Abstract: A full complement angular ball bearing with no cage and having a contact angle from 10 to 45° and an increased number of balls for use under severe conditions. The life is extended by defining the surface roughness of the inner ring and the outer ring, defining the roughness ratio of them relative to the rolling element, defining the Cr content in the alloy steel for the rolling element, forming the rolling element with oxide ceramics, or providing a dense nitride layer on the surface of the rolling element, avoiding the presence of particles with a mean diameter in excess of 3 ?m on the raceway surfaces of the outer ring and the inner ring, or coating a film of a hardness higher than that of the raceway surface of the outer ring and the inner ring on the surface of the rolling element.

Abstract: A 4-point contact ball bearing includes four ring-shaped contact surfaces for forming a ring-shaped raceway between them, each ring-shaped contact surface has a sectional profile defined by a concave curve when cut along a plane including a central axis of rotation of each ball and a central axis of rotation of the ring-shaped raceway. The concave curve is shaped so that it circumscribes the balls and that a curvature thereof is largest at a ball-contact point and is gradually decreased moving away from the ball-contact point. By defining such raceway surfaces, fluctuations in the contact points between the balls and the raceway surfaces due to machining errors can be suppressed, rotational slipping of the balls can be reduced, and differential slip between the balls and the raceway surfaces can also be reduced.

Abstract: A four-point ball bearing includes: an inner ring and an outer ring defining raceway grooves, respectively. Each of the raceway grooves is constituted by two circular arcs different in curvature provided on opposite sides of a widthwise center of the raceway groove. A plurality of balls are arranged between the inner and outer rings so that the balls can roll. In at least one of the raceway grooves, a center of curvature of one of the circular arcs and a center of curvature of the other circular arc are displaced from each other at least in a radial direction so that spin is generated in each of the balls.

Abstract: The radius of curvature r1, r2 of the cross-sectional shape of an inner ring raceway 11d is made smaller at a central portion 19 and larger at end portions 20. A contact ellipse at the end portions is made small by increasing the radius of curvature r2 of the end portions 20 to thereby secure an allowable moment load. In contrast with this, an angular gap is reduced by reducing the radius of curvature r1 of the central portion 19.

Abstract: In a ball groove profile of a ball screw, an outer diameter portion of a screw shaft of the ball screw and a substantially semi-circular ball rolling portion of a ball groove of the ball screw are connected to each other through arcuate portions. The radius of curvature of each arcuate portion ranges from a value half a radius of a rolling ball or more to twice the radius of the ball or less. The arcuate portions are connected at least to the ball rolling portion continuously and smoothly. The ball groove profile can reduce the stress concentration even if impact derived from the collision of the ball is applied to land shoulder portions of the screw shaft, so that the land shoulder portions are not damaged under high-speed operation.

Abstract: A bearing for use in a water pump or similar apparatus and a method of assembling the bearing. The bearing has a stepped shaft and a counterbored raceway at the fan or pulley end which allows for use of a larger number of balls in the raceway at the fan or pulley end, and which allows for using larger balls at the impeller end. The method of assembly of the bearing includes assembling balls and a cage to form a ball and cage assembly, assembling ball and cage assembly into the outer race at its pulley end, then sliding the shaft, impeller end first, into the outer race through the pulley end such that the first inner raceway and the first balls align with the first outer raceway. The shaft is then displaced in a direction perpendicular to its axial centerline within the outer race. A second plurality of balls is inserted onto the shaft within the outer race at its second outer raceway end, and a second cage is inserted over the shaft and within the outer race to surround the second plurality of balls.

Abstract: The radius of curvature r1, r2 of the cross-sectional shape of an inner ring raceway 11d is made smaller at a central portion 19 and larger at end portions 20. A contact ellipse at the end portions is made small by increasing the radius of curvature r2 of the end portions 20 to thereby secure an allowable moment load. In contrast with this, an angular gap is reduced by reducing the radius of curvature r1 of the central portion 19.

Abstract: An outer ring 3a is formed so as to have a large thickness and the pitch circle diameters Dp of balls 6 are shifted to the inside diameter side of the present ball bearing. The radiuses of curvature Ro, Ri of the section shapes of an outer ring raceway 2a and an inner ring raceway 4a are increased with respect to the diameter Db of the balls 6. At the same time, the diameter Db of the balls 6 and the thickness of an inner ring 5a are not set excessively small to thereby be able not only to prevent Brinell impressions from being formed in the outer ring raceway 2a but also to prevent the inner ring 5a from being damaged or cracked.

