Abstract: A generatrix shape to which crowning is applied includes a first generatrix shape which is formed in a central portion in an axial direction of at least one of an outer ring raceway surface, an inner ring raceway surface, and a rolling surface of a roller and is composed of a straight line, a pair of second generatrix shapes which are formed from both ends in the axial direction toward the outside in the axial direction of the first generatrix shape and are composed of a single arc curve, and a pair of third generatrix shapes which are formed from both ends in the axial direction toward the outside in the axial direction of the second generatrix shape and are composed of a composite curve of a single arc curve and a logarithmic curve.

Abstract: A roller for a roller bearing has a first end surface and a second end surface and a rolling surface between the first and second end surfaces. The first end surface has an at least partially ground profile having a non-constant curvature such as a logarithmic profile. Also, an assembly including a grinding tool and a roller with an end surface having a ground non-constant curvature.

Abstract: A load-variable rolling bearing includes: an outer ring having an outer ring raceway surface with spherical surface contact portions having concave arch sections and a variable contact portion having a shape of a cylinder in such a manner as to be adjacent to the spherical surface contact portions in an axial direction of the spherical surface contact portions; an inner ring having an inner ring raceway surface with spherical surface contact portions having concave arch sections and a variable contact portion having a shape of a cylinder in such a manner as to be adjacent to the spherical surface contact portions in an axial direction of the spherical surface contact portions; and a plurality of rolling elements each having a cylindrical variable contact portion and spherical surface portions formed with convex spherical surfaces on both sides of the variable contact portion.

Abstract: Provided is a double-row self-aligning roller bearing including: an inner ring; an outer ring having a spherical raceway surface; and rollers arranged in two rows and interposed between the inner ring and the outer ring, wherein a ratio of a contact angle ?1 in one row to a contact angle ?2 in the other row falls within a range of 0.25??1/?2?0.5, and a ratio of distance B1 in a bearing width direction from an end face of the bearing on a side of the one of the rows to an intersection of two lines of action defining the contact angles of the two rows, relative to a distance B2 in the bearing width direction from an end face of the bearing on a side of the other of the rows to the intersection falls within a range of 0.5?B1/B2?0.6.

Abstract: A tapered roller bearing for an automobile includes an inner ring including a raceway surface having a tapered shape on an outer periphery, an outer ring including a raceway surface having a tapered shape on an inner periphery, a plurality of tapered rollers incorporated into a space defined between the raceway surfaces, and a retainer configured to receive the tapered rollers. The inner and outer rings are each made of carburized steel, and the raceway surfaces of the inner and outer rings each have a straight generating line shape. The tapered rollers each are made of high carbon chromium bearing steel, and each have a rolling surface including a straight portion, which is formed at a center portion in an axial direction, and crowning portions, which extend from the straight portion to both end portions. The crowning portions are each formed of logarithmic crowning.

Abstract: A difference between a maximum value and a minimum value of arithmetic mean roughness Ra of an annular surface region in contact with a larger flange surface, in a larger end face of the tapered roller, is not greater than 0.02 ?m. A value of a ratio R/RBASE is not smaller than 0.75 and not greater than 0.87 where R represents a set radius of curvature of the larger end face of the tapered roller and RBASE represents a distance from a point which is an apex of a cone angle of the tapered roller to the larger flange surface of the inner ring. A ratio Rprocess/R is not lower than 0.5 where Rprocess represents an actual radius of curvature after grinding of the larger end face of the tapered roller and R represents a set radius of curvature.

Abstract: The double-row self-aligning roller bearing includes an outer ring having a spherical raceway surface, and each of rollers in two rows has an outer peripheral surface whose cross-sectional shape corresponds to the raceway surface of the outer ring. The rollers in the two rows have different lengths from each other, and the length of the longer rollers is equal to or greater than 36% of a bearing width. A ratio of a contact angle of the shorter rollers relative to a contact angle of the longer rollers is within a range of 1:4 to 1:2. The contact angle of the shorter rollers has a range of 3° to 5°, and the contact angle of the longer rollers has a range of 11° to 14°.

