scholarly journals Discussion: “Numerical Analysis of the Gas-Lubricated Spiral-Groove Thrust Bearing-Compressor” (James, D. D., and Potter, A. F., 1967, ASME J. Lubr. Technol., 89, pp. 439–443)

1967 ◽  
Vol 89 (4) ◽  
pp. 444-444
Author(s):  
J. H. Vohr
Keyword(s):  
Numerical Analysis ◽  
Thrust Bearing ◽  
Spiral Groove

Numerical Analysis of the Gas-Lubricated Spiral-Groove Thrust Bearing-Compressor

1967 ◽  
Vol 89 (4) ◽  
pp. 439-443 ◽  
Author(s):  
D. D. James ◽  
A. F. Potter
Keyword(s):  
Numerical Analysis ◽  
Gas Flow ◽  
Thrust Bearing ◽  
Graphical Form ◽  
Spiral Groove ◽  
Thrust Bearings ◽  
Performance Curves ◽  
Difference Form ◽  
Compressor Efficiency ◽  
Film Lubrication

The isothermal Reynolds differential equation of gas film lubrication is written in finite-difference form for numerical analysis of the pressure distribution within spiral-groove thrust bearings and compressors. Appropriate jump equations are presented which provide flow continuity at the land-to-groove interfaces. Gas flow, load support, static stiffness, power consumption, and compressor efficiency are computed and theoretical performance curves are presented for this device. Agreement between computed data and experiment is discussed and presented in graphical form.

The Numerical Analysis of the Velocity and Pressure Distribution of the Oil Film in Heavy Hydrostatic Thrust Bearing

2014 ◽  
Vol 541-542 ◽  
pp. 658-662
Author(s):  
Jian Li ◽  
Yuan Chen ◽  
Yang Chun Yu ◽  
Zhu Xin Tian ◽  
Yu Huang
Keyword(s):  
Mathematical Model ◽  
Numerical Analysis ◽  
Pressure Distribution ◽  
Working Conditions ◽  
Thrust Bearing ◽  
Rotation Speed ◽  
The Other ◽  
Surface Load ◽  
Oil Film ◽  
Volume Method

To study the velocity and pressure distribution of the oil film in a heavy hydrostatic thrust bearing, a mathematical model of the velocity is proposed and the finite volume method (FVM) has been used to simulate the flow field under different working conditions. Some pressure experiments were carried out and the results verified the correctness of the simulation. It is concluded that the pressure distribution varies small under different rotation speed when the surface load on the workbench is constant. But the velocity of the oil film is influenced greatly by the rotation speed. When the rotation speed of the workbench is as quick as enough, the velocity of the oil film on one radial side of the pad will be zero, that is to say the lubrication oil will be drained from the other three sides of the recess.

The Influence of Ambient Pressure on the Measured Load Capacity of Bump-Foil and Spiral-Groove Gas Thrust Bearings at Ambient Pressures up to 69 Bar on a Novel High-Pressure Gas Bearing Test Rig

2019 ◽  
Author(s):  
Jason Wilkes ◽  
Ryan Cater ◽  
Erik Swanson ◽  
Kevin Passmore ◽  
Jerry Brady
Keyword(s):  
Power Loss ◽  
Thrust Bearing ◽  
Load Capacity ◽  
Ambient Pressure ◽  
Spiral Groove ◽  
Test Rig ◽  
Thrust Bearings ◽  
Order Of Magnitude ◽  
Foil Thrust Bearing ◽  
Thrust Load

Abstract This paper will show the influence of ambient pressure on the thrust capacity of bump-foil and spiral-groove gas thrust bearings. The bearings were operating in nitrogen at various pressures up to 69 bar, and were tested to failure. Failure was detected at various pressures by incrementally increasing the thrust load applied to the thrust bearing until the bearing was no longer thermally stable, or until contact was observed by a temperature spike measured by thermocouples within the bearing. These tests were performed on a novel thrust bearing test rig that was developed to allow thrust testing at pressures up to 207 bar cavity pressure at 260°C while rotating at speeds up to 120,000 rpm. The test rig floats on hydrostatic air bearings to allow for the direct measurement of applied thrust load through linkages that connect the stationary thrust loader to the rotor housing. Test results on a 65 mm (2.56 in) bump-foil thrust bearing at 100 krpm show a marked increase in load capacity with gas density, which has not previously been shown experimentally. Results also show that the load capacity of a similarly sized spiral-groove thrust bearing are relatively insensitive to pressure, and supported an order-of-magnitude less load than that observed for the bump-foil thrust bearing. These results are compared with analytical predictions, which agree reasonably with the experimental results. Predicted power loss is also presented for the bump-foil bearing; however, measured power loss was substantially higher.

Influence of Groove Molded Lines on the Lubrication Performance of Water-Lubricated Spiral Groove Thrust Bearings

2013 ◽  
Vol 694-697 ◽  
pp. 538-542 ◽  
Author(s):  
Xiao Yan Liu ◽  
Jia Sheng Wang
Keyword(s):  
Fluid Dynamics ◽  
Computational Fluid Dynamics ◽  
Thrust Bearing ◽  
Pressure Field ◽  
Load Capacity ◽  
Loading Capacity ◽  
Spiral Groove ◽  
Thrust Bearings ◽  
Pressure Fields ◽  
Lubrication Performance

The water lubrication performance of spiral groove thrust bearings was affected by different groove molded lines. The pressure fields and the load capacity of water-lubricated spiral groove thrust bearings with different groove molded lines were simulated by computational fluid dynamics. The results show that the spiral groove which can produce the best loading capacity and steadier pressure field is appropriate to water-lubricated spiral groove thrust bearing. The line spiral groove can be used for decrease the process difficult when the loading capacity require is low.

Numerical analysis on nanoparticles-laden gas film thrust bearing

2013 ◽  
Vol 26 (4) ◽  
pp. 675-679 ◽  
Author(s):  
Zhiru Yang ◽  
Dongfeng Diao ◽  
Lei Yang
Keyword(s):  
Numerical Analysis ◽  
Thrust Bearing
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