Elastohydrodynamic (EHD) Lubrication

Lubrication Knowledge Menu

Elastohydrodynamic (EHD) Lubrication

Definition of EHD lubrication. The lubrication principles applied to rolling bodies, such as ball or roller bearings, is known as elastohydrodynamic (EHD) lubrication.

Rolling body lubrication. Although lubrication of rolling objects operates on a considerably different principle than sliding objects, the principles of hydrodynamic lubrication can be applied, within limits, to explain lubrication of rolling elements. An oil wedge, similar to that which occurs in hydrodynamic lubrication, exists at the lower leading edge of the bearing. Adhesion of oil to the sliding element and the supporting surface increases pressure and creates a film between the two bodies. Because the area of contact is extremely small in a roller and ball bearing, the force per unit area, or load pressure, is extremely high. Roller bearing load pressures may reach 34,450 kPa (5000 lb/sq in) and ball bearing load pressures may reach 689,000 kPa (1,000,000 lb/sq in). Under these pressures, it would appear that the oil would be entirely squeezed from between the wearing surfaces. However, viscosity increases that occur under extremely high pressure prevent the oil from being entirely squeezed out. Consequently, a thin film of oil is maintained.

Effect of film thickness and roughness.

The roughness of the wearing surfaces is an important consideration in EHD lubrication. Roughness is defined as the arithmetic average of the distance between the high and low points of a surface, and is sometimes called the centerline average (CLA).

As film thickness increases in relation to roughness fewer asperities make contact. Engineers use the ratio of film thickness to surface roughness to estimate the life expectancy of a bearing system. The relation of bearing life to this ratio is very complex and not always predictable. In general, life expectancy is extended as the ratio increases. Full film thickness is considered to exist when the value of this ratio is between 2 and 4. When this condition prevails, fatigue failure is due entirely to subsurface stress. However, in most industrial applications, a ratio between 1 and 2 is achieved. At these values surface stresses occur, and asperities undergo stress and contribute to fatigue as a major source of failure in antifriction bearings.

Contribute Article Spider Optimizer

© Copyright 2000 - 2018, by Engineers Edge, LLC www.engineersedge.com
All rights reserved
Disclaimer | Feedback
Advertising | Contact | Privacy Policy


Spider Optimizer

Engineering Book Store
Engineering Forum
Excel App. Downloads
Online Books & Manuals
Engineering News
Engineering Videos
Engineering Calculators
Engineering Toolbox
GD&T Training Geometric Dimensioning Tolerancing
DFM DFA Training
Training Online Engineering
Advertising Center

Copyright Notice

Publishing Program