- Email: [email protected]
Rolling bearings in machines for cold bending sheet metal
SYSTEMATIC
ABSTRACTS
OF CURRENT
LITERATURE
nal bearings were investigated numerically by Runge Kutto extrapolation techniques. Variations in L/D between 0.5 and 2.0 appear not to affect journal path shapes appreciably. Variations in initial journal centre velocity are important, at least with the short-bearing solution; large initial velocities produce instability for certain parameter combinations which are stable under small initial position or velocity disturbances. In all casesmvestigated, instability was not observed above static eccentricity ratios of 0.83. Method for Solution of Lubrication Problems with Temperature and Elasticity Effects: Application to Sector, Tilting-pad Bearings. V_Castelli and S. B. Malanoski, JOLT, 915%. F (4) (1969) 634-640; 8 figs., 3 refs. An efficient method is presented for the simultaneous solution of the Reynolds and energy equations and their coupling with elastic deformation results obtained by variational techniques. Rayleigh Step Journal Bearing-Part 11. Incompressible Fluid. B. J. Hamrock and W. J. Anderson, lOl.T, 91 ’ Ser. F (4) (1969) 641-650; 17 figs., 9 refs. A theoretical analysis of the pressure distribution, load capacity and attitude angle for a single step concentric as well as a multistep infinite length eccentric Rayleigh step journal bearing is presented. The single-step concentric analysis indicated the maximum load capacity when the film thickness ratio of the angle subtended by the ridge to the angle subtended by the pad is 0.35. From the infinite length eccentric analysis one step placed around the journal was optimal. For eccentricity ratios greater than 0.2 maximum load occurred for a bearing without a step. For eccentricity ratios less than 0.2 the optimal film thickness ratio is 1.7 whilst there are three optimal ratios of angle subtended by the ridge to the angle subtended by the pad depending on whether load capacity or stability or both load capacity and stability is more important in the application. Designing against Wear-Part 4. Wear of Rolling Bearings. A. M. Lamm, Tribology, z (4) (1969) 207~2rr; 8 figs., 3 refs. The causes of wear in rolling bearings are listed and points which a designer should consider in order to optimise freedom from wear and minimum cost are discussed. A guide is presented to the correct selection of bearing type, lubrication, lubricant selection, mounting and sealing. Hydrostatic Bearing Design-Supplement for Unequal Opposed Pads. J. P. O’Donoghue and W. B. Rowe, Tdmlogy, 2 (4) (1969) 225-232; 5 figs., I ref.
301
A complete design procedure for this type of bearing is given as a supplement to a previous article on hydrostatic bearing design. Passage of Electric Current through the Wheel Bearings of Passenger Coaches. Ball Bearing j.. I.58 (1969) 25-34; 16 figs., 2 tables. Theoretical and practical laboratory aspects of the problem of the passage of electric current through rolling bearings are presented. The results obtained were verified by a series of practical tests carried out in collaboration with the Swedish State Railways. Hub Beatings for Front-wheel-drive French Care. J. Delombre, Ball Bear&g f., 158 (1969) 2124 ; 9 figs. The article deals with a special, double-row, angular-contact ball bearing devised for mounting in the front hubs of some French cars. Rolling Bearings in Machines for Cold Bending Sheet Metal. G. Hillnor, Ball Bearing J., 158 (1969) 7-20; 24 figs., 4 refs. A method is developed of calculating the loads to provide data of use in the determination of the rolling-bearing size required for trimming presses, folding machines and rollbending machines. Examples are given on the choice and instalIation of bearings for the most important positions in these machines. The Vibratory Loading of Rolling Bearings. N. A. Kukushkin, Russian Eng. J., 49 (5) (1969) 18-20; 3 figs. (Transl. by P.E.R.A. of Gt. Britain of Vestn. Mashinostr. 49 (5) (1969) 17-19.) Formulae are derived which can be used for selecting the best speeds for the bearings and for analysing the wear on the races and rolling elements of a bearing under vibratory loading. Cavitation-free Operation of Hydrostatic Thrust Bearings. 0. M. Babaer, Rwsiarr .E%g. J., 49 (4) (196~) 40-44 : 1 fig., 2 refs. (Transl. by P.E.R.A. of Gt. Britain of vest%. Mashinostr., 49 (4) (1969) 34-38.) An investigation of the dynamic phenomena and the conditions for the occurence of cavitation in circular and annular thrust bearings. Design Parameters of Polymeric Sliding Friction Bearings. Sh. M. Bilik and V. I. Deuskikh, RussirassEng. J., 49 (4) (19691 53-55: 3 figs., 3 tables, 5 rd. (Transl. by P.E.R.A. of Gt. Britain of Fe&n. ~~as~~~zo~~~. ,49 (4) (1969) 46-48.) Wear, 1.5 (1970) 297-306