Abstract: Within bounds on both sides of an axial center of each of the raceways of an outer and inner ring, a curvature radius of a raceway portion in a dimensional range covering at least 45% of a raceway width with respect to the axial center thereof is defined to be within the range of between ±1 &mgr;m to/from a mean curvature radius of the raceway in the dimensional range.

Abstract: A radial ball bearing 14 of the three point contact type or four point contact type is used for the rolling bearing for a compressor pulley. The offset amount &dgr;, that is the axial distance between the center &agr; of the radial load applied to the follower pulley 4 from the endless belt 11, and the center &bgr; of the radial ball bearing 14 is 40% or less of the diameter of the pitch circle. In addition, the radial clearance of the radial ball bearing 14 is 0.2% or less of the diameter of the pitch circle. With this construction, the durability of the rolling bearing to support the follower pulley 4 is secured while made compact.

Abstract: A ball bearing is described, which comprises an outer ring having on its inner periphery an outer raceway, an inner ring having on its outer periphery an inner raceway, plural balls rotatably disposed between the outer raceway and the inner raceway, a cage holding the plural balls in a freely rotatable manner, and a grease packed in a space between the outer raceway and the inner raceway, wherein the inner peripheral surface of each pocket of the cage contains a spherical part consisting of a spherical concave surface whose radius of curvature is slightly larger than that of each ball and a curved part which has the radius of curvature being larger than that of the spherical part and is smoothly continuous from the end of the spherical part toward the end thereof on the opening side of the pocket.

Abstract: The frequencies generated based on the undulations existing on the inner and outer ring raceways 8, 10 and on the rolling surface of the balls 11, 11 are out of coincidence with the rotational frequency itself of the rotation member supported by the rolling bearing, and with a frequency component which is a multiple of the rotational frequency, or kinds of frequencies generated due to the undulations are out of coincidence with each other in the natural frequency domain of a rotation system which is a rotation supporting portion having the rolling bearing incorporated therein, whereby without using a special grease, the self-excited frequency of the rolling bodies hardly grows to abnormal vibration, and a rolling bearing having sufficient durability and causing no abnormal vibration and noise even if used at low temperature is realized.

Abstract: The surface roughness of the track surface 2 of the inner race 1 and the track surface 4 of the outer race 3 is made to be less than 18 nmRa preferably less than 10 nmRa, the progress of surface coarsening is to be eliminated by making the ball 5 roll smoothly to prevent the rotation vibration and the rotation noise occurring thereof.

Abstract: A bearing armed at light duty rotation consists of an outer race (20) and an inner race (10) rotatably contained inside the outer race (20). Multiple annular ribs (13) are formed between the outer race (20) and the inner race (10) to reduce the contact area between the outer race (20) and the inner race (10) to minimize the friction force. Consequently, the bearing has a simple structure and excellent rotating efficiency.

Abstract: A deep groove ball bearing has an inner ring, an outer ring and a plurality of balls located between the inner ring and the outer ring. A profile deformation quantity of a raceway groove of the inner ring and a profile deformation quantity of the outer ring are limited to values at which the maximum surface pressure values of them are each 1.6 GPa or smaller.

Abstract: A rolling bearing to exhibit outstanding initial (cage) acoustic characteristics at the start of operation under a low temperature atmosphere, suppress fretting damages (abrasions) and reduce bearing torque by making the radius of curvature of the cross-sectional shape of the inner raceway and the radius of curvature of the cross-sectional shape of the outer raceway equal to 51.0% to smaller than 60.0% of the diameter of the rolling element, and packing a grease composition comprising a base oil that is a mixture of a lubricant containing a polar group in its molecular structure and a non-polar lubricant and a metallic soap-based thickener containing a long-fiber material with a major axis part length of at least 3 &mgr;m.

Abstract: An improved rolling bearing. The improved rolling bearing utilizes a novel design in the construction and location of the raceways or rings in which the rolling elements are secured. This novel design provides for reducing of slide of the parts rolling element within rings, reducing blow loads and so noise, shock absorption, increasing endurance, durability and dependability rolling bearings.

Abstract: The radius of curvature r1, r2 of the cross-sectional shape of an inner ring raceway lid is made smaller at a central portion 19 and larger at end portions 20. A contact ellipse at the end portions is made small by increasing the radius of curvature r2 of the end portions 20 to thereby secure an allowable moment load. In contrast with this, an angular gap is reduced by reducing the radius of curvature r1 of the central portion 19.

