stand still model
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A New Wheel Model For Vehicle Dynamic Simulation
Hai Chenguang.State Key Laboratory of Automobile Dynamics
Simulation, Jilin University
Changchun,130025,China
Ji Peng.State Key Laboratory of Automobile Dynamics
Simulation, Jilin University
Changchun,130025,China
Abstract - A new wheel model was established to simulate
stand-still and starting condition which can’t be accurately
described by previous tire model. In this new model, the wheel
is simplified into two parts: wheel-rim and contact patch,
which were connected by spring-dampers. Contact patch
dynamic system was established, so tire slip ratio can be
calculate more accurately. By introducing stick-slip friction
algorithm, vehicle model can simulate stand-still and starting
condition properly. Through simulation, the new wheel model
was verified well.
Keywords - Wheel model; Stand-still; Stick-slip friction;
I. INTRODUCTION
The previously established tire model has twoshortcomings. (1) Previous tire model use wheel-spin
velocity, longitudinal and lateral velocity of wheel center to
estimate tire slip velocity, so it is inevitable to introduce
large errors, as shown in Figure 1. (2) Because previous tire
model use relaxation length method to handle zero speed of
the vehicle[1] [2]
.it bring about instability and micro
vibration of the vehicle in parking.
Tire mechanical properties largely determine the
movement of the vehicle, so it is important to establish a
more accurate wheel model.
wx x
R V S
R
ω
ω
⋅ −=
⋅
(1)
wxV
ω
R
Figure 1 the estimate of the tire slip ratio
According to shortage of previous model, this paper
presents a new wheel model. The new wheel model builds
the completely dynamical system including contact patch
and elastic tire carcass, and it furthermore establish thecompletely dynamical differential equation of contact patch,
so we can use the movement of wheel-rim to accurately
calculate the tire slip velocity. Stick-slip separation friction
model was used to calculate the friction between contact
patch and road so the force of vehicle was truly calculated
at zero speed and we can simulate stand-still parking
properly.
II. ESTABLISHMENT OF THE NEW WHEEL MODEL
A. Introduction of new wheel model
In order to accurately describe the dynamic mechanicalcharacteristics of tire, the new model simplify the wheel
into two parts: wheel-rim and contact patch, spring-dampers
which represent elasticity of carcass were used in the model
to connect wheel rim and contact patch, as shown in theFigure 2.
Figure 2 wheel model
The new wheel model has three components:
The contact patch transient model
The UniTire steady-state model
The stick-slip separation friction model between
road and contact patch
B. Coordinate system definition[3]
1 Earth-Fixed Coordinate System (XE, YE, ZE) A
coordinate system fixed in the inertial reference. The XE
and YE axes are parallel to the ground plane. The ZE axis is
aligned with the gravitational vector. The positive ZE axis
points upward. The orientation of the XE, and YE axes is
arbitrary and should be based on the needs of the analysis or
test. The location of the origin is generally an arbitrarypoint defined by the user.
2 Wheel Coordinate System(XW,YW,ZW) A
coordinate system whose XW and ZW axes are parallel to the
wheel plane, whose YW axis is parallel to the wheel-spin
axis, and whose XW is parallel to the local road plane. The
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positive ZW axis points to upward. The origin is fixed at
the wheel center.
3 Tire Coordinate System(XT,YT,ZT) A coordinate
system whose XT and YT axes are parallel to the local road
plane, with the ZT axis normal to the local road plane. The
orientation of the XT axis is defined by the intersection ofthe wheel plane and the road plane. The positive ZT points
upward. The origin is fixed at the contact center.
OT
X
T Z
T Y
C
E X
E Y
E Z
W Z
W X
W Y
Figure 3 coordinate system
C. contact patch transient model
In contact patch transient model, the completely
dynamical differential equation of contact patch was
established and we use it to calculate the tire slip velocity.
Spring-dampers were used in the model to connect wheel
rim and contact patch. Because spring-damper represent the
elasticity of the tire carcass and describe the relaxation
effect of the tire, the new model can more accurately
calculate the tire slip velocity. At the same time the elastic
deformation of the tire carcass can self-adaptively adjust the
position relationship of parts[4] [5]
. As shown in formula(2)-(4).
Figure 4 contact patch transient model
cxsxbcycxc F F V V m −=− )( ψ && (2)
cysybcxcyc F F V V m −=+ )( ψ && (3)
czszbc M M I −=ψ & (4)
Fsx, Fsy, Msz represent the force and moment road
acting on contact patch, Fcx, Fcy Mcz represent the force
and moment spring-damper acting on contact patch, Vcx,
Vcy represent tire longitudinal and lateral slip velocity[6]
.
D. UniTire steady-state model
After obtain the tire slip velocity, we use UniTiresteady-state model to calculate tire force between road and
tire. UniTire steady-state model can deal with complex tire
movement input, including large tire slip angle, large
longitudinal slip ratio, large camber angle and large vertical
load.
The advantages of UniTire steady-state model:
UniTire is based on generalized theory model, so it can
satisfy higher-order theory boundary conditions; UniTire
model construct semi-empirical formula based on
exponential function, so it has high identification accuracy
in nonlinear large-slip regional.
E. The stick-slip separation friction model between road
and contact patch
The interaction between tire and road surface can beviewed as a class of contact friction problem. When there is
a relative slip velocity between two objects in contact with
each other, the friction force will be produced to resist therelative movement and the friction force is the function of
the relative slip velocity. When the relative slip velocity is
close to zero, two objects will glue together, until there is a
sufficiently large external force to break this bond. At this
stage, because the relative velocity between two objects is
close to zero, the interaction force can not self-identify and
must dependent on outside forces.
