Cams and Followers

CAMS

Yatin Kumar Singh

8.1 Introduction

A cam is a rotating or a reciprocating element of a mechanism, which imparts rotating, reciprocating or

oscillating motion to another element, called the follower. There is line contact between the cam and the

follower, and thereby forms a higher pair. Cams are used in clocks, printing machines, automatic screw

cutting machines, internal combustion engines for operating the valves, and shoe making machines etc. In this

chapter, we shall study the various types of planar cams from the point of view of drawing their profile and

motion analysis. The three essential components of a cam mechanism are as follows:

1. The Cam,

2. The Follower, And

3. The Frame.

The cam revolves at a constant speed and drives the follower. The motion of the follower depends upon the

profile of the cam. The frame supports and guides the follower and the cam.

8.2 Classification of Cams

The planar cams can be classified according to their shape as follows:

Wedge and Flat Cams: Such a cam has a wedge A to which translational motion is given to actuate the

follower B in order to either reciprocate or oscillate it, as shown in Fig.8.1 (a) and (b). The follower is guided

in the guides C. In Fig.8.1(c), the cam is stationary and the follower guide C causes the relative motion of the

cam A and follower B. Fig.8.1 (d) shows a flat plate with a groove in which the follower is held to obtain the

desired motion.

(a) (b)

Radial and Offset Cams: A cam in which the follower moves radially from the centre of rotation of the cam is

called a radial (or disc or plate) cam, as shown in Fig.8.2(a) and (b). In such a cam, the axis of the follower

passes through the axis of the cam. If the axis of the follower does not pass through the axis of the cam, it is

called an offset cam, as shown in Fig.8.2(c).

Cylindrical Cams: In a cylindrical cam, a cylinder which has a circumferential groove cut in the surface,

rotates about its axis. The follower motion can be either oscillatory or reciprocating type, as shown in Fig.8.3

(a) and (b). They are also called Barrel or Drum Cams.

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Yatin Kumar Singh

(c) (d)

Fig.8.1 Wedge and flat cams

Fig.8.2 Radial and offset cams

Fig.8.3 Cylindrical cams

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Fig.8.4 Spiral cam Fig.8.5 Conjugate cam

Spiral Cams: A spiral cam is a face cam in which a groove is cut in the form of a spiral, as shown in Fig.8.4.

The spiral groove consists of teeth which mesh with a pin gear follower.

Conjugate Cams: It is a double disc cam in which the two discs keyed together are in constant touch with the

two rollers of a follower, as shown in Fig.8.5. Such a cam gives low wear, low noise, better control of follower,

high speed, and high dynamic loads, etc.

Globoidal Cams: A globoidal cam has either a convex or a concave surface. A circumferential groove is cut on

the surface of rotation of the cam to impart motion to the follower, which has oscillatory motion, as shown in

Fig.8.6(a) and (b). This is used where the angle of oscillation is large.

Spherical Cams: In a spherical cam, the follower oscillates about an axis perpendicular to the axis of rotation

of the cam. The spherical cam is in the form of a spherical surface, as shown in Fig.8.7.

Fig.8.6 Globoidal cam

Fig.8.7 Spherical cam

CAMS

Yatin Kumar Singh

8.3 Types of Followers

The followers can be of the following types:

Based on the surface in contact: The followers based on the type of surface in contact can be classified as:

knife edge, roller, flat faced (or mush room), and spherical-faced follower, as shown in Fig.8.8 (a) to (g).

Fig.8.8 Types of followers

Based on the motion of the follower: Depending upon the motion, the follower could be of the reciprocating

or translating, oscillating or rotating types

Based on the path of motion of follower: When the axis of the follower passes through the centre of

rotation of the cam, it is called a radial follower, and when the axis of the follower does not pass through the

axis of the cam, it is called an offset follower

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Yatin Kumar Singh

8.4 Cam Nomenclature

A radial cam with reciprocating roller follower is shown in Fig.8.9. The following nomenclature is used in

reference to planar cam mechanisms:

Base Circle: It is the smallest circle that can be drawn to the cam profile from the centre of rotation.

