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Bonding of metal lubricant films by ion plating
358
SYSTEMATICABSTRACTS OF CURRENT LITERATURE
fluids are discussed together with the areas in which they are most applicable. 3.3. Solid lubricants Bondiig
of Metal Lubricant Films by Ion Platiug. T. Spalvins, Lubrication Eng., 27 (2) (1971) 4@46; 13 figs., 12 refs. In ion plating the high energy of the plasma and the high kinetic energy of the depositing material form very adherent fiis on surfaces cleaned by sputter etching. Due to the high velocity of the evaporant the surfaces penetrated and a graded interface is formed. The type’ and structure of the interface was examined by electron microscopy. Adherence was tested by friction and tensile tests. When specimens are elongated the film plastically flows with no indication of separation or peeling of the film. Films of Ni, Au, Ti and Pb were examined. Friction and Wear Characteristics of Lubricative Composites ia Air and Vacuum. J. R. Jones and M. N. Gardos, Lubrication Eng., 27 (2) (1971) 47-53; 6 figs., 4 tables, 10 refs. The friction and wear behaviour of several commercially available self lubricating composites were studied under oscillating sliding contact with metals in both air and vacuum. Differences in friction in air and vacuum and dependence on speed were found to be characteristic of the different materials. The extent of wear was indicated by microscopical examination. The lowest wear occurred with composites containing major portions of MoS,. The heaviest wear occurred with composites containing neither MoS, nor P.T.F.E. Inflnesrce of Film Tbkkaess 08 the Performance of Solid Lubricant9. H. J. Sauer, R. E. Schowalter and S. V. Mahate, Lubrication Eng., 27 (4) (1971) 1 l&114; 3 tables, 8 refs.
5 figs.,
Using alpha LFW-1 and Falex lubricant testers results show that the film thickness is an important factor in the performance of a solid lubricant. Coefftcient of friction increased with increase in film thickness in the range 0.0007 to 0.017 inch. There was an optimum film thickness for maximum wear life. The Solid Lubricatioa of Ball Bear&s underHigh Speed-High Load Conditions from -225 to + IOOO’F. D. J. Boes, J. S. Cunningham and M. R. Chasman, Lubrication Eng., 27 (5) (1971) 15@-159; 3 figs., 8 tables, 10 refs. Wear, 19 (1972) 355-367
The paper reports the development of ball bearing systems capable of long term operation in the temperature range -225 to + 1000°F and speeds up to 20,000 r.p.m. lubricated by retainers fabricated from a solid lubricantgallium/indium and Teflon tilled silver matrix composite.
4. MACHINE
PARTS
4.1. Bearings Analysis of Bearing Vibratioa. E. Yhland and L. Johansson, Aircraft Eng., 42 (12) (1970) 18-20; 3 figs.
A discussion ofthe various methods ofmonitoring bearing performance. These provide health checks on bearings without the need for dismantling machinery and can detect bearing damage at an early stage to avoid catastrophic failure. Ball Bearings with Self Lubricating Cages. N. A. Spitsyn et al., Russian Eng. J., 50 (6) (1970) 28-30; 1 fig. 2 tables. (Transl. by P.E.R.A. of Gt. Britain of Vestn. Mashirzostr., 50 (6) (1970) 23-25.)
Types of self lubricating ball bearings and their functions are considered. The physical and mechanical properties of self lubricating cage materials are given. Surface treatments are described. Ball bearing designs are outlined. Test results and recommendations regarding bearing applications are discussed. Fluid Frictioa Plain Bearing with Increased Load Carrying Capacity. F. P. Snegovskii and V. I. Kozlov, Russian Eng. J., 50 (6) (1970) 3&33; 5 figs., 3 refs. (Transl. by P.E.R.A. of Gt. Britain of Vestn. Mashinostr., 50 (6) (1970) 25-28.)
Bearing tests under laboratory and service conditions are given. It is shown that under certain conditions of peripheral speed hydrostaticdynamic bearings have a load-carrying capacity of almost three times that of hydrodynamic bearings and that they dissipate less power. Computer Programme for Dynamically Loaded Journal Bearings. C. A. Perkins, Tribology, 4 (1) (1971) 29-30; 2 figs., 1 ref. The programme computes values of film thickness, pressure and power absorbed from input information supplied by the designer in a form acceptable to the computer.
