In an externally adjustable fluid film bearing, the hydrodynamic conditions can be changed as required in a controlled manner. The principal feature of the bearing is the facility to adjust its radial clearance and circumferential film thickness gradient. Unlike a tilting pad bearing, this bearing can have radial adjustments. The tilt adjustments are obtained by providing flexibility to the pad at one corner. This paper deals with the effect of turbulence on the steady state performance characteristics of a centrally loaded 120 deg single pad externally adjustable fluid film bearing. The bearing has an aspect ratio of 1 and operates over a wide range of eccentricity ratios with different radial and tilt adjustments. The Reynolds equation is solved numerically using the finite difference method. The linearized turbulence model of Ng and Pan (1965, “A Linearized Turbulent Lubrication Theory,” ASME J. Basic Eng., 87, pp. 675–688) as well as the simplified adiabatic model of Pinkus and Bupara (1979, “Adiabatic Solutions for Finite Journal Bearings,” ASME J. Lubr. Technol., 101, pp. 492–496) are incorporated in the solution scheme. The static performance characteristics calculated are presented in terms of load carrying capacity, attitude angle, friction variable, and Sommerfeld number. A comparative study with the combination of adjustments predicts that the static performance of the bearing is superior with negative radial and tilt adjustments.

1.
Akkok
,
M.
, and
Ettles
,
C. M.
, 1980, “
The Effect of Grooving and Bore Shape on the Stability of Journal Bearings
,”
ASLE Trans.
0569-8197,
23
(
4
), pp.
431
441
.
2.
Schuller
,
F. T.
, 1975, “
Effect of Number of Lobes and Length-Diameter Ratio on the Stability of Tilted-Lobe Hydrodynamic Journal Bearings at Zero Load
,” NASA Technical Report No. TN-D-7902, p.
5
.
3.
Schuller
,
F. T.
, 1977, “
Stability Experiments With Hydrodynamic-Tilted Lobe Journal Bearings of Various Number of Lobes and Length-to-Diameter Ratios
,”
ASLE Trans.
0569-8197,
20
, pp.
271
281
.
4.
Malik
,
M.
,
Chandra
,
M.
, and
Sinhasan
,
R.
, 1981, “
Performance Characteristics of Titled Three-Lobe Journal Bearing Configurations
,”
Tribol. Int.
,
14
(
6
), pp.
345
350
. 0301-679X
5.
Malik
,
M.
,
Chandra
,
M.
, and
Sinhasan
,
R.
, 1981, “
Design Data for Three-Lobe Bearings
,”
ASLE Trans.
0569-8197,
24
(
3
), pp.
345
353
.
6.
Martin
,
J. K.
, 1999, “
A Mathematical Model and Numerical Solution Technique for a Novel Adjustable Hydrodynamic Bearing
,”
Int. J. Numer. Methods Fluids
0271-2091,
30
, pp.
845
864
.
7.
Martin
,
J. K.
, and
Parkins
,
D. W.
, 2002, “
Theoretical Studies of Continuously Adjustable Hydrodynamic Fluid Film Bearing
,”
ASME J. Tribol.
0742-4787,
124
, pp.
203
211
.
8.
Martin
,
J. K.
, 2002, “
Extended Expansion of the Reynolds Equation
,”
Proc. Inst. Mech. Eng., Part J: J. Eng. Tribol.
1350-6501,
216
(
1
), pp.
49
51
.
9.
Martin
,
J. K.
, 2004, “
Measuring the Performance of a Novel Fluid Film Bearing Supporting a Rotor on a Stationary Shaft, by Non-Contacting Means
,”
Proc. Inst. Mech. Eng., Part K: J. of Multi-body Dynamics
,
218
(
3
), pp.
143
151
.
10.
Hargreaves
,
D. J.
, 1995,
“Predicted Performance of a Tri-Taper Journal Bearing Including Turbulence and Misalignment Effects
,”
Proc. Inst. Mech. Eng., Part J: J. Eng. Tribol.
1350-6501,
209
, pp.
85
97
.
11.
Taylor
,
C. M.
, and
Dowson
,
D.
, 1974, “
Turbulent Lubrication Theory-Application to Design
,”
ASME J. Lubr. Technol.
0022-2305,
96
, pp.
36
47
.
12.
Ng
,
C. W.
, and
Pan
,
C. H. T.
, 1965, “
A Linearized Turbulent Lubrication Theory
,”
ASME J. Basic Eng.
0021-9223,
87
, pp.
675
688
.
13.
Pinkus
,
O.
, and
Bupara
,
S. S.
, 1979, “
Adiabatic Solutions for Finite Journal Bearings
,”
ASME J. Lubr. Technol.
0022-2305,
101
, pp.
492
496
.
14.
Pinkus
,
O.
, and
Sternlicht
,
B.
, 1961,
Theory of Hydrodynamic Lubrication
,
McGraw-Hill
,
New York
, Chap. 4.
15.
Szeri
,
A. Z.
, 1998,
Fluid Film Lubrication: Theory and Design
,
Cambridge University Press
,
Cambridge, UK
, Chap. 3.
You do not currently have access to this content.