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Research Papers

Dynamic Effect of Bearing Wear on Rotor-Bearing System Response

[+] Author and Article Information
Athanasios C. Chasalevris

e-mail: chasalevris@sdy.tu-darmstadt.de

Pantelis G. Nikolakopoulos

e-mail: pnikolak@mech.upatras.gr

Chris A. Papadopoulos

e-mail: chris.papadopoulos@upatras.gr
Machine Design Laboratory,
Mechanical Engineering
Department & Aeronautics,
University of Patras,
26504 Patras, Greece

1Currently at Institute for Dynamics of Structures, School of Mechanical Engineering, Darmstadt University of Technology, 64283 Darmstadt, Germany.

2Corresponding author.

Contributed by the Design Engineering Division of ASME for publication in the JOURNAL OF Vibration and Acoustics. Manuscript received September 8, 2011; final manuscript received June 19, 2012; published online February 4, 2013. Assoc. Editor: Alan Palazzolo.

J. Vib. Acoust 135(1), 011008 (Feb 04, 2013) (12 pages) Paper No: VIB-11-1200; doi: 10.1115/1.4007264 History: Received September 08, 2011; Revised June 19, 2012

A rotor-bearing system is simulated in this study to investigate the effect of worn journal bearings on the system response and to specify the eventual development of additional frequency components. The well-known symmetric Dufrane bearing wear model is used here. The main target here is the investigation of the wear influence on the system response. An experimental layout was constructed for the needs of the current research, including an artificially worn bearing. It was observed that sub- and superharmonics are revealed in the continuous wavelet transform (CWT) of the rotor-bearing system response for worn bearings.

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References

Figures

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Fig. 1

Multistep rotor-bearing system mounted in fluid-film bearings

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Fig. 2

Worn journal bearing. Loads and wear zone for a specific equilibrium position.

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Fig. 3

Matrix P definition according to model geometry. The functions of displacement “U”, slope “S”, bending moment “M”, and shearing forces “V” include the variables of unknowns qi,j, which coefficients (multipliers) are the elements of the matrix.

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Fig. 4

The fluid film thickness as a function of the angular coordinate of the bearing for the cases of the intact bearing and the worn bearing for three different values of the Sommerfeld number (lightly, middle, heavily loaded bearing)

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Fig. 5

Matrix P definition according to model geometry. The functions of displacement “U”, slope “S”, bending moment “M”, and shearing forces “V” include the variables of unknowns qi,j, which coefficients (multipliers) are the elements of the matrix.

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Fig. 6

(a) Photo of experimental layout with definition in the main parts, (b) photo of the experimental rotor and measuring system, and (c) mechanical drawing of experimental rotor bearing system

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Fig. 7

(a) Arrangement used to apply vertical external force in journal #2 to produce wear. (b) Journal bearing #2 during wear progress (burs visible). (c) 40% cr worn bearing #2 in housing just after removing the shaft (wear zone visible, with the thermocouple plugged in bearing also visible). (d) 40% cr worn bearing after disassembly and cleaning (wear zone is also visible here).

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Fig. 8

Continuous wavelet transform (scalogram) for analytical time histories (horizontal plane) of Journal 1 during start up: (a) wear depth 0% cr, (b) wear depth 20% cr, and (c) wear depth 40% cr

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Fig. 9

Continuous wavelet transform (scalogram) for experimental time histories (horizontal plane) of Journal 1 during start up: (a) wear depth 0% cr, (b) wear depth 20% cr, and (c) wear depth 40% cr

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Fig. 10

Continuous wavelet transform (scalogram) for analytical time histories (vertical plane) of Journal 1 during start up: (a) wear depth 0% cr, (b) wear depth 20% cr, and (c) wear depth 40% cr

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Fig. 11

Continuous wavelet transform (scalogram) for experimental time histories (vertical plane) of Journal 1 during start up: (a) wear depth 0% cr, (b) wear depth 20% cr, and (c) wear depth 40% cr

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