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RESEARCH PAPERS

Dynamic Analysis of Cage Behavior in a Tapered Roller Bearing

[+] Author and Article Information
Tomoya Sakaguchi

R&D Center, NTN Corporation, 066, Higashikata, Kuwana, Mie 511-8678, Japantomoya_sakaguchi@ntn.co.jp

Kazuyoshi Harada

R&D Center, NTN Corporation, 066, Higashikata, Kuwana, Mie 511-8678, Japankazuyoshi_harada@ntn.co.jp

J. Tribol 128(3), 604-611 (Mar 04, 2006) (8 pages) doi:10.1115/1.2197527 History: Received August 09, 2005; Revised March 04, 2006

A three-dimensional dynamic simulation analysis of a tapered roller bearing was performed using commercially available software. Without cage pocket shape simplification, the dynamic motion of the cage and rollers was calculated in six degrees of freedom. The motion of the cage and rollers was measured experimentally to verify the analysis. Under all axially loaded conditions, cage whirl was analytically predicted and experimentally confirmed. Whirl amplitude increased as the inner-ring rotational speed and axial-load magnitude increased. The maximum whirl amplitude reached the radial clearance between a roller and its pocket. Under combined load conditions, the cage also whirled. However, the whirl amplitude was smaller than only under axial load. Load distribution due to the addition of radial load to axial load equalized roller distribution. Equally distributed rollers limited the cage’s movable distance to circumferential clearance between a roller and its pocket.

Copyright © 2006 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

Experimental apparatus

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Figure 2

Schematic of the bearing and the sensors

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Figure 3

Clearance between a roller and cage

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Figure 4

Interactions considered in this analysis

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Figure 5

Friction coefficient model under boundary lubrication mode with respect to slide-roll ratio

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Figure 6

Effect of oil film parameter on friction coefficient

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Figure 7

Schematic of cage pocket

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Figure 8

Measured cage center loci under axial load conditions. (a) Various velocities (Fa=0.05Cr). (b) Various axial loads (3000rpm).

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Figure 9

Measured cage axial motion under axial load condition (Fa=0.05Cr)

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Figure 10

Rotational displacement of cage under axial load conditions. (a)Fa=0.02Cr, 1000rpm. (b)Fa=0.08Cr, 3000rpm.

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Figure 11

Measured cage center loci under combined load conditions (Fa=0.08Cr). (a) Various velocities (ε=1.49). (b) Various load distribution factors ε(2000rpm).

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Figure 12

Numerical simulated cage center loci under axial load conditions. (a) Various velocities (Fa=0.05Cr). (b) Various axial load (3000rpm).

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Figure 13

Interaction force between roller and cage under axial load condition (Fa=0.05Cr)

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Figure 14

Effect of axial load on spacing angles between adjacent 5 rollers under axial load conditions (3000rpm). (a)Fa=0.02Cr. (b)Fa=0.08Cr.

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Figure 15

Numerical simulated cage center loci under axial load conditions with roller diameter variation at only the 0.02 Cr load (3000rpm)

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Figure 16

Numerical simulated cage center loci under combined load (2000rpm, Fa=0.08Cr)

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Figure 17

Cage movable distances with unequal or equal distributions of rollers. (a) Unequal distribution (larger movement). (b) Equal distribution (smaller movement).

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Figure 18

Angles between adjacent 5 rollers under combined load (2000rpm, Fa=0.08Cr, ε=1.49)

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