simple mechanisms -...
TRANSCRIPT
Chapter 5
Simple Mechanisms
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5.2. Kinematic Link or Element
kinematic link (link) or element: Each part of a machine, which moves relative to some other part. A link need not to be a rigid body
It must be a resistant body.
A resistant body: capable of transmitting required forces with negligible deformation.
Thus a link should have the following two characteristics: 1. It should have relative motion
2. It must be a resistant body
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5.3. Types of Links In order to transmit motion, the driver and the follower may be connected by the following three types of links:
1. Rigid link: does not undergo any deformation while transmitting motion.
2. Flexible link: is partly deformed in a manner not to affect the transmission of motion. Example: belts, ropes, chains and wires
3. Fluid link: is formed by having a fluid in a container and the motion is transmitted through the fluid by pressure or compression only Example: hydraulic presses, jacks and brakes
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5.4. Structure and a Machine Structure: assembly of a number of resistant bodies
(members) having no relative motion between them and meant for carrying loads having straining action. Examples: A railway bridge, a roof truss, machine frames
Differences between a machine and a structure:
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Machine Structure
Parts move relative to one
another
members do not move relative to
one another
A machine transforms available
energy into some useful work
in a structure no energy is
transformed into useful work
links of a machine may transmit
both power & motion
members of a structure transmit
forces only
5.6. Kinematic Pair
a pair: two links of a machine, in contact
with each other.
If the relative motion between them is
completely or successfully constrained
(i.e. in a definite direction), the pair is
known as kinematic pair.
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5.7. Types of Constrained Motions
Three types of constrained motions:
1. Completely constrained motion
2. Incompletely constrained motion
3. Successfully constrained motion
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5.7. Types of Constrained Motions Completely constrained motion
Motion between a pair is limited to a definite direction irrespective of direction of force applied.
Example: piston and cylinder (in a steam engine) form a pair and motion of piston is limited to a definite direction relative to cylinder irrespective of direction of motion of crank.
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5.7. Types of Constrained Motions Incompletely constrained motion
Motion between a pair can take place in more
than one direction.
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5.7. Types of Constrained Motions Successfully constrained motion
When motion between elements, forming a pair is such that the constrained motion is not completed by itself, but by some other means, then motion is said to be successfully constrained motion.
Fig. 5.5: shaft may rotate in a bearing or it may move upwards. a case of incompletely
constrained motion.
If load is placed on shaft to prevent axial upward movement of shaft, then motion of pair is said to be successfully constrained motion.
Motion of piston reciprocating inside an engine cylinder.
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5.8. Classification of Kinematic Pairs
1. According to type of relative motion between elements
a. Sliding pair
b. Turning pair
c. Rolling pair
d. Screw pair
e. Spherical pair
2. According to type of contact between elements
a. Lower pair
b. Higher pair
3. According to type of closure
a. Self closed pair
b. Force - closed pair
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5.8. Classification of Kinematic Pairs According to type of relative motion between elements
a. Sliding pair.
one pair can only slide relative to the other.
A sliding pair has a completely constrained motion.
Examples:
The piston & cylinder
tail stock on lathe bed
b. Turning pair.
one pair can only turn or revolve about a fixed axis of another
link.
A turning pair has a completely constrained motion.
Examples:
A shaft with collars at both ends fitted into a circular hole
Crankshaft in a journal bearing in an engine
lathe spindle supported in head stock
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5.8. Classification of Kinematic Pairs According to type of relative motion between elements
c. Rolling pair.
one pair rolls over another fixed link.
Example: Ball and roller bearings.
d. Screw pair.
one element can turn about the other by screw threads.
Example: Lead screw of a lathe with nut.
e. Spherical pair.
one element (with spherical shape) turns or swivels about
the other fixed element.
Examples: Ball and socket joint, attachment of a car
mirror, pen stand.
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5.8. Classification of Kinematic Pairs According to type of contact between the elements
a. Lower pair.
The two elements of a pair have a surface contact when
relative motion takes place
surface of one element slides over surface of the other.
Examples: Sliding pairs, turning pairs and screw pairs.
b. Higher pair.
The two elements of a pair have a line or point contact
when relative motion takes place
the motion between the two elements is partly turning and
partly sliding.
Examples: A pair of friction discs, toothed gearing, belt
and rope drives, ball and roller bearings, and cam and
follower.
