Abstract: A rolling bearing which has at least one bearing ring and a plurality of rollers. The bearing ring has a raceway for the rollers and at least one lateral rim for axially guiding the rollers. The roller has front face facing the rim and the rim has a rim hearing surface facing the roller. At least sections of at least the front face or the rim bearing surface have a toroidal camber in the direction of the rim bearing surface or the front face.

Abstract: A thin-wall bearing, comprising a retainer (4) formed in a divided type having a plurality of resin plate-like members (5), (5), . . . curved along an inner ring (1) and an outer ring (2). The retainer (4) comprises pockets (6) opening to the axial end part thereof and rollingly holding balls (3). Slit-like through holes (14) extending in the axial direction and opening to the axial end part where the opening parts (7) of the pockets (6) are positioned are formed at the center parts of pillars (10) between the pockets (6) and (6) adjacent to each other. As a result, the thin-wall bearing can have excellent lubricity.

Abstract: A system and method for reducing roller skew, which involve ascertaining first and second thrust load properties applied to a roller while a rotary body rotates in opposing rotational directions, and adjusting an orientation of at least one bearing assembly for the roller until an amplitude difference between the first and second thrust load properties is below a predetermined threshold.

Abstract: There is realized a self-aligning roller bearing with retainer that stabilizes the orientation of spherical rollers and prevents these spherical rollers from skewing, and which can be rotated at high speed, and furthermore which enables efficient lubricant feed into pockets 9. By rotating a turning tool 14 as it revolves, the surfaces on both sides in the circumferential direction of respective column sections are processed into concave curved surfaces that oppose a rolling surface of the respective spherical rollers across a pocket clearance into which lubricant oil can be fed. The length of the column sections 8c is less than the length in the axial direction of the spherical rollers, and greater than a half of the length, and an end portion of the side surface in the circumferential direction of the respective column sections 8c projects further in the circumferential direction than an intermediate portion thereof, and the spherical rollers are embraced in the pockets 9.

Abstract: There is provided a bearing assembly including: a sleeve having a hole; a shaft rotatably disposed in the hole; a thrust plate in contact with the end of the shaft to reduce friction in rotation of the shaft; and a holder accommodating the sleeve and the thrust plate and having a contact surface in contact with the thrust plate.

Abstract: A tapered roller bearing includes bearing rings including an inner ring and an outer ring, a roller rolling between the inner ring and the outer ring, and a cage having a pocket holding the roller and located adjacent to the outer ring. A radial clearance ? between the cage and the outer ring when the cage is in a neutral position, a radial clearance ?pr between the roller held in the pocket and the cage, and a circumferential clearance ?pc between the roller held in the pocket and the cage satisfy relations ?pr>?pc and ?2?(???pr)/(?pr??pc)?0.

Abstract: A double row self-aligning roller bearing in which spherical rollers are arranged in double rows between an inner ring and an outer ring, characterized in that the curvature radius of the ridge line of the spherical roller in one row is R1, the curvature radius of the ridge line of the spherical roller positioned in the other row is R2, the curvature radius of the inner ring track surface being in contact with the spherical roller in one row is N1, and the curvature radius of the inner ring track surface being in contact with the spherical roller in the other row is N2, a relation such that N1/R1>N2/R2 is satisfied.

Abstract: A double-row self-aligning roller bearing includes left and right rows of rollers, arranged between an inner race and an outer race. A raceway surface of the outer race represents a spherical shape and the rollers have an outer peripheral surface following the shape of the raceway surface of the outer race. The rollers of the left and right roller rows have respective lengths different from each other. Also, the left and right roller rows have respective contact angles different from each other.

Abstract: A tapered roller bearing according to the invention is such that when an arithmetical mean roughness as a surface roughness of a large end face of a tapered roller is ?1 and an arithmetical mean roughness as a surface roughness of a large rib surface of an inner ring is ?2, ?1 is 0.04 ?m or larger, and a composite roughness that is expressed by a square root of a sum of a squared value of ?1 and a squared value of ?2 is 0.17 ?m or smaller. Raceway surfaces of an outer ring and the inner ring and a rolling contact surface of the tapered roller are crowned, and a total crowning amount is set to 50 ?m or larger, an outer ring crowning rate is set to 40% or larger, and a roller crowning rate is set to 20% or smaller.

