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Research Papers

Dynamic Analysis of a Motorized Spindle With Externally Pressurized Air Bearings

[+] Author and Article Information
Chundong Xu

School of Mechanical Engineering,
Southeast University,
2 Southeast Road,
Jiangning District,
Nanjing 211189, China

Shuyun Jiang

Professor
School of Mechanical Engineering,
Southeast University,
2 Southeast Road,
Jiangning District,
Nanjing 211189, China
e-mail: jiangshy@seu.edu.cn

1Corresponding author.

Contributed by the Technical Committee on Vibration and Sound of ASME for publication in the JOURNAL OF VIBRATION AND ACOUSTICS. Manuscript received July 9, 2014; final manuscript received January 22, 2015; published online March 12, 2015. Assoc. Editor: Patrick S. Keogh.

J. Vib. Acoust 137(4), 041001 (Aug 01, 2015) (16 pages) Paper No: VIB-14-1251; doi: 10.1115/1.4029675 History: Received July 09, 2014; Revised January 22, 2015; Online March 12, 2015

The purpose of this paper is to investigate the dynamic characteristics of a motorized spindle with externally pressurized air bearings. The externally pressurized air bearings consist of a journal bearing and a double pad thrust bearing with orifice restrictors. The equations of motion for the rotor-bearing system are established considering five degrees-of-freedom (DOF). The perturbation method and the finite difference method are introduced to calculate the static and dynamic characteristics of the air bearings; and the effects of the rotating speed and tilt angle of the rotor on the dynamic characteristics of the air bearings are analyzed. With the dynamic coefficients of the air bearings and the 5DOF rotor-dynamic model obtained, the stability, the unbalance response, and the forced response of the rotor-bearing system are investigated. Finally, the static and dynamic characteristics of the spindle are verified by an experimental study.

Copyright © 2015 by ASME
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References

Figures

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Fig. 1

Schematic view of the motorized spindle for the wheel

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Fig. 2

The dynamic model of the motorized spindle

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Fig. 3

The cylindrical coordinate system

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Fig. 4

The journal position associated with translation and tilt: (a) translation and (b) tilt

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Fig. 5

Tilt of the thrust pad

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Fig. 6

Meshes of the gas film

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Fig. 7

The variation of the dynamic coefficients of the journal bearing against the rotating speed: (a) translational components of dynamic coefficients due to translational motion, (b) tilt components of dynamic coefficients due to tilt motion, (c) translational components of dynamic coefficients due to tilt motion, and (d) tilt components of dynamic coefficients due to translational motion

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Fig. 8

The variation of the dynamic coefficients of the journal bearing against the tilt angle: (a) translational components of dynamic coefficients due to translational motion, (b) tilt components of dynamic coefficients due to tilt motion, (c) translational components of dynamic coefficients due to translational motion, (d) tilt components of dynamic coefficients due to tilt motion, (e) translational components of dynamic coefficients due to tilt motion, (f) translational components of dynamic coefficients due to tilt motion, (g) tilt components of dynamic coefficients due to translational motion, and (h) tilt components of dynamic coefficients due to translational motion

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Fig. 9

The variation of the dynamic coefficients of the thrust bearing against the rotating speed: (a) translational components of dynamic coefficients due to translational motion and (b) tilt components of dynamic coefficients due to tilt motion

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Fig. 10

The variation of the dynamic coefficients of the thrust bearing against the tilt angle: (a) translational components of dynamic coefficients due to translational motion, (b) tilt components of dynamic coefficients due to tilt motion, (c) translational components of dynamic coefficients due to tilt motion, (d) tilt components of dynamic coefficients due to tilt motion, and (e) tilt components of dynamic coefficients due to translational motion

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Fig. 11

Stability of the motorized spindle: (a) cylindrical whirling motion, (b) conical whirling motion, and (c) axial whirling motion

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Fig. 12

Unbalance response of the spindle

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Fig. 13

Schematic view of the grinding forces

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Fig. 14

The cut-in force Fp versus time t

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Fig. 15

Test rig for measuring the axial stiffness: (a) schematic diagram and (b) photograph

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Fig. 16

Test rig for measuring the radial stiffness: (a) schematic diagram and (b) photograph

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Fig. 17

Test rig of the unbalance response

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