Fig.8.9 Cam nomenclature

Prime Circle: It is the smallest circle drawn to the pitch curve from the centre of rotation of the cam.

Pitch Point: It is a point on the pitch curve having the maximum pressure angle.

Pitch Circle: It is the circle drawn through the centre and pitch point.

Trace Point: It is a reference point on the follower and is used to generate the pitch curve. In the case of a

knife edge follower, it is the knife edge, and in the case of a roller follower, it is the centre of the roller.

Pitch Curve: It is the curve generated by the trace point as the follower moves relative to the cam.

Cam Angle: It is the angle turned through by the cam from the initial position.

Pressure Angle: It is the angle between the direction of the follower motion and a normal to the pitch curve.

Lift: It is the maximum travel of the follower from the lowest position to the topmost position. It is also called

throw or stroke of the cam.

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Yatin Kumar Singh

Cam Profile: The surface in contact with the follower is known as the cam profile.

Angle of Ascent: It is the angle of rotation of the cam during which the follower rises up.

Angle of Descent: It is the angle of rotation of the cam during which the follower lowers down.

Angle of Dwell: It is the angle of rotation of cam during which the follower remains stationary.

8.5 Follower Motions

The follower can have following type of motions:

1. Simple Harmonic Motion (SHM)

2. Uniform Acceleration and Deceleration

3. Uniform Velocity

4. Parabolic Motion, and

5. Cycloidal Motion.

8.5.1 Simple Harmonic Motion (SHM)

Consider a particle at A rotating in a circle about point O with uniform angular speed, as shown in Fig.8.10 (a),

and executing simple harmonic motion (SHM). The displacement curve shown in Fig.8.10 (b) can be

constructed as follows:

Draw a semicircle with follower lift as the vertical diameter.

Divide this semicircle into n equal parts (say 6, i.e., 30° each).

Draw cam rotation angle along the x-axis. Mark the angles of ascent, dwell, descent, and dwell on this line.

Divide the angles of ascent and descent into same equal number of parts.

Draw vertical lines at these points.

Draw horizontal lines from the points on the circumference of the semicircle to intersect the vertical lines.

Mark the points of intersection and join by a smooth curve to obtain the displacement diagram.

Fig.8.10 Simple harmonic motion of follower

Motion Analysis

Let y = displacement of the follower

h = lift of the follower (maximum displacement or rise)

θ = angle turned through by the crank OA from given datum ϕ = cam rotation angle for the maximum follower displacement

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Yatin Kumar Singh

= angle on harmonic circle

= � − � = ( ) × − .

For the ascent or descent h of the follower displacement, the cam is rotated through an angle ϕ, whereas a

point on the harmonic semicircle traverses angle π radians. Thus, the cam rotation is proportional to the

angle turned through by the point on the harmonic semicircle, i.e.,

= ��

Thus Eq. (8.1a) becomes,

= ( ) [ − ( �� )] .

Now θ = ωt

= ( ) [ − ( �� )] .

V��oc�t�, � =

Differentiating Eq. (8.1c), we get

= ( ) ( �� ) � ( �� ) = ( ) ( �� ) � ( �� ) . Let θ1 = angle of ascent; θ2 = angle of dwell; θ3 = angle of descent

V��oc�t� du��n� asc�nt, = ( ) ( �� ) � ( �� ) . V��oc�t� du��n� d�sc�nt, = ( ) ( �� ) � ( �� ) . V��oc�t� �s �a��u� w��n � = �

= ( ) ( �� ) .

Ma��u� V��oc�t� o� �o��ow�� du��n� asc�nt = ( ) ( �� ) . Ma��u� V��oc�t� o� �o��ow�� du��n� d�sc�nt = ( ) ( �� ) . Acc��at�on, =

Differentiating Eq. (8.2), we get

= ( ) ( �� ) ( �� ) . Acc��at�on du��n� asc�nt, = ( ) ( �� ) ( �� ) .

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Yatin Kumar Singh

Acc��at�on du��n� d�sc�nt, = ( ) ( �� ) ( �� ) .

Fig.8.11 Displacement, velocity and acceleration distribution in SHM of follower The acceleration is maximum when θ = °. = ( ) ( �� ) .