Friction model algorithm: when there is a relative slip
velocity between tire and road, we use UniTire steady-state
model to calculate the friction force between tire and road;
when the slip velocity is very small and close to zero, the
friction model is considered to enter static friction state, the
friction force between tire and road balance with theexternal force, which is the elastic force of the equivalenttire carcass; when elastic force of tire carcass is larger than
maximum static friction force provided by road face,
friction model Re-enter the sliding friction state.
Static friction model introduces stability margins in
longitudinal, lateral, yaw direction and improve the stability
of the vehicle model, so the model able to generate enough
resistance effect when subject to small perturbations. At thesame time, the introduction of the static friction model
make the vehicle model can simulate stand-still (zero
speed) truly and solve the problem of the previous model.
III. THE SIMULATION AND ANALYSIS OF THE NEW WHEELMODEL.
ADAMS software is widely used within the
automotive industry. By programming the subroutine of the
new wheel model, we embed the wheel model into
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ADAMS and carry out the simulation of the vehicle
stand-still and vehicle starting [7]
.
A. The simulation of stand-still (Static equilibrium)
max_ µ F −
max_ µ F
Figure 5 friction model
Static equilibrium: parking without interference of
the external force. Simulation results are shown in Figure
6-7.
0 1 2 3 4 5
-0.015
-0.010
-0.005
0.000
0.005
0.010
0.015
0.020
0.025
0.030
0.035
0.040
0.045
0.050
0.055
l o n g i t u d i n a l v e l o c i t y ( k m / h )
Time
new wheel model
PAC89
Figure 6 longitudinal velocity of vehicle CG
0 1 2 3 4 5
-1.50
-1.49
-1.48
-1.47
-1.46
-1.45
l o n g i t u d i n a l d i s p l a c e m e n t ( m )
time(s)
new wheel model
PAC89
Figure 7 longitudinal displacement of vehicle CG
From simulation results we can see:
When we use PAC89 tire model to simulate
stand-still (static equilibrium), the vehicle will have largeresidual velocity and zero-drift phenomenon will happen.
When we use the new wheel model, the vehicle can
enter static equilibrium state immediately and almost not
have residual velocity, so the new wheel model can makethe vehicle model simulate stand-still (zero speed) truly.
B. The simulation of vehicle starting
Vehicle starting: driving torque is exerted on thefront wheel, Simulation results are shown in Figure 8-9.
0 1 2 3 4
-0.1
0.0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0.9
l o n g i t u d i n a l a c c e l e r a t i o n ( m / s 2 )
time (s)
new wheel model
PAC89
Figure 8 longitudinal acceleration of vehicle CG
0 1 2 3 4
-0.5
0.0
0.5
1.0
1.5
2.0
2.5
3.0
3.5
4.0
4.5
l o
n g i t u d i n a l v e l o c i t y ( k m / h )
A
new wheel model
PAC89
Figure 9 longitudinal velocity of vehicle CG
From simulation results we can see:
The new wheel model has the ability to resist thesmall driving force. Although driving force is exerted on
the wheels, if the driving force does not exceed the
maximum static friction force provided by road, at this
time vehicle dose not start. When the driving force is
larger than maximum static friction force provided byroad, vehicle begins to start.
The PAC89 tire model does not have the ability to
resist the small driving force. As long as the small driving
force is exerted on the wheels, vehicle will begin to startimmediately. This is inconsistent with the actual.
IV. CONCLUSION
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This paper represents a new wheel model. The new
wheel model simplifies the wheel into two parts:
wheel-rim and contact patch, spring-dampers which
represent elasticity of carcass were used to connect wheel
rim and contact patch; the new wheel model builds the
completely dynamical system including contact patch and
elastic tire carcass; Stick-slip separation friction model
between tire and road is introduced and the determination
method of static friction force is found; the subroutine ofthe new wheel model is programmed and it is carried out
in ADAMS software.
Simulation results show that: (1) by contact patch
dynamic, the model can calculate out the tire slip ratio
more accurately, furthermore to calculate out the more
accurate tire force. (2) By introducing stick-slip
separation friction model between road and tire, the
vehicle model can simulate stand-still (zero speed) and
starting properly, so it overcomes the shortcomings of
previous models. (3) The new wheel model introduces
stability margins in longitudinal, lateral, yaw direction
and improves the stability of the vehicle model, so the
model able to generate enough resistance effect when
subject to small perturbations
V. ACKNOWLEDGMENT
The authors wish to thank Prof. Guan Xin and
Prof. Zhan Jun, of State key Laboratory of Automotive
Dynamic Simulation Jilin University, for their support
in my development.
REFERENCES
[1] I.J.M. Besselink, H.B.Pacejka. The SWIFT tyre model: overviewand application[J]. AVEC, 2004:525-530
[2] Konghui Guo, Lei Ren. A Non-steady and Non-linear Tire Model
Under Large Lateral Slip Condition[J]. SAE paper, 2000-01-0358.[3] SAE J670
[4] Konghui Guo, Ye Zhuang. Friction Coefficient Switching In Tire
Semi-empirical Model [J], Automobile technology. 2004
[5] Zhongcheng Yuan. Study of UniTire Steady State Tire Model [D].
Changchun, Jilin University, 2006.
[6] Hans B.Pacejka. Tyre and Vehicle Dynamics[M]. Oxford:
Butterworth-Heinemann, 2002.
[7] ADAMS2005. Help document. Solver
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