4569846498
Kinematics and dynamics of rigid bodies 55 F Pz Z 1 M Q21z P O 1 Body 1 F Py X 1 Y F 1 Px Q M Body 2 Q21x M Q21y PQ z PQ y PQ x Fig. 2.26 Reaction moment between two bodies Taking the above equations (2.146–2.148) and arranging in matrix form gives ⎡M ⎢ ⎢M ⎢ ⎣M Qx Qy Qz ⎤ ⎡ 0 ⎥ ⎢ ⎥ ⎢ PQz ⎥ ⎢ ⎦ ⎣ PQ y PQz 0 PQ x PQy PQ 0 x ⎤ ⎡F ⎥ ⎢ ⎥ ⎢ F ⎥ ⎦ ⎣⎢ F (2.149) From (2.149) it can be seen that the moment {M Q } 1 can be found from the cross product of the relative position vector {R PQ } 1 and the force {F P } 1 : {M Q } 1 {R PQ } 1 {F P } 1 (2.150) It should be noted that in using the vector cross product to compute the moment of a force about a point that the order of the operation is critical. The relative position vector is crossed with the force so that it is the relative position vector that is arranged in skew-symmetric form and not the force vector. The relative position vector must also be the vector from the point about which the moment is taken to the point of application of the force. Px Py Pz ⎤ ⎥ ⎥ ⎦⎥ 2.7 Dynamics of a particle In the remaining sections of this chapter the authors have broadly followed the approach given by D’Souza and Garg (1984) to derive the equations of motion for a rigid body. The starting point is to consider the dynamics of a particle, a body for which the motion is restricted to translation without rotation. The resultant moment acting on the body is therefore zero. In the absence of rotation the velocity and acceleration will be the same at all points on the body and hence a particle may be treated as a point mass. From Newton’s second law it can be seen that the time rate of change of linear momentum {L} 1 for a particle is equal to the resultant force acting on it: d d ∑{} F 1 {} L 1 mV {} 1 (2.151) dt d t ( )
56 Multibody Systems Approach to Vehicle Dynamics The resultant force is represented by the vector {F} 1 , m is the mass and {V} 1 is the velocity vector measured relative to an inertial reference frame O 1 . The linear momentum of the body is m{V} 1 . The components of the vectors in (2.151) are all resolved parallel to the axes of O 1 . Taking the mass to be constant (2.151) may be written as ∑ d {} F m {} V m{} A d t 1 1 1 (2.152) The accelerations in (2.152) are also measured relative to the inertial reference frame O 1 . Since the velocities and accelerations used here are measured relative to a non-moving frame we refer to them as absolute. Expanding the vector equation given in (2.152) gives ⎡Fx ⎤ ⎡Ax ⎤ ⎢ F ⎥ y m ⎢ A ⎥ ∑ ⎢ ⎥ ⎢ y ⎥ ⎣⎢ Fz ⎦⎥ ⎣⎢ Az ⎦⎥ (2.153) 2.8 Linear momentum of a rigid body As a body translates and rotates in space it will have linear momentum {L} 1 associated with translation and angular momentum {H} 1 associated with rotation. For the rigid body, Body 2, shown in Figure 2.27 the mass centre is located at G 2 by the vector {R G2 } 1 relative to the reference frame O 2 . A small element of material with a volume V is located at P relative to O 2 by the position vector {R P } 1 . Assuming Body 2 to be of uniform density , we can say that the element of material has a mass m given by m V (2.154) and that as the element becomes infinitesimal the mass of the body m 2 is given by ∫ m2 d V d m vol ∫ vol (2.155) GRF Z 1 X 1 O 1 Y 1 {V P } 1 P δV {R P } 1 Z 2 Body 2 G 2 O 2 {R G2 } 1 Y X 2 2 {ω 2 } 1 Fig. 2.27 Linear momentum of a rigid body
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Kinematics and dynamics of rigid bodies 55<br />
F Pz<br />
Z 1<br />
M Q21z<br />
P<br />
O 1<br />
Body 1<br />
F Py<br />
X 1<br />
Y F 1 Px<br />
Q<br />
M<br />
Body 2<br />
Q21x<br />
M Q21y<br />
PQ z<br />
PQ y<br />
PQ x<br />
Fig. 2.26<br />
Reaction moment between two bodies<br />
Taking the above equations (2.146–2.148) and arranging in matrix form gives<br />
⎡M<br />
⎢<br />
⎢M<br />
⎢<br />
⎣M<br />
Qx<br />
Qy<br />
Qz<br />
⎤ ⎡ 0<br />
⎥ ⎢<br />
⎥ ⎢ PQz<br />
⎥ ⎢<br />
⎦ ⎣<br />
PQ<br />
y<br />
PQz<br />
0<br />
PQ<br />
x<br />
PQy<br />
PQ<br />
0<br />
x<br />
⎤ ⎡F<br />
⎥ ⎢<br />
⎥ ⎢<br />
F<br />
⎥<br />
⎦ ⎣⎢<br />
F<br />
(2.149)<br />
From (2.149) it can be seen that the moment {M Q } 1 can be found from the<br />
cross product of the relative position vector {R PQ } 1 and the force {F P } 1 :<br />
{M Q } 1 {R PQ } 1 {F P } 1 (2.150)<br />
It should be noted that in using the vector cross product to compute the<br />
moment of a force about a point that the order of the operation is critical.<br />
The relative position vector is crossed with the force so that it is the relative<br />
position vector that is arranged in skew-symmetric form and not the force<br />
vector. The relative position vector must also be the vector from the point<br />
about which the moment is taken to the point of application of the force.<br />
Px<br />
Py<br />
Pz<br />
⎤<br />
⎥<br />
⎥<br />
⎦⎥<br />
2.7 Dynamics of a particle<br />
In the remaining sections of this chapter the authors have broadly followed<br />
the approach given by D’Souza and Garg (1984) to derive the equations of<br />
motion for a rigid body. The starting point is to consider the dynamics of a<br />
particle, a body for which the motion is restricted to translation without<br />
rotation. The resultant moment acting on the body is therefore zero. In the<br />
absence of rotation the velocity and acceleration will be the same at all<br />
points on the body and hence a particle may be treated as a point mass.<br />
From Newton’s second law it can be seen that the time rate of change of linear<br />
momentum {L} 1 for a particle is equal to the resultant force acting on it:<br />
d d<br />
∑{} F 1 {} L 1 mV {} 1<br />
(2.151)<br />
dt<br />
d t<br />
( )