Ma��u� Acc��at�on o� �o��ow�� du��n� asc�nt = ( ) ( �� ) . Ma��u� Acc��at�on o� �o��ow�� du��n� d�sc�nt = ( ) ( �� ) . The motion of the follower is shown in Fig.8.11. It can be observed from Fig.8.11 that there is an abrupt

change of acceleration from zero to maximum at the beginning of the follower motion and also from

maximum (negative) to zero at the end of the follower motion. The same pattern is repeated during descent.

This leads to jerk, vibration and noise etc. Therefore, SHM should be adopted only for low and moderate cam

speeds.

8.5.2 Motion with Uniform Acceleration and Deceleration

In such a motion, there is acceleration during the first half of the follower motion and deceleration during the

later half. The magnitude of both acceleration and deceleration is the same in the two halves. The

displacement diagram, as shown in Fig.8.12, can be constructed as follows:

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Yatin Kumar Singh

Draw the cam rotation angle along the x-axis and the follower lift along the y-axis.

Mark the angles of ascent, dwell, descent and dwell on the horizontal line and the lift on the vertical line at the

origin.

Divide the angles of ascent and descent into equal number of parts (say 6). Also divide the lift line into same

equal number of parts.

Draw horizontal and vertical lines at these points.

Fig.8.12 Displacement diagram for uniform acceleration and deceleration of follower

Join the origin with the points of intersection on the middle line of ascent upto half the lift. Also join the points

on the other half of the middle line of lift with the topmost point of the last line.

Mark the points of intersection of these lines with the vertical lines.

Join these points with a smooth curve to get the displacement diagram.

Motion Analysis

Let f = uniform acceleration or deceleration of the follower.

y = displacement of follower

=

Integrating, we have = +

where C1 is a constant of integration

If at t = 0, v = 0, then C1 = 0. Hence = Now = =

Integrating again, we have = +

where C2 is another constant of integration.

As y = 0 at t = 0, therefore C2 = 0. Hence

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Yatin Kumar Singh

=

= = � . �

Cons�d��n� t�� o��ow�� at ��dwa�, w� �av�, = and = �/�

= [� � ] = �� .

Ma��u� Acc��at�on du��n� asc�nt, = �� .

Ma��u� Acc��at�on du��n� d�sc�nt, = �� .

= = �� (��) = ( �� ) � .

The velocity is maximum when the follower is at midway position, i.e., θ = ϕ/2

Ma��u� v��oc�t�, = ( �� ) (�) = �� .

Ma��u� v��oc�t� du��n� asc�nt = �� .

Ma��u� v��oc�t� du��n� d�sc�nt = �� .

The motion of the follower is shown in Fig.8.13.

Fig.8.13 Motion with uniform acceleration and deceleration

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It may be observed from Fig.8.13 that there are abrupt changes in the acceleration at the beginning, midway

and at the end of the follower motion. At the midway, an infinite jerk is produced. Therefore, this motion is

adopted for moderate speeds only.

8.5.3 Motion with Uniform Velocity

In this case, the displacement of the follower is proportional to the angle of cam rotation. Therefore, slope of

the displacement curve is constant.

Let y = cθ Where c = constant of proportionality, and θ = angle of cam rotation.

If h = follower rise ϕ = angle through which the cam is to rotate to lift the follower by h. ��n, = �

so t�at = �

∴ = �� .

V��oc�t�, � = (�) . ( �) = �� .

Ac��at�on, = (�) . ( �) = �� .

The variation of displacement, velocity and acceleration are shown in Fig.8.14. It may be observed that

although the acceleration is zero during ascent or descent of the follower, it is infinite at the beginning and

end of the motion. There are abrupt changes in velocity at these points. This results in infinite inertia forces

and is therefore unsuitable from practical point of view.

Fig.8.14 Motion with uniform velocity

This can be avoided by rounding the sharp corners of the displacement curve so that the velocity changes are

gradual at the beginning and end of the follower motion. During these periods the acceleration may be

assumed to be constant and of finite values. A modified uniform velocity motion is shown in Fig.8.15.