Abstract: A tapered roller bearing comprises an inner ring having a conical surface-like raceway surface in it outer periphery and formed with a cone back face rib and a cone front face rib on the opposite sides of the raceway, an outer ring having a conical surface-like raceway in its inner periphery, a plurality of tapered rollers interposed between the raceways of the inner and outer rings, and a cage for holding the tapered rollers in predetermined circumferential intervals, wherein the ratio R/RBASE of the radius of curvature R of the large end face (32) of the tapered roller (30) to the distance RBASE from the apex of cone of the tapered roller (30) to the cone back face rib surface (18) of the inner ring (10) is set at 0.75 to 0.87, and the end face deflection of the large end face (32) of the tapered roller (30) is 3 ?m or less.

Abstract: A needle roller bearing (11) includes an outer ring (12) having a first outer ring member (13) having a center angle larger than 180° and a second outer ring member (14) having a center angle smaller than 180°, needle rollers (15), and a retainer (16) having a pair of ring sections and a plurality of column sections (17c) (18c) arranged between the pair of ring sections, and d<X<D and a formula (1) below are satisfied in which reference D represents an inner diameter dimension of the outer ring (12), reference r represents a radius of the needle roller (15), reference d represents an outer diameter dimension of the retainer (16), and reference X represents a length of a line segment l1 connecting circumferential ends of an inner diameter surface of the first outer ring member (13), and when a line l2 passing through the center of the outer ring (12) and parallel to the line segment l1 passes through the column section (17c), reference ? represents an angle formed between the line l2 and a line l3 connec

Abstract: A relief groove (23) is provided at a corner in which a track surface (21) and a flange surface (24) cross, in an inner ring (20) of a cylindrical roller bearing. A chamfer (42) is provided at a corner part in which a rolling surface (41) and an end surface (43) cross, in a cylindrical roller (40). When it is assumed that the height of the chamfer (42) from the rolling surface (41) is “h” and the curvature radius of the chamfer is “R”, the relation such that 1.0?R/h?1.5 is satisfied.

Abstract: A system and method for reducing roller skew, which involve ascertaining first and second thrust load properties applied to a roller while a rotary body rotates in opposing rotational directions, and adjusting an orientation of at least one bearing assembly for the roller until an amplitude difference between the first and second thrust load properties is below a predetermined threshold.

Abstract: A roller with cage assembly 11 comprises a plurality of crowned rollers 12 each including a column part 12a having a constant diameter and inclined parts 12b connected to both sides of the column part 12a and inclined to reduce the diameter gradually, and a cage 13 having a pair of ring parts 14 and 15, a plurality of pillar parts 16 connecting the pair of ring parts to each other, pockets 17 formed between the adjacent pillar parts 16 to house the rollers 12, and guiding surfaces 16d having a predetermined width in a radial direction on wall surfaces of the pillar parts 16 opposed to the column part 12a. Thus, when it is assumed that a length from an end face 12c of the roller 12 to the boundary part between the column part 12a and the inclined part 12b is Dp, and an axial shortest distance from the wall surface of the pocket 17 opposed to the end face 12c of the roller 12 to the guiding surface 16d is A, the relation between them satisfies that Dp<A.

Abstract: A tapered roller bearing is designed to have a roller loading ratio in the range of 0.7 to 0.92 and a ratio of roller length to roller diameter in the range of 1.1 to 1.7 whereby oil agitation loss and rolling viscous resistance are reduced for achieving the reduction of running torque. Crownings are provided which are designed to have an outer-ring crowning parameter (=RCO/LRO) in the range of 30 to 150 and an inner-ring crowning parameter (=RCI/LRI) in the range of 50 to 260, provided that RCO denotes the radius of an outer ring crowning, LRO denotes the raceway length of an outer ring, RCI denotes the radius of an inner ring crowning and LRI denotes the raceway length of an inner ring. Thus, the rolling viscous resistance is reduced for achieving the reduction of running torque.

Abstract: A rolling bearing is adapted for an auxiliary device driven by an internal combustion engine via a belt. The rolling bearing comprises an inner race, an outer race, and a plurality of rolling elements disposed between the inner race and the outer race for rolling capabilities. A substantially half of a tolerance value of a clearance in a radial direction of the rolling bearing falls in a negative value, under a condition where the rolling bearing is mounted in the auxiliary device.

Abstract: Let r be the radius of curvature of the corners of pockets of a cage, and Lw be the length of cylindrical rollers. They are set such that the relation r/Lw?0.1 holds. Further, the relation r/k1?1 holds, where k1 is the minimum dimension on the inner diameter side of the annulus of the cage.