Abstract: The arrangement is such that the ratio of the diameter of balls 3 in the ultrathin-walled ball bearing to the pitch circle diameter PCD is not more than 0.03, and that the balls 3 are arranged in a single row and in two-point contact with the raceway surfaces 1a and 2a of the outer and inner members 1 and 2. The inner member 2 is composed of first and second raceway rim members 21 and 22 opposed to each other with an axial clearance S defined therebetween, and the internal clearances of the bearing are made negative by adjusting the width of the axial clearance S.

Abstract: A 4-point contact ball bearing includes four ring-shaped contact surfaces for forming a ring-shaped raceway between them. Each ring-shaped contact surface has a sectional profile defined by a concave curve when cut along a plane including a central axis of rotation of each ball and a central axis of rotation of the ring-shaped raceway. The concave curve is shaped so that it circumscribes the balls and that a radius of curvature thereof is largest at a ball-contact point and is gradually decreased moving away from the ball-contact point. By defining such raceway surfaces, fluctuations in the contact points between the balls and the raceway surfaces due to machining errors can be suppressed, rotational slipping of the balls can be reduced, and differential slip between the balls and the raceway surfaces can also be reduced.

Abstract: An outer ring 3a is formed so as to have a large thickness and the pitch circle diameters Dp of balls 6 are shifted to the inside diameter side of the present ball bearing. The radiuses of curvature Ro, Ri of the section shapes of an outer ring raceway 2a and an inner ring raceway 4a are increased with respect to the diameter Db of the balls 6. At the same time, the diameter Db of the balls 6 and the thickness of an inner ring 5a are not set excessively small to thereby be able not only to prevent Brinell impressions from being formed in the outer ring raceway 2a but also to prevent the inner ring 5a from being damaged or cracked.

Abstract: A rolling bearing in which the attainment of excellent current-carrying capability is compatible with cost reduction. The rolling bearing comprises an inner ring, an outer ring, and a plurality of rolling elements arranged between the inner and outer rings, oil films being interposed between the rolling elements and raceway surfaces of the-rings. Here, the inner raceway surface and the outer raceway surface are made coarser to such a surface roughness (Ra=0.1 &mgr;m or so) that they come into metal contact wit the rolling elements for electric connection.

Abstract: Within bounds on both sides of an axial center of each of the raceways of an outer and inner ring, a curvature radius of a raceway portion in a dimensional range covering at least 45% of a dimension between shoulders of the raceway with respect to the axial center thereof is defined to be within the range of between ±1 &mgr;m to/from a mean curvature radius of the raceway in the dimensional range.

Abstract: A rolling bearing to exhibit outstanding initial (cage) acoustic characteristics at the start of operation under a low temperature atmosphere, suppress fretting damages (abrasions) and reduce bearing torque by making the radius of curvature of the cross-sectional shape of the inner raceway and the radius of curvature of the cross-sectional shape of the outer raceway equal to 51.0% to smaller than 60.0% of the diameter of the rolling element, and packing a grease composition comprising a base oil that is a mixture of a lubricant containing a polar group in its molecular structure and a non-polar lubricant and a metallic soap-based thickener containing a long-fiber material with a major axis part length of at least 3 &mgr;m.

Abstract: A ball bearing in which the heat value in an inner ring is decreased and the heat value in an outer ring is brought closer to the heat value in the inner ring by making the radius of curvature for the inner ring groove larger, and defining the radius of curvature for the outer ring groove as 50.5% to 53.0% of the ball diameter. The arrangement of the present invention suppresses the heat value in the entire ball bearing and extends the bearing life at a reduced cost without using a large flow rate lubrication method or a preloading method such as constant preloading. In addition, a decrease in heat generation, seizing resistance and wear resistance can be attained further by optimizing a relation between the raceway groove and the ball diameter, by optimizing the number of balls, by controlling the ingredient composition for the material of the bearing ring, and by forming a hard deposition film on the surface of the raceway groove.

Abstract: In the ball bearing, the ratio of the radius of curvature of an inner race raceway 4 to the outside diameter of balls 8, 8 is set in the range of 0.51 to 0.54. Also, the ratio of the radius of curvature of an outer race raceway 6 to the outside diameter of balls 8, 8 is set in the range of 0.54 to 0.56. Further, an interior geometric clearance c is set at 13 &mgr;m or less. Thanks to these specifications, the balls 8, 8 can be prevented from running up onto the edge of the outer race raceway 6.

