Research Papers: Other (Seals, Manufacturing)

Modeling Dry Wear of Piston Rod Sealing Elements of Reciprocating Compressors Considering Gas Pressure Drop Across the Dynamic Sealing Surface

[+] Author and Article Information
A. Kaufmann

HOERBIGER Ventilwerke,
Seestadtstraße 25,
Vienna 1220, Austria
e-mail: andreas.kaufmann@hoerbiger.com

T. Lindner-Silwester

HOERBIGER Ventilwerke,
Seestadtstraße 25,
Vienna 1220, Austria
e-mail: tino.lindner-silwester@hoerbiger.com

T. Antretter

Institute of Mechanics,
Montanuniversität Leoben,
Franz-Josef Straße 18,
Leoben 8700, Austria
e-mail: Thomas.antretter@unileoben.ac.at

1Corresponding author.

Contributed by the Tribology Division of ASME for publication in the JOURNAL OF TRIBOLOGY. Manuscript received November 2, 2017; final manuscript received December 21, 2017; published online xx xx, xxxx. Assoc. Editor: Stephen Boedo.

J. Tribol 140(4), 042201 (Jan 31, 2018) (7 pages) Paper No: TRIB-17-1414; doi: 10.1115/1.4038863 History: Received November 02, 2017; Revised December 21, 2017

The wear of dynamic sealing elements, i.e., elements that seal against a moving counter-surface, is highly complex. In dry-running reciprocating compressors, these sealing elements, commonly referred to as packing rings, have to seal the compressed gas against the environment along the reciprocating rod. Since the packing rings' seal effect arises from the differential pressure to be sealed, it is of paramount importance to take into account the gas pressure drop across the dynamic sealing surface. This paper presents a numerical model that allows us to calculate how the wear of such a packing ring evolves with time. An analytical solution is used to verify the numerical model.

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Fig. 1

Gas pressure and contact forces acting on a packing ring in a packing cup, neglecting friction forces

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Fig. 2

Worn axisymmetric ring at t=t1. (Left) Loaded worn ring (pressure p1 acting on outer diameter, contact pressure pC acting on inner diameter), assumed to be in a state of plane strain to make the problem analytically amenable. (Right) dimensions of the worn ring in the undeformed state.

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Fig. 5

The “wear box”

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Fig. 6

Scheme of the two interacting abaqus models used to calculate the sealing element wear

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Fig. 3

Change of wear gap (R(i)−D/2), accumulated wear w, and contact pressure pC over time for a ring with h0=8 mm on a rod of diameter D=57.16 mm. The ring wear stops before ring is fully worn away.

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Fig. 4

Change of wear gap (R(i)−D/2), accumulated wear w, and contact pressure pC over time for a ring with h0=5 mm on a rod of diameter D=57.16 mm. The ring wear continues until ring is fully worn away.

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Fig. 7

Variation of contact pressure pC with inner radius overD = 2 < R(i) < R(o) for different pressure loadings p1 (case A: p1 = 30 MPa, case B: p1 = 21.2 MPa and case C: p1 = 10 MPa)

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Fig. 8

Ultimate wear w∞ referred to initial ring height h0 for rings of different aspect ratios h0/D that are loaded by the nondimensional pressure p1/G

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Fig. 9

Numerical versus analytical results

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Fig. 10

Stresses along a radial path r¯ for different times

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Fig. 11

von Mises stress distribution. Time is advancing from left to right: left 2.8 h, middle 10.4 days, and right 20.8 days.

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Fig. 12

Wear-pattern evolution



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