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Contact Mechanics

A New Quasi-Static Cylindrical Roller Bearing Model to Accurately Consider Non-Hertzian Contact Pressure in Time Domain Simulations

[+] Author and Article Information
Simon Kabus

Technology R&D, Motion Systems,  Vestas Wind Systems, Aarhus, 8200 DenmarkSIKAB@Vestas.com

Michael R. Hansen

Department of Engineering,  University of Agder, Agder, 4604 NorwayMichael.R.Hansen@uia.no

Ole Ø. Mouritsen

Mechanical and Manufacturing Engineering,  Aalborg University, Aalborg, 9220 Denmarkoom@m-tech.aau.dk

J. Tribol 134(4), 041401 (Aug 21, 2012) (10 pages) doi:10.1115/1.4007219 History: Received November 03, 2011; Revised June 26, 2012; Published August 21, 2012; Online August 21, 2012

The accuracy of the fatigue life calculations in rolling bearing simulations is highly dependent on the precision of the roller-raceway contact simulations. Several different methods exist to simulate these pressure distributions and in time domain bearing simulations, where many contacts need evaluation, the simple and time efficient methods are more popular, yielding erroneous life estimates. This paper presents a new six degree of freedom frictionless quasi-static time domain cylindrical roller bearing model that uses high precision elastic half-space theory to simulate the contact pressures. The potentially higher computational demand using the advanced contact calculations is addressed by preprocessing a series of contacts at different centerline approaches and roller tilt angles, which are used for interpolating contact results during time domain simulations. It is demonstrated that this new model allows for simulation of bearing misalignments, roller centrifugal forces, and flange contact induced roller tilt moments, and that the effect of these conditions is directly evaluated in a detailed fatigue life analysis. Finally, the stiffness of the bearing model is validated against existing experimental data with good correlation.

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Copyright © 2012 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

Bearing cut view

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Figure 2

Mapping 3D pressure distribution into 2D slice pressures, αi=2 mrad and δi=0.08mm

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Figure 3

Preprocessed forces and moments of inner raceway contact

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Figure 4

Inner raceway slice pressures of three different slices

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Figure 5

Bearing simulation flow chart

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Figure 6

Bearing reference life of aligned/misaligned study

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Figure 7

Unwrapped raceway contact pressure for aligned and misaligned contact

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Figure 8

Bearing reference life of axial loading study

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Figure 9

Unwrapped raceway contact pressure for combined axial and radial loading

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Figure 10

Verification test bearing geometry from Ref. [7]

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Figure 11

Result comparison

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