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Research Papers: Gas Turbines: Structures and Dynamics

Performance Analysis of Oil Lubricated Foil Bearing With Flexible Supported Back Spring Structure—Part II: Comparison of Predictions and Measured Test Data

[+] Author and Article Information
Guanghui Zhang

Assistant Professor
School of Energy Science and Engineering,
Harbin Institute of Technology,
Mailbox 458, No. 92, Xi-Dazhi Street,
NanGang District, Harbin,
HeiLongjiang Province 150001, China
e-mail: zhanggh@hit.edu.cn

Xie Liang, Yu Wang

School of Energy Science and Engineering,
Harbin Institute of Technology,
Mailbox 458, No. 92, Xi-Dazhi Street,
NanGang District, Harbin,
HeiLongjiang Province 150001, China

Zhansheng Liu

School of Energy Science and Engineering,
Harbin Institute of Technology
Mailbox 458, No. 92, Xi-Dazhi Street,
NanGang District, Harbin,
HeiLongjiang Province 150001, China

Contributed by the Structures and Dynamics Committee of ASME for publication in the JOURNAL OF ENGINEERING FOR GAS TURBINES AND POWER. Manuscript received May 9, 2013; final manuscript received April 3, 2014; published online May 16, 2014. Assoc. Editor: Patrick S. Keogh.

J. Eng. Gas Turbines Power 136(11), 112502 (May 16, 2014) (10 pages) Paper No: GTP-13-1126; doi: 10.1115/1.4027603 History: Received May 09, 2013; Revised April 03, 2014

As described in Part I (Zhang et al., “Performance Analysis of Oil Lubricated Foil Bearing With Flexible Supported Back Spring Structure—Part I: Model Development and Numerical Investigation”, ASME J. Eng. Gas Turbines Power, 136(11), p. 112501), a new type of multileaf oil lubricated foil bearing with flexible supported back spring structure was proposed and the characteristics were obtained by theoretical analysis and numerical simulation. Until now, nearly no paper about the modeling method and experimental verification for this type foil bearing published. So it is necessary to study the performance of this kind bearing by experiments. The experimental rig for the static and dynamic characteristics of the bearing was installed and the experiments were carried out. The stiffness of the back supported spring was measured. By employing the dynamic coefficients identification algorithm for oil foil bearing, the data acquisition delay was compensated. The load capacity, stiffness coefficients and damping coefficients were obtained. The load capacity resulting from the experiment was coincided with the theoretical simulation well. The stiffness and damping coefficients from the experiments had the similar tendency with those from the theoretical analysis. The stiffness coefficients obtained from experiments were coincided well with the numerical simulation results, and the difference of damping coefficients was a little bigger.

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References

Figures

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Fig. 1

Description of the stiffness measuring rig for back support spring

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Fig. 2

Flow diagram for the experimental study of the foil bearing

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Fig. 3

Diagram for the experimental test rig

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Fig. 4

Drawing for the rotating shaft and turbine

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Fig. 5

Diagram of detail characteristics for experimental test rig (a) floating mechanism, (b) static load mechanism, and (c) dynamic motion and load measure mechanism

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Fig. 6

Schematic diagram of the test rotor bearing system

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Fig. 7

Simplified dynamic model for the rotor bearing system

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Fig. 8

The difference between the two groups extracting time

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Fig. 9

Flow chart for the identification procedure with compensation algorithm

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Fig. 10

Diagram for the spring stiffness measuring rig

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Fig. 11

Measured and fitting spring stiffness line

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Fig. 12

Drawing of experimental apparatus for static characteristics: (a) schematic drawing for test foil bearing, (b) physical drawing for test foil bearing, and (c) temperature measurement for test bearing

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Fig. 13

Foil bearing load versus temperature

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Fig. 14

Diagram of the bearing orbits which are mutually perpendicular

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Fig. 15

The comparison of the main stiffness coefficients between the theoretical and experimental results

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Fig. 16

The comparison of the cross coupling stiffness coefficients between the theoretical and experimental results

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Fig. 17

The comparison of the main damping coefficients between the theoretical and experimental results

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Fig. 18

The comparison of the cross coupling damping coefficients between the theoretical and experimental results

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Fig. 19

Comparison of the main stiffness coefficient varying with rotating angular speed for different bearing load

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Fig. 20

Comparison of the main damping coefficient varying with rotating angular speed for different bearing load

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