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Research Papers: Elastohydrodynamic Lubrication

An Efficient Elastic Displacement Analysis Procedure for Simulating Transient Conformal-Contact Elastohydrodynamic Lubrication Systems

[+] Author and Article Information
Shangwu Xiong1

Department of Mechanical Engineering, Northwestern University, 2145 Sheridan Road, Evanston, IL 60208s-xiong2@northwestern.edu

Chih Lin

 Baker Hughes, Inc., Houston, TX 77252chih.lin@bakerhughes.com

Yansong Wang

 Baker Hughes, Inc., Houston, TX 77252yansong.wang@bakerhughes.com

Wing Kam Liu

Department of Mechanical Engineering, Northwestern University, 2145 Sheridan Road, Evanston, IL 60208w-liu@northwestern.edu

Q. Jane Wang

Department of Mechanical Engineering, Northwestern University, 2145 Sheridan Road, Evanston, IL 60208qwang@northwestern.edu

1

Corresponding author.

J. Tribol 132(2), 021502 (Apr 06, 2010) (9 pages) doi:10.1115/1.4001120 History: Received February 16, 2009; Revised January 26, 2010; Published April 06, 2010; Online April 06, 2010

A compliance operator is often utilized to evaluate the elastic displacement of surfaces in the simulation of transient and steady-state elastohydrodynamic lubrication of conformal-contact systems. The values of the compliance operator represent the elastic responses of all nodes when only one node is under a unit load. The accuracy of compliance operator values, computational cost, and storage size are important issues. Our study of steady-state conformal-contact elastohydrodynamic lubrication analyses suggests a method of selective-fine-mesh with selective-storage, as well as a special technique of the combined selective-fine-mesh with selective-storage mapping. These two techniques enable an efficient elasticity procedure for the simulation of steady-state and transient conformal-contact elastohydrodynamic lubrication systems by means of the finite element method.

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Copyright © 2010 by American Society of Mechanical Engineers
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Figures

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Figure 1

Illustration of three approaches: (a) selective-storage, (b) selective-fine-mesh with selective-storage, and (c) combined selective-fine-mesh with selective-storage mapping (|Eji/Eii|>êmin inside the diamond-like region, Eji for nodes in the rectangular-storage block (thick solid line) is stored, and the finer mesh is used inside the thick dashed block)

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Figure 2

Pressure from the analysis of smooth surfaces in a dry contact: (a) schematic mesh for the conventional approach, (b) schematic mesh for the combined selective-fine-mesh with selective-storage mapping method, (c) number of nodes to be stored, (d) pressure distribution, (e) section A-A, and (f) section B-B

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Figure 3

Pressure from the analysis of smooth surfaces in a dry contact under displacement boundary condition (X=Y=0 while Z free) at the nodes on the external surface of the bearing: (a) pressure distribution, (b) section A-A, and (c) section B-B

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Figure 4

Comparison of the results obtained with the conventional and the new approach: (a) schematic mesh distributions along the circumferential direction; (b) elastic displacement and pressure; (c) difference of the elastic displacement at the central section along the circumferential direction; and (d) elastic displacement, pressure, and film thickness at the x=πR section along the width direction (full: conventional, selective: new)

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Figure 5

The pressure, film thickness, and elastic displacement obtained from EHL of a smooth surface, journal-bearing viewed at (a) the central section along the circumferential direction and (b) the exit region indicated by the circle in (a)

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Figure 6

An example of time convergent curve of transient pressure, elastic displacement and film thickness for only one nodal point x=Rπ at center section along circumferential direction: (a) nx=20 and (b) nx=60

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Figure 7

Pressure distributions: (a) steady-state and (b) transient (uRt/lx=4π)

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Figure 8

Pressure, film thickness and elastic displacement at the central section along the circumferential direction: (a) steady-state and (b) transient (nx=20, uRt/lx=4π)

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Figure 9

Pressure, film thickness, and elastic displacement at the edge section along the circumferential direction: (a) steady-state and (b) transient (nx=60, uRt/lx=4π)

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Figure 10

Comparison of the numerical results for the steady-state with that for the transient state in the same locations: (a) maximum pressure and (b) maximum elastic displacement and minimum film thickness (nx=20)

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Figure 11

Friction coefficient obtained by different uniform meshes (nx=20): (a) both steady and transient cases and (b) enlargement of the transient case

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