Abstract: An anti-frictional bearing which is reduced in its asynchronous rotational run out so that the cumbersome analyzing operation of the raceway surface and selecting operation of inner and/or outer races are not required. The bearing will contribute for the high packaging density and high speed operation of the hard disk device. An anti-frictional bearing including an inner raceway is formed on an outer peripheral surface of an inner race 1, an outer raceway 2a formed on an inner peripheral surface of an outer race 2, and a plurality of rotating bodies 3 interposed between the raceways and retained by retainers 4 in a predetermined distance with each other, wherein an out of roundness of a raceway surface 1a, 2a of at least one of said inner and outer races 1, 2 is equal to or less than 0.05 &mgr;m.

Abstract: A deep groove ball bearing has an inner ring, an outer ring and a plurality of balls located between the inner ring and the outer ring. A profile deformation quantity of a raceway groove of the inner ring and a profile deformation quantity of the outer ring are limited to values at which the maximum surface pressure values of them are each 1.6 GPa or smaller.

Abstract: An arrangement in which respective roughnesses are defined for orbital grooves of inner and outer rings and a surface of rolling members which are constituents of a rolling bearing and in which their conditions of contact are controlled whereupon a minimum amount lubricating oil is adhered at a strong bonding force to thereby obtain a condition in which lubricating oil is continuously interposed at mutual contacting portions of the inner and outer rings, the rolling members and a cage to thereby enable favorable sliding properties and remarkable restrictions in generation of dust.

Abstract: In the ball bearing, the ratio of the radius of curvature of an inner race raceway 4 to the outside diameter of balls 8, 8 is set in the range of 0.51 to 0.54. Also, the ratio of the radius of curvature of an outer race raceway 6 to the outside diameter of balls 8, 8 is set in the range of 0.54 to 0.56. Further, an interior geometric clearance c is set at 13 &mgr;m or less. Thanks to these specifications, the balls 8, 8 can be prevented from running up onto the edge of the outer race raceway 6.

Abstract: A sheave assembly for use in a high performance pulley block has an inner race 14, a sheave 10 defining an outer race and a plurality of balls 13 arranged between the outer race of the sheave 10 and the inner race 14, so as rotatably to mount the sheave on the inner race. The inner race 14 is formed principally of a plastics material, but incorporates an annular insert 20 of metal, the outer surface of the insert extending parallel to the axis of the assembly, and defining an inner track for the balls 13. The axial width of the insert 20 is significantly less than, and typically 33% to 67% of, the diameter of the balls 13.

Abstract: A wheel bearing unit is with an outer race member having two rows of raceway surfaces formed in its inner peripheral surface. In the vicinity of the groove bottom portion of the raceway surface of an inner race member is provided a projection having a diameter greater than the inscribed circle diameter. The raceway surface, the outer peripheral surface of the projection, and smaller end face are concurrently ground to keep within a predetermined range of standard values the radius difference between the diameter of the groove bottom portion of the raceway surface of the inner race member and the outer diameter of the projection, as well as the core deviation between the groove bottom portion and the smaller end face.

Abstract: An angular contact ball bearing is configured so that the inner bearing ring (6) comprises two spaced apart points of contact, B and C, and the outer bearing ring comprises one point of contact A, the point of contact C of the inner bearing ring (6) being formed only after a tilting of the inner bearing ring (6). Due to this third point of contact C, a tilting of the inner bearing ring is almost completely prevented.

Abstract: In order to allow a ball bearing to be inserted into a housing which is closed at one end, without any bearing parts being damaged during the axial insertion process, the outer ring of the bearing has a radially inwardly directed flange that extends radially into the region of the inner ring while toward the open end of the housing, the inner ring is formed on the axially outward side of the bearing balls, without a shoulder on the inner ring. An axial compression spring is arranged between the closed end of the housing and the inner ring. The flange on the outer ring may be either axially inward of or axially outward of the row of bearing balls.

Abstract: A rolling bearing 1 is provided to support the rotating member of a small motor of an information-processing device wherein the groove radius ratio of the raceway groove of the inner race 2 is in the range from 52% up to 54%, while the groove radius ratio of the raceway groove of the outer race 3 is in the range from 54% up to 56%, and whereby the small motor rotates at a high rotation speed with a prolonged acoustic life.

Abstract: A high-speed rolling bearing has an outer ring and an inner ring arranged inside the outer ring. Rolling bodies are positioned between the inner ring and the outer ring and contact the inner ring and the outer ring. The outer ring has two oppositely positioned contact points for each rolling body on which the rolling bodies are supported, respectively. The contact points are configured such that a contact angle of the rolling bodies is at least approximately independent of a rotational speed of a rotary part supported by the high-speed rolling bearing.

