Select this link to see the chart that was used to
create this graph.
The main difference in this design is that the entire tooth is based
upon the involute curve rather than just the addendum. The shape
of the involute curve is determined by the size (radius) of the
generating circle (that the straight line rolls around). Since the
entire tooth is based upon the involute curve, the tooth flank (the
lower part, below the pitch circle) does not point to the circle
center (as happens in the radial flanks): the tooth is wider at the
base and is therefore much stronger by design.
The portion of the Involute Curve that would be used to design a clock gear tooth is steeper (it has a larger gradient) than the Epicycloidal Curve. A portion of the two curves is compared in the graph below. The axes both indicate displacement in inches. Since the radius of the generating circle is one, the X axis also indicates the angle in radians for the Epicycloidal Curve. The portion of the curves used to design a clock gear tooth would be equivalent to a rotation of 60º (if a 6 tooth pinion were used) or p/3 (=1.05) radians. To compare the curves, I used a mirror image of the Involute Curve by subtracting the X values from p before creating the graph (with Displacement in Inches on the both axes).
Note that one way to strengthen the tooth design with the epicycloidal
design would be to design the flank based upon a hypocycloidal
curve, which is defined as a curve that is generated by rolling a circle
around the circumference inside another circle (compare with the
epicycloidal curve, rolling a circle around the circumference
outside another circle). The result is that the tooth space (between
two gear teeth) has a somewhat more similar shape below the pitch
circle (in the dedendum portion) to the shape of the addendum of
the tooth of the other gear that goes into it.
Go to Module and Gear Cutters
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Escapements in Motion