Abstract: Durability of a pair of inward flange portions 4b and 4c formed on both ends of a shell 1c is ensured while maintaining load capacity, irrespective of a thrust load applied from each needle 2a. Inside surfaces 10a and 10b of both inward flange portions 4b and 4c are formed as inclined surfaces inclined in a direction where a distance between the surfaces increases toward the radial inward direction. Each of both axial end surfaces of the needle 2a is constructed from a beveled portion 8 on an outer peripheral edge and a flat surface portion 9. The structure prevents a large moment load from being applied to base end portions of the inward flange portions 4b (4c) even when end surfaces of the needles 2a are abutted against an inside surface 10a (10b) of an inward flange portion 4b (4c) by a thrust load.

Abstract: The invention relates to a radial roller bearing which is embodied as a single-grooved grooved ball bearing. The bearing bodies are embodied as spherical disks having two symmetrical, parallel lateral surfaces from a spherical base shape.

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 machine, method and tooling to precision cold-form roller blanks for anti-friction bearings. The machine is a multistage progressive former using floating die cavities to enable simultaneous shaping of the ends of the roller with high accuracy and without flash. The tools and staged forming create an improved roller with an advantageous grain pattern and devoid of structural defects previously attributable to the presence of sheared end face material in the radiused corners of the blank and flash at its mid-section.

Abstract: A barrel-shaped bearing which comprises an external ring and an internal ring, at least one row of barrel-shaped rolling bodies arranged therebetween, the cage in the form of a disk which turns together with the rolling bodies, engages inside a peripheral groove around each rolling body and is provided with recesses corresponding to the number of the rolling bodies of the one row arranged on the external periphery of the cage. The total rolling surface of the internal ring is embodied such that the cross section thereof is concave along the entire axial length of the rolling body. The smallest distance between both sides of the cavity of the disk-shaped cage in the area of the external periphery thereof is less than the diameter of a rolling body in the area of the peripheral groove thereof.

Abstract: The ball roller according to the present invention has a unique shape so that it can be handled just as easily as a conventional ball while being endurable against high load as is a roller. The ball roller comprises a rolling portion having an arcuate surface, and two spherical end portions spherically protruding from both ends of the rolling portion. The rolling portion has a radius of curvature larger than that of each of the spherical end portions, curvature centers of the spherical end portions are located on the rotational axis of the rolling portion. In another embodiment of the present invention, a ratio between the maximum diameter d of the rolling portion and the distance W between the two apexes of the spherical end portions falls within a rage of approximately 80%±17%.

Abstract: Driving rollers 2, 3 which rotate in the same direction are arranged in parallel to each other. A plurality of convex portions 5a, 5b, 5c having different radii of curvature Rr1, Rr2 and Rr3 are formed along the axial direction at opposing positions on the driving rollers 2, 3. A rolling element 4 which is fed into the gap between the driving rollers 2, 3 and rotated is moved along tracks having different radii of curvature Rw1, Rw2 and Rw3 in the axial direction. There is provided a superfinishing grindstone 6 which is pressed on the rolling surface of the rolling element 4 moving on tracks having different radii of curvature to superfinish the rolling surface of the rolling element 4.

Abstract: A spherical roller bearing having a sealing arrangement and a closure arrangement to prevent the loss of lubricants from the bearing and to prevent the entrance of contaminants into the bearing.

Abstract: The contact portion of the end face of a conical roller, which is a portion to be slidingly contacted with a collar portion, is ground such that the outer contour line of the section thereof has a continuously curved line which passes through at least not only the first point but also between the third position and fourth position.

Abstract: A method of producing rolling elements for a rolling bearing comprises mixing to process rounded elements made of steel balls and spherical rolling elements having outer diameter portion portion becoming a rolling contact face. The rolling contact face has curvatures in an axial direction and a radial direction normal to the axial direction, and has at least one plane. The thus mixed elements are placed and processed in a space between two processing boards opposing each other via the determined space. Thereby, the surfaces of the rounded balls and the rolling elements are processed to be rounded.

