Research Papers

Prediction of Mechanical Power Loss of Planet Gear Roller Bearings Under Combined Radial and Moment Loading

[+] Author and Article Information
D. Talbot

e-mail: talbot.11@osu.edu

S. Li

e-mail: li.600@osu.edu

A. Kahraman

e-mail: kahraman.1@osu,edu
Department of Mechanical
and Aerospace Engineering,
The Ohio State University,
201 W. 19th Avenue,
Columbus, OH 43210

1Corresponding author.

Contributed by the Power Transmission and Gearing Committee of ASME for publication in the JOURNAL OF MECHANICAL DESIGN. Manuscript received June 3, 2013; final manuscript received August 21, 2013; published online September 20, 2013. Assoc. Editor: Qi Fan.

J. Mech. Des 135(12), 121007 (Sep 20, 2013) (11 pages) Paper No: MD-13-1240; doi: 10.1115/1.4025350 History: Received June 03, 2013; Revised August 21, 2013

A modeling methodology is proposed to predict load-dependent (mechanical) power loss of cylindrical roller bearings under combined radial and moment loading with focus on planetary gear set planet bearings. This methodology relies on two models. The first model is a bearing load distribution model to predict load intensities along rolling element contacts due to combined force–moment loading. This model takes into account planet bearing macrogeometry as well as micromodifications to the roller and race surfaces. The second model is an elastohydrodynamic lubrication (EHL) model employed to predict rolling power losses of bearing contacts with load intensities predicted by the load distribution model. The bearing mechanical power loss methodology is applied to bearings of an automotive planetary gear set to quantify the sensitivity of mechanical power loss to key bearing, lubrication and surface parameters as well as operating speed, load and temperature conditions.

Copyright © 2013 by ASME
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Fig. 1

Mechanical components of a planetary needle bearing setup

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Fig. 2

Definition of the needle bearing parameters used in the load distribution model

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Fig. 3

Surface roughness profiles of (a) planet pin and (b) roller used in EHL simulation

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Fig. 4

Roller load intensity distributions at (a) TPB = 42 Nm, (b) TPB = 100 Nm, and (c) TPB = 333 Nm

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Fig. 5

Effect of oil inlet temperature on Pmb at (a) Ωb = 5300 rpm and (b) Ωb = 7100 rpm. Sco = 0.141μm.

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Fig. 6

Effect of composite surface roughness, Sco, on Pmb at (a) Ωb = 1800 rpm, (b) Ωb = 3500 rpm, (c) Ωb = 5300 rpm, and (d) Ωb = 7100 rpm. Oil inlet temperature is 90 °C.

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Fig. 7

Effect of roller diameter, dr, on Pmb at (a) Ωb = 1800 rpm, (b) Ωb = 3500 rpm, (c) Ωb = 5300 rpm, and (d) Ωb = 7100 rpm. Oil inlet temperature is 90 °C and Sco = 0.141μm.

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Fig. 8

Roller load intensity distributions at TPB = 333 Nm for (a) dr = 2.015 mm, (b) dr = 3.015 mm, and (c) dr = 5.015 mm

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Fig. 10

Roller load intensity distributions at TPB = 333 Nm for (a) Cd = 1μm, (b) Cd = 9μm, and (c) Cd = 14μm

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Fig. 9

Effect of diametral clearance, Cd, on Pmb at (a) Ωb = 1800 rpm, (b) Ωb = 3500 rpm, (c) Ωb = 5300 rpm, and (d) Ωb = 7100 rpm. Oil inlet temperature is 90 °C and Sco = 0.141μm.

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Fig. 11

Effect of single roller length, ℓ, on Pmb at (a) Ωb = 1800 rpm, (b) Ωb = 3500 rpm, (c) Ωb = 5300 rpm, and (d) Ωb = 7100 rpm. Oil inlet temperature is 90 °C and Sco = 0.141μm.

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Fig. 12

Effect of planet gear helix angle, β, on Pmb at (a) Ωb = 1800 rpm, (b) Ωb = 3500 rpm, (c) Ωb = 5300 rpm, and (d) Ωb = 7100 rpm. Oil inlet temperature is 90 °C and Sco = 0.141μm.

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Fig. 13

Roller load intensity distribution at TPB = 333 Nm for (a) β = 0 deg, (b) β = 20 deg, and (c) β = 30 deg



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