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Research Papers: Hydrodynamic Lubrication

Three-Dimensional Thermo-Elasto-Hydrodynamic Computational Fluid Dynamics Model of a Tilting Pad Journal Bearing—Part I: Static Response

[+] Author and Article Information
Jongin Yang

Mem. ASME
Department of Mechanical Engineering,
Texas A&M University,
College Station, TX 77840
e-mail: jiyang@tamu.edu

Alan Palazzolo

James J. Cain Professor I
Fellow ASME
Department of Mechanical Engineering,
Texas A&M University,
College Station, TX 77840
e-mail: a-palazzolo@tamu.edu

Contributed by the Tribology Division of ASME for publication in the Journal of Tribology. Manuscript received October 26, 2018; final manuscript received March 27, 2019; published online April 30, 2019. Assoc. Editor: Stephen Boedo.

J. Tribol 141(6), 061702 (Apr 30, 2019) (21 pages) Paper No: TRIB-18-1447; doi: 10.1115/1.4043349 History: Received October 26, 2018; Accepted March 28, 2019

This paper presents the first simulation model of a tilting pad journal bearing (TPJB) using three-dimensional (3D) computational fluid dynamics (CFD), including multiphase flow, thermal-fluid, transitional turbulence, and thermal deformation of the shaft and pads employing two-way fluid–structure interaction (FSI). Part I presents a modeling method for the static performance. The model includes flow between pads BP, which eliminates the use of an uncertain, mixing coefficient (MC) in Reynold's equation approaches. The CFD model is benchmarked with Reynold's model with a 3D thermal-film, when the CFD model boundary conditions are consistent with the Reynolds boundary conditions. The Reynolds model employs an oversimplified MC representation of the three-dimensional mixing effect of the BP flow and heat transfer, and it also employs simplifying assumptions for the flow and heat transfer within the thin film between the journal and bearing. This manufactured comparison shows good agreement between the CFD and Reynold's equation models. The CFD model is generalized by removing these fictitious boundary conditions on pad inlets and outlets and instead models the flow and temperature between pads. The results show that Reynold's model MC approach can lead to significant differences with the CFD model including detailed flow and thermal modeling between pads. Thus, the CFD approach provides increased reliability of predictions. The paper provides an instructive methodology including detailed steps for properly applying CFD to tilt pad bearing modeling. Parts I and II focus on predicting static and dynamic response characteristic responses, respectively.

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Figures

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Fig. 2

Computation structure of the FSI-CFD TPJB model for the static response

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Fig. 1

Configuration of tilting pad journal bearing model: (a) assembled view and (b) exploded view

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Fig. 3

Illustration of a typical moving node: (a) tilting and pivot motion of a pad and (b) translational motion of a shaft

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Fig. 7

Geometry and mesh of example TPJB: (a) overview (427,558 elements), (b) exploded view (scaled factor; shaft 0.7, fluid-film 0.9), (c) xy view, and (d) xz view

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Fig. 9

Eccentricity and attitude angle for “without mixing effect” model and (a) case A, (b) case B, and (c) case C effects

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Fig. 10

Drag torque and side leakage for “without mixing effect” model and (a) case A, (b) case B, and (c) case C effects

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Fig. 12

Eccentricity for “with mixing effect” model and (a) case A, (b) case B, and (c) case C effects

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Fig. 6

Geometry of example tilting pad journal bearing TPJB

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Fig. 8

BP subdomain CFD model for the “with and without mixing effect” cases: (a) without mixing effect and (b) with mixing effect

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Fig. 11

Shaft average and pad maximum temperature for “without mixing effect” model and (a) case A, (b) case B, and (c) case C effects

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Fig. 4

Boundary conditions imposed in the TPJB model

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Fig. 5

FSI-CFD TPJB modeling procedure for the static response

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Fig. 23

Surface temperature contours “with mixing effect” at 3000 rpm: (a) overview, (b) x–y view, and (c) x–z view

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Fig. 24

Surface temperature contours “with mixing effect” condition at 15,000 rpm: (a) overview, (b) x–y view, and (c) x–z view

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Fig. 13

Attitude angle for “with mixing effect” model and (a) case A, (b) case B, and (c) case C effects

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Fig. 14

Drag torque for “with mixing effect” model and (a) case A, (b) case B, and (c) case C effects

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Fig. 15

Side leakage of “with mixing effect” condition: (a) case A, (b) case B, and (c) case C

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Fig. 16

Shaft average temperature of “with mixing effect” condition: (a) case A, (b) case B, and (c) case C

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Fig. 17

Maximum pad temperature of “with mixing effect” condition: (a) case A, (b) case B, and (c) case C

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Fig. 18

CFD shaft surface contours “with mixing effect” condition at 3000 rpm: (a) pressure, (b) shear stress, and (c) heat flux

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Fig. 19

CFD shaft surface contours “with mixing effect” condition at 15,000 rpm: (a) pressure, (b) shear stress, and (c) heat flux

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Fig. 20

Pressure distribution “with mixing effect” condition: (a) 3000 rpm and (b) 15,000 rpm

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Fig. 21

Film Thickness “with mixing effect” condition: (a) 3000 rpm and (b) 15,000 rpm

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Fig. 22

Heat flux and temperature at shaft surface “with mixing effect”: (a) heat flux (w/m2), (b) circumferentially averaged heat flux distribution, (c) temperature (°C), and (d) circumferentially averaged temperature distribution

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Fig. 25

Velocity vector field and eddy viscosity contour between pads 1 and 5: (a) 3000 rpm and (b) 15,000 rpm

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