Abstract: A tapered roller bearing comprises: an outer race 12 having a raceway surface 21; an inner race 11 having a raceway surface 20; and a plurality of rolling elements 15 located between the raceway surfaces and formed by third generatrices having a fixed radius of curvature R3 such that the rolling contact surface is convex in the axial direction; and where the center section 20a, 21a of the raceway surfaces 20, 21 is formed by first generatrices having a fixed radius of curvature R1 in an axially concave-shape, and the opposite ends 20b, 21b in the axial direction adjacent to the center section 20a, 21a are formed by second generatrices having a fixed radius of curvature R2 such that they separate from the rolling contact surface of the rolling element 15; and where the radius of curvature R3 of the third generatrices surface satisfies Equation [1] below. R3=s×R1 wherein 0.65≦s≦0.95  Eq. [1].

Abstract: The large-end-face roughness &sgr;1 of the tapered roller is set to be not less than 0.04 &mgr;mRa, consequently the assembling torque becomes generally constant and smaller in fluctuation over a range that the cone-back rib face roughness &sgr;2 is 0.03-0.23 &mgr;mRa. Also, the composite roughness &sgr;=(&sgr;12+&sgr;22)½ is set to be not more than 0.17 &mgr;mRa, consequently the preload retention rate on the regression curve can be made 90%. Further, the radius of curvature ratio R1/R2 resulting from dividing the convex radius of curvature R1 of the large end face of the tapered roller by the concave radius of curvature R2 of the cone-back rib face of the inner ring is set to be not more than 0.35, consequently the rotating torque becomes smaller in variation and also smaller in fluctuations over a range that the composite roughness &sgr; is 0.05-0.22 &mgr;mRa.

Abstract: The roller bearing 10 comprises a plurality of rollers 15 which are respectively interposed between a concave-shaped race surface 12 formed on an outer race 11 and a concave-shaped race surfaces 14 formed on an inner race 13. Each of the rollers 15 is structured such that the central portion of the rolling surface thereof is formed by a first convex-shaped bus 17 which corresponds to the concave-shaped race surfaces 12 and 14, while the two end portions of the rolling surface thereof are respectively formed by second buses 16 which have a radius of curvature smaller than the radius of curvature of the first bus 17.

Abstract: An antifriction bearing includes a plurality of rolling elements each having a lateral surface possessing a conical shape, with the rolling elements being positioned between a conical raceway and a cylindrical raceway to roll along the conical raceway and the cylindrical raceway. The lateral surface of each rolling element forms an angle with a center axis of the rolling element that is 3° at maximum, and the lateral surface of each rolling element has a convex curvature that is superimposed on the conical shape. The bearing can also include a first bearing ring having a running surface constituting one of the conical and cylindrical raceways. An antifriction bearing arrangement incorporating such an antifriction bearing is also provided with a stop element having a stop face contacting the end face of each of the rolling elements.

Abstract: In the roller bearing, plural of rollers 15 are interposed between an outer raceway 11 of an outer race 12 and an inner raceway 13 of an inner race 14, and a collar portion 16 is formed along one of the axial-direction end portions of the inner raceway 13. The central portion of one of the outer race and inner raceways 11, 14 and the opposing outer peripheral surface of the roller 15 is formed of a first bus with a given radius of curvature. The two end portion sides adjacent to the central portion are formed of a second bus with such a radius of curvature that causes the two end portion sides to part away from the other. The collar surface 19 of the collar portion 16 contacting with an end face of the roller 15 being a convex-shaped spherical surface is formed as a concave-shaped spherical surface.

Abstract: A tapered roller bearing that is well-suited for supporting a pinion in an automotive differential has a cone and a cup provided with opposed raceways that are crowned. The cone also has a thrust rib provided with a rib face at the large end of its raceway. In addition, the bearing has tapered rollers, each having a tapered side face that is crowned and a large end that is spherical. The rollers contact the raceways along their crowned side faces and the rib face along their spherical end faces. The roller length to large end diameter is less than 1.5. The crowning on the raceway, together with the crowning of the roller side face provide total end relief ranging between 700 &mgr;in. and 1500 &mgr;in. per inch. The centers of contact between the side faces and raceways are offset toward the rib face. The height of the rib face amounts to 30%-45% of the diameter of the large ends of the rollers. The radius of the spherical large end face for a roller exceeds 90% of the roller apex length.

