Kinematics Final Print
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8/13/2019 Kinematics Final Print
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ENGINEERING DYNAMICS KINEMATICSMEC 2300
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[ENGINEERING DYNAMICSKINEMATICS MEC 2300] 1
Kinematics Assignment
Introduction
Mechanisms are of utmost importance in mechanical engineering. A mechanism is used
to produce a mechanical transformation in a machine. The transformation may be but
not only:
In this particular case we are dealing with the last of the aforementioned
transformations that is the conversion of angular motion into rectilinear motion. Thereare several means by which one can achieve this, one of which may be the linkage
method. This method uses pins and linkage bars attached to one another with pins
sliding inside the differently shaped links. One such example is the Whitworth quick-
return mechanism.
Converting one speed to anotherspeed.
Converting one torque to anothertorque.
Converting rectilinear motion intoangular motion.
Converting angular motion intorectilinear motion.
A problem however arises with this approach in
many applications as these linkage mechanisms
b hi hl l h d diff t
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[ENGINEERING DYNAMICSKINEMATICS MEC 2300] 2
Design
The aim of the assignment was to modify and re-design the model given to us so that
it is able to work continuously as a cam and follower mechanism. Initially one can
notice that the set-up, be it the slotted arm path or the offset distance of the rotating
axis to the vertical bar doesnt produce continuous linear motion.
Originally different concepts were put forward. One of the issues in the
design was the path prescribed by the pin. The choice of the latter is determined by
the type of cycle one requires. For example in relation to the automotive industry the
follower motion has to be expressed in relation to the angular displacement of thecam. This is because; as it is in most other applications the motion must be
synchronized.
To determine the right cam design for a specific use in a machine one must
have afollower displacement diagram. This will have the vertical displacement in this
case of the follower bar plotted against time (Graph 1) or angular cam displacement
(Graph 3) according to the constraints requested by the designer. This means that
this graph would show the relative positions of the vertical bar and the cam. It is
important to note that this whole mechanism would be part of a bigger system;
going back to the original reference, the automobile, the vertical displacement must
open and close a valve and the timing of this has to be close to perfection. Hence
these graphs alongside a good kinematic analysis will help choose the right design
for the path.
It is important to note that there are
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[ENGINEERING DYNAMICSKINEMATICS MEC 2300] 3
= 1 + 2 + 3 + 4 + 5
These are the parameters involved:
Type of displacement Time (Sec) m
Starting Position 0 0
Rise 0.7 0.985Fall 0.3 1.623
Rise 1.3 1.606
Fall 0.55 1.101
Rise 0.3 0.133
H = Total follower displacement during the rise or fall. T = Total time period for the rise or fall. = Time into rise or fall interval that defines the instantaneous follower properties. = Rotation angle of cam during the rise or fall = Speed of the cam.
R = Magnitude of the instantaneous follower displacement at time t or cam angle . = Magnitude of the instantaneous follower velocity = dR/dt.
Before analyzing the system one
must establish the requirements of
this cam and follower mechanism.
The table on the right shows thetype of displacement required by
the follower at a given time in one
cycle. Using the equations below
the table one can find the cycle time
and consequently the angular
velocity of the cam is found. We are
assuming constant angular velocity
i hi
Table 1
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[ENGINEERING DYNAMICSKINEMATICS MEC 2300] 4
Using simulation software the following of information was acquired. It is important to note that this
information takes into consideration the previously mentioned dynamic considerations such as
gravity forces and the smoothness of the curved path in relation to friction. Hence as illustrated ingraph 3, which plots the follower displacement versus angular displacement from table 2 and table 3,
in reality it is not a linear relationship but much different. This is also due to the fact that one can
never achieve absolute constant velocity or acceleration. For example when starting the mechanism a
starting torque is applied and this is varied accordingly until a steady angular speed is reached.
Once we obtain a follower
displacement diagram, we have a
relationship between the followerdisplacement and angular
displacement at various sections
in the cycle.
Using differentiation techniques
since the angular velocity is
assumed to be constantthroughout the follower motion
hence using a kinematic analysis
we can compute a Velocity vs
Angular Displacement (Graph 2)
and Velocity vs Time ( Graph 4).
From the last graph we can tell
what type of motion the system
d di d i l
R Velocity ofFollower
Rotation of cam
Seconds m m/s Degrees
0 0 0 0
0.15 0.146 1.138 17.18873
0.3 0.344 1.513 34.37747
0.45 0.602 1.921 51.5662
0.6 0.897 1.782 68.75494
0.75 0.866 -4.133 85.94367
0.9 -0.331 -7.683 103.1324
1.05 -0.633 0.323 120.3211
1.2 -0.551 0.672 137.5099
1.35 -0.44 0.792 154.6986
1.5 -0.312 0.92 171.8873
1.65 -0.162 1.098 189.0761
1.8 0.021 1.359 206.2648
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[ENGINEERING DYNAMICSKINEMATICS MEC 2300] 5
Graph 3
-0.8
-0.6
-0.4
-0.2
0
0.2
0.4
0.6
0.8
1
1.2
0 50 100 150 200 250 300 350 400
RectilinearDisplacementoffollower
Angular Displacement of cam in degrees
Rectilinear Motion of follower vs Angular Displacement of cam
Including Dynamic considerations"
Not including Dynamic considerations
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[ENGINEERING DYNAMICSKINEMATICS MEC 2300] 6
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-8
-6
-4
-2
0
2
4
0 0.5 1 1.5 2 2.5 3 3.5
Follower velocity vs Time
Graph 4
The velocity on start-up is almost at constant acceleration. Before the peak it changes into cycloidal motion. The fall is a very abrupt one at very
sharp deceleration and followed by an almost immediate acceleration. Once again the acceleration reaches its peak with a cycloidal type of
motion. The second fall is similar to the first one. However the final rise has a decreasing acceleration.