Abstract: The radius of curvature r1, r2 of the cross-sectional shape of an inner ring raceway 11d is made smaller at a central portion 19 and larger at end portions 20. A contact ellipse at the end portions is made small by increasing the radius of curvature r2 of the end portions 20 to thereby secure an allowable moment load. In contrast with this, an angular gap is reduced by reducing the radius of curvature r1 of the central portion 19.

Abstract: An improved single-row multi-point-contact ball bearing for an electromagnetic clutch and pulley and for a compressor for an automobile air conditioner is provided, which has a low relative inclination between the inner and outer rings and rotatable at a high revolution of about 10,000 rpm, and yet inexpensive requiring a small axial space. A single-row four-point contact angular ball bearing is provided which comprises an one-piece inner and outer rings. Each raceway surface of the inner and outer rings is made to form a Gothic-arched configuration having two curved surfaces, and each radius of curvature of the two curved surfaces is made to range substantially 0.515 to 0.55 of the outer diameter of a ball.

Abstract: A ball bearing 36 supports a rotor 35 of an electromagnetic clutch 31 in such a manner that the rotor 35 can be rotated about the axis of the ball bearing 36. The ball bearing 36 includes an outer race 12, an inner race 13, a ball 14, and a retainer 15. The outer and inner races 12 and 13 are each formed in a circular-ring shape. The ball 14 is rollingably interposed between the outer and inner races 12 and 13. In the inner peripheral surface 16 and outer peripheral surface 17 of the outer and inner races 12 and 13, there are respectively formed grooves 12a and 13a each of which extends along the race peripheral direction and has an arc-shaped section. The grooves 12a and 13a are each formed in such a range in which their respective radii of curvature re and ri satisfy 1.0≦(re+ri)/Da≦0.9746 (Da/dm)−0.0304, where Da: the diameter of the ball, and dm: the mean value of the diameters of the inner and outer races of the ball bearing.

Abstract: A bearing used for an electromagnetic clutch includes an inner race, an outer race, and a plurality of balls provided between the inner and outer races. The plurality balls are arranged in single row, and each of the balls contacts both inner and outer races at two contact points, respectively. Thus, even when the outer race inclines due to an external force, each ball continuously contacts both the inner race and the outer race at at least one point, respectively. Accordingly, the balls do not fall due to gravity, thereby preventing noise generated by balls falling and colliding with the races.

Abstract: A torque limiting device capable of transferring torque within a power train, and also capable of disengaging the torque transfer connection when the torque level exceeds a specific point. A specific ball bearing joint is formed where a radial boss mates with the inner circumference of a flange. The ball bearing joint consists of an outer radial groove formed on the aforesaid inner circumference, an inner radial groove formed on the boss and facing the outer groove, and ball bearings inserted between the two radial grooves. Each radial groove is formed to a V-shape cross section having a radius of curvature smaller than that of the ball bearings, thus providing ball bearing support at two points within each groove, and four points of bearing support in total. Rotation of the torque output part is thus supported adequately in both the radial and axial thrust directions by a single ball bearing structure which allows the torque limiter to be made to compact dimensions.

Abstract: An angular bearing of a dual cavity toroidal type continuously variable transmission, includes: a torque input shaft having a shaft-side raceway groove formed in an outer peripheral surface of a flange portion provided in an end thereof; a loading cam unit of a loading cam unit having a disc-side raceway groove formed in an inner peripheral surface of a jointing opening thereof, the loading cam unit located around the end of the torque input shaft; and a plurality of balls held between the shaft-side raceway groove and the disc-side raceway groove to bear thrust loads exerted on the cam disc, wherein each of an angular contact angle between the balls and the shaft-side raceway groove and an angular contact angle between the balls and the disc-side raceway groove is 60° or smaller, and each of a curvature radius of a groove surface of the shaft-side raceway groove and that of a groove surface of the disc-side raceway groove is from 52% to 55% of a diameter of the ball.

Abstract: A ball bearing in which races are well prevented from flaking in early stages under an environment using lubricating oil having a high traction coefficient so that a long life of the ball bearing is attained, while the cost of the bearing is reduced. The ball bearing has a plurality of balls disposed between a fixed race and a rotating race, and the ball bearing is used under an environment using lubricating oil having a traction coefficient of 0.07 or more under the conditions that a slip factor is 5% and a temperature is 40.degree. C. At least the groove radius of the rotating race is set to be in a range of from 0.53 Dw to 0.58 Dw both inclusive when Dw designates the diameter of balls. In addition, the hardness of the race is set to be in a range of from HRC 58 to HRC 64 both inclusive.

