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TECHNICAL PAPERS

Thermoelastohydrodynamic Behavior of Mechanical Gas Face Seals Operating at High Pressure

[+] Author and Article Information
Sébastien Thomas

Laboratoire de Mécanique des Solides, UMR CNRS 6610,  Université de Poitiers, Boulevard Marie et Pierre Curie, SP2MI, Boîte Postale 30179, 86962 Futuroscope Chasseneuil Cedex, Francesebastien.thomas@lms.univ-poitiers.fr

Noël Brunetière, Bernard Tournerie

Laboratoire de Mécanique des Solides, UMR CNRS 6610,  Université de Poitiers, Boulevard Marie et Pierre Curie, SP2MI, Boîte Postale 30179, 86962 Futuroscope Chasseneuil Cedex, France

J. Tribol 129(4), 841-850 (Mar 30, 2007) (10 pages) doi:10.1115/1.2768086 History: Received November 06, 2006; Revised March 30, 2007

A numerical modeling of thermoelastohydrodynamic mechanical face seal behavior is presented. The model is an axisymmetric one and it is confined to high pressure compressible flow. It takes into account the behavior of a real gas and includes thermal and inertia effects, as well as a choked flow condition. In addition, heat transfer between the fluid film and the seal faces is computed, as are the elastic and thermal distortions of the rings. In the first part of this paper, the influence of the coning angle on mechanical face seal characteristics is studied. In the second part, the influence of the solid distortions is analyzed. It is shown that face distortions strongly modify both the gap geometry and the mechanical face seal’s performance. The mechanical distortions lead to a converging gap, while the gas expansion, by cooling the fluid, creates a diverging gap.

Copyright © 2007 by American Society of Mechanical Engineers
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Figures

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Figure 1

Geometry of the model

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Figure 2

Geometry of the solids

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Figure 3

Thermal boundary conditions used in the determination of the influence coefficients ai,j

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Figure 4

Mechanical boundary conditions used in the determination of the influence coefficients bi,j

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Figure 5

Geometry of a converging and diverging fluid film

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Figure 6

Exit pressure versus minimum film thickness for different values of coning angle

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Figure 7

Load capacity versus the minimum film thickness for different values of coning angle

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Figure 8

Pressure field for a coning angle of β=4×10−4rad and two values of film thickness

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Figure 9

Mass flow versus the minimum film thickness for different values of coning angle

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Figure 10

Geometry of the fluid film when elastic distortions are considered

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Figure 11

Pressure fields for several geometries of the fluid film

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Figure 12

Temperature field in the fluid film when elastic distortions are considered

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Figure 13

Fluid film geometry when thermal distortions are considered for two values of angular velocity

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Figure 14

Pressure field when thermal distortions are considered and ω=2500rpm

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Figure 15

Temperature field in the fluid film when thermal distortions are considered and ω=2500rpm

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Figure 16

Comparison of the geometry of the fluid film when elastic and thermal distortions are considered

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Figure 17

Pressure field when elastic and thermal distortions are considered

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Figure 18

Temperature field in the fluid film when elastic and thermal distortions are considered

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