Abstract: A tapered roller bearing comprises: an outer race 12 having a raceway surface 21; an inner race 11 having a raceway surface 20; and a plurality of rolling elements 15 located between the raceway surfaces and formed by third generatrices having a fixed radius of curvature R3 such that the rolling contact surface is convex in the axial direction; and where the center section 20a, 21a of the raceway surfaces 20, 21 is formed by first generatrices having a fixed radius of curvature R1 in an axially concave-shape, and the opposite ends 20b, 21b in the axial direction adjacent to the center section 20a, 21a are formed by second generatrices having a fixed radius of curvature R2 such that they separate from the rolling contact surface of the rolling element 15; and where the radius of curvature R3 of the third generatrices surface satisfies Equation [1] below.

Abstract: The ball roller according to the present invention has a unique shape so that it can be handled just as easily as a conventional ball while being endurable against high load as is a roller. The ball roller comprises a spherical rolling portion with an arched surface, and two spherical end portions spherically protruding from both ends of the spherical rolling portion. The spherical rolling portion has a radius of curvature larger than that of each of the spherical end portions, curvature centers of the spherical end portions are located on the rotational axis of the spherical rolling portion. In another embodiment of the present invention, a ratio between the maximum diameter d of the spherical portion 2 and the distance W between the two apexes of the spherical end portions falls within a rage of approximately 80%±17%.

Abstract: A method of producing rolling elements for a rolling bearing comprises mixing to process rounded elements made of steel balls and spherical rolling elements having outer diameter portion portion becoming a rolling contact face. The rolling contact face has curvatures in an axial direction and a radial direction normal to the axial direction, and has at least one plane. The thus mixed elements are placed and processed in a space between two processing boards opposing each other via the determined space. Thereby, the surfaces of the rounded balls and the rolling elements are processed to be rounded.

Abstract: The large-end-face roughness &sgr;1 of the tapered roller is set to be not less than 0.04 &mgr;mRa, consequently the assembling torque becomes generally constant and smaller in fluctuation over a range that the cone-back rib face roughness &sgr;2 is 0.03-0.23 &mgr;mRa. Also, the composite roughness &sgr;=(&sgr;12+&sgr;22)½ is set to be not more than 0.17 &mgr;mRa, consequently the preload retention rate on the regression curve can be made 90%. Further, the radius of curvature ratio R1/R2 resulting from dividing the convex radius of curvature R1 of the large end face of the tapered roller by the concave radius of curvature R2 of the cone-back rib face of the inner ring is set to be not more than 0.35, consequently the rotating torque becomes smaller in variation and also smaller in fluctuations over a range that the composite roughness &sgr; is 0.05-0.22 &mgr;mRa.

Abstract: A rolling member is utilized for such as a rolling bearing and the rolling members are disposed to be rollable between members which are relatively movable with respect to each other. The rolling member is provided with a rolling portion contacting the movable members during the rolling motion thereof and longitudinal both end portions. The rolling portion is formed to provide a protruded circular arc shape and the end portions are formed so as to provide a spherical shape, the circular rolling portion has a radius of curvature larger than a radius of each of the end spherical portions, and a distance between the end spherical portions is larger than a maximum diameter of the circular rolling portion.

Abstract: An antifriction bearing includes a plurality of rolling elements each having a lateral surface possessing a conical shape, with the rolling elements being positioned between a conical raceway and a cylindrical raceway to roll along the conical raceway and the cylindrical raceway. The lateral surface of each rolling element forms an angle with a center axis of the rolling element that is 3° at maximum, and the lateral surface of each rolling element has a convex curvature that is superimposed on the conical shape. The bearing can also include a first bearing ring having a running surface constituting one of the conical and cylindrical raceways. An antifriction bearing arrangement incorporating such an antifriction bearing is also provided with a stop element having a stop face contacting the end face of each of the rolling elements.

