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Oil flow in plain journal bearings

Oil flow in plain journal bearings I t is further recognised that, for any given type of oil-feed design, the two oil-flow components are related to bearing dimensions and operating variables. oil flow in plain This relationship may be expressed by the following dimensionless equations : journal bearings A SIMPLIFIED method of analysis for the rate of oil flow in plain journal bearings has been developed by S. A. McKee, head of the National Bureau of Standards (U.S.A.) engines and lubrication where μ=absolute viscosity of the lubricant at laboratory. This problem is important to bearing atmospheric pressure and bearing temperature, design and operation ; an adequate oil flow is essential p=oil-feed, P=load per unit projected bearing area, to insure not only the maintenance of a load-carrying N=spee d of journal, D=journal diameter, L=bear- oil film, but also the disposal of frictional heat ing length, and C=diametral bearing clearance. developed in the bearing. The new method (1) indicates that flow of oil from As indicated above, the functions Ψ , and Ψ 1 2 the ends of plain journal bearings fed through an oil depend upon the oil-feed design of the bearing. These hole, an axial groove on the unloaded side, or a have been determined experimentally for three basic circumferential groove may be affected by two designs : (1) one oil hole on the unloaded side of the bearing, (2) an axial groove on the unloaded side of factors. One results from the oil-feed pressure, and the bearing, and (3) a circumferential groove. The results may be shown graphically by plotting the parameter containing Q" against the Sommerfeld number, S=(μN/P) (D/C)2 and by plotting the parameter containing Q' against the reciprocal of the Sommerfeld number. I n obtaining the above information, it is necessary to separate the observed total oil flow, Q, into its components Q' and Q". For this purpose, a simple method was used. Briefly, the separation is done by plotting Qμ against p for constant values of μN/P . On such a plot, the data for each value of μN/ P fall on a straight line, the slope of which is equal to Q'μ/p, while the intercept at p= 0 equals Q"μ. I t is of interest to note tha t in the case of a bearing with a circumferential groove, the oil flow due to hydrodynamic-film pressure is negligible. However, the other from the hydrody- namic-film pressure supporting the load. In the case of a bearing with a circumferential groove, the flow due to the hydrodynamic-film pressure is negligible in comparison with tha t due t o th e oil-feed pressure. For the other two types of bearings, however, both causes produce appreciable flow. I n the present work, analy­ tical simplicity is achieved by postulating that the rate of oil flow, Q, is made up of two components, as follows: for the other two oil-feed arrangements, this com­ ponent is quite significant. Q=Q'+Q " (l) The good correlation of the parameter Q"μ/PC3 where Q' is the flow rate caused by the oil feed with Sommerfeld number, at different clearances, is pressure and Q" is the flow rate produced by the noteworthy. The differences obtained with bearings hydrodynamic-film pressure supporting the load. of different clearances when plotting Q'μ/pC3 against the reciprocal of Sommerfeld number are attributed to bearing out-of-roundness caused chiefly by (1) "Oil flow in plain journal bearings," S.A. McKee, A.S.M.E. Annua l Meeting, November 25-30, 1951. deformations under load. Scientific LUBRICATION May, 1952 35 http://www.deepdyve.com/assets/images/DeepDyve-Logo-lg.png Industrial Lubrication and Tribology Emerald Publishing

Oil flow in plain journal bearings

Industrial Lubrication and Tribology , Volume 4 (5): 1 – May 1, 1952

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Publisher
Emerald Publishing
Copyright
Copyright © Emerald Group Publishing Limited
ISSN
0036-8792
DOI
10.1108/eb052174
Publisher site
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Abstract

I t is further recognised that, for any given type of oil-feed design, the two oil-flow components are related to bearing dimensions and operating variables. oil flow in plain This relationship may be expressed by the following dimensionless equations : journal bearings A SIMPLIFIED method of analysis for the rate of oil flow in plain journal bearings has been developed by S. A. McKee, head of the National Bureau of Standards (U.S.A.) engines and lubrication where μ=absolute viscosity of the lubricant at laboratory. This problem is important to bearing atmospheric pressure and bearing temperature, design and operation ; an adequate oil flow is essential p=oil-feed, P=load per unit projected bearing area, to insure not only the maintenance of a load-carrying N=spee d of journal, D=journal diameter, L=bear- oil film, but also the disposal of frictional heat ing length, and C=diametral bearing clearance. developed in the bearing. The new method (1) indicates that flow of oil from As indicated above, the functions Ψ , and Ψ 1 2 the ends of plain journal bearings fed through an oil depend upon the oil-feed design of the bearing. These hole, an axial groove on the unloaded side, or a have been determined experimentally for three basic circumferential groove may be affected by two designs : (1) one oil hole on the unloaded side of the bearing, (2) an axial groove on the unloaded side of factors. One results from the oil-feed pressure, and the bearing, and (3) a circumferential groove. The results may be shown graphically by plotting the parameter containing Q" against the Sommerfeld number, S=(μN/P) (D/C)2 and by plotting the parameter containing Q' against the reciprocal of the Sommerfeld number. I n obtaining the above information, it is necessary to separate the observed total oil flow, Q, into its components Q' and Q". For this purpose, a simple method was used. Briefly, the separation is done by plotting Qμ against p for constant values of μN/P . On such a plot, the data for each value of μN/ P fall on a straight line, the slope of which is equal to Q'μ/p, while the intercept at p= 0 equals Q"μ. I t is of interest to note tha t in the case of a bearing with a circumferential groove, the oil flow due to hydrodynamic-film pressure is negligible. However, the other from the hydrody- namic-film pressure supporting the load. In the case of a bearing with a circumferential groove, the flow due to the hydrodynamic-film pressure is negligible in comparison with tha t due t o th e oil-feed pressure. For the other two types of bearings, however, both causes produce appreciable flow. I n the present work, analy­ tical simplicity is achieved by postulating that the rate of oil flow, Q, is made up of two components, as follows: for the other two oil-feed arrangements, this com­ ponent is quite significant. Q=Q'+Q " (l) The good correlation of the parameter Q"μ/PC3 where Q' is the flow rate caused by the oil feed with Sommerfeld number, at different clearances, is pressure and Q" is the flow rate produced by the noteworthy. The differences obtained with bearings hydrodynamic-film pressure supporting the load. of different clearances when plotting Q'μ/pC3 against the reciprocal of Sommerfeld number are attributed to bearing out-of-roundness caused chiefly by (1) "Oil flow in plain journal bearings," S.A. McKee, A.S.M.E. Annua l Meeting, November 25-30, 1951. deformations under load. Scientific LUBRICATION May, 1952 35

Journal

Industrial Lubrication and TribologyEmerald Publishing

Published: May 1, 1952

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