Abstract: Tapered roller bearings and gas turbine engine systems involving such bearings are provided. In this regard, a representative bearing cage for a gas turbine engine includes: an outer cage rim and an inner cage rim; the outer cage rim having a rounded edge at a location of contact between the outer cage rim and a roller.

Abstract: Deep groove ball bearings are used as bearings supporting both side portions of a worm. In the first bearing on the side of a motor, the curvature radius of a raceway groove in an inner ring or the curvature radius of a raceway groove in an outer ring are set to a specific numerical range with respect to the diameter of a ball.

Abstract: A full crowning provided on an outer diameter surface (13) of a roller (11) includes a first crowning (14a), a second crowning (14b), and a third crowning (14c). When a length of the roller (11) in its rolling axial direction is twice a length of the roller (11) in its radial direction and less, a curvature radius R1 of the first crowning (14a) positioned at a distance of 32% of the length of the roller (11) in the rolling axial direction from an end face (12a) of the roller (11) is R551 to R1000, a curvature radius R2 of the second crowning (14b) positioned at a distance of 23% of the length of the roller in the rolling axial direction from the end face (12a) of the roller (11) is R321 to R550, and a curvature radius R3 of the third crowning 14c positioned at a distance of 15% of the length of the roller in the rolling axial direction from the end face (12a) of the roller 11 is R200 to R320.

Abstract: The sectional shape of a rolling surface of at least one of bearing component parts has the following relation between the order n (n being an arbitrarily chosen natural number) and the amplitude r of waviness relative to the circularity of the sectional shape. The order n and the amplitude r are logarithmically transformed to define X=Log(n) from the order n and Y=Log (rn) from the amplitude r of n-order. When a regression line Y=aX+b is determined, the ratio ?/? of the deviation ? at each X from the regression line of Y to the standard deviation ? is chosen to be smaller than 4.

Abstract: A ball bearing for spindle turning device for use in the spindle turning device of a machine tool, and a spindle turning device for a machine tool using the same, which is compatible with machine tools whose recent trend is for more composite configurations while maintaining and achieving higher accuracy (higher rotational accuracy), greater stiffness and reductions in torque and heat generation is to be provided. In a ball bearing for spindle turning device for use in the spindle turning device of a machine tool, the sectional size ratio (B/H) between the axially cut sectional width B and the radially cut sectional height H is set to be (B/H)<0.63 where it is a single row ball bearing or the sectional size ratio (B2/H2) between the axially cut sectional width B2 and the radially cut sectional height H2 (B2/H2)<1.2 where it is a double row ball bearing.

Abstract: In a cylindrical roller bearing 20 for continuously variable belt and pulley transmissions which is used at rotational support portions of a continuously variable belt and pulley transmission and in which a plurality of cylindrical rollers 23 are rollably provided in a circumferential direction between an outer ring 21 and an inner ring 22, a raceway surface 23a of the cylindrical roller 23 is made to take the shape of a full crowning, and a radius curvature R of the full crowning is made to satisfy a relationship of 0.01?L2/(Da×R)?0.03 relative to a diameter Da and a roller length L of the cylindrical roller 23.

Abstract: A tapered roller bearing according to the invention is such that the surface hardnesses of a raceway surface of an inner ring and rolling contact surfaces of tapered rollers are set to 63 to 69HRC. In addition, respective raceway surfaces of an outer ring and the inner ring and the rolling contact surfaces of the tapered rollers are crowned and are set such that a total crowning amount is 50 ?m or larger, an outer crowning rate is 40% or larger and a roller crowning rate is 20% or smalled.

Abstract: According to the invention, there is provided a tapered roller bearing in which, where D represents a larger end diameter of the tapered roller and L represents a roller length thereof, the roller length L is 18 mm or smaller, and a ratio of the large end diameter and the roller length of the tapered roller which is expressed by D/L is in the range of 0.55 to 0.9. In addition, respective raceway surfaces of the outer ring and the inner ring and rolling contact surfaces of the tapered rollers are crowned, and a total crowning amount is set to be 50 ?m or larger, an outer ring crowning rate is set to be 40% or larger, and a roller crowning rate is set to be 20% or smaller.

Abstract: A tapered roller bearing (1) used in transmissions or differentials for automobiles includes an inner ring (2), an outer ring (3), a plurality of tapered rollers (4) rollably disposed between the inner and outer rings (2 and 3), and a cage (5) for holding the tapered rollers (4) at circumferential predetermined intervals, wherein the roller coefficient ? exceeds 0.94, where ? is (the number of rollers×mean roller diameter)/(?·PCD).