Abstract: When a crowning is subjected to a roller or on a rolling surface using a combination of two arcs, a crowning profile is specified in such a manner that each crowning quantity at two points where distances x in a bus extending direction from the center line of the roller are respectively situated at positions of 0.425 and 0.5 times an effective contact length Le, are respectively present between the value of a well-known logarithmic crowning when a bearing load P is 0.4 times a basic load rating C and the value of the logarithmic crowning when the bearing load P is 0.6 times the basic load rating C.

Abstract: An antifriction bearing having inner and outer races and rollers between the races accommodates axial misalignment of the races and also axial displacement of one race relative to the other. In one form, the inner race has a cylindrical raceway presented outwardly, whereas the outer race has a spherical raceway presented inwardly toward the cylindrical raceway. Each roller has two arcuate end surfaces and a cylindrical intervening surface. The arcuate end surfaces generally conform to and roll along the spherical raceway, while the cylindrical intervening surface rolls along the cylindrical raceway. In another form, the inner race has a spherical raceway that is presented outwardly and the outer race has a cylindrical raceway that is presented inwardly toward the spherical raceway. Each roller has two cylindrical end surfaces and an arcuate intervening surface.

Abstract: A bearing is provided which can be sufficiently processed by a usual NC grinding machine, and attain a life period that is substantially equal to that of a bearing having a theoretical crowning shape which is derived from the elastic contact theory, even when the bearing is used in a portion to which a heavy load or a high torque load is applied. As means for realizing such a bearing, a generating line of a rolling surface of a roller or a raceway surface of an inner or outer race is divided into a plurality of zones, and the shape of the generating line is approximated to a special curve shape which is theoretically derived, by a plurality of circular arcs which are contacted with each other on the border line between the corresponding zones. Therefore, it is possible to obtain a roller bearing which can be practically used, and which can attain a life period that is substantially equal to that of a bearing having an ideal crowning shape.

Abstract: The roller bearing 10 comprises a plurality of substantially cylindrical-shaped rollers 15 which are respectively interposed between a concave shaped race surface 12 formed on an outer race 11 and a concave-shaped race surfaces 14 formed on an inner race 13. Each of the rollers 15 is structured such that the central portion of the rolling surface thereof is formed by a first convex-shaped bus 17 which corresponds to the concave-shaped race surfaces 12 and 14, while the two end portions of the rolling surface thereof are respectively formed by second buses 16 which have a radius of curvature smaller than the radius of curvature of the first bus 17.

Abstract: In a case where crowning is provided on a contact surface of a tappet roller by the combination of, for example, two circular arcs, a logarithmic crowning is determined in which an edge load does not occur in the bearing pressure even if its inclination with respect to the cam is {fraction (5/1,000)} or thereabouts, and a crowning profile is set between two logarithmic crownings. In addition, the crowning profile is defined so as to be present between the logarithmic crownings in a case where the axial position x with the center in the direction of a bus set as an origin is at a position 0.85-fold and at a position 1.0-fold the half Le of the effective contact length, respectively.

Abstract: A self-aligning roller bearing includes an external ring with one curved external track, an internal ring with two curved internal tracks, two rows of rollers disposed between the external and internal rings, and a guide ring. The guide ring is located between the rows of rollers and is preferably configured as an circular annular disk. The guide ring has a rectangular cross section with the center line of the cross section running parallel to the bearing axis. The guide ring may also be dimensioned in such a way that the rollers are axially prestressed. The front faces of the rollers which face the guide ring are configured in a manner that the front faces only touch the guide ring at one point.

Abstract: A roller bearing with roller elements constructed as rollers (4) or balls arranged between an inner race (3) and an outer race (5), and with a thick-walled outer ring (6) if provided. The inner surface of the outer ring forms the outer race (5) and the outer surface is provided for direct rolling on a cylindrical matching roller path, and has a crowned contour (7) curved in longitudinal section. In accordance with the invention, the spherical crowned contour (7) of the outer ring (6) is formed from several arcs that pass smooth into one another whereby the radius of curvature of a central arc and the radius of curvature of an outer arc have in a ratio from 2 to 1 up to 5 to 1 in relation to one another.