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5.8. Classification of Kinematic Pairs According to type of closure
a. Self closed pair.
The two elements of a pair are connected together
mechanically in such a way that only required kind of
relative motion occurs.
The lower pairs are self closed pair.
b. Force - closed pair.
The two elements of a pair are not connected
mechanically but are kept in contact by the action of
external forces.
Example: The cam and follower, as it is kept in contact by
the forces exerted by spring and gravity.
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5.9. Kinematic Chain A kinematic chain:
a combination of kinematic pairs, joined in such a way that each link forms a part of two pairs
Relative motion between the links or elements is completely or successfully constrained.
Example: crankshaft of an engine forms a kinematic pair with the
bearings which are fixed in a pair, connecting rod with crank forms a second kinematic
pair,
piston with connecting rod forms a third pair piston with cylinder forms a fourth pair. The total combination of these links is a kinematic chain.
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5.9. Kinematic Chain If each link is assumed to form two pairs with two
adjacent links, then the relation between number of pairs (p) forming a kinematic chain and number of links (l) may be expressed as:
l = 2 p – 4
Relation between number of links (l) and number of joints (j) which constitute a kinematic chain is given by:
Equations (i) and (ii) are applicable only to kinematic chains, in which lower pairs are used.
These equations may also be applied to kinematic chains, in which higher pairs are used. each higher pair may be taken as equivalent to two lower
pairs with an additional element or link.
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5.9. Kinematic Chain Examples
Fig. 5.6: arrangement of three links AB, BC and CA with pin joints at A, B and C
it is not a kinematic chain and hence no relative motion
is possible.
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5.9. Kinematic Chain
Examples – constrained kinematic chain of one DOF
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5.9. Kinematic Chain Examples
it is not a kinematic chain
unconstrained chain
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5.9. Kinematic Chain Examples – compound kinematic chain
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A chain having more than four links is
known as compound kinematic chain
5.10. Types of Joints in a Chain 1. Binary joint
Two links are joined at the same connection. Fig. 5.10: four links and four binary joins at A, B, C and D.
To determine nature of chain, i.e. whether chain is a locked chain (structure) or kinematic chain or unconstrained chain, the following relation between number of links and number of binary joints, as given by A.W. Klein, may be used :
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j = Number of binary joints
h = Number of higher pairs
l = Number of links
5.10. Types of Joints in a Chain 2. Ternary joint
Three links are joined at the
same connection.
Fig. 5.11:
six links
three binary joints at A, B & D
two ternary joints at C & E
One ternary joint is equivalent to
two binary joints
Equivalent binary joints = 3 + 2 ×
2 = 7
l = 6 and j = 7
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kinematic chain or
constrained chain
5.10. Types of Joints in a Chain 3. Quaternary joint
Four links are joined at the same connection
It is equivalent to three binary joints
When l number of links are joined at same
connection, joint is equivalent to (l – 1) binary
joints.
Fig. 5.12 (a):
one binary joint at D
four ternary joints at A, B, E and F equivalent to
8 binary joints
two quaternary joints at C & G equivalent to 6
binary joints
total number of binary joints in chain are
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Since LHS is greater than RHS, chain, is not a kinematic chain locked chain and forms a rigid frame or structure.
5.10. Types of Joints in a Chain 3. Quaternary joint
total number of binary
joints are 1 + 2 × 6 = 13
Since LHS is equal to RHS,
chain is a kinematic chain
or constrained chain
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5.11. Mechanism
When one of the links of a kinematic chain is
fixed, the chain is known as mechanism.
It may be used for transmitting or transforming
motion e.g. engine indicators, typewriter etc.
simple mechanism: four links
compound mechanism: more than four links
When a mechanism is required to transmit
power or to do some particular type of work, it
becomes a machine.
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5.12. Number of DOF for Plane Mechanisms
DOF: number of input parameters which
must be independently controlled in order
to bring the mechanism into a useful
engineering purpose.
It is possible to determine number of DOF
of a mechanism directly from:
number of links
number and types of joints
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5.12. Number of DOF for Plane Mechanisms
Fig. 5.13 (a)
Only one variable is
needed to define the
relative positions of all
the links.
number of DOF of a
four bar chain is one.
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5.12. Number of DOF for Plane Mechanisms
Fig. 5.13 (b).
Two variables q1 and q2
are needed to define
completely the relative
positions of all the links.
