Heat Separation in Frictional Rotor-Seal Contact

[+] Author and Article Information
Björn Larsson

Dept. of Machine Diagnosis, Alstom Power Sweden, Finspång, Sweden

J. Tribol 125(3), 600-607 (Jun 19, 2003) (8 pages) doi:10.1115/1.1472456 History: Received February 29, 2000; Revised February 07, 2002; Online June 19, 2003
Copyright © 2003 by ASME
Your Session has timed out. Please sign back in to continue.


Berry,  G. A., and Barber,  J. R., 1984, “The Division of Frictional Heat—A Guide to the Nature of Sliding Contact,” ASME J. Tribol., 106, pp. 405–415.
Carslaw, H. S., and Jaeger, J. C., 1959, Conduction of Heat in Solids, Oxford Univ. Press, Clarendon Press, Oxford.
Childs,  D. W., 1982, “Fractional-Frequency Rotor Motion Due to Nonsymmetric Clearance Effects,” Quarterly J. Math., 104, pp. 533–541.
Childs, D. W., and Jordan, L. T., 1997, “Clearance Effects on Spiral Vibrations Due to Rubbing,” ASME Design Engineering Technical Conference, ASME, New York, DETC97/VIB-4058.
de Jongh,  F. M., and Morton,  P. G., 1996, “The Synchronous Instability of a Compressor Due to Bearing Journal Differential Heating,” ASME J. Eng. Gas Turbines Power, 118, pp. 816–824.
Dimarogonas, A. D., 1970, “An Analytic Study of the Packing Rub Effect in Rotating Machinery,” Dissertation, Rensselaer Polytechnic Institute, Troy, NY.
Dimarogonas, A. D., 1983, Analytical Methods in Rotor Dynamics, Applied Science Publishers Ltd., England.
Ehrich,  F. F., 1992, “Observations of Subcritical Superharmonic and Chaotic Response in Rotor Dynamics,” ASME J. Vibr. Acoust., 114, pp. 93–100.
Ericsson, U., 1980, “Temperature Distribution in the Oil Film of a Vibrating Tilting-Pad Bearing,” dissertation, Chalmers University of Technology, Gothenburg.
Gomiciaga,  R., and Keogh,  P. S., 1999, “Orbit Induced Journal Temperature Variation in Hydrodynamic Bearings,” ASME J. Tribol., 121, pp. 77–84.
Greenwood, J. A., and Tabor, D., 1957, “The Properties of Model Friction Junctions,” Inst. Mech. Engs. Proc. of Conference on Lubrication and Wear, Paper 92, pp. 314–318.
Greenwood,  J. A., 1967, “The Area of Contact between Rough Surfaces and Flats,” ASME J. Lubr. Technol., 1, pp. 81–91.
Isaksson, J., 1997, “Dynamics of Rotors Influenced by Rubbing Contacts,” Dissertation, Linköping University, Linköping, Sweden.
Jaeger,  J. C., 1943, “Moving Sources of Heat and the Temperature at Sliding Contacts,” Proc. of the Royal Society of New South Wales, 76, pp. 203–224.
Kellenberger,  W., 1980, “Spiral Vibrations Due to the Seal Rings in Turbogenerators: Thermally Induced interaction Between Rotor and Stator,” ASME J. Mech. Des., 102, pp. 177–184.
Keogh,  P. S., and Morton,  P. G., 1993, “Journal Bearing Differential Heating Evaluation With Influence on Rotor Dynamic Behavior,” Proc. R. Soc. London, Ser. A, 441, pp. 527–548.
Keogh,  P. S., and Morton,  P. G., 1994, “The Dynamic Nature of Rotor Thermal Bending Due to Unsteady Lubricant Shearing Within a Bearing,” Proc. R. Soc. London, Ser. A, 445, pp. 273–290.
Kuhlmann-Wilsdorf,  D., 1996, “What Role for Contact Spots and Dislocations in Friction and Wear?” Wear, 200, pp. 8–29.
Larsson,  B., 1999, “Journal Asymmetric Heating—Part I: Non-Stationary Bow,” ASME J. Tribol., 121, pp. 157–163.
Larsson,  B., 1999, “Journal Asymmetric Heating—Part II: Alteration of Rotor Dynamic Properties,” ASME J. Tribol., 121, pp. 164–168.
Larsson, B., 2000, “Rub-Heated Shafts in Turbines,” accepted for IMechE Rotor Dynamic Conference, Nottingham.
Marsher, W. D., 1981, “A Critical Evaluation of the Flash Temperature Concept,” ASLE Preprint, 81-AM-ld-3, pp. 1–18.
Muszynska,  A., 1989, “Rotor-to-Stationary Element Rub-Related Vibration Phenomena in Rotating Machinery-Literature Survey,” River, 21(3), pp. 3–11.
Newkirk,  B. L., 1926, “Shaft Rubbing,” Mech. Eng. (Am. Soc. Mech. Eng.), 48(8), pp. 830–832.
Quinn,  T. F. J., 1967, “The Effect of Hot-Spot Temperatures on the Unlubricated Wear of Steel,” ASLE Trans., 10, pp. 158–168.
Quinn, T. F. J., 1968, “Dry Wear of Steel as Revealed by Electron Microscopy and X-ray Diffraction,” Proc. Instn Mech Engrs Convention on Tribology, 182 , Part 3N, pp 201–213.
Schmied, J., 1987, “Spiral Vibrations of Rotors,” Rotating Machinery Dynamics, Proceedings of the ASME Design Technology Conference, 2 , ASME, New York.
Timoshenko, S. P., and Goodier, J. N., 1982, Theory of Elasticity, Third Edition, McGraw-Hill.


