Prediction of Dry-Friction Whirl and Whip Between a Rotor and a Stator

[+] Author and Article Information
Dara W. Childs

Turbomachinery Laboratory, Texas A&M University, College Station, TX 77843dchilds@tamu.edu

Avijit Bhattacharya

Turbomachinery Laboratory, Texas A&M University, College Station, TX 77843avijitbh@gmail.com

J. Vib. Acoust 129(3), 355-362 (Jan 30, 2007) (8 pages) doi:10.1115/1.2731412 History: Received September 11, 2006; Revised January 30, 2007

This paper addresses recent test results for dry-friction whip and whirl. Authors of these publications suggest that predictions from Black’s 1968 paper (J. Mech. Eng. Sci., 10(1), pp. 1–12) are deficient in predicting their observed transition speeds from whirl to whip and the associated precession frequencies of whirl and whip motion. Predictions from Black’s simple Jeffcott-rotor/point-mass stator are cited. This model is extended here to a multimode rotor and stator model with an arbitrary axial location for rotor-stator rubbing. Predictions obtained from this new model are quite close to experimental observations in terms of the transition from whip to whirl and observed precession frequencies. Paradoxically, nonlinear numerical simulations using Black’s model fail to produce the whirl and whip solutions. The Coulomb friction force in Black’s model has a fixed direction, and Bartha showed in 2000 (“Dry Friction Backward Whirl of Rotors,” Dissertation, THE No. 13817, ETH Zurich) that by making the friction-force direction depend on the relative sliding velocity, nonlinear simulations would produce the predicted whirl solutions. He also showed that Black’s proposed whip solution at the upper precession-frequency transition from whirl to whip was unstable. The multimode extension of Black’s model predicts a complicated range of whirl and whip possibilities; however, nonlinear time-transient simulations (including the sgn function definition for the Coulomb force) only produce the initial whirl precession range, initial whirl-whip transition, and initial whip frequency. Simulation results for these values agree well with predictions. However, none of the predicted higher-frequency whirl results are obtained. Also, the initial whip frequency persists to quite high running speeds and does not (as predicted) transition to higher frequencies. Hence, despite its deficiencies, correct and very useful predictions are obtained from a reasonable extension of Black’s model.

Copyright © 2007 by American Society of Mechanical Engineers
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Figure 3

Simple rotor with mid and quarter span contact setup (not to scale)

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Figure 4

Prediction for simple shaft model at midspan of the shaft as shown in Fig. 3

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Figure 5

Prediction for simple shaft model at quarter span of the shaft as shown in Fig. 3

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Figure 6

The Yu rotor-stator model with noncentered contact location (based on figures in (8-9) and not to scale)

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Figure 7

Experimental plots from Yu (8) and Bently (9)

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Figure 11

Reduction in whirl and whip frequencies not predicted using Black’s (1-2) analysis

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Figure 10

Prediction for Bartha’s (6-7) model

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Figure 9

Simple layout of Bartha’s rotor stator model (modeled based on figures in (6) and not to scale)

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Figure 8

Prediction for the Yu model (8)

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Figure 2

Rotor-stator interaction motion

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Figure 1

Jeffcott rotor model interacting with a point-mass stator across a clearance from (11)



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