Number of DOF is two.
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5.12. Number of DOF for Plane Mechanisms
Fig. 5.14 (a): two links AB and CD in a plane motion,
each link of a mechanism has 3 DOF before it is connected to any other link
when link CD is connected to link AB by a turning pair at A, the position of link CD is now determined by a single variable and thus has one DOF
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5.12. Number of DOF for Plane Mechanisms
when a link is connected to a fixed link by a
turning pair (i.e. lower pair), two DOF are
destroyed
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5.12. Number of DOF for Plane Mechanisms
Consider a plane mechanism with l number of links.
Since in a mechanism, one of the links is to be fixed, therefore: number of movable links = (l – 1)
total number of DOF = 3 (l – 1) before they are connected to any other link.
A mechanism with l number of links connected by j number of binary joints or lower pairs (single DOF pairs) and h number of higher pairs (two DOF pairs), then number of DOF of a mechanism is given by
Kutzbach criterion for movability of a mechanism having plane motion
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5.13. Application of Kutzbach
Criterion to Plane Mechanisms
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a structure and no relative motion between the links is possible
there are redundant constraints in the
chain and it forms a statically
indeterminate structure
5.13. Application of Kutzbach
Criterion to Plane Mechanisms
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5.13. Application of Kutzbach
Criterion to Plane Mechanisms
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Fig. 5.17 (a): three links, two binary joints and one higher pair, i.e. l = 3,
j = 2 and h = 1.
Fig. 5.17 (b): four links, three binary joints and one higher pair, i.e. l = 4, j
= 3 and h = 1
5.14. Grubler’s Criterion for
Plane Mechanisms Grubler’s criterion applies to mechanisms with only
single DOF joints
Substituting n = 1 and h = 0 in Kutzbach equation, we have
1 = 3 (l – 1) – 2 j or 3l – 2j – 4 = 0
This equation is known as the Grubler's criterion for plane mechanisms with constrained motion.
A plane mechanism with a movability of 1 and only single DOF joints can not have odd number of links.
The simplest possible mechanisms of this type are a four bar mechanism and a slider-crank mechanism in which l = 4 and j = 4.
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5.15. Inversion of Mechanism
We can obtain as many mechanisms as the number of links in a kinematic chain by fixing different links in a kinematic chain.
Inversion of the mechanism: method of obtaining different mechanisms by fixing different links in a kinematic chain. Relative motions between various links is not changed in
any manner through the process of inversion, but their absolute motions may be changed drastically.
Driver: part of a mechanism which initially moves with respect to the frame or fixed link
Follower: part of mechanism to which motion is transmitted.
Most of mechanisms are reversible, so that same link can play the role of a driver and follower at different times.
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5.16. Types of Kinematic Chains
The most important kinematic chains are
those which consist of four lower pairs, each
pair being a sliding pair or a turning pair.
The following three types of kinematic chains
with four lower pairs are important from the
subject point of view :
1. Four bar chain or quadric cyclic chain
2. Single slider crank chain
3. Double slider crank chain
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5.17. Four Bar Chain or
Quadric Cycle Chain
Four links, each of them forms a turning pair at A, B, C & D.
The four links may be of different lengths.
Grashof ’s law for a four bar mechanism: sum of shortest and longest link lengths should not be greater than the sum of remaining two link lengths if there is to be continuous relative motion between the two links.
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5.17. Four Bar Chain or
Quadric Cycle Chain Input crank makes a complete
revolution relative to other links.
The mechanism in which no link makes a complete revolution will not be useful.
One of the links, in particular the shortest link, will make a complete revolution relative to the other three links, if it satisfies the Grashof ’s law. Such a link is known as crank or driver.
Link BC (link 2) which makes a partial rotation or oscillates is known as lever or rocker or follower and link CD (link 3) which connects crank and lever is called connecting rod or coupler. The fixed link AB (link 1) is known as frame of mechanism.
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5.18. Inversions of Four Bar Chain 1. Beam engine (crank and lever mechanism)
When crank rotates about the fixed center A, the lever oscillates about a fixed center D. The end E of the lever CDE is connected to a piston rod which reciprocates due to the rotation of the crank.
The purpose of this mechanism is to convert rotary motion into reciprocating motion.
