Research Papers: Design of Direct Contact Systems

A Load Distribution Model for Planetary Gear Sets

[+] Author and Article Information
Y. Hu, A. Kahraman

Gear and Power Transmission
Research Laboratory,
The Ohio State University,
Columbus, OH 43210

D. Talbot

Gear and Power Transmission
Research Laboratory,
The Ohio State University,
Columbus, OH 43210
e-mail: talbot.11@osu.edu

1Corresponding author.

Contributed by the Power Transmission and Gearing Committee of ASME for publication in the JOURNAL OF MECHANICAL DESIGN. Manuscript received August 31, 2017; final manuscript received January 17, 2018; published online March 9, 2018. Assoc. Editor: Mohsen Kolivand.

J. Mech. Des 140(5), 053302 (Mar 09, 2018) (14 pages) Paper No: MD-17-1597; doi: 10.1115/1.4039337 History: Received August 31, 2017; Revised January 17, 2018

A load distribution model of planetary gear sets presented is capable of simulating planetary gear sets having component- and system-level design variations such as component supporting conditions, different kinds of gear modifications and planetary gear sets with different numbers of equally or unequally spaced planets as well as different gear set kinematic configurations while considering gear mesh phasing. It also accounts for classes of planetary gear set manufacturing and assembly related errors associated with the carrier or gears, i.e., pinhole position errors, run-out errors, and tooth thickness errors. Example analyses are provided to indicate the need for a model of this type when studying load distribution of planetary gear sets due to unique loading of the gear meshes associated with planetary gear sets. Comparisons to measurements existing in the literature are provided.

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Fig. 1

Schematic representations of (a) a sun-planet mesh and (b) a ring-planet mesh for phasing formulations

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Fig. 2

Schematic representation of sun gear coordinate system and six possible rigid body motions as well as the contact normal vector of a point j on gear tooth

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Fig. 5

Influence of gear face width and planet bearing tilting stiffness kθxθx=kθyθy=kθθ on maximum tilting motion of planet 2, θxp2, under Ts=200 Nm

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Fig. 3

A carrier-planet i pair

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Fig. 4

Schematic representations of (a) a carrier pinhole position error and (b) gear and carrier runout errors

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Fig. 8

Contact stress distribution for varying load and planet gear modification

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Fig. 9

Measured [12] and predicted load sharing of four-planet gear set with (a) Ts=600 Nm, (b) Ts=800 Nm, and (c) Ts=1000 Nm

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Fig. 10

Measured [12] and predicted load sharing of five-planet gear set with Ts=800 Nm

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Fig. 11

Measured [12] and predicted load sharing of six-planet gear set with Ts=800 Nm

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Fig. 12

((a1)–(c1)) Measured [15] and ((a2)–(c2)) predicted sun gear orbit of in-phased ((a1) and (a2)), sequentially phased ((b1) and (b2)) and CP ((c1) and (c2)) gear set

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Fig. 6

Load distribution of a SP planetary gear set with 40 mm face width and planet bearing tilting stiffness of 6(10)4 N·m/rad under Ts=200 Nm

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Fig. 7

Load sharing factor for varying load and planet gear modification




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