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Research Papers: Friction & Wear

Thermomechanical Coupling in Oscillatory Systems With Application to Journal Bearing Seizure

[+] Author and Article Information
Jun Wen

Department of Mechanical Engineering, Louisiana State University, 2508 Patrick Taylor Hall, Baton Rouge, LA 70808

M. M. Khonsari1

Department of Mechanical Engineering, Louisiana State University, 2508 Patrick Taylor Hall, Baton Rouge, LA 70808khonsari@me.lsu.edu

1

Corresponding author.

J. Tribol 131(2), 021601 (Mar 06, 2009) (14 pages) doi:10.1115/1.3071976 History: Received September 01, 2008; Revised December 14, 2008; Published March 06, 2009

A method for treating the thermomechanical interaction of bodies that undergo relative oscillatory motion is developed. The approach utilizes a combination of the transfer matrix and the finite element methods. The thermomechanical coupling process between the contacting bodies involves a transient solution scheme where the frictional heat is automatically partitioned between the contacting surfaces. The coupling between thermal and mechanical interactions is treated iteratively. An application of the proposed model in the study of thermomechanical behavior of journal bearings with oscillatory motion undergoing thermally induced seizure is presented. The results of a wide range of operating parameters are presented. The significance of applied load, contact clearance, friction coefficient, oscillation parameters, convective heat transfer, and variable load direction condition in the thermally induced seizure is discussed in light of the numerical results.

Copyright © 2009 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

A configuration of the journal bearing: (a) Oscillating shaft and stationary bushing. (b) Oscillating bushing and stationary shaft.

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Figure 2

A finite element model of the journal bearing

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Figure 3

Flow chart of the basic steps of the simulation algorithm

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Figure 4

Comparison of contact pressure between finite element result and analytical solution for journal bearing under applied load of 4400 N

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Figure 5

A rotating shaft subjected to surface heating and convective cooling

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Figure 6

Comparison of surface temperature distribution at steady state by the present method and analytical solution

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Figure 7

Temperature rise for Case 2S at (a) Cycle 300, (b) Cycle 379, and (c) Cycle 391 when seizure occurs. W=4400 N, C=0.025 mm, μ=0.15, A=30 deg, f=10 Hz, and he=80 W/m2 K with the solid oscillating shaft.

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Figure 8

Variation in (a) clearance along the contact surface, (b) profile of the inner surface of the bushing, and (c) profile of the outer surface of the shaft at Cycles 300, 379, and 391 when W=4400 N, C=0.025 mm, μ=0.15, A=30 deg, f=10 Hz, and he=80 W/m2 K with the solid oscillating shaft in Case 2S

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Figure 9

Temperature variations at contact points A (θ=π/2) and B (θ=3π/2) when W=4400 N, C=0.025 mm, μ=0.15, A=30 deg, f=10 Hz, and he=80 W/m2 K with the solid oscillating shaft in Case 2S

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Figure 10

Distributions of contact pressure along the contact surface at the beginning and Cycles 300, 379, and 391 when W=4400 N, C=0.025 mm, μ=0.15, A=30 deg, f=10 Hz, and he=80 W/m2 K with the solid oscillating shaft in Case 2S

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Figure 11

Variation in frictional torque up to seizure when W=4400 N, C=0.025 mm, μ=0.15, A=30 deg, f=10 Hz, and he=80 W/m2 K with the solid oscillating shaft in Case 2S

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Figure 19

Temperature rise for Case 18S at Cycle 300 under oscillating shaft when W=4400 N, C=0.025 mm, μ=0.15, A=30 deg, f=10 Hz, and he=80 W/m2 K with the solid shaft

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Figure 20

Comparison between Case 2S under constant load and 18S with variable load directions in (a) clearance along the contact surface, (b) profile of the inner surface of the bushing, and (c) profile of the outer surface of the shaft at Cycle 300 when W=4400 N, C=0.025 mm, μ=0.15, A=30 deg, f=10 Hz, and he=80 W/m2 K with the solid shaft

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Figure 21

Temperature variation over oscillatory cycle for the cases of (a) oscillating shaft in Case 20S and (b) oscillating bushing in Case 24S when W=4400 N, C=0.05 mm, μ=0.05, A=30 deg, f=5 Hz, and he=80 W/m2 K with the solid shaft

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Figure 22

Temperature contours at steady state for (a) oscillating shaft in Case 20S and (b) oscillating bushing in Case 24S when W=4400 N, C=0.05 mm, μ=0.05, A=30 deg, f=5 Hz, and he=80 W/m2 K with the solid shaft

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Figure 23

Comparison of the contact clearance at steady state between the cases of oscillating shaft (Case 20S) and oscillating bushing (Case 24S) when W=4400 N, C=0.05 mm, μ=0.05, A=30 deg, f=5 Hz, and he=80 W/m2 K with the solid shaft

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Figure 24

Percentage of the frictional heat into shaft for (a) oscillating shaft in Case 20S and (b) oscillating bushing in Case 24S when W=4400 N, C=0.05 mm, μ=0.05, A=30 deg, f=5 Hz, and he=80 W/m2 K with the solid shaft

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Figure 13

Comparison between Cases 2S, 10S, and 11S with different lubricant convections under oscillating shaft in (a) clearance along the contact surface, (b) profile of the inner surface of the bushing, and (c) profile of the outer surface of the shaft at Cycle 300 when W=4400 N, C=0.025 mm, μ=0.15, A=30 deg, f=10 Hz, and he=80 W/m2 K

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Figure 12

Temperature rise for Case 10S at Cycle 300 under oscillating shaft with good lubrication (hg=240 W/m2 K) when W=4400 N, C=0.025 mm, μ=0.15, A=30 deg, f=10 Hz, and he=80 W/m2 K with the solid shaft

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Figure 17

Comparison between cases of oscillating shaft (Case 2S) and oscillating bushing (Case 21S) in (a) clearance along the contact surface, (b) profile of the inner surface of the bushing, and (c) profile of the outer surface of the shaft at Cycle 300 when W=4400 N, C=0.025 mm, μ=0.15, A=30 deg, f=10 Hz, and he=80 W/m2 K with the solid shaft

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Figure 16

Temperature rise for Case 21S at Cycle 300 under oscillating bushing when W=4400 N, C=0.025 mm, μ=0.15, A=30 deg, f=10 Hz, and he=80 W/m2 K with the solid shaft

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Figure 15

Comparison between cases of solid (Case 2S) and hollow (Cases 15H and 17H) oscillating shafts in (a) clearance along the contact surface, (b) profile of the inner surface of the bushing, and (c) profile of the outer surface of the shaft at Cycle 300 when W=4400 N, C=0.025 mm, μ=0.15, A=30 deg, f=10 Hz, and he=80 W/m2 K

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Figure 14

Temperature rise under oscillating hollow shaft with (a) hi=80 W/m2 K in Case 15H and (b) hi=1000 W/m2 K in Case 17H at Cycle 300 when W=4400 N, C=0.025 mm, μ=0.15, A=30 deg, f=10 Hz, and he=80 W/m2 K

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Figure 18

Variation of load directions in one load cycle for Case 18S

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