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Modelling and assembly of the full vehicle 341 Traditional leaf spring Simple equivalent spring model SAE 3-link model Bush Link Link Link Lumped mass/beam elements Bush Masses Beams Fig. 6.15 Leaf spring modelling strategies The next approach is based on modelling the leaf spring as three bodies (SAE 3-link model) interconnected by bushes or revolute joints with an associated torsional stiffness that provides equivalent force–displacement characteristics as found in the actual leaf spring. The last approach shown in Figure 6.15 uses a detailed ‘as is’ approach representing each of the leaves as a series of distributed lumped masses interconnected by beam elements with the correct sectional properties for the leaf. This type of model is also
342 Multibody Systems Approach to Vehicle Dynamics complicated by the need to model the interleaf contact forces between the lumped masses with any associated components of sliding friction. 6.6 Anti-roll bars As shown in Figure 6.16 anti-roll bars may be modelled using two parts connected to the vehicle body by revolute joints and connected to each other by a torsional spring located on the centre line of the vehicle. In a more detailed model the analyst could include rubber bush elements rather than the revolute joints shown to connect each side of the anti-roll bar to the vehicle. In this case for a cylindrical bush the torsional stiffness of the bush would be zero to allow rotation about the axis, or could have a value associated with the friction in the joint. In this model the connection of the anti-roll bars to the suspension system is not modelled in detail, rather each anti-roll bar part is connected to the suspension using an inplane joint primitive that allows the vertical motion of the suspension to be transferred to the anti-roll bars and hence produce a relative twisting motion between the two sides. A more detailed approach, shown in Figure 6.17, involves including the drop links to connect each side of the anti-roll bar to the suspension systems. The drop link is connected to the anti-roll bar by a universal joint and is connected to the suspension arm by a spherical joint. This is similar to the modelling of a tie rod as discussed in Chapter 4 where the universal joint is used to constrain the spin of the link about an axis running along its length, this degree of freedom having no influence on the overall behaviour of the model. The stiffness K T of the torsional spring can be found directly from fundamental torsion theory for the twisting of bars with a hollow or solid circular cross-section. Assuming here a solid circular bar and units that are consistent with the examples that support this text we have GJ KT (6.3) L where G is the shear modulus of the anti-roll bar material (N/mm 2 ) Right anti-roll bar part Revolute joints to vehicle body REV INPLANE REV Torsional spring Left anti-roll bar part Front wheel knuckle INPLANE Front wheel knuckle Fig. 6.16 Modelling the anti-roll bars using joint primitives
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342 Multibody Systems Approach to Vehicle Dynamics<br />
complicated by the need to model the interleaf contact forces between the<br />
lumped masses with any associated components of sliding friction.<br />
6.6 Anti-roll bars<br />
As shown in Figure 6.16 anti-roll bars may be modelled using two parts connected<br />
to the vehicle body by revolute joints and connected to each other by<br />
a torsional spring located on the centre line of the vehicle. In a more detailed<br />
model the analyst could include rubber bush elements rather than the revolute<br />
joints shown to connect each side of the anti-roll bar to the vehicle. In<br />
this case for a cylindrical bush the torsional stiffness of the bush would be<br />
zero to allow rotation about the axis, or could have a value associated with<br />
the friction in the joint. In this model the connection of the anti-roll bars to<br />
the suspension system is not modelled in detail, rather each anti-roll bar part<br />
is connected to the suspension using an inplane joint primitive that allows the<br />
vertical motion of the suspension to be transferred to the anti-roll bars and<br />
hence produce a relative twisting motion between the two sides.<br />
A more detailed approach, shown in Figure 6.17, involves including the<br />
drop links to connect each side of the anti-roll bar to the suspension systems.<br />
The drop link is connected to the anti-roll bar by a universal joint and<br />
is connected to the suspension arm by a spherical joint. This is similar to<br />
the modelling of a tie rod as discussed in Chapter 4 where the universal<br />
joint is used to constrain the spin of the link about an axis running along its<br />
length, this degree of freedom having no influence on the overall behaviour<br />
of the model.<br />
The stiffness K T of the torsional spring can be found directly from fundamental<br />
torsion theory for the twisting of bars with a hollow or solid circular<br />
cross-section. Assuming here a solid circular bar and units that are<br />
consistent with the examples that support this text we have<br />
GJ<br />
KT <br />
(6.3)<br />
L<br />
where<br />
G is the shear modulus of the anti-roll bar material (N/mm 2 )<br />
Right anti-roll<br />
bar part<br />
Revolute joints to<br />
vehicle body<br />
REV<br />
INPLANE<br />
REV<br />
Torsional<br />
spring<br />
Left anti-roll bar part<br />
Front wheel<br />
knuckle<br />
INPLANE<br />
Front wheel<br />
knuckle<br />
Fig. 6.16<br />
Modelling the anti-roll bars using joint primitives