CAMS

Yatin Kumar Singh

Fig.8.15 Modified motion with uniform velocity

8.5.4 Parabolic Motion

In the parabolic motion, the displacement of the follower is proportional to the square of the angle of cam

rotation. Let the parabolic motion, for the first half, be represented by = �

where c = a constant of proportionality Fo� = ; � = �

∴ = �

o� = �

��nc� = (��) .

V��oc�t�, � = �� .

Ac��at�on, = (��) = � .

Fo� v��oc�t� to b� �a��u�, � = �

Ma��u� v��oc�t�, = �� .

For the second half, we have

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Yatin Kumar Singh

= + � + �

Fo� � = ; = and = . A�so �o� � = � = ∴ = + � + � = � + �� o� = + �

��nc�, = − ; = � ; = − �

= [ − ( − ��) ] .

= ( �� ) ( − ��) .

= − (��) .

The variation of displacement, velocity and acceleration are shown in Fig.8.16.

Fig.8.16 Parabolic motion

In this case, the displacement of the follower is proportional to the angle of cam rotation.

CAMS

Yatin Kumar Singh

8.5.5 Cycloidal Motion

A cycloid is the locus of a point on a circle rolling on a straight line. The cycloidal curve, as shown in Fig.8.17,

can be constructed by adopting the following steps:

Draw a horizontal line to a convenient scale equal to the angle of ascent of the cam.

At the origin, draw another line perpendicular to the previous line, on a convenient scale, equal to the lift of

the cam.

Divide the angle of ascent into equal number of parts (say 6), and number them from 0 to 6.

Erect vertical lines at these points.

Draw the diagonal QR passing through the origin and produce it backward.

Calculate the radius of the circle, ch08-ueq16, where h = lift.

Select a convenient point P on the diagonal produced backwards and draw a circle with radius equal to r:

Divide the circle into six equal parts and number the ends of the diameters from 0 to 6.

Join points 1–2 and 4–5, intersecting the vertical diameter at points m and n, respectively.

From points m and n, draw lines parallel to QR intersecting vertical lines at 1 and 2 at a and b and lines at 4

and 5 at d and e. The diagonal PQR shall intersect line at 3 at c.

Join the points Q, a, b, c, d, e, and R by a smooth curve to get the cycloidal curve.

Fig.8.17 Cycloidal curve

CAMS

Yatin Kumar Singh

Motion Analysis:

A cycloid is expressed by,

= ( ) [ �� − ( ) � ( �� )] .

= = ( �) ( �) = [� − { } ( � ) ( �� )] . � = �� − ( �� ) ( �� )

= ( �� ) [ − ( �� )] .

Ma��u� v��oc�t�, = �� at � = � .

Ac��at�on, = = ( �) ( �) = ( �� ) . ( �� ) × [ � ( �� )] � = × (��) � ( �� ) .

= × (��) at � = � .

Fig.8.18 Displacement, velocity and acceleration with cycloidal motion

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The variation of cycloidal motion is shown in Fig.8.18. It may be observed that there are no abrupt changes in

the velocity and acceleration at any stage of the motion. Therefore, cycloidal motion is the most ideal for high

speed follower motion.

8.6 Cam Profile with Knife–Edge Follower

The following procedure may be adopted to draw the cam profile with knife edge follower:

Draw the displacement diagram for follower motion.

Consider that cam remains stationary and that the follower moves round it in a direction opposite to the

direction of cam rotation.

Draw the cam base circle and divide its circumference into equal number of divisions depending upon the

divisions used in the displacement diagram.

Draw various positions of follower with dotted lines corresponding to different angular displacement from

the radius from which ascent is to commence.

Draw a smooth curve tangential to the contact surface in different positions.

Example: A disc cam is to give SHM to a knife edge follower during out stroke of 50 mm. The angle of ascent

is 120°, dwell 60°, and angle of descent 90°. The minimum radius of cam is 50 mm. Draw the profile of the

cam when the axis of the follower passes through the axis of the camshaft. Also calculate the maximum

velocity and acceleration during ascent and descent when the camshaft revolves at 240 rpm.

