KINEMATICS OF MECHANISMS
position – velocity – acceleration; driving forces are neglected
2
v 2
v dt
s d dt
s d dt a
sK dsK K K K K
K
For a point K we have linear displacement sK(t), velocity vK and acceleration aK
2 2
dt d dt
d dt
d k k
k k
k k
k
For a link k we have angular displacement k(t), angular velocity k and angular acceleration k
METHODS OF KINEMATIC ANALYSIS
graphical (use only: pencil, ruler, compass, calculator)
analytical
numerical
A
B C
D
M
BC
CDv
MDOF = 1 1 driver, this case: crank AB – known (t)
LENGTH SCALE
A B
C
D
Length scale:
mm
m BC
BC
l
100
1 )
(
SCALE DEFINITION (for graphical methods)
Scale (general)
) (i
i
i
real valuegraphical value
mm ms )
v (
v
-1
vVelocity scale
mm ms )
a (
a
-2
aAcceleration scale
FORCE SCALE
Force scale:
mm
N F
F
F
1
100 100 )
(
4 BAR LINKAGE
a lot of applications
4 bar linkage has a few inversions
Harbor crane
R
R
R T
hand press
pipe spanner,
pipe wrench
Four-bar linkage: crank rocker
A
D
C1 C2
B2
B1
0-l0
3-l3
2-l2
1-l1
For the crank-rocker we have:
1. Grashof inequalities fulfilled,
2. shortest link (l1) is a crank (rotates around frame)
4 BAR LINKAGE (4R)
0 2
3 1
0 3
2 1
3 2
0 1
l l
l l
l l
l l
l l
l l
3 1 2 1 0
1
l l l l l
l
Grashof inequalities
A D C
B
Grashof inequalities fulfilled, shortest link (l1) is a frame
A D
C
B
Grashof inequalities fulfilled, shortest link (l1) is a coupler
DOUBLE CRANK
DOUBLE ROCKER
Transforming a fourbar crank-rocker to crank-slider
R T
Slider block translates
R R
Slider block has complex motion
R R
Slider block rotates
R T
Slider block is stationary 4 BAR - crank-slider - INVERSIONS
B
A
C C
’ B
’
r
BCD
GRAPHICAL POSITION ANALYSIS
B
A
C C’
B’
r
BC(t)
Data: (t) Find: xc’, yc’ xB’ = AB cos yB’ = AB sin
(xC’ – xB’)2 + (yC’ – yB’)2 = BC2
yC’ = 0
From the system of equations:
xC’ , yC’
y
x
GRAPHICAL POSITION ANALYSIS
B
A D
C
C
’ B
’
r
BCD
GRAPHICAL POSITION ANALYSIS
B
A D
C
C’
B’
y
x
(t)
Data: (t) Find: xc’, yc’ xB’ = AB cos yB’ = AB sin
(xC’ – xB’)2 + (yC’ – yB’)2 = BC2
(xC’ – xD)2 + (yC’ – yD) 2 = CD2
r
BCFrom the system of equations : xC’ , yC’
GRAPHICAL POSITION ANALYSIS
A
B C
DM
GRAPHICAL POSITION ANALYSIS
Draw a mechanism for a given
Link dimensions are known: AB, BC, CD, AD and BM, CM
A
B C
D
M
GRAPHICAL POSITION ANALYSIS
A
B C
D
M
GRAPHICAL POSITION ANALYSIS
A
B C
D C*
M
Two positions for given
GRAPHICAL POSITION ANALYSIS
A D B
B1
C
E
F
1 driver: AB AB
1GRAPHICAL POSITION ANALYSIS
A D B
B1
C
E
F
C1
F1 E1
GRAPHICAL POSITION ANALYSIS
A D
B C
E
F F1
R=EF
1 driver: slider F F
1GRAPHICAL POSITION ANALYSIS
D G C
C
’ B
A
B
’ r
BD
CE
F
D
y E
’
F
’
1 2
GRAPHICAL POSITION ANALYSIS - III class mechanism
Kinematics – graphical methods
INSTANT CENTERS OF VELOCITY
VELOCITY AND ACCELARATION
From planar complex motion to rotation
(2 links: frame 0 and moving body k)
A
vB
B
A A v
k
{0}
0
B
tangent to trajectory
instant center of rotation
k0 B k0
A
BS v AS
v
k
( )
tg
k
(BS ) ) (v )
(AS v
k0 B k0
A
angular velocity:
B
a A
b
VA VB VAB = VBA = 0
SAB
{0}
2 bodies in motion
number of IC:
( )
2 1 2
n n n i
An instant center of velocity is a point, common to two bodies in plane motion, which has the same instantaneous velocity in each body
23 13 12
03 02
01
S S S
S S
( ) S
2 6 1 4
4
i
13 02
S S
23 12
03 01
S S
S S
?
V
BV
CV
BV
CS
201, 2, 0 S12 & S10 S20 3, 2, 0 S32 & S30 S20
1, 3, 0 S10 & S30 S31
INFINITY
Find v
Mdirection
0
1 3
2
M
1st method: trajectory of point M and tangent ???
2 method: instant center of velocity S20
23 13 12
03 02
01
S S S
S S
S
0
1 3
30
M
10 21
2
0
1 3
2
30 32
M
10
23 13 12
03 02
01
S S S
S S
S
21
0
1 3
2
30 21
32
20 31
M
VM
10
Cam mechanism
1
2
0
S
12S
01S
02cam
follower
12 1
2
0
10 20
V12
S
10– S
12– S
20common tangent (axis of slip)
Cam with roller
1
2
10
20
V
13= 0 S
13at contact point
3