ABSTRACTS
OF CURRENT
LITERATURE
nal bearings were investigated numerically by Runge Kutto extrapolation techniques. Variations in L/D between 0.5 and 2.0 appear not to affect journal path shapes appreciably. Variations in initial journal centre velocity are important, at least with the short-bearing solution; large initial velocities produce instability for certain parameter combinations which are stable under small initial position or velocity disturbances. In all casesmvestigated, instability was not observed above static eccentricity ratios of 0.83. Method for Solution of Lubrication Problems with Temperature and Elasticity Effects: Application to Sector, Tilting-pad Bearings. V_Castelli and S. B. Malanoski, JOLT, 915%. F (4) (1969) 634-640; 8 figs., 3 refs. An efficient method is presented for the simultaneous solution of the Reynolds and energy equations and their coupling with elastic deformation results obtained by variational techniques. Rayleigh Step Journal Bearing-Part 11. Incompressible Fluid. B. J. Hamrock and W. J. Anderson, lOl.T, 91 ’ Ser. F (4) (1969) 641-650; 17 figs., 9 refs. A theoretical analysis of the pressure distribution, load capacity and attitude angle for a single step concentric as well as a multistep infinite length eccentric Rayleigh step journal bearing is presented. The single-step concentric analysis indicated the maximum load capacity when the film thickness ratio of the angle subtended by the ridge to the angle subtended by the pad is 0.35. From the infinite length eccentric analysis one step placed around the journal was optimal. For eccentricity ratios greater than 0.2 maximum load occurred for a bearing without a step. For eccentricity ratios less than 0.2 the optimal film thickness ratio is 1.7 whilst there are three optimal ratios of angle subtended by the ridge to the angle subtended by the pad depending on whether load capacity or stability or both load capacity and stability is more important in the application. Designing against Wear-Part 4. Wear of Rolling Bearings. A. M. Lamm, Tribology, z (4) (1969) 207~2rr; 8 figs., 3 refs. The causes of wear in rolling bearings are listed and points which a designer should consider in order to optimise freedom from wear and minimum cost are discussed. A guide is presented to the correct selection of bearing type, lubrication, lubricant selection, mounting and sealing. Hydrostatic Bearing Design-Supplement for Unequal Opposed Pads. J. P. O’Donoghue and W. B. Rowe, Tdmlogy, 2 (4) (1969) 225-232; 5 figs., I ref.
301
A complete design procedure for this type of bearing is given as a supplement to a previous article on hydrostatic bearing design. Passage of Electric Current through the Wheel Bearings of Passenger Coaches. Ball Bearing j.. I.58 (1969) 25-34; 16 figs., 2 tables. Theoretical and practical laboratory aspects of the problem of the passage of electric current through rolling bearings are presented. The results obtained were verified by a series of practical tests carried out in collaboration with the Swedish State Railways. Hub Beatings for Front-wheel-drive French Care. J. Delombre, Ball Bear&g f., 158 (1969) 2124 ; 9 figs. The article deals with a special, double-row, angular-contact ball bearing devised for mounting in the front hubs of some French cars. Rolling Bearings in Machines for Cold Bending Sheet Metal. G. Hillnor, Ball Bearing J., 158 (1969) 7-20; 24 figs., 4 refs. A method is developed of calculating the loads to provide data of use in the determination of the rolling-bearing size required for trimming presses, folding machines and rollbending machines. Examples are given on the choice and instalIation of bearings for the most important positions in these machines. The Vibratory Loading of Rolling Bearings. N. A. Kukushkin, Russian Eng. J., 49 (5) (1969) 18-20; 3 figs. (Transl. by P.E.R.A. of Gt. Britain of Vestn. Mashinostr. 49 (5) (1969) 17-19.) Formulae are derived which can be used for selecting the best speeds for the bearings and for analysing the wear on the races and rolling elements of a bearing under vibratory loading. Cavitation-free Operation of Hydrostatic Thrust Bearings. 0. M. Babaer, Rwsiarr .E%g. J., 49 (4) (196~) 40-44 : 1 fig., 2 refs. (Transl. by P.E.R.A. of Gt. Britain of vest%. Mashinostr., 49 (4) (1969) 34-38.) An investigation of the dynamic phenomena and the conditions for the occurence of cavitation in circular and annular thrust bearings. Design Parameters of Polymeric Sliding Friction Bearings. Sh. M. Bilik and V. I. Deuskikh, RussirassEng. J., 49 (4) (19691 53-55: 3 figs., 3 tables, 5 rd. (Transl. by P.E.R.A. of Gt. Britain of Fe&n. ~~as~~~zo~~~. ,49 (4) (1969) 46-48.) Wear, 1.5 (1970) 297-306