Research Papers: Hydrodynamic Lubrication

Acoustic Journal Bearing With Changeable Geometry and Built-in Flexibility

[+] Author and Article Information
T. A. Stolarski

Department of Mechanical
and Aerospace Engineering,
Brunel University London,
Kingston Lane,
Uxbridge UB8 3PH, Middlesex, UK
e-mail: mesttas@brunel.ac.uk

M. Miyatake

Department of Mechanical Engineering,
Tokyo University of Science,
6-3-1, Niijuku, Katsushika-ku,
Tokyo 125-8585, Japan
e-mail: m-miyatake@rs.tus.ac.jp

Contributed by the Tribology Division of ASME for publication in the JOURNAL OF TRIBOLOGY. Manuscript received February 11, 2018; final manuscript received May 21, 2018; published online July 12, 2018. Assoc. Editor: Stephen Boedo.

J. Tribol 140(6), 061707 (Jul 12, 2018) (9 pages) Paper No: TRIB-18-1066; doi: 10.1115/1.4040416 History: Received February 11, 2018; Revised May 21, 2018

The influence of embodiment flexibility on the performance of an acoustic journal bearing is presented. Two completely different embodiments of the bearing were investigated using three criteria of performance assessment that is torque at the start-up, amount of separation due to squeeze film pressure, and motion stability of the shaft running at speed. The embodiment with built-in flexibility proved to perform far better than the bearing for which overall flexibility was much less. However, considerations pertinent to the easy of machining and fatigue endurance mitigate the ranking of performance of the two embodiments investigated.

Copyright © 2018 by ASME
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Fig. 1

Essence of the squeeze film mechanism

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Fig. 2

Schematic showing geometry of elastically deformed bearing

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Fig. 3

Bearing in deformed state. (1) housing, (2) bearing shell, (3) PZT, and (4) oscillating “half-moon” gap.

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Fig. 4

Diagram of bearing system for its analytical model

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Fig. 5

Photograph showing the first embodiment of the bearing: (1) PZT (there are three PZTs spaced by 120 deg); (2) supporting and constraining arm fixing the bearing to its housing; and (3) inner surface of the bearing shell

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Fig. 6

Image of the bearing (first embodiment) showing its deformation when applied offset voltage to PZTs was 60 V

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Fig. 7

Photograph of the bearing in its second embodiment: (1) “elastic hinge”; (2) inner surface; (3) outer surface totally constrained in the housing; and (4) slot for PZT

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Fig. 8

Image of the bearing (second embodiment) showing its deformation when applied offset voltage to PZTs was 95 V

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Fig. 9

(a) Schematic of experimental apparatus; (b) photograph showing experimental setup; (c) photographs showing top part of the apparatus: PZTs (rod type), shaft, and tested bearing are all visible; and (d) photograph showing aerostatic thrust bearing of the apparatus together with displacement probes to monitor shaft's motion

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Fig. 10

Schematic illustrating orientation of X and Y axes relative to the position of PZTs. The load on the bearing acts along y-axis that is between two adjacent PZTs.

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Fig. 11

Separation of the shaft from inner bearing surface as a function of applied load: series 1, calculated separation for the second embodiment; series 2, calculated separation for the first embodiment; series 3, measured separation for the first embodiment; series 4, measured separation for the second embodiment

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Fig. 12

Torque required to start-up motion of the shaft for different loads (first embodiment)

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Fig. 13

Torque required to start-up motion of the shaft for different loads (second embodiment)

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Fig. 14

Change in the magnitude of stability coefficient, S, as a function of load on the bearing in its first embodiment

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Fig. 15

Change in the magnitude of stability coefficient, S, as a function of load on the bearing in its second embodiment



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