 Open Access
 Total Downloads : 561
 Authors : Santosh Kumar, Rojalin Behera
 Paper ID : IJERTV4IS100453
 Volume & Issue : Volume 04, Issue 10 (October 2015)
 DOI : http://dx.doi.org/10.17577/IJERTV4IS100453
 Published (First Online): 23102015
 ISSN (Online) : 22780181
 Publisher Name : IJERT
 License: This work is licensed under a Creative Commons Attribution 4.0 International License
Numerical Analysis of Cam Follower Mechanism And Effect of its Physical Parameter
Santosh Kumar1
School of Mechanical Engineering KIIT University
Bhubaneswar, Odisha
Rojalin Behera2
School of Mechanical Engineering KIIT University
Bhubaneswar, Odisha
Abstract Cam and follower mechanism is modelled numerically. The contact force is analysed with considering the asperity interaction. Reynolds equation is applied for analysing the film thickness and the effect of physical parameter like cam radius, nose flank, cam angle is studied. How the film associated with the speed and frequency of the cam follower mechanism is analysed.
Keywords Contact force; Reynolds equation; hydrodynamic pressure; fluid film thikness; asperity interaction

INTRODUCTION
We know the availability of the organic fuel is limited so manufacture always tries to improve the efficiency of the IC engine. There are many losses in the IC engine. To reduce the power loss a fundamental understanding of the lubrication model is necessary. Theoretical lubrication model is known as mixed lubrication which includes the effect of surface elastic deformation, asperity interaction and squeeze film action.
Theoretical results say that when engine speed and load increased the noise level also increased. Bishop in 195051 given a theoretical model. He said that a rate of change of velocity is responsible for the noise. He proposed an improved cam profile model by considering the discontinuity of acceleration. He defined the profile by sine wave. Due to discontinuity of acceleration the efficiency of engine increased. The type of failure usually found in cam and follower mechanism is pitting, scuffing and wear of polish. Due to variation of load the Hertzian stress also developed in the cam which causes the failure of nose of cam. Hertizian stress in the cam should be less than the critical stress. It also depends upon the property of material. S. Carra, R. Garziera and M. Pellegrini[1] mentioned in their paper that by using cam mechanism, a simple machine can be designed with maximum force and negative rollerfollower radius. They represented that the pressure angle is easily evaluated and because of pressure angle, the mechanism is practical and economic with restricting the space. Hua Qiu, ChangJun Lin, ZiYe Li, Hiroaki Ozaki, Jian Wang and Yong Yue[2] were proposed optimal technique for designing the cam curve.
concluded that the cam profile may concave, convex and flat in the upper portion because of the variation of the velocity. Zhiliang Qian[4] was represented that the analysis and calculation of the value of all the angles are in the cam follower mechanism with considering of transmission angle having constant cam diameter were done. Livija Cveticanin[5] was done the analysis of the dynamic behavior in camfollower mechanism with the consideration of the nonlinear properties. It was investigated through numerical examples. The stability of the camfollower mechanism was checked. E.E. Zayas, S. Cardona and L. Jordi[6] were represented that how the displacement is calculated in case of constant breadth cam mechanism. The displacement may translational or oscillating. it is obtained by some numerical analysis. T.K. Naskar and S. Acharyya[8] were analyzed experimentally the dynamic behavior of the mechanism and they compared the result experimentally and theoretically. They concluded that the experimental and theoretical results are approximately equal and it shows that the system was elastically deformed due to the stress developed. Yanan Yao, Ce Zhang and HongSen Yan[13] were investigating the properties to control the motion because of the speed. They concluded that the motion properties of the follower are performed better with the increase in the input speed. Wen Tung Chang and LongIong Wu[15] were represented that how the tools are dealt for analyzing and synthesizing the error for designing the linkages. By analysis, it is concluded that the tools are used to design or manufacture of the linkage with minimum error. HongSen Yan and WenTeng Chang[16] were defining the surface for the system. The curvature of the mechanism was analyzed with considering limit conditions. After the analysis, they concluded that the hyperbolical and globoidal surfaces are suitable for the roller follower mechanism.