Grahic Jump Location
Outer and inner seal holder in radial-axial view. Each seal cam is about 0.2 mm thick in the axial direction and the distance between them is 5 mm.
Grahic Jump Location
Inner seal holder in radial-radial view. The whole seal consists of six parts, each 60 deg. The radial distances are not proportional, but seal cam and seal holder are enlarged for visibility.
Grahic Jump Location
Coordinates in rotor seal system. The X-Y system refers to the seal, with γseal at the first ellipse major radius, and the x-y to the shaft, both non-rotating. The angle γshaft refers to stationary shaft position relative to the X-Y system. In the rotating shaft we have the r-ϕ system.
Grahic Jump Location
Geometrical contact relations between shaft and seal disregarding contact forces. Stars indicate minimum gap, and will be the actual contact spots when contact forces are included. (a) Contact position with a centered forward whirl. (b) Contact position with a forward eccentric whirl. (c) Contact position with a forward whirl, in an elliptic seal.
Grahic Jump Location
Seal dynamic model. The seal cams are represented by kseal.
Grahic Jump Location
Force-deformation diagram. Both force and deformation refer to the radial direction.
Grahic Jump Location
Nonlinear relation between vibration and heat generation. The smoothing relative to Fig. 6 is due to increasing contact times for higher levels of vibration.
Grahic Jump Location
Geometries for approximation of heat conduction in shaft. The cylinder has infinite length, and convection on the surface.
Grahic Jump Location
Temperature in the axial-peripheral plane at the shaft surface. Steady state with a source of 1 W.
Grahic Jump Location
Temperature along the z-axis (peripheral position zero, and radial at the shaft surface) at steady state with a source of 1W. The solid line is the half-space solution and the stars are the cylinder solution. Left: h=200 W/m2K, right: h=400 W/m2K.
Grahic Jump Location
Step response of mean temperature at contact area for shaft (thick line) and seal (sawtooth line, uniform around the periphery). They are different because a source of 100 W is assumed into each part.
Grahic Jump Location
Heat conduction in seal
Grahic Jump Location
Bow step response of a Q=1400 W source into the shaft
Grahic Jump Location
Bode plot of bow response (full solution). The absolute error between the full solution and the approximation is dashed. It is seen that the interesting dynamic region is between about 10−4 and 10−1 s.



Some tools below are only available to our subscribers or users with an online account.

Related Content

Customize your page view by dragging and repositioning the boxes below.

Related Journal Articles
Related eBook Content
Topic Collections

Sorry! You do not have access to this content. For assistance or to subscribe, please contact us:

  • TELEPHONE: 1-800-843-2763 (Toll-free in the USA)
  • EMAIL: asmedigitalcollection@asme.org
Sign In