Abstract: A rotation support device for a compressor pulley, wherein a three-point contact radial ball bearing (14b) is used as a rolling bearing for supporting a driven pulley, the cross sectional shape of an inner ring raceway track (19b) coming into contact, at one point, with the rolling contact surface of each ball (17a) is formed in a composite arc by smoothly and continuously connecting arcs with different radii of curvature R1 and R2 to each other, and the radius of curvature R1 on a center side in the width direction is made smaller and the radii of curvature R2 on the both end sides in the width direction are made larger (R1<R2) whereby the durability of the rolling bearing for supporting the driven pulley can be assured while reducing the size of the rolling bearing.

Abstract: There are provided tapered roller bearings which support a pinion shaft. Inner races have large rib faces each having a recessed surface shape on which large-diameter end faces of tapered rollers slide. The surface roughness of the large-diameter end face is ?1 [?mRa] is 0.025 or more. In addition, assuming the surface roughness of the large rib face is ?2 [?mRa], (?12+?22)1/2 is 0.17 [?mRa] or less. The sliding portion of the large-diameter end face and the sliding portion of the large rib face are made of a carburized steel, and the carbon content in a matrix phase in a surface layer portion of each of the sliding portions to a depth of 50 ?m from a surface is 0.8 wt % or more, the surface hardness thereof is in the range of Rockwell C63 to 67, and a surface retained austenite amount is set to be 20% or more and 25% or less.

Abstract: A cylindrical roller bearing includes an inner ring having a flange portion provided with a roller guide-surface which guides the end faces 4a of the cylindrical rollers having diameter of Da. The end face 4a away from a center axis of the cylindrical roller by 0.40 Da in the radial direction is a first position A, and the end face 4a away from the center axis by 0.35 Da is a second position B, the end face 4a contacts with the roller guide-surface between the first and second positions A and B, the end face 4a has a convex-shaped crowning portion 4b having a continuous curve which passes the first and second positions A and B, and an angle ? formed between a line connecting the first and second positions A and B and a line perpendicular to the center axis is set to be 0.5° or less.

Abstract: A tapered roller bearing according to the present invention, in which the rolling surface of a tapered roller and raceway surfaces of internal and outer rings undergoes crowning. The total crowning amount of that crowning and the crowning amount of each raceway surface and rolling surface are set to preferred values. This allows reduction of the rolling friction of the internal and outer rings and the tapered roller, and the rotation torque of the tapered roller bearing according to the present invention.

Abstract: A roller bearing including a plurality of rollers which are provided between an outer circumferential surface of an inner member and an inner circumferential surface of an outer member; and a substantially cylindrical roller holder which has a plurality of pockets holding the plurality of rollers, respectively, such that each of the rollers is rotatable about an axis line thereof and which is rotatable around the inner member. A sign of a skew angle of each of the rollers is constant irrespective of how much the each roller is inclined relative to a corresponding one of the pockets in a circumferential direction of the roller holder.

Abstract: There is disclosed a bearing unit (5, 5a) for a wheel comprising a stationary race (6) having stationary race track surfaces (11a, 11b) on a peripheral surface on the stationary side thereof to be supported and fixed by a suspension system in its used state, a rotating race (8) having rotating race track surfaces (14a, 14b) on a peripheral surface on the rotating side so as to fix a wheel and a braking rotating member in its used state, and a plurality of balls (17) provided between the rotating race tracks and the stationary race tracks, wherein a standard value for the mutual difference in diameter between these balls is not more than 1.0 ?m.

Abstract: When a minimum thickness of a part where an outer ring raceway is provided on a middle portion in the axial direction of an outer ring is h, and a diameter of each rolling element is Da, the relationship 0.4 Da?h 0.8 Da is satisfied. As a result, even when the outer ring 4a is fixed in a transmission case of low-rigidity, elastic deformation of the outer ring can be prevented without needlessly increasing the thickness h of the outer ring. When an outer diameter of an outer ring is D, a width of this outer ring in the axial direction is W, a minimum thickness of a part where the outer ring raceway is provided on a middle portion in the axial direction of the outer ring is h, and a diameter of each ball is Da, the respective dimensions are controlled such that a value K calculated by {(h1.5·W)/(Da1.1·.D0.5)} satisfies the relationship 1.20?K?2.00.