Abstract: In the toroidal-type continuously variable transmission, the radial needle roller bearing includes a plurality of needle rollers, the two end portions of each of the needle rollers in the axial direction thereof are crowned, and the crowning amount is set such that, in the portion of the needle roller that is situated by 7-13% of the axial-direction length toward the axial-direction central portion of the needle roller from the axial-direction end face of the needle roller, the crowning amount is 0.1-0.4% of the outside diameter of the axial-direction central portion of the needle roller.

Abstract: A roller bearing with symmetric barrel shaped rollers comprising an inner race (13), an outer race (14) and rollers (11), each of which rollers have at least one rounded end, and being of the bearing type where rollers and race tracks have longitudinal section profiles with substantially the same radius of curvature, whereby the rollers during normal operating conditions are axially moveable between the race tracks without hindrance from axial confinements at the race tracks for allowing relative misalignment and axial displaceability of the race tracks, wherein the end drop zone has a length (d1) which is lower than 5% of the length (1a) of the roller, and which commences where the bend of the curvature of the roller in axial direction exceeds the normal curvature of the roller by 0.1°, and where the end drop of the roller is otherwise determined by the following relations, r/1a≧0.35 for &ggr; values up to 0.7°, and r/1a is ≧0.2 for &ggr; values between 0.7° and 1.4°.

Abstract: A roller bearing comprising an inner and an outer ring in concentrical arrangement, a series of roller elements being arranged in the space between said rings and being in contact with raceways provided in said rings. The bearing is characterized in that said raceways are provided with parallel grooves, each one of said grooves being arranged in the plane of rotation of said rings and extending along the entire envelope surface, and in mutual correspondence to said inner and outer rings and being arranged for mating interaction with protruding flanges of said roller elements corresponding to said grooves, said protruding flanges extending along the entire envelope surface of said roller elements.

Abstract: A muddy-water-proofed vehicle wheel supporting structure for mounting a wheel through a double-row tapered roller bearing on an end of an axle comprises a seal member interposed between a shoulder of the axle and a part constituting a sealing device, for example, a seal slinger, fitted to one of a pair of inner rings of the bearing that is brought into contact with the shoulder.

Abstract: A solid lubrication type self-aligning roller bearing is low in frictional torque and high in high-speed rotation performance. Only the space between fingers of the retainer protruding into the spaces between the outer ring and adjacent rollers arranged in two rows is filled with a lubricating composition manufactured by solidifying a mixture of an ultra-high-molecular-weight polyolefin and a grease to reduce the number of contact portions of the solid lubricating composition with the outer ring and the rollers. It is thus possible to considerably reduce torque and heat buildup due to sliding friction at the contact portions.

Abstract: A change bearing for rollers includes a mounting ring and a roller bearing set into the mounting ring. The mounting ring has a bore and an outside radial surface, and the roller bearing includes an inside ring, an outside ring and a plurality of cylinder-shaped pin rollers positioned between the inside ring and the outside ring. The pin rollers have a radius of curvature whose center is located diametrically across from the bearing axis. The inside ring is located at a predetermined position in relation to the outside radial surface of the mounting ring and the outside ring is positioned in the bore of the mounting ring at a position that is based on component tolerances and desired bearing play.

Abstract: The raceway groove width (W) of the inner ring 2 and the length (L) of the tapered roller 3 are finished within predetermined dimensional tolerances. The retaining rib face 2b of the inner ring 2 is machined such that it is a surface parallel to the small end faces 3b of the tapered rollers 3. The clearances .delta. which are defined when the tapered rollers 3 are disposed on the raceway surface 2a of the inner ring 2 and are contacted at the large end faces 3a thereof with the cone back face rib face 2c is secured to be within the dimensional range, .delta..ltoreq.0.4 mm.