Solution:

Given: h = mm, N = rpm, θ = °, θ3 = 90°

An�u�a� v��oc�t� o� ca� s�a�t, � = � × = . � /

Ma��u� V��oc�t� du��n� asc�nt = (�ℎ) (�� ) = � × × − × .� × = . / Ma��u� V��oc�t� du��n� d�sc�nt = (�ℎ) (�� ) = � × × − × .� × = . / Ma��u� Acc��at�on du��n� asc�nt = ( ) ( �� ) = [� × .� × ] × × − = . / Ma��u� Acc��at�on du��n� d�sc�nt = ( ) ( �� ) = [� × .� × ] × × − = . / Displacement Diagram: The displacement diagram shown in Fig.8.19 (a) may be drawn as follows:

Draw a vertical line 0–6 equal to the lift of 50 mm.

Draw a semicircle on this line and divide the semicircle into six equal parts of 30° each.

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Draw a horizontal line 00′ perpendicular to 0–6 line representing cam rotation angle θ on a scale of cm =

20°.

Divide the ascent angle of 120° into six equal parts and also the descent angle of 90° into six equal parts.

Erect perpendiculars at points 0 to 6 and 6′ to 0′.

Draw horizontal lines from points 1 to 5 on the semicircle to intersect vertical lines drawn previously, as

shown in the figure.

Join the points of intersection with a smooth curve to get the displacement diagram.

Cam Profile:

The cam profile shown in Fig.8.19 (b) may be drawn as follows:

Draw a circle of radius equal to the base circle radius of 50 mm with center O.

Draw angles of ascent, dwell and descent of 120°, 60° and 90°, respectively.

Divide the angles of ascent and descent into six equal parts. Draw radial lines for these angles.

Mark points 0 to 6 and 6′ to 0′ on the base circle in the angles of ascent and descent, respectively.

Measure distance 1a, 2b, 3c, 4d, 5e, and 6f from the displacement diagram for ascent and cut-off

corresponding distances on the radial lines drawn in the cam profile. Repeat the same process during

descent.

Join the points so obtained by a smooth curve to get the cam profile.

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Fig.8.19 Cam profile with radial knife-edge follower having SHM

Example: Draw the cam profile when the knife-edge follower is offset by 20 mm.

Solution: Displacement diagram remains the same as in Example 1. The cam profile as shown in Fig.8.20 can

be drawn as follows:

Draw the offset circle with radius equal to the offset of 20 mm and the base circle with radius 50 mm at centre

O.

Divide the angles of ascent and descent in the offset circle into six equal parts. Draw radial lines intersecting

the offset circle from g to m and n to u in the angle of ascent and descent respectively.

Draw tangents at points g to u intersecting the base circle at 0 to 6 and 6′ to 0′ in the angle of ascent and

descent, respectively.

Measure distances 1a, 2b, 3c, 4d, 5e, and 6f on the displacement diagram for ascent and cut-off corresponding

distances on the tangential lines drawn in the cam profile. Repeat the same process for the angle of descent.

Join the points so obtained by a smooth curve to get the cam profile.

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Fig.8.20 Cam profile with offset knife-edge follower having SHM

8.7 Cam Profile with Roller Follower

8.7.1 Radial Roller Follower

The profile of a cam with radial roller follower has been shown in Fig.8.21. The following steps may be used

to draw the cam profile:

Draw the base circle.

Draw the follower in its 0° position, tangent to the base circle.

Draw the reference circle through the centre of the follower in its 0° position.

Draw radial lines from the centre of the cam, corresponding to the vertical lines in the displacement diagram.

Transfer displacements a, b, c, …, etc. from the displacement diagram to the appropriate radial lines, measuring from the reference circle.

Draw in the follower outline on the various radial lines.

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Draw a smooth curve tangent to these follower outlines.

Example: A disc cam with base circle radius of 50 mm is operating a roller follower with SHM. The lift is 25

mm, angle of ascent 120°, dwell 90°, return 90°, and dwell during the remaining period. The cam rotates at

300 rpm. Find the maximum velocity and acceleration during ascent and descent. The roller radius is 10 mm.

Draw the cam profile when the line of reciprocation of follower passes through the cam axis.