Abstract: A single-row or multi-row rolling bearing comprising thin-walled bearing races which are made of a martensitic, through hardened steel and have the following characteristics: a surface hardness of ?613 HV (56 HRC) in the area of the bearing face; a core hardness of ?285 HV (28 HRC); a difference of ?150 HV (9 HRc) between the surface hardness and the core hardness. The core hardness is reached at a depth ranging between 8 percent of the diameter of the rolling elements and 90 percent of the wall thickness on the bottom of the track. There is a ratio of ?20 between the diameter of a pitch circle Tk and the diameter of a rolling element DW.

Abstract: A rolling bearing for supporting a shaft on which a fan is provided, has an inner ring having an inner ring race on an outer surface thereof, an outer ring having an outer ring race on an inner surface thereof, balls provided between the inner ring race and the outer ring race and a retainer which keeps the balls apart each other in a circumferential direction, wherein an inner diameter of the bearing is set to be 3 mm or more and 17 mm or less, an outer diameter of the bearing is set to be 8 mm or more and 40 mm or less, when a thickness ti and a thickness te satisfies a relationship te?1.24 ti, and a residual austenite content in the inner ring is 7 wt % or less.

Abstract: A bearing to be used for a pulley in an auxiliary device for the engine of an automobile includes an outer ring 3, an inner ring 5, double rows of balls 7 and 8, retainers 9 and 10, and seals 11 and 12 which are disposed on the rear surface sides of the retainers 9 and 10 so as to be spaced therefrom thereby to form spaces for accommodating grease, respectively. The bearing for a pulley used in an auxiliary device for the engine of an automobile is arranged in a manner that the outer diameter of the bearing is 65 mm or less, the width of the bearing is 45% or less of the inner diameter thereof, the diameter of each of the balls 7 and 8 is 4 mm or less, and a distance L between the rear surfaces 19 of the retainers 9 and 10 and the inner surfaces 20 of the seals 11 and 20 are set to be 13% or more of the diameter Da of the ball.

Abstract: Contact surface pressure P increases rather drastically in proportion to skew angle ? within the range of 0<???T, but because the critical skew ?T is restricted to be small, the contact surface pressure P changes in a low range below a certain level P0 at which wear occurs in contact portions. Thus restricting the critical skew angle ?T to a small angle reduces the contact surface pressure P and suppresses heat generation and wear in the contact portions.

Abstract: A hub bearing assembly comprising a hub having a radially outwardly directed flange at one axial end for mounting the wheel of a vehicle, an outer ring having axially spaced raceways and a plurality of rolling elements arranged in two rows in the annular space between the outer ring and the hub, the diameter of the pitch circle of the outboard row of rolling elements adjacent said flange being greater than the diameter of the pitch circle of the rolling elements in the inboard row.

Abstract: A rolling element having comprises an inner ring, an outer ring and a series of rolling elements which are in contact with the raceways of the rings, an ultra-low viscosity fluid being present in the contacts having a kinematic viscosity ?=(?o/?) of less than 2 mm2/s, wherein the surfaces of the rings and the rolling elements have asperities which can have solid-to-solid contact during operation of the bearing. A factor <i>Dq</i> is defined which is equal to (I) whereby the solid-to-solid contact of the asperities is reduced by selecting such design parameters and operating conditions of the bearing that <i>Dq</i> is in the range from 8.0×10?6 mrad s1/2 to 1.36×10?4 mrad s1/2.

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 cylindrical roller bearing suited for higher rotation speeds is provided, which can control heat generation, wearing, and other problems at contact portions between cylindrical rollers and flange portions. A cylindrical roller bearing is composed of an inner ring having a raceway on an outer circumference thereof, an outer ring having a raceway on an inner circumference thereof, a plurality of cylindrical rollers disposed to roll freely between the raceway of the inner ring and the raceway of the outer ring, flange portions formed on both sides of the raceway of the inner ring, and recess grooves formed between flange surfaces of the flange portions on both sides and the raceway. The flange surfaces are inclined at the same angle from a base end portion to a tip end portion thereof. A radial dimension of chamfers of the cylindrical rollers is smaller than a radial height from the raceway near the recess grooves formed in the races.

