Analysis of Contact Mechanics for Rotor-Bristle Interference of Brush Seal

[+] Author and Article Information
R. J. Stango

Deburring and Surface Finishing Research Laboratory, Marquette University, 1515 W. Wisconsin Avenue, Milwaukee, WI 53233

H. Zhao

Department of Mechanical and Industrial Engineering, Marquette University, Milwaukee, WI 53233

C. Y. Shia

YUN Technologies, Germantown, WI

J. Tribol 125(2), 414-421 (Mar 19, 2003) (8 pages) doi:10.1115/1.1510879 History: Received February 14, 2002; Revised July 02, 2002; Online March 19, 2003
Copyright © 2003 by ASME
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Basu,  P., Datta,  A., Loewenthal,  R., Short,  J., and Johnson,  R., 1994, “Hysteresis and Bristle Stiffening Effects in Brush Seals,” J. Propul. Power, 10(4), pp. 569–575.
Sharatchandra,  M. C., and Rhode,  D. L., 1996, “Computed Effects of Rotor-induced Swirl on Brush Seal Performance: Part 2—Bristle Force Analysis,” ASME J. Tribol., 118, pp. 920–926.
Aksit,  M. F., and Tichy,  J. A., 1998, “Wear of Brush Seals: Background and New Modeling Approach,” Tribol. Trans., 41(3), pp. 368–374.
Turner,  M. T., Chew,  J. W., and Long,  C. A., 1998, “Experimental Investigation and Mathematical Modeling of Clearance Brush Seals,” ASME J. Eng. Gas Turbines Power, 120, pp. 573–579.
Chen,  L. H., Wood,  P. E., Jones,  T. V., and Chew,  J. W., 1999, “An Iterative CFD and Mechanical Brush Seal Model and Comparison with Experimental Results,” ASME J. Eng. Gas Turbines Power, 121, pp. 656–662.
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Stango,  R. J., Heinrich,  S. M., and Shia,  C. Y., 1989, “Analysis of Constrained Filament Deformation and Stiffness Properties of Brushes,” ASME J. Ind., 111(3), pp. 238–243.
Stango,  R. J., and Shia,  C. Y., 1994, “On the Frictional Response of Circular Filamentary Brush in Contact with Planar Workpart,” Int. J. Mach. Tools Manuf., 34(4), pp. 573–589.
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(a) Front view of brush seal depicting force system exerted by shaft onto bristle tip due to diametral interference, (b) section view of annular front and back plate that constrain bristle pack, (c) depiction of hypothetical free-body diagram in x-y plane, and (d) geometry of deformed bristle illustrating length coordinate and fiber slope in local frame of reference.
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(a) experimental system used for measurement of bristle tip forces Fn and Fs, (b) force data acquired over 6 sec interval for normal force Fn (solid line) and shear force Fs (dashed line), and (c) comparison of normal force Fn based upon mechanics approach (square) and experimentation (diamond).
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(a) Relationship between dimensionless force and dimensionless penetration depth for lay angles of 30, 45, and 60 deg. Shaded region corresponds to range of feasible eccentricities. Open circles denote upper bound for validity of linear (i.e., small displacement) beam theory for each lay angle. (Results shown are for frictionless contact with Rs/H*=15), and (b) numerical solution for bristle tip normal force based upon actual brush seal dimensions reported in Ref. 9.
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Relationship between dimensionless force and dimensionless penetration depth for shaft/seal configurations Rs/H*=10, 15, and 50 (results shown are for frictionless contact and 45 deg lay angle)
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Relationship between dimensionless force and dimensionless penetration depth for friction coefficient 0, 0.2, and 0.6. (Results shown are for 45 deg lay angle, and Rs/H*=15).
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(a) Equilibrium position of bristle tip on rotor surface at point A in absence of friction, and (b) inclusion of friction gives rise to shear force Fs=μFn, and revised equilibrium position of bristle tip toward point C on rotor.
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Relationship between bristle stress and bristle/rotor interference for lay angles 30, 45, and 60 deg. (Results shown are for frictionless contact with Rs/H*=15).
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Outline of computational algorithm developed and used for obtaining convergent solutions to governing nonlinear differential equation (Eq. 6).



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