MOTION MECHANISM OF CAM AND FOLLOWER:
We assume that the situation in which the contact rising flank of cam. This is part number 1. Cam rotate about O and O is the centre of curvature of cam surface at point C.
Therefore the absolute velocity in the X, Y direction will be,
Both dynamic and static optimization was done at the same time because of the newly proposed technique which can be used to control the vibration. LongIong Wu, WenTung Chang and ChunHsien Liu[3] were mentioned that the follower motion and other cam parameter were analyzed by giving velocity to the camfollower mechanism. They
u2 0
. (1)
M M m
e 3 .(8)
I= inertia force
I M e a
(9)
Spring force is s
s Kd
At stationary
s K(L d)
When the deflection is equal to (L) d= initial compression of the spring. Therefore the total force on the cam is
W I S Me g ..(10)
Fig.1. schematic diagram of cam and follower
4. REYNOLDS EQUATION:
The lubricated cam mechanism can be treated as cylinder acting on a plane where the cylinder is infinitely wide.
v dL c
2 dt
(2)
Assumption:

Neglect side leakage.

Lubricant density does not change by temperature and
If a is the acceleration then,
d2 L dc
pressure.
1D Reynolds equation for incompressible fluid:
a 2
d p dp dh
dz dz
dt dt
(3)
u
v1 v2 u2 2 u1 1
Velocity in Xdirection in contact with follower,
u1 (Rb L) ..(4) Velocity of contact point along cam surface (ds/dt),
dx 12 dx
Where,
dx dx dx
..(11)
u u
ds
dt
u de
1 dt
(R L) de
b dt
..(5)
u 1 2
2
R ds dt ds
c dt d d
If the surface of follower is flat,
R 1 ds
c dt
.(6)
Combining equation (3),(5) and (6),
R R L de R L a
c b dt b 2
. . (7)


LOAD IN CONTACT MECHANISM:
Experimentally the calculation of load carried out by the cam and follower is very complex. Simply we can say that the force generated in the cam follower is the inertia force.
Fig.2.cam and follower as a cylinder and plane
The spring load generated because of relative motion the
v u
dh h
v 0
parts which are in contact. This force affects the stiffness, damping coefficient and also try to deform the structure.
1 1 dx t 2
dz dh dz
There is certain assumption for the calculation of contact force like

Friction force is neglected.

Mechanism is rigid.

And damping coefficient, stiffness is omitted.
Product of mass and acceleration gives the inertia force of the mechanism. If the total mass is Me then,
1
dx dx
2 0
dx
Equation (11) became,
d p
dp
dh h
6. RELATIONSHIP BETWEEN PRESSURE AND
dx 12
dx u dx
.(12)

t
<>VISCOSITY:
Viscosity changes as change in pressure. For isothermal condition the pressure and viscosity relationship,
Boundary condition for the damaging of film,
0 exp(p)
.(15)
p() 0
and
dp (x dx m
) p(xm
) 0
=pressure viscosity constant
0 = reference viscosity at atm.
The assumption is valid when the profile is parabolic in
x
nature and the magnitude of is small compared to unity.
When the pressure is very high,
n 0 exp(p)
c
R 0 exp[p1
1
( p p1 )]
..(16)
2 2 for P > P and P P
x 1 1
h h0 Rc
R 1
c R
c
= pressure viscosity coefficient
When we apply the Reynolds equation in equation (16), the result non linear which cannot be solved by simple integration, so an another parameter taken into consideration known as reduced pressure (q)
1 1 exp(p)
q 1
[1 exp({p1 ( p p1 )}]
for P P1 and P > P1 Replacing p in equation (12)
[1 exp(p1 )]
d p
dq 12
u dh h
dh
dx
0 dx t
.(17)
Fig.3. asperity interaction of cam follower
Expand the bracket and neglect the fourth and higher power term,
x 2
For isoviscous lubricant,
q in the solution of (17) became ,
1 ln[1 q]
p 1
……….(18)
h h0
2Rc
..(13)
p1
ln[1 (q q1 ) exp(p1 )]
5. ANALYSIS OF CAM AND FOLLOWER BASED ON ELASTICITY APPROACH:
In operating condition the cam and follower surface exerts the heavy load. Due to heavy load the surface of cam and follower deformed elastically.
From fig (2), Elastic deformation at a point at distance x from origin on the surface subjected to non linear pressure p(s) between s s1 and s s1
s1
For q q1 and q > q1
Where, q 1 [1 exp(p )]
1 1
7. AVERAGE REYNOLDS EQUATION:
In operating condition the cam follower is treated as the rough cylinder with rough plane. For rough surface the Reynolds equation becomes,
v(x) 2 p(s) ln(x s)2 ds C
d p d p (u u ) d h u u d h
1 2 1 2 1 s
1
E' s
….(14)
dx
x 12
dx
2 dx
2 dx t
.(19)
Boundary condition
d p (x
) p(x
) 0, p() 0