Abstract: The present invention refers to a method for clearance adjustment in a rolling bearing having an angle of contact close to 0.degree., and of the type incorporating a number of rollers provided between and in contact with two race tracks, said rollers and race tracks having longitudinal section profiles of essentially the same radii of curvature, said rollers thereby being axially movable along the race tracks without being hindred by axial limitations at the race tracks, in order to allow relative misalignment and axial displaceability of the race tracks.

Abstract: A roller bearing comprising an outer ring having an outer ring raceway, an inner ring having an inner ring raceway, the inner peripheral surface at the end portion of the outer ring and/or the outer peripheral surface at the end portion of the inner ring formed with a flange portion, and a plurality of rollers having a rolling surface in contact with the outer and inner ring raceways, a sliding contact face in sliding contact with the inner face of the flange portion, and a chamfered portion provided between the sliding contact face and the rolling face, the sliding contact face smoothly connected to the chamfered portion in a curved surface the radius of curvature of which is at least 0.08 mm, and provided that the center line average height roughness of the sliding contact surface is .delta..sub.1 while the center line average height roughness of the inner face in contact with the sliding surface is .delta..sub.2, the composite roughness represented by the formula (.delta..sub.1.sup.2 +.delta..sub.2.sup.2).

Abstract: A spin bearing assembly including, a pair of mutually opposing complementary bearing support members having mutually spaced apart bearing support surfaces which may be, for example, bearing races and a set of spin bearings located therebetween. Each spin bearing includes a pair of end faces, a central rotational axis passing through the end faces, a waist region substantially mid-way between the end faces and having a first thickness dimension, and discrete side surface regions located between the waist region and the end faces and having a second thickness dimension different from the first thickness dimension of the waist region and wherein the side surface regions further have respective curvilinear contact surfaces adapted to provide a plurality of bearing contact points on the bearing support members.

Abstract: A bearing arrangement, designed in an X-configuration for a planet gear is provided with two angular roller bearings mounted a certain distance apart. Barrel-shaped needles have a large radius of curvature and their length is considerably greater than their diameter. Raceways of the two angular roller bearings have a circular curvature, center of which is located in the radial direction, outside the raceway diameter and in the axial direction, between inner lateral surface and axial center of angular roller bearing in question. As a result, the bearing arrangement is able to pivot slightly even though its dimensions are very small and can also absorb axial loads.

Abstract: The boundary between the rolling surface 3a and the larger end surface 3b of a roller 3 and the boundary between the rolling surface 3a and the smaller end surface 3c are formed with rounded portions Rb and Rc, respectively. The rolling surface 3a and the rounded portion Rb associated with the larger end surface 3b are smoothly continuous with each other through a first arc R1, while the larger end surface 3b and the rounded portion Rb are smoothly continuous with each other through a second arc R2.

Abstract: A self aligning roller bearing with retainer comprises an outer ring having an outer ring raceway in a shape of a spherical concave surface with a single center, an inner ring having a pair of inner ring raceways opposite to the outer ring raceway, a plurality of convex rollers provided rotatable between the outer ring raceway and the inner ring raceway, and a pair of retainers comprising a main portion formed in a hollow cylindrical frustum shape and having a plurality of crossbars, an outwardly flanged portion extending radially outward from the larger diameter end of the main portion and an inwardly flanged portion extending radially inward from the smaller diameter end of the main portion, and connected to the outwardly flanges portion by the crossbars so as to form a plurality of pockets each defined by two of the crossbars and outwardly and inwardly flanged portions to receive one of the convex rollers, the outwardly flanged portion having protrusions each protruding towards the pocket so as to rub agai

Abstract: A retainerless self-aligning angular contact antifriction bearing apparatus including an inner race member having a spheroidal inner race surface, an outer race member including a pair of convex outer race surfaces opposing the inner race surface, and a plurality of rollers arranged in axially oppositely inclined rows. Each roller includes a concave longitudinal profile having a radius of curvature greater than the radius of curvature of each of the spheroidal inner race surface and the associated convex outer race surface.