Solution:

Given: N = rpm, h = mm, θ1 = °, θ3 = 90° An�u�a� v��oc�t� , � = � × = . �ad/s

Ma��u� V��oc�t� du��n� asc�nt, �� = (�ℎ) (�� ) = (� × . ) × .� × = . / Ma��u� V��oc�t� du��n� d�sc�nt, �� = (�ℎ) (�� ) = (� × . ) × .� × = . / Ma��u� Acc��at�on du��n� asc�nt = ��ℎ = .. = . / Ma��u� Acc��at�on du��n� d�sc�nt = ��ℎ = .. = . /

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Fig.8.21 Cam with radial roller follower

Cam Profile: The cam profile shown in Fig.8.22 (b) may be drawn as explained below:

Draw the base circle with centre O and radius 50 mm.

Draw the reference circle with radius equal to the sum of the radius of base circle and roller radius, i.e., 60

mm. Draw angles of ascent, dwell, and descent of 120°, 60°, and 90°, respectively.

Divide the angle of ascent and descent into six equal parts.

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Draw radial lines intersecting the reference circle at point 0 to 6 in the angle of ascent and 6′ to 0′ in the angle

of descent.

Measure distances 1a, 2b, etc. from the displacement diagram and mark corresponding distances on the

radial lines in the cam profile from the reference circle.

Repeat the same process in the angle of descent.

Draw circles at points 0 to f and f′ to 0′ with radius equal to the roller radius of 10 mm.

Draw a smooth curve touching (asymptotic) the roller radii to obtain the cam profile.

Fig.8.22 Cam profile with radial roller follower having SHM

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8.7.2 Offset Roller Follower

A cam profile with offset roller follower is shown in Fig.8.23. The following steps may be used to draw the

cam profile:

Draw the base circle.

Draw the follower in its 0° position, tangent to the base circle.

Draw the reference circle through the centre of the follower in its 0° position.

Draw the offset circle tangent to the follower centre line.

Divide the offset circle into a number of divisions corresponding to the divisions in the displacement diagram.

Draw tangents to the offset circle at each number.

Lay off various displacements a, b, c, …, etc. along the appropriate tangent lines, measuring from the reference circle.

Draw in the follower outlines on the various tangent lines.

Draw a smooth curve to these follower outlines.

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Fig.8.23 Cam profile with offset roller follower

8.8 Cam Profile with Translational Flat-Faced Follower

A cam with flat-faced follower is shown in Fig.8.28. The following steps may be adopted to draw the cam

profile:

Draw the base circle, which also serves the reference circle in this case.

Draw the follower in the home position, tangent to the base circle.

Draw radial lines corresponding to the divisions in the displacement diagram, and number accordingly.

Draw in the follower outline on the various radial lines by laying off the appropriate displacements and

drawing lines perpendicular to the radial lines.

Draw a smooth curve tangent to the follower lines.

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8.11 Analytical Methods

8.11.1 Tangent Cam with Roller Follower

A tangent cam with roller follower is shown in Fig.8.39.

Let r = distance between cam and nose centres

r1 = least radius of cam; r2 = nose radius; r3 = roller radius

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l = r2 + r3

= angle of ascent ϕ = angle of contact of cam with straight flank

Fig.8.39 Tangent cam with roller follower

(a) Roller in contact with Straight Flank: At position B, let θ be the angle turned through by the cam, as shown in Fig. . (a). Then lift,

��n ��t, = � − � = � � − � = � − �� = � + � − �� .

V��oc�t�, = = ( �) ( �) = � � + � (− � �� ) .

Maximum velocity occurs at θ = ϕ.

= � � + � (− � �� ) .

Acc��at�on, = = ( �) ( �) = � � + � − �� .

Minimum acceleration occurs at θ = 0° = � � + � .

(b) Follower in contact with Circular Nose:

Fig.8.39 (b) shows the follower in contact with circular nose.

Let OP = r = const.

PD = r2 + r3 = l = const.

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OPD is a slider crank chain in which OP is the crank, PD the connecting rod, and D the slider.

Let θ1 = − θ

For a slider crank chain, the displacement from top dead centre is given by, = �[ − � + − − � � . ]

Where n = l/r

For the cam mechanism shown in Fig.8.41, we have = �[ − � + � + � �⁄ − [{ � + � �⁄ } − � � ] . ] = � − � + − − � � � . .