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5.18. Inversions of Four Bar Chain 2. Coupling rod of a locomotive (Double crank mechanism)
links AD and BC (having equal length) act as cranks and are connected to the respective wheels.
link CD acts as a coupling rod and link AB is fixed in order to maintain a constant center to center distance between them. This mechanism is meant for transmitting rotary motion from one wheel to the other wheel.
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5.18. Inversions of Four Bar Chain 3. Watt’s indicator mechanism (Double lever mechanism)
Watt's straight line mechanism
consists of four links:
fixed link at A
link AC
link CE
link BFD.
Links CE & BFD act as levers
Displacement of link BFD is
directly proportional to pressure
of gas or steam which acts on
the indicator plunger.
On any small displacement of
mechanism, the tracing point E
at end of link CE traces out
approximately a straight line.
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5.19. Single Slider Crank Chain
It is a modification of the basic four bar chain.
one sliding pair and three turning pairs.
It converts rotary motion into reciprocating motion and vice versa.
Links 1 & 2, links 2 & 3, and links 3 & 4 form three turning pairs while links 4 and 1 form a sliding pair.
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5.20. Inversions of Single Slider Crank Chain 1. Pendulum pump or Bull engine
Fixing cylinder or link 4 (sliding pair)
When crank (link 2) rotates, connecting rod (link 3) oscillates about a pin pivoted to the fixed link 4 at A and the piston attached to piston rod (link 1) reciprocates.
The duplex pump which is used to supply feed water to boilers have two pistons attached to link 1, as shown in Fig. 5.23.
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5.20. Inversions of Single Slider Crank Chain 2. Oscillating cylinder engine
Used to convert reciprocating motion into rotary motion.
Link 3 forming the turning pair is fixed.
When crank (link 2) rotates, the piston attached to piston rod (link 1) reciprocates and cylinder (link 4) oscillates about a pin pivoted to the fixed link at A.
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5.20. Inversions of Single Slider Crank Chain 3. Rotary internal combustion engine or Gnome engine
It consists of seven cylinders in one plane and all revolves about fixed center D, while crank (link 2) is fixed.
when connecting rod (link 4) rotates, piston (link 3) reciprocates inside the cylinders forming link 1.
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5.20. Inversions of Single Slider Crank Chain 4. Crank and slotted lever quick return motion mechanism
used in shaping machines, slotting machines and in rotary internal combustion engines.
Link AC (link 3) is fixed. Link 3 corresponds to the connecting rod of
a reciprocating steam engine.
Driving crank CB revolves with uniform angular speed about fixed center C.
A sliding block attached to crank pin at B slides along the slotted bar AP and thus causes AP to oscillate about
the pivoted point A.
A short link PR transmits motion from AP to ram which carries tool and reciprocates along line of stroke R1 R2. The line of stroke of ram is perpendicular to AC.
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5.20. Inversions of Single Slider Crank Chain 4. Crank and slotted lever quick return motion mechanism
AP1 & AP2 are tangential to the circle and cutting tool is at the end of the stroke.
Forward or cutting stroke occurs when crank rotates from position CB1 to CB2 (angle b) in the cw direction.
Return stroke occurs when crank rotates from position CB2 to CB1 (angle a) in cw direction.
Since crank has uniform angular speed, therefore,
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5.20. Inversions of Single Slider Crank Chain 4. Crank and slotted lever quick return motion mechanism
Since tool travels a distance of R1 R2 during cutting
and return stroke, therefore travel of tool or length
of stroke
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5.20. Inversions of Single Slider Crank Chain 5. Whitworth quick return motion mechanism
Used in shaping and slotting machines.
Link CD (link 2) is fixed. Link 2 corresponds to a crank in a reciprocating steam engine.
Driving crank CA (link 3) rotates at a uniform angular speed.
Slider (link 4) attached to crank pin at A slides along the slotted bar PA (link 1) which oscillates at a pivoted point D.
Connecting rod PR carries ram at R to which a cutting tool is fixed.
Motion of tool is constrained along line RD
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5.20. Inversions of Single Slider Crank Chain 5. Whitworth quick return motion mechanism
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5.20. Inversions of Single Slider Crank Chain 5. Whitworth quick return motion mechanism
When driving crank CA moves from position CA1
to CA2 (or link DP from position DP2 to DP1)
through an angle a in cw direction, tool moves
from left hand end of its stroke to right hand end
through a distance 2 PD.