Abstract: Two projecting portions (45a and 45b) configured to guide a tapered roller (3) on distal end surfaces thereof are formed on a side surface (43a) of a pillar portion (43) of a retainer (4) so as to be separated apart from each other in a roller axis direction. The projecting portions (45a and 45b) are separated apart from each other in the roller axis direction with respect to both a small-diameter-side annular portion (41) and a large-diameter-side annular portion (42). The projecting portions (45a and 45b) each have a force-fit margin (F).

Abstract: A tapered roller bearing includes inner and outer rings including raceway surfaces having tapered shapes on their outer and inner peripheries, respectively, tapered rollers between the raceway surfaces, and a retainer configured to receive the tapered rollers. At least the raceway surface of the inner ring includes cut crowning of a complex curve including a center curve and end portion curves formed on both sides of the center curve each have a curvature radius smaller than a curvature radius of the center curve. The tapered rollers each have a rolling surface including a straight portion and logarithmic crowning portions formed on both sides of the straight portion. When the raceway surface of the inner ring has an effective raceway surface width represented by LG, and the straight portion of the rolling surface of the tapered roller has a width represented by LW1, 0.7?LW1/LG<0.95 is satisfied.

Abstract: A double-row self-aligning roller bearing, which is suitable for receiving an axial load and a radial load, and loads having different magnitudes acting on rollers in two rows, and achieves sufficient load capacity for the rollers that receive axial load within the constraint of dimensional standards, is provided. The double-row self-aligning roller bearing includes inner and outer rings; and rollers in two rows arranged in a bearing width direction interposed between the inner and outer rings and having lengths different from each other. The roller has an outer peripheral surface of a cross-sectional shape along a raceway surface of the outer ring having a spherical shape. Length of the longer rollers is equal to or greater than 39% of the bearing width. A ratio of contact angle of the shorter rollers and contact angle of the longer rollers is within a range of 1:4 to 1:2.

Abstract: A wind turbine rotor shaft arrangement comprising a shaft supporting wind turbine blades and a non-rotating first housing structure (mounted to a wind turbine nacelle framing) along with a first rolling bearing supporting (in a first axial direction) the shaft to the first housing structure at a first support point. The first rolling bearing is a self-aligning bearing comprising a first inner ring, a first outer ring and a set of rolling elements interposed therebetween. Each roller is asymmetric, having a curved raceway-contacting surface contacting at least one of the curved inner/outer raceways of the first inner/outer ring, respectively. A contact angle between each roller and the respective raceway is inclined respective to the shaft radial direction. A non-rotating second housing structure (mounted to the wind turbine nacelle framing) supports the shaft. A second rolling bearing supports the shaft by the second housing structure at a second support point.

Abstract: A self-aligning roller bearing includes an outer ring, an inner ring, spherical rollers, a cage having a plurality of pockets that contain the spherical rollers, and a guide ring. Each spherical roller may be rotated on an imaginary line passing through a contact point at which the spherical roller contacts an outer raceway surface and a contact point at which the spherical roller contacts an inner raceway surface. Each pocket has a clearance between the pocket and a corresponding spherical roller, and the size of the pocket is set so that the rotation of the corresponding spherical roller is limited. The guide ring has such a side-surface shape that a small clearance is ensured between the spherical roller and the guide ring even when the spherical roller is rotated, in the pocket, on the imaginary line by a maximum amount at which the rotation of the spherical roller is limited.

Abstract: A roller bearing of the type having a flange on which thrust loads are received shows improved ability to form an oil film at the contact surface portions of the end surface of a roller and the flange. The contact surface portions are both inclined at an angle of not less than 0.1° and not more than 1.5° with respect to the radial direction, over the entire circumferences of the respective contact surface portions.

