Research Papers: Hydrodynamic Lubrication

Optimization of Journal Bearing Profiles With Respect to Stiffness and Load-Carrying Capacity

[+] Author and Article Information
Christoph Weißbacher

Gleitlagertechnik Weißbacher GmbH,
Weseler Straße 32,
Alpen 46519, Germany
e-mail: cweissbacher@gtwalpen.de

Christian Schellnegger

Andritz Hydro GmbH,
Dr. Karl-Widdmann-Straße 5,
Weiz 8160, Austria
e-mail: christian.schellnegger@andritz.com

Alexander John

Andritz Hydro GmbH,
Dr. Karl-Widdmann-Straße 5,
Weiz 8160, Austria
e-mail: alexander.john@andritz.com

Thomas Buchgraber

Andritz Hydro GmbH,
Dr. Karl-Widdmann-Straße 5,
Weiz 8160, Austria
e-mail: thomas.buchgraber@andritz.com

Walter Pscheidt

Andritz Hydro GmbH,
Dr. Karl-Widdmann-Straße 5,
Weiz 8160, Austria
e-mail: walter.pscheidt@andritz.com

1Corresponding author.

Contributed by the Tribology Division of ASME for publication in the JOURNAL OF TRIBOLOGY. Manuscript received December 23, 2013; final manuscript received March 16, 2014; published online May 6, 2014. Assoc. Editor: Daniel Nélias.

J. Tribol 136(3), 031709 (May 06, 2014) (6 pages) Paper No: TRIB-13-1258; doi: 10.1115/1.4027399 History: Received December 23, 2013; Revised March 16, 2014

This paper presents an optimization algorithm for journal bearing profiles with respect to stiffness and load-carrying capacity and an application example of the same. An analytical approach for finding the optimum is derived. How the optimization procedure works when using numerical calculation tools is briefly explained. The application example is introduced and the expected performance of the optimized bearing profile is compared to the expected performance of state-of-the-art bearing profiles. Finally, the measured bearing performance data is compared to the expected values. The findings indicate the effectiveness of the introduced optimization algorithm.

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Fig. 1

Typical, with COMBROS [11] numerically calculated, pressure distributions of the cylindrical (solid line), four-lobe-bore (dashed line), and four pad tilting pad bearing (dotted line). The load direction is 180 deg for all cases.

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Fig. 2

General description of a two-lobe-bore bearing profile with load on an oil supply pocket. The direction of rotation is counterclockwise.

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Fig. 3

Optimum profile offset angle αopt for Ψs=2 (gray) and Ψs=3 (black) and B/D=0.5 (dotted lines) B/D=0.75 (dashed lines) and B/D=1 (solid lines)

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Fig. 4

Reisseck II rotor with the bearings mounted. The rotor outer diameter is 3202 mm, the rotor length 8705 mm, and the rotor mass 186,082 kg.

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Fig. 5

Bearing metal temperature measurement positions. Both temperature sensors are situated approximately 17 mm below the Babbitt surface.

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Fig. 6

Comparison of the bearing metal temperatures T1 and T2 as predicted (solid dark gray/dashed light gray lines) and measured (dark gray diamonds/light gray squares) for the DE bearing (top) and NDE bearing (bottom)

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Fig. 7

Bearing Babbitt surface at the minimum oil film position after the first centrifuging run

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Fig. 8

Shaft vibration measurement setup close to the DE bearing, highlighted by the white box

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Fig. 9

Absolute shaft vibration measurement results at the DE (top) and NDE (bottom) bearing positions for the rotation frequency (light gray), the first harmonic (dark gray) and the sum of all frequencies (black)



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