 6 7 8
TO
RQ
UE
(N
m)
TIME (s)
HILL CLIMBING
Converter Out
Indicated
Torque Transients
Converter Pump
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SUMMARY AND CONCLUSIONS
A steady-state, phenomenological, zero-dimensional model has been used as the foundation for the development of a transient, single-cylinder, engine simulation module.
The transient extension has involved the implementation of instantaneous engine torque and engine dynamics models on a crank-angle basis.
The transient simulation has been successfully validated against experimental results from a single-cylinder engine.
Multy-cylinder engine response has been validated against transient test results for the DDC 60 engine.
Integrated powertrain-vehicle simulation provides the capability to study complex interactions between the engine, driveline, vehicle structure and the terrain.