BULETINUL INSTITUTULUI POLITEHNIC DIN IAŞI - Universitatea ...

138 Ion Bostan et al
3. Calculation by CAE Simulation of Kinetostatics
Parameters of Processional Transmission
3.1. 3D Model elaboration of Planetary Processional Transmission
Calculation of planetary processional transmission by a simulation is carried
out using the simplified 3D model created in program Motion Inventor 2004+
but (4) from which it is possible to determine and check up dynamic loadings in
bearings which have been designed earlier.
Dynamic processes in planetary processional transmission derive, to a great
extent, from the interaction of conical rollers of the satellite crowns with
generating surfaces of central wheel teeth. The bearing capacity defined by gear
forces (static and dynamic), the noise emission and the transmission
vibroactivity, depend on the gear dynamic processes on the whole. With
account of these important factors in the elaboration of 3D model of the initial
processional gearing, the linear contour of central wheel teeth profile (fig. 3, a)
were designed applying parametric equations:
(2)
Where:
X = k Z + d ;
Y k Z d ;
(k d
=
k d )
−
m m m m
1E 2 1E 2
m
1E =
m
1
m
1E −
m
1
m
Z1E
m m m m
1 1 − 2 2
m2 m2
k1 + k2 + 1
(k d − k d ) + (k + k + 1) ⋅(R −d−d )
Z ,
m m m m 2 m2 m2 2 m2 m2
m
1E =
1 1 2 2 1 2
m2 m2
k1 + k2 + 1
D 1 2
⎛ ⎞
• • •
m m m m m m 2 m
X1D⎜X1D X1D+ Y1DY1D⎟ + Z1D X1D
+
m m
1 =
⎝ ⎠
2 = −
• •
m
m⎛ m m m m ⎞
X1D
Z1DX1DY1D−Y1D X1D
k ; k
⎜ ⎟
⎝ ⎠
2 m m
( Rcos D β + dY 1 1D)
•
2 m
m Rcos D β X1D
1 = • •
⎛ m m m m⎞ X1DY1D− X1DY1D m
2 =
m
X1D
d ; d .
⎜ ⎟
⎝ ⎠
m m m ( kY 1 1D Z1D)
The 3D model of the central wheel (fig. 3, b) was designed by using CAD
Autodesk Inventor (5) (B o s t a n et al, 2007).
;