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Research Papers: Elastohydrodynamic Lubrication

Performance of Spur Gears Considering Surface Roughness and Shear Thinning Lubricant

[+] Author and Article Information
S. Akbarzadeh

Department of Mechanical Engineering, Louisiana State University, 2508 CEBA, Baton Rouge, LA 70803

M. M. Khonsari1

Department of Mechanical Engineering, Louisiana State University, 2508 CEBA, Baton Rouge, LA 70803Khonsari@me.lsu.edu

1

Corresponding author.

J. Tribol 130(2), 021503 (Apr 07, 2008) (8 pages) doi:10.1115/1.2805431 History: Received June 10, 2007; Revised September 12, 2007; Published April 07, 2008

A model is developed for predicting the performance of spur gears with provision for surface roughness. For each point along the line of action, the contact of pinion and gear is replaced by that of two cylinders. The radii of cylinders, transmitted load, and contact stress are calculated, and lubricant film thickness is obtained using the load-sharing concept of Johnson (1972, “A Simple Theory of Asperity Contact in Elastohydrodynamic Lubrication  ,” Wear, 19, pp. 91–108) To validate the analysis, the predicted film thickness and the friction coefficient are compared to published theoretical and experimental data. The model is capable of predicting the performance of gears with non-Newtonian lubricants—such as that of shear thinning lubricants—often used in gears. For this purpose, a correction factor for shear thinning film thickness introduced by Bair (2005, “Shear Thinning Correction for Rolling/Sliding Electrohydrodynamic Film Thickness  ,” Proc. Inst. Mech. Eng., Part J: J. Eng. Tribol., 219, pp. 1–6) has been employed. The results of a series of simulations presenting the effect of surface roughness on the friction coefficient are presented and discussed. The results help to establish the lubrication regime along the line of action of spur gears.

Copyright © 2008 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

Representation of pinion and gear with rollers

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Figure 2

Variation of load along LoA

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Figure 3

Variation of equivalent radius of curvature along LoA

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Figure 4

Variation of load along LoA

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Figure 5

Variation of contact stress along LoA

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Figure 6

Comparison of film thickness with results from Ref. 4

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Figure 7

Comparison of model results with experimental data (3)

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Figure 8

Characteristics of shear thinning lubricant

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Figure 9

Variation of film thickness along LoA

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Figure 12

Variation of friction coefficient along the LoA and comparison with Newtonian lubricant for σ=0.1×10−6m

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Figure 13

Variation of friction coefficient along the LoA and comparison with Newtonian lubricant for σs=0.4×10−6m

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Figure 14

Variation of friction coefficient along the LoA and comparison with Newtonian lubricant for σs=0.7×10−6m

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Figure 15

Scaling factors along LoA for σs=0.7×10−6m

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Figure 11

Variation of film parameter (Λ) along LoA

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Figure 10

Variation of ϕ along LoA

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