SYSTEMATICABSTRACTS OF CURRENT LITERATURE
fluids are discussed together with the areas in which they are most applicable. 3.3. Solid lubricants Bondiig
of Metal Lubricant Films by Ion Platiug. T. Spalvins, Lubrication Eng., 27 (2) (1971) 4@46; 13 figs., 12 refs. In ion plating the high energy of the plasma and the high kinetic energy of the depositing material form very adherent fiis on surfaces cleaned by sputter etching. Due to the high velocity of the evaporant the surfaces penetrated and a graded interface is formed. The type’ and structure of the interface was examined by electron microscopy. Adherence was tested by friction and tensile tests. When specimens are elongated the film plastically flows with no indication of separation or peeling of the film. Films of Ni, Au, Ti and Pb were examined. Friction and Wear Characteristics of Lubricative Composites ia Air and Vacuum. J. R. Jones and M. N. Gardos, Lubrication Eng., 27 (2) (1971) 47-53; 6 figs., 4 tables, 10 refs. The friction and wear behaviour of several commercially available self lubricating composites were studied under oscillating sliding contact with metals in both air and vacuum. Differences in friction in air and vacuum and dependence on speed were found to be characteristic of the different materials. The extent of wear was indicated by microscopical examination. The lowest wear occurred with composites containing major portions of MoS,. The heaviest wear occurred with composites containing neither MoS, nor P.T.F.E. Inflnesrce of Film Tbkkaess 08 the Performance of Solid Lubricant9. H. J. Sauer, R. E. Schowalter and S. V. Mahate, Lubrication Eng., 27 (4) (1971) 1 l&114; 3 tables, 8 refs.
5 figs.,
Using alpha LFW-1 and Falex lubricant testers results show that the film thickness is an important factor in the performance of a solid lubricant. Coefftcient of friction increased with increase in film thickness in the range 0.0007 to 0.017 inch. There was an optimum film thickness for maximum wear life. The Solid Lubricatioa of Ball Bear&s underHigh Speed-High Load Conditions from -225 to + IOOO’F. D. J. Boes, J. S. Cunningham and M. R. Chasman, Lubrication Eng., 27 (5) (1971) 15@-159; 3 figs., 8 tables, 10 refs. Wear, 19 (1972) 355-367
The paper reports the development of ball bearing systems capable of long term operation in the temperature range -225 to + 1000°F and speeds up to 20,000 r.p.m. lubricated by retainers fabricated from a solid lubricantgallium/indium and Teflon tilled silver matrix composite.
4. MACHINE
PARTS
4.1. Bearings Analysis of Bearing Vibratioa. E. Yhland and L. Johansson, Aircraft Eng., 42 (12) (1970) 18-20; 3 figs.
A discussion ofthe various methods ofmonitoring bearing performance. These provide health checks on bearings without the need for dismantling machinery and can detect bearing damage at an early stage to avoid catastrophic failure. Ball Bearings with Self Lubricating Cages. N. A. Spitsyn et al., Russian Eng. J., 50 (6) (1970) 28-30; 1 fig. 2 tables. (Transl. by P.E.R.A. of Gt. Britain of Vestn. Mashirzostr., 50 (6) (1970) 23-25.)
Types of self lubricating ball bearings and their functions are considered. The physical and mechanical properties of self lubricating cage materials are given. Surface treatments are described. Ball bearing designs are outlined. Test results and recommendations regarding bearing applications are discussed. Fluid Frictioa Plain Bearing with Increased Load Carrying Capacity. F. P. Snegovskii and V. I. Kozlov, Russian Eng. J., 50 (6) (1970) 3&33; 5 figs., 3 refs. (Transl. by P.E.R.A. of Gt. Britain of Vestn. Mashinostr., 50 (6) (1970) 25-28.)
Bearing tests under laboratory and service conditions are given. It is shown that under certain conditions of peripheral speed hydrostaticdynamic bearings have a load-carrying capacity of almost three times that of hydrodynamic bearings and that they dissipate less power. Computer Programme for Dynamically Loaded Journal Bearings. C. A. Perkins, Tribology, 4 (1) (1971) 29-30; 2 figs., 1 ref. The programme computes values of film thickness, pressure and power absorbed from input information supplied by the designer in a form acceptable to the computer.