Abstract: An improved single-row multi-point-contact ball bearing for an electromagnetic clutch and pulley and for a compressor for an automobile air conditioner is provided, which has a low relative inclination between the inner and outer rings and rotatable at a high revolution of about 10,000 rpm, and yet inexpensive requiring a small axial space.A single-row four-point contact angular ball bearing is provided which comprises an one-piece inner and outer rings. Each raceway surface of the inner and outer rings is made to form a Gothic-arched configuration having two curved surfaces, and each radius of curvature of the two curved surfaces is made to range substantially 0.515 to 0.55 of the outer diameter of a ball.

Abstract: A deep-raceway ball bearing 1 as a ball bearing includes an inner ring 2, an outer ring 3 and a rolling element 4. The inner ring 2 is annular as a whole and circular in cross section. A rotary shaft 5 is fastened to the inner peripheral surface of the inner ring 2. The outer ring 3 is annular as a whole and circular in cross section, and larger in inside diameter than the inner ring 2. A plural number of rolling elements 4 are disposed in reliable fashion between the inner ring 2 and the outer ring 3, while being in contact with the outer peripheral surface 6 of the inner ring 2 and the inner peripheral surface 7 of the outer ring 3. The outer peripheral surface 6 of the inner ring 2, while extending in the circumferential direction thereof, is curved inward to form an inner raceway 8 circular in cross section. The inner peripheral surface 7 of the outer ring 3, while extending in the circumferential direction thereof, is also curved inward to form an outer raceway 9 circular in cross section.

Abstract: A bearing outer-race performed piece has a turning stock on an outer periphery thereof and has a circular bearing groove on an inner surface thereof. The bearing groove has a cross-section which includes circular portions defined by a circle of a greater diameter than that of a bearing groove of a bearing outer-race product, and a flat portion being arranged between the circular portions at a location shifted toward the center of the circle of the circular portions from a bottom locus of the circular portions.

Abstract: A release bearing (1) for actuating a gearshift clutch of an automotive vehicle comprises an angular contact ball bearing (3) in which forces are transmitted from one bearing raceway to another bearing raceway at an angle of pressure .alpha. to the transverse plane of the angular contact ball bearing (3). To improve the bearing capacity of such a release bearing (1), the angle of pressure .alpha. is configured to be .gtoreq.36.degree. and <45.degree.. Friction between the balls and the raceways of the angular contact ball bearing is reduced by the fact that an osculation K.sub.AU on the outer ring (6) is .gtoreq.1.15 and an osculation K.sub.IR on the inner ring (10) is .gtoreq.1.07.

Abstract: A rolling or sliding machine part that has an improved oil film formation capacity. The machine part has a rolling or sliding contact surface formed with discontinuous grooves, which are dispersedly arranged and extend across the direction in which the machine part rolls or slides.

Abstract: A rolling bearing unit having undulation on the rolling surfaces of the rolling elements where the total value of the wave components having an even number of waves per circumference is smaller than the total value of the wave components having an odd number of waves per circumference, or having undulation on the inner ring raceway and outer ring raceway, where the undulation on at least one of the raceway is conditioned such that the maximum waviness amplitude among (nZ), (nZ+1) and (nZ -1) waves per circumference is smaller than the maximum waviness amplitude among (nZ+2) and more waves per circumference, where n is a positive integer and Z is the number of rolling elements, thereby making it possible to obtain a low-cost, high-performance rolling bearing in which the vibration characteristics of the rolling bearing are improved without having to increase the precision required for manufacturing the rolling elements and inner ring raceway and outer ring raceways.

Abstract: A radially and axially preloaded bearing that has a very low mass and axial profile and which can be used in a actuator pivot of a direct access storage device without the need for a second bearing to counter the preload. An outer race of the bearing is split in order to form an open ring. Three balls are placed between the outer race and an inner race. Both the inner surface of the outer race and the outer surface of the inner race are formed such that two contact points exist between each ball and each race. Alternatively, the outer race is a closed toroid. The inner race is radially split to form a lower and an upper race, each being a closed toroid. In yet another alternative, the outer race is radially split into an upper outer race and a lower outer race. The inner race is a single closed toroid. A limiter is used to limit the movement of each of the balls. Alternatively, a conventional ball cage is used.