A ball bearing assembly is disclosed wherein dynamic and inertial force unbalances and variations inherent in conventional bearings produced by inconsistent ball-to-cage and cage-to-land contact forces resulting in bearing instability and vibration are compensated by configuring the ball cage such that the relative mass positions of the balls and the cage are predetermined, maintained constant and are compensated within the rotating system whereby the radial inertial forces are rendered predictable and constant in direction and magnitude resulting in balanced and stable bearing performance free of vibrations transmitted therefrom to the bearing support or supported members and free of dynamic cage instabilities.
An anti-friction bearing wherein the anti-friction balls or rollers are sed different distances from one another to provide an increased number of loading patterns and a reduced frequency of any particular loading pattern.
A bearing unit A comprises a main shaft gear 1 integrally having a tooth section 1a always meshed with a sub shaft gear 6 at the outer circumference, a pair of inner rings 2 fitted in the outer circumference of the main shaft 5, double-row tapered rollers 3 disposed between the raceway surface of the main shaft gear 1 and that of the inner ring 2, and a pair of cages 4 for respectively retaining each row of tapered rollers 3. The pockets 4a of the cage 4 are unequally pitched, wherein the tapered rollers 3 housed in the pockets 4a are unequally disposed at the circumference.
A method and apparatus which provides a bearing design with an irregular or semi-rhythmic ball spacing. The method of the invention includes the steps of a) choosing an initial pattern for the position of the balls with an arbitrary irregular spacing therebetween; b) determining the degree to which the bearing is suitable for a given application with the chosen spacing between the balls; c) moving the balls in the pattern to change the spacing therebetween and d) repeating steps b) and c) until the bearing is suitable for a given application.
An object is to exert the intended fretting-preventive effect without being influenced by the size of variation in rotation (variation in speed) or the size of vibration. An arrangement comprising a main shaft gear 1 having a raceway surface 1c on its inner peripheral surface, a bearing inner ring 2 having a raceway surface 2a on the outer periphery, tapered rollers 3 disposed between the raceway surface 1c of the main shaft gear 1 and the raceway surface 2a of the bearing inner ring 2 and held at predetermined circumferential intervals by a cage 4, an imbalance means which produces a circumferential weight imbalance in the assembly of the tapered rollers 3 and cage 4, wherein the roughness of the cone back face 2b of the bearing inner ring 2 is 0.01-0.04 .mu.mRa, and the roughness of the large end faces 3b of the tapered rollers 3 is 0.01-0.05 .mu.mRa, and the radius of the large end faces 3b are worked such that the maximum value thereof including the working precision is substantially equal to the reference radius. Further, full crowning is applied to the rolling contact surfaces 3a of the tapered rollers 3 and the surfaces of the tapered rollers 3 are formed with coating films of the MoS.sub.2 type.
A crown cage is applied to a ball bearing for high-speed rotation for a dental hand piece or the like. The cage has a cylinder formed by injection molding of a thermoplastic resin, and pockets for holding balls that are formed at a predetermined circumferential pitch in the cylinder. A first recess including a gate cutting trace at the time of molding, and second recesses for correcting rotational imbalance of the cylinder caused by the first recess, are formed in the cylinder. The recesses have almost the same shape, and are arranged at a predetermined circumferential pitch.
