4569846498
Kinematics and dynamics of rigid bodies 73 Z 3 Z 1 Body 1 Body 2 Y 2 ,Y 3 G 3 θ Y 1 X Body 3 O 3 1 X 1 {ω 3 } 2/2 {ω 2 } 1/1 Fig. 2.37 Swing arm suspension dynamics with a constant angular velocity of 100 rad/s about the axis of the revolute joint representing the wheel bearing. The following data may be used to represent the mass properties of the road wheel: m 3 16 kg I 31 I 3xx 0.5 kg m 2 I 32 I 3yy 1.0 kg m 2 I 33 I 3zz 0.5 kg m 2 In order to determine the reaction torque on the wheel bearing when the axle is still in a horizontal position, 0, we can use the following to give us the required angular velocity vector { 3 } 1/3 : ⎡10⎤ ⎡ 0 ⎤ ⎡ 10 ⎤ { } / ⎢ 2 12 0 ⎥ rad/s { } / ⎢ 23 100 ⎥ rad/s { } / ⎢ 13 100 ⎥ rad/s ⎢ ⎥ 3 ⎢ ⎥ 3 ⎢ ⎥ ⎣⎢ 0 ⎦⎥ ⎣⎢ 0 ⎦⎥ ⎣⎢ 0 ⎦⎥ In the absence of angular acceleration equation (2.233) can be adapted to give for this problem Σ{ M3} 13 / [ 3] 13 / [ I3] 13 / { 3} 13 / (2.238) Expanding this gives ∑ ⎡M ⎢ ⎢ M ⎣⎢ M 3x 3y ⎤ ⎥ ⎥ ⎦⎥ 3z 1/3 ⎡ 0 ⎢ ⎢ ⎢ ⎣ 0 3z 3y 3z 3x 3y 3x 0 ⎤ ⎥ ⎥ ⎥ ⎦ 1/3 ⎡I3xx 0 0 ⎤ ⎢ ⎢ 0 I ⎥ 3yy 0 ⎥ ⎣⎢ 0 0 I ⎦⎥ 3zz 3/3 ⎡ ⎢ ⎢ ⎣⎢ 3x 3y ⎤ ⎥ ⎥ ⎦⎥ 3z 1/3 (2.239)
74 Multibody Systems Approach to Vehicle Dynamics Substituting in the numerical data for this problem gives ∑ ∑ ⎡M ⎢ ⎢ M ⎣⎢ M ⎡M ⎢ ⎢ M ⎣⎢ M 3x 3y 3x 3y ⎤ ⎥ ⎥ ⎦⎥ 3z 1/3 ⎤ ⎥ ⎥ ⎦⎥ 3z 1/3 ⎡ 0 0 100 ⎤ ⎡05 . 0 0 ⎤ ⎡ 10 ⎤ ⎢ 0 0 10 ⎥ ⎢ 0 10 . 0 ⎥ ⎢ 100 ⎥ Nm ⎢ ⎥ ⎢ ⎥ ⎢ ⎥ ⎣⎢ 100 10 0 ⎦⎥ ⎣⎢ 0 0 05 . ⎦⎥ ⎣⎢ 0 ⎦⎥ ⎡ 0 0 100 ⎤ ⎡50 . ⎤ ⎢ 0 0 10 ⎥ ⎢ 100 ⎥ Nm ⎢ ⎥ ⎢ ⎥ ⎣⎢ 100 10 0 ⎦⎥ ⎣⎢ 0 ⎦⎥ ∑ ⎡M ⎢ ⎢ M ⎣⎢ M 3x 3y ⎤ ⎥ ⎥ ⎦⎥ 3z 1/3 ⎡ 0 ⎤ ⎢ 0 ⎥ Nm ⎢ ⎥ ⎣⎢ 500⎦⎥ (2.240) As can be seen from the result in (2.240) the reaction torque on the wheel bearing is about the z-axis and is due to gyroscopic effects as the wheel spins about the y-axis and rotates about the x-axis. It should be noted that in addition to the derivation of the equations of motion based on the direct application of Newton’s laws, variational methods, including, for example, Lagranges equations, provide an elegant alternative and are often employed in MBS formulations. Many texts on classical dynamics such as D’Souza and Garg (1984) include a thorough treatment of these methods. Variational methods are attractive for a number of reasons. Equations are formulated using kinetic energy and work resulting in scalar rather than vector terms. Solutions can also be more efficient since constraint forces that do not perform work can be omitted. Variational methods also make use of generalized rather than physical co-ordinates reducing the number of equations required. The theory and methods described in this chapter form a basis for the multibody systems formulations covered in the next chapter. The vector notation used here will be used to describe the part equations and the constraint equations required to represent joints constraining relative motion between interconnected bodies. In Chapter 4 the vector-based methods described here will be used to carry out a range of analyses from first principles on a double wishbone suspension system and to compare the calculated results with those found using MSC.ADAMS.