When driving crank moves from position CA2 to
CA1 (link DP from DP1 to DP2) through an angle b
in cw direction, tool moves back from right hand
end of its stroke to left hand end.
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5.20. Inversions of Single Slider Crank Chain 5. Whitworth quick return motion mechanism
Time taken during left to right movement of ram (cutting stroke)
will be equal to time taken by driving crank to move from CA1 to
CA2.
Time taken during right to left movement of ram (return stroke) will
be equal to time taken by driving crank to move from CA2 to CA1.
Since crank link CA rotates at uniform angular velocity therefore
time taken during cutting stroke is more than time taken during
return stroke.
Mean speed of ram during cutting stroke is less than mean speed
during return stroke.
Ratio between time taken during cutting & return strokes is given
by
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Example 5.1
A crank and slotted lever mechanism used in a shaper has a center distance of 300 mm between the center of oscillation of the slotted lever and the center of rotation of the crank. The radius of the crank is 120 mm. Find the ratio of the time of cutting to the time of return stroke.
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Example 5.2 In a crank and slotted lever quick return motion mechanism, distance between the fixed centers is 240 mm and the length of driving crank is 120 mm. Find the inclination of the slotted bar with the vertical in the extreme position and the time ratio of cutting stroke to the return stroke.
If the length of the slotted bar is 450 mm, find the length of the stroke if the line of stroke passes through the extreme positions of the free end of the lever.
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Example 5.2 September 28, 2013
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Example 5.3
Fig. 5.30 shows the layout of a quick return mechanism of oscillating link type, for a special purpose machine. The driving crank BC is 30 mm long and time ratio of the working stroke to the return stroke is to be 1.7. If the length of the working stroke of R is 120 mm, determine the dimensions of AC and AP.
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Example 5.3 September 28, 2013
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Example 5.4
In a Whitworth quick return motion mechanism, Fig.
5.32, distance between the fixed centers is 50 mm and
length of driving crank is 75 mm. The length of slotted
lever is 150 mm and length of connecting rod is 135
mm. Find the ratio of time of cutting stroke to time of
return stroke and also the effective stroke.
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Example 5.4
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5.21. Double Slider Crank Chain
It is a kinematic chain which consists of
two turning pairs and two sliding pairs.
Link 2 & link 1 form one turning pair and
link 2 & link 3 form the second turning
pair.
Link 3 & link 4 form one sliding pair and
link 1 & link 4 form the second sliding
pair.
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5.21. Double Slider Crank Chain
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5.22. Inversions of Double Slider Crank Chain
1. Elliptical trammels
When links 1 and 3 slide along their
respective grooves, any point on link 2
such as P traces out an ellipse on the
surface of link 4, Fig. 5.34 (a).
AP and BP are semi-major axis and semi-
minor axis of the ellipse respectively.
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5.22. Inversions of Double Slider Crank Chain
1. Elliptical trammels
Link BA is inclined at an angle q with the
horizontal, Fig. 5.34 (b).
Coordinates of point P on link BA will be
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5.22. Inversions of Double Slider Crank Chain
2. Scotch yoke mechanism
Used for converting rotary motion into a reciprocating motion.
Inversion is obtained by fixing either link 1 or link 3.
When Link2 (crank) rotates about B as center, link 4 (frame) reciprocates.
The fixed link 1 guides the frame.
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5.22. Inversions of Double Slider Crank Chain
3. Oldham’s coupling
Used for connecting two parallel shafts
whose axes are at a small distance apart.
The shafts are coupled in such a way that if
one shaft rotates, the other shaft also rotates
at the same speed.
This inversion is obtained by fixing link 2, Fig.
5.36 (a).
The shafts to be connected have two
flanges (link 1 and link 3) rigidly fastened at
their ends by forging.
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5.22. Inversions of Double Slider Crank Chain
3. Oldham’s coupling If distance between the axes of the shafts is constant, the center of
intermediate piece will describe a circle of radius equal to the distance between the axes of the two shafts.
Max sliding speed of each tongue along its slot = peripheral velocity of the center of the disc along its circular path.
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5.22. Inversions of Double Slider Crank Chain
3. Oldham’s coupling
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Homework
All questions at the end of chapter
Homework assignment should be
submitted
However, a quiz will be held after finishing
the chapter
1st quiz will be held on 22/9/2013 @ 14:00
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