This package was created to aid with the designing process of mechanisms involving linkages, cams, and gears. In regard to linkages, it is capable of implementing a kinematic analysis with the knowledge of the degrees of freedom for the vectors that make up the mechanism. With the aid of numerical solving and iteration, the position, velocity, and acceleration of these vectors and points may be acquired.
In regard to cams, this package is capable of supplying coordinates of a cam profile, plotting SVAJ diagrams, and getting a cam and follower animation for roller and flat faced followers. In turn, the coordinates may be supplied to a machinist or imported into SolidWorks. All that is needed to know is the motion description (i.e. rise 2 inches in 1 second, dwell for 1.5 seconds, fall 2 inches in 3 seconds). As of right now, the kinds of motion supported are naive/uniform motion (how the cam shouldn't be designed), harmonic motion, and cycloidal motion. It is possible that this gets updated in the future with better options such as modified sinusoidal motion.
For gears, this package is capable of providing the coordinates of a spur gear tooth profile given a set of properties.
The analysis is based on the diametral pitch, number of teeth, and pitch diameter if desired over the number of teeth.
An argument for AGMA standards may be set to True if desired.
Install this package via pip: pip install mechanism.
To effectively use these tools, it is necessary to have some understanding on free body diagrams and vector loops that define a mechanism. These tutorial videos are provided to help accommodate this issue.
For the most simple four bar linkage (the one introduced in this readme), watch this video:
Additionally, here is a breakdown of this real world example:
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fourbarlinkage.py
fivebarlinkage.py
crunode_coupler.py
crankslider.py
engine.py
non_grashof.py
offset_crankslider.py
cam2_example.py
In order to use the contents of mechanism.py, a basic knowledge of vector loops must be known. The structure of the
vector loops function is shown in several files under the examples folder. To gain a greater understanding of this
package's usage, this walk through is provided.
A four bar linkage is the basic building block of all mechanisms. This is similar to how the triangle is the basic building block of all structures. What defines a mechanism or structure is the system's overall number of degrees of freedom, and the number of degrees of freedom is determined via Kutzbach’s equation.
Kutzbach's equation is: total degrees of freedom = 3(#links - 1) - 2(J1) - J2 where J1 is the number of full joints (also known as a revolute joint) and J2 is the number of half joints. For this four bar linkage, there are 4 full joints.
The number of degrees of freedom is: 3(4 - 1) - 2(4) = 1
This means that we need one known input to find the unknowns of the system. This can be explained further with a diagram of the vectors that make up the four bar linkage.
From the above image, the vector "a" is the crank. The speed at which it rotates will be considered as the input to the system, and thus, it is the defining parameter to the system.
The lengths of all the vectors are known. The only two unknowns are the angle that corresponds to vector "b" and "d". It is important to note that the objects that make up this package are vectors, and the polar form of the vectors is the main interest.
There is only one loop equation which provides two equations when breaking down the vectors into its components. With two equations and two unknowns, this system becomes solvable.
Consider the four bar linkage shown above. The lengths of a, b, c, and d are 5", 8", 8" and 9". The crank (a) rotates at
a constant 500 RPM. Use mechanism to get an animation of this linkage system and plot the angles, angular velocity,
and angular acceleration of vector d as a function of time.
The four bar linkage is a grashof linkage because it satisfies the grashof condition (9 + 5 < 8 + 8). This means that the crank is able to fully rotate. The input can be deduced by integrating and differentiating the constant value of the constant angular velocity of the crank.
Always begin with defining the joints and vectors.
from mechanism import *
import numpy as np
import matplotlib.pyplot as plt
# Declare the joints that make up the system.
O, A, B, C = get_joints('O A B C')
# Declare the vectors and keep in mind that angles are in radians and start from the positive x-axis.
a = Vector((O, A), r=5)
b = Vector((A, B), r=8)
c = Vector((O, C), r=8, theta=0, style='ground')
d = Vector((C, B), r=9)Always define the vectors in the polar form. The first argument is the joints, and the first joint is the tail of the vector, and the second is the head. Additionally, extra keyword arguments will be passed to plt.plot() for styling.
By not defining the angles for a vector (like a, b, and c) you are saying that this vector will have a varying
angle and the same is true for the length argument (r). If both the length and the angle are defined, as with c,
then the vector is stationary and will remain at this length and angle. If neither r or theta is specified, then you
are saying that the vector changes in length and angle, so you should expect two degrees of freedom for the input of
this vector in the vector loop equations. There should be half as many loop equations as there are unknown. The input
vector "a" does not need to have its known values at its declaration. Instead, it's values will be accounted for in the
loop equation. The next thing to do is to define the known input and guesses for the first iteration of the unknown
values.
