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Modelling and analysis of suspension systems 137 heights (A 1z , B 1z , C 1z and D 1z ), and the corner stiffness (k A , k B , k C and k D ), and wheel locations are the inputs to the calculations. The unknowns that are found from (4.16) are the body heights at three corners (A 2z , B 2z and C 2z ). These are used to find D 2z from (4.15) leading to the force solution in each corner from equations (4.11–4.14). Thus, the presence of an elastic suspension for the roadwheels allows a solution to the ‘wobbly table’ problem for vehicles with four or more wheels even when traversing terrain that is not smooth. 4.1.2 Body isolation The interaction of a single wheel with terrain of varying height is frequently idealized as shown in Figure 4.5. This is a so-called ‘quarter vehicle’ model and is widely used to illustrate the behaviour of suspension systems. It may be thought of as a stationary system under which a ground profile passes to give a time-varying ground input, z g . Note that at this point we are assuming the tyre to be rigid. Whether classical models or ‘literal’ multibody system models are used, the methods used to comprehend body isolation are the same. Classically, the system may be formulated as a single second order differential equation: mz ˙˙ c( z˙z ˙ g) ks( z zg) 0 (4.20) In order to more fully understand the isolation behaviour of the suspension, a fully developed (steady state) harmonic solution of the equation above may be presumed to apply. ‘Harmonic’ simply means that both input and output may be described with sine functions and that the phase relationships are fixed. This may be conveniently expressed in the form z A e (jt) (4.21) where j is the imaginary square root of 1. Thus for the two derivatives of z it may be written: Vehicle body or sprung mass m z Body response Suspension spring and damper k c Z Z g Ground input X Time (s) Fig. 4.5 A classical quarter vehicle ride model
138 Multibody Systems Approach to Vehicle Dynamics and ˙ż Ae z (4.22) (4.23) The original equation (4.20) can then be written: m 2 z jc(z z g ) k(z z g ) 0 (4.24) Rearranging this in the form of a transfer function gives H( ) (4.25) This expression relates the amplitude and phase of ground movements to the amplitude and phase of the body movements and is commonly reproduced in many vibration theory books and courses. Considering the transfer function, several behaviours may be observed. At frequencies of zero and close to zero, the transfer function is unity. This may reasonably be expected; if the ground is moved very slowly the entire system translates with it, substantially undistorted. The behaviour of the system may be described as ‘static’ where its position is governed only by the preload in the spring and the mass carried by the spring; dynamic effects are absent. At one particular frequency where k/m, —– the real part of the denominator becomes zero and the transfer function is given by H( ) ( j t ) ż j Ae j z 2 ( j t ) 2 (4.26) At this frequency, the behaviour of the system is called ‘resonant’. Examination of the transfer function shows it is at its maximum value. Since k, c and . are all positive real numbers, the transfer function shows that ground inputs are amplified at this frequency. If c is zero, i.e. there is no damping present in the system, then the transfer function is infinite. If c is very large, the transfer function has an amplitude of unity. For typical values of c, the amplitude of the transfer function is greater than unity. At substantially higher frequencies where k/m, —– the transfer function is dominated by the term m 2 in the denominator and tends towards 1 H( ) m 2 ( k) j( c) 2 ( km ) j( c) ( k) j( c) jk jc ( ) jc ( ) 1 (4.27) At these higher frequencies, the amplitude of the transfer function falls away rapidly. It may therefore be noted that if it is desired to have the body isolated from the road inputs, the system must operate in the latter region where —– k/m. In fact this is a general conclusion for any dynamic system; for isolation to occur it must operate above its resonant frequency. Given that the mass of the vehicle body is a function of things beyond the suspension designer’s control, it is generally true that the only variables available
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138 Multibody Systems Approach to Vehicle Dynamics<br />
and<br />
˙ż<br />
Ae z<br />
(4.22)<br />
(4.23)<br />
The original equation (4.20) can then be written:<br />
m 2 z jc(z z g ) k(z z g ) 0 (4.24)<br />
Rearranging this in the form of a transfer function gives<br />
H( )<br />
<br />
(4.25)<br />
This expression relates the amplitude and phase of ground movements to<br />
the amplitude and phase of the body movements and is commonly reproduced<br />
in many vibration theory books and courses.<br />
Considering the transfer function, several behaviours may be observed. At<br />
frequencies of zero and close to zero, the transfer function is unity. This<br />
may reasonably be expected; if the ground is moved very slowly the entire<br />
system translates with it, substantially undistorted. The behaviour of the<br />
system may be described as ‘static’ where its position is governed only by<br />
the preload in the spring and the mass carried by the spring; dynamic<br />
effects are absent.<br />
At one particular frequency where k/m, —– the real part of the denominator<br />
becomes zero and the transfer function is given by<br />
H( )<br />
<br />
( j<br />
t )<br />
ż<br />
j Ae j z<br />
2 ( j<br />
t ) 2<br />
(4.26)<br />
At this frequency, the behaviour of the system is called ‘resonant’.<br />
Examination of the transfer function shows it is at its maximum value.<br />
Since k, c and . are all positive real numbers, the transfer function shows<br />
that ground inputs are amplified at this frequency. If c is zero, i.e. there is<br />
no damping present in the system, then the transfer function is infinite. If c<br />
is very large, the transfer function has an amplitude of unity. For typical<br />
values of c, the amplitude of the transfer function is greater than unity.<br />
At substantially higher frequencies where k/m, —– the transfer function<br />
is dominated by the term m 2 in the denominator and tends towards<br />
1<br />
H( )<br />
m <br />
2<br />
( k) j( c)<br />
2<br />
( km ) j( c)<br />
( k) j( c)<br />
jk<br />
jc ( ) jc ( )<br />
1<br />
(4.27)<br />
At these higher frequencies, the amplitude of the transfer function falls<br />
away rapidly.<br />
It may therefore be noted that if it is desired to have the body isolated<br />
from the road inputs, the system must operate in the latter region where<br />
—– k/m. In fact this is a general conclusion for any dynamic system;<br />
for isolation to occur it must operate above its resonant frequency. Given<br />
that the mass of the vehicle body is a function of things beyond the suspension<br />
designer’s control, it is generally true that the only variables available