ASPERITY HEIGHT BETWEEN THE SURFACE OF CAM AND FOLLOWER IN CONTACT
dx m m
Asperity contact force,
And
x ,s
p h 1 2
Empirical pressure and shear flow factor.
W 16
a 15
2( )2
1
E'
2
h
AF
5
p
s Can be calculated by pressure gradient x
At=A= apparent area ,
2
Pressure flow of bearing,
AF h W
F h dx
p p p
p
5 a
5
t
x 12 x
t 0 (20)
y 12 y
2
2 .(26)
Boundary condition
A 2 2 AF
h
p(0, y) pa , p(Lx , y) pb
t 2
p x, o p x, L 0
h h
y y y
AF2 W F2 dx
And no flow at contact.
Solving equation (20) numerically,

NUMERICAL SIMULATION RESULTS:
1 l
p
p
p
p
Table1
L
Rotation of cam shaft 
Min film thickness 

Frequency 
Nose 
Flank 
1200rpm (20Hz) 
0.095 m 
2.16 m 
3000rpm(50Hz) 
0.20 m 
3.46 m 
s y t dy
y 0 12 x 12 x
Where p
x
pb pa L
x
For two parallel surface,

variation of film thickness with base circle radius
p p p
p h
t
t t
x 12 x
Boundary condition,
y 12 y t
p(0, y) p(Lx , y) 0
p x,0 p (x, L ) 0
y y y
8. EFFECT OF ROUGHNESS AND SLIDING IN NET FLOW:
p p
1 Ly
Lx p p
x t
t dxdy
12 x
Lx L y 0 0
12 x
Mean flow Qx due to sliding,
2

p p
E
s
U s
t
12 x
Fig.4 base circle vs film thickness.
Where
U u2 u1
s 2


Variation of cam radius with cam angle
Fig.5. cam angle vs cam radius

Variation of velocity with cam angle:
Fig.6. cam angle vs velocity

Variation of cam angle with thickness:
Fig.7. cam angle vs film thickness
11. CONCLUSION:
The cam and follower is solved numerically and the data is plotted between various physical parameter and it is found that the initially the film thickness is lower and gradually it goes on increasing and after some time it became stable with change in base circle radius, means lubricant film thickness is not only depend upon the base circle radius, nose radius and frequency which is clearly shown in table (1) There will be good lubrication in the cam follower mechanism when base circle increase. it gives more efficiency compare to lower base circle radius cam.cam angle vs. cam radius graph is plotted between 100 degree to 100 degree, cam angle and found to be maximum at 40 degree and 40 degree. It shows there should be a lower cam angle compare to the cam radius for easy working of cam. The velocity is also important parameter of the cam follower mechanism, when the cam angle increases there will be sudden increase in the velocity at certain point and it gives the jerk to the system. Film thickness also get maximum at certain interval when cam angle attain maximum. So effect of physical parameter on cam and follower is analyzed. All the above validated the classical result of design of cam and follower motion. So design consideration is the main parameter for cam and follower mechanism, mainly its efficiency depend upon the cam radius and the lubricant film thickness.
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