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Research Papers

Behavior Analysis of Controllable Electrorheology Fluid Plain Journal Bearings

[+] Author and Article Information
Yong-Bok Lee

Center for Urban Energy System Research,
Korea Institute of Science and Technology,
39-1, Hawolgok-dong, Sungbuk-gu,
Seoul 136-791, Korea
e-mail: lyb@kist.re.kr

Contributed by the Dynamic Systems Division of ASME for publication in the JOURNAL OF DYNAMIC SYSTEMS, MEASUREMENT, AND CONTROL. Manuscript received March 13, 2014; final manuscript received December 9, 2014; published online February 4, 2015. Assoc. Editor: Heikki Handroos.

J. Dyn. Sys., Meas., Control 137(6), 061013 (Jun 01, 2015) (8 pages) Paper No: DS-14-1116; doi: 10.1115/1.4029369 History: Received March 13, 2014; Revised December 09, 2014; Online February 04, 2015

Electrorheological (ER) lubricant is applied to a rigid rotor system supported by a hydrodynamic bearing that is subjected to a sudden imbalance and a dynamic periodic rotating load. The pressure of the ER film, which exhibits a Bingham flow, varies with the electrical field strength and depends on the yield shear stress and the thickness of the ER fluid film. The ER lubricant was found to offer a good load capacity relative to a Newtonian lubricant and its performance could be controlled to handle sudden dynamic loads. Increasing the magnitude of the electric field strength provides a greater load capacity within certain physical limitations and also reduces the magnitude of an unbalanced force due to unbalanced mass and vibration caused by vibration in the dynamically rotating load. These results could be applied to the control of a suddenly imbalanced system, such as one with rotor blades, or for reducing vibration in cyclic loading rotor systems, such as in internal combustion engines.

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References

Winslow, W. M., 1947, U.S. Patent No. 2,417,850.
Winslow, W. M., 1949, “Induced Vibration of Suspensions,” J. Appl. Phys., 20(12), pp. 1137–1140. [CrossRef]
Dien, I. K., and Elrod, H. G. A., 1983, “Generalized Steady-State Reynolds Equation for Non-Newtonian Fluids, With Application to Journal Bearings,” ASME J. Tribol., 105(3), pp. 385–390.
Najji, B., Bou-Said, B., and Berthe, D., 1989, “New Formulation for Lubrication With Non-Newtonian Fluids,” ASME J. Tribol., 111(1), pp. 29–34. [CrossRef]
Andrew, D. D., and Alexander, K., 1992, “Electrorheological Fluid-Controlled “Smart” Journal Bearings,” STLE Tribol. Trans., 35(4), pp. 611–618. [CrossRef]
Tichy, J., and Dorier, C., 1992, “Behavior of a Bingham-Like Viscous Fluid in Lubrication Flows,” J. Non-Newtonian Fluid Mech., 45(3), pp. 291–310. [CrossRef]
Jang, S., and Tichy, J. A., 1996, “Dynamic Coefficients of Submerged Electro-Rheological Bingham-Like Fluid Journal Bearing,” Proceedings of the 6th International Symposium on Transport Phenomena and Dynamics of Rotating Machinery, pp. 659–668.
Dowson, D., 1962, “A Generalized Reynolds Equation for Fluid-Film Lubrication,” Int. Mech. Sci., 4(2), pp. 159–170. [CrossRef]
Tanner, R. I., 1965, “Study of Anisothermal Short Journal Bearings With Non-Newtonian Lubricants,” ASME J. Appl. Mech., 32(4), pp. 781–797. [CrossRef]
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Kirk, R. G., and Gunter, E. J., 1976, “Short Bearing Analysis Applied to Rotor Dynamics—Part 2: Results of Journal Bearing Response,” ASME J. Tribol., 98(2), pp. 319–329.
Kim, C. H., Lee, N. S., Lee, Y. B., and Choi, D. H., 1998, “Vibration Control of a Pressurized, Sealed, Electro-Rheological Fluid Squeezed-Film Damped Supported Rotor,” Proceedings of the 7th International symposium on Transport Phenomena and Dynamics of Rotating Machinery, pp. 238–247.
Hull, E. E., 1958, “Oil-Whip Response,” Trans. ASME (A), 80, pp. 1490–1496.

Figures

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Fig. 1

Concept of journal and bearing

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Fig. 2

Geometry of plain journal bearing

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Fig. 3

Flowchart of the hydrodynamic bearing submerged ER fluid

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Fig. 4

Pressure distribution of Newtonian lubricant

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Fig. 5

Pressure distribution of ER lubricant (4.0 kV/mm)

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Fig. 6

Modified Sommerfeld number versus eccentricity for Newtonian lubricant and ER lubricants subjected to electric field strength 2.4 kV/mm and 4.0 kV/mm

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Fig. 7

Comparison of friction torque for Newtonian lubricant and ER lubricants

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Fig. 8

Comparison of transient motion to the static equilibrium for Newtonian lubricant bearing and ER lubricant bearings (2.4 kV/mm,4.0 kV/mm)

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Fig. 9

Comparison of the transient orbits for Newtonian lubricant and ER lubricants subjected variable clearance (C = 63.5 μm,127 μm,254 μm) at 4.0 kV/mm

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Fig. 10

Comparison of the transient orbits for Newtonian lubricant and ER lubricants subjected small unbalance case (eμ = 25 μm)

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Fig. 11

Comparison of the transient orbits for Newtonian lubricant and ER lubricants subjected large unbalance case (eμ = 50 μm)

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Fig. 12

Comparison of the transient orbits for Newtonian lubricant and ER lubricants subjected backward half-frequency with cyclic rotating load (100 N)

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