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74 Multibody Systems Approach to Vehicle Dynamics<br />
Substituting in the numerical data for this problem gives<br />
∑<br />
∑<br />
⎡M<br />
⎢<br />
⎢<br />
M<br />
⎣⎢<br />
M<br />
⎡M<br />
⎢<br />
⎢<br />
M<br />
⎣⎢<br />
M<br />
3x<br />
3y<br />
3x<br />
3y<br />
⎤<br />
⎥<br />
⎥<br />
⎦⎥<br />
3z<br />
1/3<br />
⎤<br />
⎥<br />
⎥<br />
⎦⎥<br />
3z<br />
1/3<br />
⎡ 0 0 100 ⎤ ⎡05<br />
. 0 0 ⎤ ⎡ 10 ⎤<br />
<br />
⎢<br />
0 0 10<br />
⎥ ⎢<br />
0 10 . 0<br />
⎥ ⎢<br />
100<br />
⎥<br />
Nm<br />
⎢<br />
⎥ ⎢<br />
⎥ ⎢ ⎥<br />
⎣⎢<br />
100 10 0 ⎦⎥<br />
⎣⎢<br />
0 0 05 . ⎦⎥<br />
⎣⎢<br />
0 ⎦⎥<br />
⎡ 0 0 100 ⎤ ⎡50<br />
. ⎤<br />
<br />
⎢<br />
0 0 10<br />
⎥ ⎢<br />
100<br />
⎥<br />
Nm<br />
⎢<br />
⎥ ⎢ ⎥<br />
⎣⎢<br />
100 10 0 ⎦⎥<br />
⎣⎢<br />
0 ⎦⎥<br />
∑<br />
⎡M<br />
⎢<br />
⎢<br />
M<br />
⎣⎢<br />
M<br />
3x<br />
3y<br />
⎤<br />
⎥<br />
⎥<br />
⎦⎥<br />
3z<br />
1/3<br />
⎡ 0 ⎤<br />
<br />
⎢<br />
0<br />
⎥<br />
Nm<br />
⎢ ⎥<br />
⎣⎢<br />
500⎦⎥<br />
(2.240)<br />
As can be seen from the result in (2.240) the reaction torque on the wheel<br />
bearing is about the z-axis and is due to gyroscopic effects as the wheel<br />
spins about the y-axis and rotates about the x-axis.<br />
It should be noted that in addition to the derivation of the equations of<br />
motion based on the direct application of Newton’s laws, variational methods,<br />
including, for example, Lagranges equations, provide an elegant alternative<br />
and are often employed in MBS formulations. Many texts on classical<br />
dynamics such as D’Souza and Garg (1984) include a thorough treatment<br />
of these methods.<br />
Variational methods are attractive for a number of reasons. Equations are<br />
formulated using kinetic energy and work resulting in scalar rather than<br />
vector terms. Solutions can also be more efficient since constraint forces<br />
that do not perform work can be omitted. Variational methods also make<br />
use of generalized rather than physical co-ordinates reducing the number<br />
of equations required.<br />
The theory and methods described in this chapter form a basis for the<br />
multibody systems formulations covered in the next chapter. The vector<br />
notation used here will be used to describe the part equations and the constraint<br />
equations required to represent joints constraining relative motion<br />
between interconnected bodies. In Chapter 4 the vector-based methods<br />
described here will be used to carry out a range of analyses from first principles<br />
on a double wishbone suspension system and to compare the calculated<br />
results with those found using MSC.ADAMS.