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RESEARCH PAPERS

An Experimental Study of Static and Dynamic Characteristics of a 580mm(22.8in.) Diameter Direct Lubrication Tilting Pad Journal Bearing

[+] Author and Article Information
Kazunori Ikeda, Toshio Hirano, Tatsuo Yamashita, Makoto Mikami, Hitoshi Sakakida

Power and Industrial Systems Research and Development Center,  Toshiba Corporation, 2-4, Suehiro-cho, Tsurumi-ku, Yokohama, 230-0045, Japan

J. Tribol 128(1), 146-154 (Aug 19, 2005) (9 pages) doi:10.1115/1.2114929 History: Received February 23, 2004; Revised August 19, 2005

Direct lubrication tilting pad journal bearings (DLTPJ bearings) have rarely been applied to large-scale rotating machinery, such as turbines or generators, whose journal diameters are more than 500mm. In this paper, static and dynamic characteristics of a 580mm(22.8in.) diameter DLTPJ bearing were studied experimentally using a full-scale bearing test rig. In the static test, distribution of metal temperature, oil film pressure, and bearing loss were measured in changing oil flow rate, with mean bearing pressure ranging up to 2.9MPa. The maximum metal temperature of the DLTPJ bearing was compared to that of a conventional flood lubrication bearing, and it was confirmed that the direct lubrication could increase load capacity. In the dynamic test, spring and damping coefficients of oil film were obtained by exciting the bearing casing that was floated by air bellows. These data will be used for analysis and design of steam turbine rotors and their bearing systems. Also, vibration of pads was investigated because metal failure on upper pads due to vibration has been found in some actual machines. In order to generate oil film pressure on the surface of upper pads, a Rayleigh-step was machined there, and it was confirmed that vibration was reduced by the Rayleigh-step.

Copyright © 2006 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

Cross section of test bearing

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Figure 2

Flow of lubricant oil on pads

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Figure 3

Cross section of bearing test rig

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Figure 4

Location of thermocouples in pads

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Figure 5

Attachment of pressure sensor in the journal

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Figure 6

Attachment of proximity probe for the measurement of pad vibration

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Figure 7

Journal center position

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Figure 8

Contour plot of metal temperature of lower pads (N=60rps, Pm=1.96MPa, Q=0.8Q0)

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Figure 9

Circumferential distribution of metal temperature along the bearing center (N=60rps, Pm=1.96MPa, Q=0.8Q0)

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Figure 10

Relation between oil flow rate and maximum metal temperature of lower pads (N=60rps, Pm=1.96MPa)

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Figure 11

Circumferential distribution of oil film pressure along the bearing center (N=60rps, Pm=1.96MPa, Q=0.8Q0)

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Figure 12

Relation between oil flow rate and maximum oil film pressure on lower pads (N=60rps, Pm=1.96MPa)

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Figure 13

Relation between oil flow rate and vibration displacement of lower pads (N=60rps, Pm=1.96MPa)

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Figure 14

Relation between oil flow rate and frictional coefficient (N=60rps, Pm=1.96MPa)

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Figure 15

Relation between mean bearing pressure and maximum metal temperature of lower pads (N=60rps, Q=0.81Q0)

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Figure 16

Spring coefficients of oil film

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Figure 17

Damping coefficients of oil film

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Figure 18

Uncertainty of γyy and contribution of error in each measured value at Soeff=0.41

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Figure 19

Uncertainty of βyy and contribution of error in each measured value at Soeff=0.41

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Figure 20

Rayleigh-step on upper pad

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Figure 21

Circumferential distribution of oil film pressure along the bearing center after machining a Rayleigh-step on the upper pads (N=60rps, Pm=1.96MPa, Q=0.81Q0)

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Figure 22

Vibration displacement of upper pads (N=60rps, Q=0.81Q0)

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