The assumption of the hydrodynamic lubrication theory is that the viscosity of the lubricant is equal, that is, the viscosity of the lubricating oil does not change with the change of pressure at a certain temperature; Under the action of load and oil film pressure, the elastic deformation is not considered.
| STE0800W180N | RIE0170F010N | RIE0230P010N |
| STE1000W180N | RIE0230F010N | RIE0300P010N |
| STE1200W180N | RIE0300F010N | RIE0400P010N |
| RAE0040F005N | RIE0400F010N | RIE0500P010N |
Under the above assumptions, for general non-heavy load (contact pressure at 15MPa) sliding bearings, this assumption is close to the actual situation.

However, when the contact pressure between the rolling bearing and the gear surface increases to 400~1500MPa, the above assumptions are different from the actual situation.
At this time, the deformation of the friction surface can reach several times the thickness of the oil film, and the elastic deformation of the lubricated metal friction surface and the change of the viscosity of the lubricating oil with the pressure are two factors to study and calculate the formation law and thickness of the oil film, the cross-sectional shape and shape of the oil film. The pressure distribution in the oil film is more realistic and this kind of lubrication is called elastohydrodynamic lubrication.
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