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Tyre characteristics and modelling 297 {U S } 1 {Rw} 1 φ GRF O 1 W {X sae } 1 {R PW } 1 {V } 1 P {R P } 1 {Y sae } 1 {Z sae } 1 Fig. 5.54 Tyre geometry and kinematics. (This material has been reproduced from the Proceedings of the Institution of Mechanical Engineers, K1 Vol. 214 ‘The modelling and simulation of vehicle handling. Part 3: tyre modelling’, M.V. Blundell, page 7, by permission of the Council of the Institution of Mechanical Engineers) If the angular velocity vector of the wheel is denoted by {} 1 then the velocity {V P } 1 of point P is given by: {V P } 1 {V W } 1 {V PW } 1 (5.35) where {V PW } 1 {} 1 {R PW } 1 (5.36) It is now possible to determine the components of {V P } 1 which act parallel to the SAE co-ordinate system superimposed at P. The longitudinal slip velocity V XC of point P is given by: V XC {V P } 1 • {X SAE } 1 (5.37) The lateral slip velocity V Y of point P is given by: V Y {V P } 1 • {Y SAE } 1 (5.38) The vertical velocity V Z at point P, which will be used to calculate the damping force in the tyre, is given by: V Z {V P } 1 • {Z SAE } 1 (5.39) Considering the angular velocity vector of the wheel {} 1 in more detail we can represent the vector as follows. The wheel develops a slip angle which is measured about {Z SAE } 1 , a camber angle which is measured about {X SAE } 1 and a spin angle which is measured about {U S } 1. The total angular velocity vector of the wheel is the summation of all three motions and is given by: {} ˙{ ZSAE} ˙{ XSAE} ˙{ U s } 1 1 1 1 (5.40)
298 Multibody Systems Approach to Vehicle Dynamics It is possible to consider an angular velocity vector { S } 1 that only considers the spinning motion of the wheel and does not contain the contributions due to and . This vector for angular velocity that only considers spin is given by: { } ˙{ U } (5.41) S 1 S Using this it is possible to determine V C the ‘circumferential velocity’ component of point P relative to the centre of the wheel W and measured parallel to {X SAE } 1 : V C ({ S } 1 {R PW } 1 ) • {X SAE } 1 (5.42) At this stage it may be worth considering the usual two-dimensional representation of longitudinal slip for straight-line braking. Referring back to section 5.4.4 a definition of slip ratio, S, during braking was given by V R S B e (5.43) V Based on the velocities which have been determined for the threedimensional case it is now possible to calculate a longitudinal slip ratio, S, during braking which is given by: VXC S (5.44) | VX | For this formulation of slip ratio V XC can be considered to be the contact patch velocity relative to the road surface. This is equivalent to V B R e in the two-dimensional model, albeit using the loaded radius in the vectorbased formulation. The circumferential velocity V C of P measured relative to the wheel centre can be subtracted from V XC to give V X the actual longitudinal velocity of P ignoring the rotation effect. This can be thought of as the velocity of an imaginary point in the ground that follows the contact patch and is also equivalent to V in the two-dimensional model. During traction, the longitudinal slip ratio is formulated using: VXC S (5.45) | Vc | The lateral slip of the contact patch relative to the road is defined by the slip angle where arctan{V Y /V X } (5.46) During braking a lateral slip ratio S is computed as: S |tan | |V Y /V X | (5.47) During braking S will have a value of zero when V Y is zero and can have a maximum value of 1.0, which equates to a slip angle of 45 degrees. Slip angles in excess of this are not usual for vehicle handling but may occur in other applications where a tyre model is used, for example, to simulate aircraft taxiing on a runway. During traction the formulation becomes: S (1 S)|tan | |V Y /V C | (5.48)
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298 Multibody Systems Approach to Vehicle Dynamics<br />
It is possible to consider an angular velocity vector { S } 1 that only considers<br />
the spinning motion of the wheel and does not contain the contributions<br />
due to and . This vector for angular velocity that only considers<br />
spin is given by:<br />
{ } ˙{ U }<br />
(5.41)<br />
S 1<br />
S<br />
Using this it is possible to determine V C the ‘circumferential velocity’<br />
component of point P relative to the centre of the wheel W and measured<br />
parallel to {X SAE } 1 :<br />
V C ({ S } 1 {R PW } 1 ) • {X SAE } 1 (5.42)<br />
At this stage it may be worth considering the usual two-dimensional representation<br />
of longitudinal slip for straight-line braking. Referring back to<br />
section 5.4.4 a definition of slip ratio, S, during braking was given by<br />
V R<br />
S B e<br />
(5.43)<br />
V<br />
Based on the velocities which have been determined for the threedimensional<br />
case it is now possible to calculate a longitudinal slip ratio, S,<br />
during braking which is given by:<br />
VXC<br />
S <br />
(5.44)<br />
| VX<br />
|<br />
For this formulation of slip ratio V XC can be considered to be the contact<br />
patch velocity relative to the road surface. This is equivalent to V B R e<br />
in the two-dimensional model, albeit using the loaded radius in the vectorbased<br />
formulation. The circumferential velocity V C of P measured relative<br />
to the wheel centre can be subtracted from V XC to give V X the actual longitudinal<br />
velocity of P ignoring the rotation effect. This can be thought of as<br />
the velocity of an imaginary point in the ground that follows the contact<br />
patch and is also equivalent to V in the two-dimensional model. During<br />
traction, the longitudinal slip ratio is formulated using:<br />
VXC<br />
S (5.45)<br />
| Vc<br />
|<br />
The lateral slip of the contact patch relative to the road is defined by the slip<br />
angle where<br />
arctan{V Y /V X } (5.46)<br />
During braking a lateral slip ratio S is computed as:<br />
S |tan | |V Y /V X | (5.47)<br />
During braking S will have a value of zero when V Y is zero and can have a<br />
maximum value of 1.0, which equates to a slip angle of 45 degrees. Slip<br />
angles in excess of this are not usual for vehicle handling but may occur in<br />
other applications where a tyre model is used, for example, to simulate aircraft<br />
taxiing on a runway.<br />
During traction the formulation becomes:<br />
S (1 S)|tan | |V Y /V C | (5.48)