Abstract: A ball screw having: a screw shaft having a spiral ball rolling groove; a ball nut having a ball rolling groove corresponding to the ball rolling groove; and a large number of balls interposed between the ball rolling grooves so as to roll freely; wherein the ball rolling groove of at least one of the screw shaft and the ball nut is ground so that a maximum value component of a number of undulation peaks per lead in the ball rolling groove is not in a range of from 0.95 nm to 1.05 nm centered on an integral multiple nm of a number m of load balls per lead calculated by an expression: ( ? ? ? d m ) 2 + L 2 P in which P is a distance between centers of the adjacent load balls disposed at substantially equal intervals in the ball rolling groove, dm is a ball pitch circle diameter, and L is a lead.

Abstract: This invention is to provide a hydrodynamic bearing assembly, which realizes the high rotation rate in a stable manner and the robust rigidity. The hydrodynamic bearing assembly has a total radial gap of 3 microns or less for preventing the contact in the thrust bearing. The thrust bearing is a pomp-out type one, and the radial bearing has offset grooves on the surface thereof to supply the fluid flow sufficiently to the thrust bearing. The grooves also eliminate a half-whirl. A depth ratio relative to the diameter of bearing is preferably 0.005 or less to avoid the reduced translation rigidity. The radial gap is smoothly enlarged from the center to both ends along the axis, and the shaft is biased to incline the shaft relative to the sleeve, so that the shaft can be rotated with the robust rigidity. Also, a pair of the thrust bearings is provided on both ends of the radial bearing so as to realize the robust rigidity.

Abstract: A radial roller bearing has: an outer ring; an inner ring; and, a cylindrical roller interposed between the outer ring and the inner ring, the outer and inner rings respectively including flange portions formed in the end portions thereof so as to be opposed to the end face of the cylindrical roller, wherein, in the end face of the cylindrical roller, there is formed a circular-ring-shaped contact portion of the roller end having centers of curvature continuously existing on a circle which lies on a plane parallel to the end face of the cylindrical roller and also the center of the circle is on the rotation axis of the cylindrical roller.

Abstract: A roller bearing includes an inner ring, an outer ring, a plurality of cylindrical rollers each provided between rolling contact surfaces of the inner ring and the outer ring. Each of the cylindrical rollers includes an end face having a peripheral part that is crowned. A flange portion is formed at an outer circumferential face end part of the inner ring and/or an inner circumferential face end part of the outer ring. The peripheral part is crowned in a curving shape represented by an exponential function of y=a·exp(?b·x); where a and b are constants, x is a distance from the rolling contact surface in a radial direction of the cylindrical roller, and y is a crowning fall-off amount from a central part of the end face of the cylindrical roller in an axial direction of the cylindrical roller.

Abstract: The outer ring (3) of a motor-vehicle wheel-hub bearing (1) is housed in a cylindrical seat (9) of a strut (10) and is locked axially, on one side of the strut (10), by means of a radially inwardly-projecting rim (18) formed by cold deformation of a tubular portion (17) of the seat (9) and, on the other side, by means of a shoulder (11). A resiliently compressible ring (19) is inserted into the seat (9) of the strut (10) so as to be compressed axially between a lateral surface (12, 13) of the outer ring (3) of the bearing and the shoulder (11) or the deformed rim (18) of the seat (9), respectively, to compensate for any relative thermal expansion between the bearing and the seat.

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: In order to improve a seizure resistance as well as restricting of a dispersion of a rotation torque, surface roughness of a large diameter side end face (4A) of a tapered roller (4) is defined as a value satisfying both the following conditional expressions (1) and (2). 0.04 ?m?Ra(r)?0.1 ?m??(1) 0.8?Ra(r)/Ra(c)?1.1??(2) where, Ra(r) is an arithmetic average of roughness in a radial direction on the large diameter side end face of the tapered roller, and Ra(c) is an arithmetic average of roughness in a peripheral direction on the large diameter side end face of the tapered roller.

Abstract: A bearing configuration in which a shaft is supported by a first and second bearings, the second bearing being spaced from the first bearing. The first bearing and said second bearing are supported by a corresponding first bore and second bore in a shaft housing, a first axis being coincident with an axis of the first bore and a second axis being coincident with an axis of the second bore. The first axis and the second axis are purposefully offset from one another a sufficient distance to substantially eliminate internal clearance within the first bearing.

Abstract: In a tapered roller bearing having an outer ring whose outside diameter is D, an inner ring whose inside diameter is d, and a plurality of tapered rollers whose pitch circle diameter is dm, a setting is provided such that a PCD parameter expressed by 2 dm/(D+d) is a value which falls within the range of 0.96 to 0.985.