# Define the known input to the system.
# For a 500 RMP crank, the time it takes to rotate one rev is 0.12s
time = np.linspace(0, 0.12, 300)
angular_velocity = 50*np.pi/3 # This is 500 RPM in rad/s
theta = angular_velocity*time # Integrate to find the theta
omega = np.full((time.size,), angular_velocity) # Just an array of the same angular velocity
alpha = np.zeros(time.size)
# Guess the unknowns
pos_guess = np.deg2rad([45, 90])
vel_guess = np.array([1000, 1000])
acc_guess = np.array([1000, 1000])The guess values need to be arrays of the same length as the number of unknowns. These arrays will be passed as the first iteration. The next thing to do is to define the loop function and create the mechanism object.
# Define the loop equation(s)
def loop(x, i):
return a(i) + b(x[0]) - c() - d(x[1])
# Create the mechanism object
mechanism = Mechanism(vectors=(a, b, c, d), origin=O, loops=loop, pos=theta, vel=omega, acc=alpha,
guess=(pos_guess, vel_guess, acc_guess))This example is simpler than most others because there is only one loop equation. For multiple loop equations, it is
important that the function returns a flattened array of the same length as there are unknown, and the indexing of the
first array argument to the loop corresponds to the input guess values. The second argument is the input. It is strongly
encouraged to view the examples for the more rigorous structure of the loop function. The last thing to do is to
call mechanism.iterate(), which is necessary if the input from pos, vel, and acc are arrays. If they are not
arrays, then it is assumed that the mechanism at an instant is desired. If this is the case, then
call mechanism.calculate() then call mechanism.plot() (see plot_at_instant.py).
# Call mechanism.iterate() then get and show the animation
mechanism.iterate()
ani, fig_, ax_ = mechanism.get_animation()
# Plot the angles, angular velocity, and angular acceleration of vector d
fig, ax = plt.subplots(nrows=3, ncols=1)
ax[0].plot(time, d.pos.thetas, color='maroon')
ax[1].plot(time, d.vel.omegas, color='maroon')
ax[2].plot(time, d.acc.alphas, color='maroon')
ax[0].set_ylabel(r'$\theta$')
ax[1].set_ylabel(r'$\omega$')
ax[2].set_ylabel(r'$\alpha$')
ax[2].set_xlabel(r'Time (s)')
ax[0].set_title(r'Analysis of $\vec{d}$')
for a in (ax[0], ax[1], ax[2]):
a.minorticks_on()
a.grid(which='both')
fig.set_size_inches(7, 7)
# fig.savefig('../images/analysis_d.png')
plt.show()This will produce the following output:
There are several kinds of motion types for a cam, but there is an important corollary when designing cams: The jerk function must be finite across the entire interval (360 degrees) (Robert Norton's Design of Machinery). Usually, the cycloidal motion type achieves this corollary, but it comes at a cost. It produces an acceleration and velocity that is typically higher than the other motion types. More motion types are to come later (hopefully).
Design a cam using cycloidal motion that has the following motion description:
- Dwell at zero displacement for 90 degrees
- Rise 1 inch in 90 degrees
- Dwell for 90 degrees
- Fall 1 inch in 90 degrees
The cam's angular velocity is 2*pi radians per second. Show the SVAJ diagram as well as the cam's profile. Size the cam for a roller follower with a radius of 1/2" with a maximum pressure angle of 30 degrees. Also size the cam for a flat faced follower. Get an animation for both a roller/flat faced follower. Finally, save the coordinates of the profile to a text file and show the steps for creating a part in SolidWorks.
Begin by creating a cam object with the correct motion description.
import numpy as np
from mechanism import Cam
import matplotlib.pyplot as plt
cam = Cam(motion=[
('Dwell', 90),
('Rise', 1, 90),
('Dwell', 90),
('Fall', 1, 90)
], degrees=True, omega=2*np.pi)The motion description is a list of tuples. Each tuple must contain 3 items for rising and falling and two items for dwelling. The first item of the tuple is a string equal to "Rise", "Fall", or "Dwell" (not case-sensitive). For rise and fall motion, the second item in the tuple is the distance at which the follower falls or rises. For dwelling, the second item in the tuple is either the time (in seconds) or angle (in degrees) for which the displacement remains constant. The third item in the tuple for rising and falling is equivalent to the second item for dwelling. If degrees is set to true, then the last item in each tuple is interpreted as the angle for which the action occurs. A manual input for the angular velocity is then required if conducting further analysis via SVAJ.
This is all that's required to call the following methods.
fig1, ax1 = cam.plot(kind='all')
fig2, ax2 = cam.svaj(kind='cycloidal')
plt.show()This produces the following:
Looking at the acceleration plot, there are no vertical lines. This means that there is no infinite derivative at any instant along the cam's profile; the jerk function is finite across each instant, making this an acceptable motion type.
