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Fig. 18 The system of a
parallel-double-inverted
pendulum
where
I 1 þ
M 1 l 1 ;
I 2 þ
M 2 l 2 ;
I 1 ¼
I 2 ¼
ð
21
Þ
M
¼
M 0 þ
M 1 þ
M 2
ð
22
Þ
a 1 ¼
M 1 l 1 ;
a 2 ¼
M 2 l 2 ;
a 3 ¼
M 1 l 1 g
;
a 4 ¼
M 2 l 2 g
ð
23
Þ
_
where x is the position of the cart,
x is the velocity of the cart,
u
stands for the
u
angular velocity of the
first pendulum with respect to the vertical line,
is the
a
angular velocity of the
first pendulum,
is the angular position of the second
a
pendulum,
represents the angular velocity of the second pendulum, M 1 is the mass
of the
first pendulum, M 2 is the mass of second pendulum, M 0 is the mass of the
cart, l 1 denotes the length of the
first pendulum with respect to its center, l 2 stands
for the length of the second pendulum with respect to its center, f r is the friction
coef
cient of the cart with ground, I 1
first pendulum
with respect to its center, I 2 represents the inertia moment of the second pendulum
with respect to its center, C 1 is the angular frictional coef
is the inertia moment of the
cient of the
rst pen-
dulum, C 2 stands for the angular frictional coef
cient of the second pendulum, and
u is the control effort.
To obtain the state space representations of the dynamic equations, the state
space variables are defined as x ¼½x 1 ; x 2 ; x 3 ; x 4 ; x 5 ; x 6
T . This vector includes the
position of the cart, the velocity of the cart, the angular position and velocity of the
first pendulum, the angular position and velocity of the second pendulum. After
linearization around the equilibrium point x a ¼½
T , the state space
x 1 ;
0
;
0
;
0
;
0
;
0
representation is obtained according to Eq. ( 25 ).
 
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