= � � = �� [� � � + � � �− � � � . ] .

= � � = � � [ � + � � + � � �− � � � / ] .

Fig.8.41 Circular arc cam operating flat-faced follower

8.12 Radius of Curvature and Undercutting

There is no restriction on the radius of curvature of the cam profile with a knife-edge follower. The cam

profile must be convex everywhere for a flat-faced follower. In the case of a roller follower, the concave

portion of the cam profile must have a radius of curvature greater than that of the roller to ensure proper

contact along the cam profile.

To determine the pitch surface of a disc cam with radial roller follower, let the displacement R of the centre of

the follower from the centre of the cam be given by (Fig.8.49):

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� = � + � .

where R0 = minimum radius of the pitch surface of the cam.

f θ = radial motion of the follower as a function of cam angle.

Once the value of R0 is known, the polar coordinates of the centres of the roller follower can be generated.

Fig.8.49 Disc cam operating roller follower

8.12.1 Kloomok and Muffley Method

Let ρ = radius of curvature of the pitch surface

Rr = radius of roller These values are shown in Fig. . together with the radius of curvature ρc of the cam surface, ρ is held

constant and Rr is increased so that ρc decreases. If this continued until Rr equals ρ, then ρc will be zero and

the cam becomes pointed as shown in Fig.8.51 (a). As Rr is further increased, the cam becomes undercut as

shown in Fig.8.51 (b), and the motion of the follower will not be as prescribed. Therefore, to prevent a point

or an undercut from occurring on the cam profile, Rr must be less than ρmin, where ρmin is the minimum value of ρ over the particular segment of profile being considered. )t is impossible to undercut a concave portion of

a cam. The radius of curvature at a point on a curve can be expressed as:

Fig.8.50 Cam and pitch surfaces

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Fig.8.51 Undercutting in cams

= [� + ( ��) ] /[� + ( ��) − � ( �� )]

Where R = f(ϕ). Here f θ = f ϕ) �� = ′ � ; �� = ′′ �

� , = [� + { ′ � } ] /[� + { ′′ � } − �{ ′′ � }] .

� � � � � , �� , + ��

P��ssu�� An��, = � − (� . ��) .

8.12.2 Pressure Angle

The pressure angle is one of the most important parameters in cam design. By increasing the size of the cam,

the pressure angle can be reduced. Consider a cam with offset roller follower, as shown in Fig.8.52

Let = pressure angle; r1 = prime circle radius; e = offset; y = f θ ; θ = angle of cam rotation; ω = angular

velocity of cam

The cam mechanism has four elements, namely, the fixed link 1, cam 2, roller 3, and follower rod 4. The

instantaneous centres are:

12: at O

34: at roller centre

14: at infinity

23: lies on the common normal at the point of contact of the roller and cam surface

24: at the intersection of common normal at the point of contact and horizontal axis on which 14 lies.

CAMS

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Fig.8.52 Cam with offset roller follower

As the movement of the follower rod is pure translation, all points on it have the same velocity. Thus, the

velocity of follower during rise is:

= = � − = �[ + + � ] .

w�� = (� − ) .

� = [ − ][ � + � − . ] = [ � − ][ � + � − . ] .

Du��n� t�� tu�n, � = [| �| + ][ � + � − . ] .

For maximum pressure angle, using rise, we have �� = [ � + (� − ) . ] � − ( � − ) ( �) =

( � − )[ � + � − . ] = ( � )( �) = .

Solve Eq. . to get the value of θ0. Then

CAMS

Yatin Kumar Singh

= � − [( � )( �) ]�=�

.

8.13 Cam Size

The cam size is defined by the following parameters:

Pressure Angle

Radius of Curvature of Cam Profile

Hub Size.

The following methods may be used to reduce the pressure angle:

1. Increase the diameter of the base circle.

2. Increase the angle of rotation of the cam, thereby lengthening the pitch curve for the specified follower

displacement. The cam profile becomes flatter and the pressure angle becomes smaller.

3. Select the motion curve for a smaller pressure angle.

4. By changing the offset of the follower.

Cams and Followers

Engineering

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