If a roller follower with a 1/2" radius is desired, an analysis depending on the cam's radius of curvature and pressure angle can be conducted to determine the base circle of the cam.
roller_analysis = cam.get_base_circle(kind='cycloidal', follower='roller', roller_radius=1/2, max_pressure_angle=30,
plot=True)
fig3, ax3 = cam.profile(kind='cycloidal', base=roller_analysis['Rb'], show_base=True, roller_radius=1/2,
show_pitch=True)
plt.show()Output:
For a flat faced follower, the radius of curvature at the point of contact should be positive (or greater than 0.25") for all theta. There is an option to return the base radius such that the radius of curvature of the cam's profile is positive for all values of theta (this is the conservative approach).
flat_analysis = cam.get_base_circle(kind='cycloidal', follower='flat', desired_min_rho=0.25)
print(flat_analysis['Rb'])
print(flat_analysis['Min Face Width'])
fig4, ax4 = cam.profile(kind='cycloidal', base=flat_analysis['Rb'], show_base=True)
plt.show()Output:
The base circle radius was found to be 1.893" and the minimum face width for the follower was found to be 2.55".
To get the roller animation, call this:
ani, fig5, ax5, follower = cam.get_animation(kind='cycloidal', base=roller_analysis['Rb'], roller_radius=1/2, length=2,
width=3/8, inc=5)
fig6, ax6 = follower.plot()
plt.show()Output:
The graph above shows the actual follower displacement due to the circle having to always be tangent to the surface of the cam. Note that as a result of this physical limitation, the follower will have higher magnitudes of velocity and acceleration.
For the flat faced follower,
ani_flat, fig7, ax7, follower = cam.get_animation(kind='cycloidal', base=flat_analysis['Rb'], face_width=2.75, length=2,
width=3/8, inc=5)
fig8, ax8 = follower.plot()
plt.show()Output:
Save the coordinates to a text file.
cam.save_coordinates('cam_coordinates.txt', kind='cycloidal', base=1.3, solidworks=True)Select Curve Through XYZ Points
The cam profile will always be extended to the front plane due to the manner in which SolidWorks defines the global coordinates. Next, select browse and choose the saved coordinate file, making sure that text files are able to be seen.
Create a sketch on the front plane. Select the curve and then convert entities. The sketch is now projected to the front plane.
Notice that the sketch is not closed. Add a line to close the sketch, then extrude the sketch.
To use this feature, a knowledge of gear nomenclature must be known. Here is a figure from Robert Norton's Design of Machinery:
For gears, a general rule of thumb is that the base circle must fall below the dedendum circle because the curve below base circle cannot be an involute curve. This package will send a warning if this occurs, and if it is desired to continue, the curve below the circle is just a straight line, and undercutting will occur.
For a reference, here are the AGMA (American Gear Manufacturers Association) standards from Design of Machinery:
Design a gear that has a diametral pitch of 32 and has 60 teeth using mechanism. The gear follows the AGMA standards.
Compare the gear to SolidWorks' gear from the tool library.
Define a gear object with the known information and save the coordinates to a file.
from mechanism import SpurGear
import matplotlib.pyplot as plt
gear = SpurGear(N=60, pd=32, agma=True, size=500)
fig, ax = gear.plot()
fig.savefig('../images/gear60.PNG', dpi=240)
plt.show()
gear.save_coordinates(file='gear_tooth_coordinates.txt', solidworks=True)
gear.rundown()output:
| Property | Value |
|---|---|
| Number of Teeth (N) | 60 |
| Diametral Pitch (pd) | 32.00000 |
| Pitch Diameter (d) | 1.87500 |
| Pitch Radius (r) | 0.93750 |
| Pressure Angle (phi) | 20.00000 |
| Base Radius | 0.88096 |
| Addendum (a) | 0.03125 |
| Dedendum (b) | 0.03906 |
| Circular Tooth Thickness | 0.04846 |
| Circular Space Width | 0.04971 |
| Circular Backlash | 0.00125 |
Keep in mind that the size argument refers to the size of the coordinates that make up the involute curve. The more
points, the sharper it is, but SolidWorks sometimes struggles with points being too close together. To fix this issue,
make the size smaller. The default value is 1000.
Follow the same steps to get the curve into SolidWorks from the cam example. Make sure that the units in SolidWorks matches the units of the analysis.
The results are a near identical match, and the addendum and dedendum fit perfectly. If analyzed closely, the only difference is the tooth thickness. The gray gear (the resulting gear from this package) has a slightly larger tooth thickness compared to SolidWorks' gear. This is due to the fact that SolidWorks doesn't use an involute gear tooth profile, as gears from the SolidWorks toolbox are for visuals only. Instead, the tooth profile is circular. Their gears should not be used for manufacturing as this is not accurate at all. The purpose of the involute tooth profile is that the meshing of gears will always produce a constant angular velocity, even when the gears aren't perfectly placed tangent to the pitch circles.