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Research Papers: Hydrodynamic Lubrication

Design of Hybrid Hydrostatic/Hydrodynamic Journal Bearings for Optimum Self-Compensation Under Misaligning External Loads

[+] Author and Article Information
L. F. Martinez Esparza

Mem. ASME
College of Aeronautics,
Embry-Riddle Aeronautical
University-Worldwide,
P. O. Box 3891,
Chinle, AZ 86503
e-mail: martil24@erau.edu

J. G. Cervantes de Gortari

Fellow ASME
Facultad de Ingeniería,
Universidad Nacional Autónoma de México,
Ciudad Universitaria,
Coyoacán, D. F. 04510, México
e-mail: jgonzalo@unam.mx

E. J. Chicurel Uziel

Mem. ASME
Instituto de Ingeniería,
Universidad Nacional Autónoma de México,
Ciudad Universitaria,
Coyoacán, D. F. 04510, México
e-mail: ecu@pumas.iingen.unam.mx

1Corresponding author.

Contributed by the Tribology Division of ASME for publication in the JOURNAL OF TRIBOLOGY. Manuscript received August 1, 2016; final manuscript received October 22, 2016; published online April 4, 2017. Assoc. Editor: Joichi Sugimura.

J. Tribol 139(4), 041702 (Apr 04, 2017) (12 pages) Paper No: TRIB-16-1238; doi: 10.1115/1.4035157 History: Received August 01, 2016; Revised October 22, 2016

A method to design hybrid hydrostatic/hydrodynamic journal bearings, with the criterion of optimized self-compensation under misaligning loads, is presented. An analysis considering laminar and turbulent flow of a Newtonian incompressible lubricant between the bearing and a misaligned shaft, with restricted lubricant supply to each recess, is discussed. The mathematical model considers the modified steady-state Reynolds lubrication equation, an exact function for the local bearing radial clearance with a misaligned shaft, the continuity integral–differential equations at the recess limits, and boundary conditions at the cavitation zone and outer limits. The finite-difference method was used, and a modular computer program was developed. The procedure follows a univariate search to determine the optimum size and position of recesses and therefore obtain the design with the maximum reactive moment under misaligning loads. A validation of the model was obtained comparing the results with experimental and calculated data from the literature. Results for a 4 + 4 LBP hybrid bearing design are presented.

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References

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Figures

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Fig. 1

Reference systems, eccentric-misaligned journal

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Fig. 2

Reference systems, misalignment angles

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Fig. 3

Cross section parallel to plane X-Y at a point G of Fig. 2

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Fig. 4

Lubrication system, manifold at constant pressure ps

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Fig. 5

Computer program flow diagram

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Fig. 6

Relative eccentricity versus Sommerfeld number, hydrodynamic partial bearing, comparison with experimental data [24]

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Fig. 7

Relative eccentricity versus specific load, hydrodynamic partial bearing. This model's results and experimental data from Ref. [24].

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Fig. 8

Maximum approach angle versus relative eccentricity, hydrodynamic partial bearing, comparison with experimental data [24]

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Fig. 9

This model's sample pressure distribution hydrodynamic partial bearing with cavitation zone

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Fig. 10

Hydrostatic bearing, 4 recesses, LOP, 4 axial slots [25]

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Fig. 11

Dimensionless load capacity and dimensionless lubricant flow versus relative eccentricity, comparison with data from Ref. [25]

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Fig. 12

This model's pressure distribution, hydrostatic bearing, 4 recesses, LOP, 4 axial slots between recesses

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Fig. 13

Hybrid bearing, 4 + 4 recesses, LBP

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Fig. 14

Moment of force versus recess relative axial position

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Fig. 15

Dimensionless moment and ε versus relative recess axial position

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Fig. 16

Dimensionless moment and ε versus recess relative axial length

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Fig. 17

Dimensionless moment and ε versus recess relative width

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Fig. 18

Dimensionless moment and ε versus recess angular position

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Fig. 19

Dimensionless moment and ε versus restrictor's capillary resistance

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Fig. 20

Dimensionless moments and ε versus Sommerfeld number

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Fig. 21

Dimensionless flow and ε versus Sommerfeld number

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Fig. 22

This model's pressure distribution, hybrid bearing, and design for optimum self-compensation based on Fig. 13, view 1. S=0.5433,pmax=23.5 MPa.

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Fig. 23

This model's pressure distribution, hybrid bearing, and design for optimum self-compensation based on Fig. 13, view 2. S=0.5433,pmax=23.5 MPa.

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Fig. 24

This model misaligned radial clearance distribution, hybrid bearing, design from Fig. 13

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