Abstract: A roller bearing apparatus including inner and outer rings defining a pair of raceway spaces, a plurality of rollers arranged in oppositely axially inclined rows each occupying one of the raceway spaces, and a guide member. The guide member includes a ring between the roller rows and oppositely extending shortened prongs or stubs extending only a short distance between the rollers so as not to take up space that otherwise could be used for one or more additional rollers. The pocket bottoms are angled to skew the rollers to promote roller precession or indexing. Alternatively, the guide member can include a reduced number of larger prongs to replace one or more of the stubs.

Abstract: A roller bearing constructed in accordance with the invention comprises inner and outer rings and rollers therebetween as is known. The rings have no ribs, flanges or grooves but instead axial inner surfaces of the rings provide raceways which are substantially convex and the axial outer surfaces of the rollers are substantially concave to match. These concave and convex surfaces contact one another over contact zones. Each roller has an external surface which is asymmetrical relative to the center of the roller and the geometry is such that during use frictional moments develop at the contact zones between the rollers and the rings to generate a positive skew force on the rollers. This renders the bearing self-tracking.

Abstract: A double-row spherical roller bearing comprises an inner race, an outer race, two retainers each molded of a synthetic resin, and double-rows of spherical rollers rotatably received in pockets of the retainers and arranged one after another in the equally spaced relationship in the circumferential direction. Each retainer is molded such that an annular portion on the large diameter side and an annular portion on the small diameter side are integrally jointed to each other with a plurality of retainer bars bridges therebetween. Each retainer bar comprises an inner portion located on the inner race side and an outer portion on the outer race side. Each side surface of the inner portion is defined by a part of the spherical surface extending around the spherical surface of each spherical roller. In addition, each side surface of the outer portion is defined by a first surface, a second surface and a third surface.

Abstract: At least one of the inner race, the outer race and rolling elements in the improved ball-and-roller bearing is made of an alloy steel that contains 0.1-1.2 wt % of C, 3.0-18.0 wt % of Cr, 0.01-1.5 wt % of Si, 0.3-1.5 wt % of Mn, up to 2.5 wt % of Mo, up to 0.002 wt % of O.sub.2 and up to 0.015 wt % of S and which is subjected to plasma-assisted carburization to such an extent that the relative surface carbon area is at least 15% the surface carbon concentration is in the range of 1.6-3.5 wt % and the amount of surface retained austenite is in the rang of 20 vol %-45 vol %. The bearing can work effectively for a prolonged lifetime even if it is placed under hostile conditions as exemplified by an increased areal pressure of load and entrance of foreign matter into lubricating oils.

Abstract: The clutch includes inner and outer rotation members which respectively have the inner and outer raceways of mono-hyperboloids of revolution or cylindrical surfaces about the same axis line facing each other to form combined raceways, a plurality of intermediate rotation members of cylindrical shapes disposed slantly at an angle with the axis of the inner and outer rotation members with the raceways so that the surface thereof is in line contact with the raceways, and an energizing member which energizes either the inner rotation member or the outer rotation member in a direction to clutch both the members. Depending on rotational direction, the clutch functions as a free rotating rolling-contact bearing or clutch.

Abstract: A radial roller bearing consisting of rings and rollers, either the rolling contact surface of each roller or the raceway surfaces of the rings or both are crowned, the amount of crowning which is defined as .DELTA.t/l i.e., the depth of crowning .DELTA.t to the effective roller length of l, is set to 0.0007 to 0.002, the ring has a rib at its one end, the end surface of each roller which makes contact with the rib is spherically convex, while the contacted surface of the rib is spherically concave.

Abstract: A self-aligning roller bearing having a plurality of spherical rollers disposed between the track surface of an inner race and the track surface of an outer race. Each roller has a rolling surface generator having central portion corresponding to at least 80% of the rolling surface axial length and of a single radius of curvature smaller than those of the inner and outer track surfaces. The rolling surface generator also has opposite end portions each with one or more radii of curvature smaller than that of the central portion.