Abstract: A radial rolling bearing (10) with rolling bodies (24) which are received in at least one cage (26, 28) and which are arranged between an inner ring (20) and an outer ring (22). The radial rolling bearing (12) is radially separable, and the radially multipart inner ring (20) can be fixed on a shaft (16) using two clamping rings (36, 38) which are attached to the axial ends of said inner ring. The inner ring (20) is designed without rims on the axially outer sides, and the clamping rings (36, 38) take on the function of inner ring rims, the rolling bodies (24) running against inner run-on surfaces (50) of the clamping rings (36, 38) in the axial direction. On the basis of the at least partial positioning of the clamping rings (36, 38) axially below the cages (26, 28) or the outer ring (22), the clamping rings (36, 38) take on two additional functions in addition to the actual clamping ring main function of fixing the inner ring (20) on the shaft (16).

Abstract: An in-transit mixing machine drive (2) having an output bearing (8) for supporting an output shaft for rotation relative to a drive housing, in which the output shaft is arranged inclined relative to a horizontal plane (5) at an angle (?) and the output bearing (8) is formed by a pendulum roller bearing (9) whose rolling bodies (13, 14) roll in two bearing rows (10, 11) at pressure angles (?, ?) about a bearing axis (12). The pressure angles (?, ?) of the two bearing rows (10, 11) differ from each other or the rolling bodies (13, 14) of the two bearing rows (10, 11) differ from each other.

Abstract: In a tapered roller bearing assembly, a crowning profile formed portion of the roller rolling surface is made up of a contact area crowned portion, which is held in contact with an inner ring raceway surface, and a non-contact area crowned portion which is held in non-contact with the inner ring raceway surface. The contact area crowned portion and the non-contact area crowned portion have their generatrices extending in an axial direction of a roller, which generatrices are represented by corresponding continuous lines represented by different functions and continued smoothly at a point of connection, and the curvature of the generatrix of the non-contact area crowned portion in the vicinity of the connection point is chosen to be smaller than the curvature of the generatrix of the contact area crowned portion.

Abstract: The present invention relates to a spacer device for roller elements in a toroidal roller bearing, and a method for manufacturing a toroidal roller bearing comprising a plurality of spacer devices. The toroidal roller bearing allows for axial and angular displacement between an inner and outer bearing ring. The spacer device provides first and second roller-contacting surfaces having a concave shape adapted to conform with respective convex contacting surfaces of the toroidal roller elements, and at least one axial end portion which is elastically deformable.

Abstract: A ball roller bearing, which has an outer and inner bearing ring with a groove-shaped raceways and ball rollers, which roll between the bearing rings in the raceways. The rollers are held at distances from each other in the circumferential direction by a bearing cage and which have a width that is dimensioned larger than the radial distance between the inside and the outside of the bearing rings. The raceways are divided into two segments by an axially centered annular groove such that a first ball roller rolls on two first diagonally opposed track segments and a second ball roller rolls on two second diagonally opposed track segments of the bearing rings. Both bearing rings are single-piece components, and the bearing cage is formed by two identical double prong-type cages acting independently of each other. The bearing is filled with the ball rollers by an axial tilt cam assembly method.

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 bearing ring comprises a raceway for a rolling member as well as at least one lateral rim for axially guiding the rolling member. To produce the bearing ring a notch is introduced into a running surface of the bearing ring which faces the rolling member. A final contour of the bearing ring is created by means of a hard turning process.

Abstract: A method for producing, ball rollers. The following method steps are performed to produce the ball rollers: (A) cutting unfinished sections at a defined length from a round wire that has a defined diameter, (B) compression molding ball roller blanks that have end face depressions in the form of a die tool, and (C) grinding the ball roller blanks to the desired final dimensions in a ball grinding machine. The cut-off unfinished sections have a volume by which during compression molding an approximately tangential raceway transition from one ball roller half to the other ball roller half and material fibers extending under the running surfaces of the ball rollers parallel or approximately parallel to the running surfaces arise. In addition, the ball roller blanks are ground to the final dimensions in a horizontal ball grinding machine loaded exclusively with ball roller blanks of the same size.

Abstract: A tapered roller bearing (1a, 1b) satisfies the following three conditions: (a1) 0.8?Hi/Dw?1.2, (b1) 1.01?dm/dh?1.05, and (c1) 2.1?L/Dw?3.0, where a pitch circle diameter at a center of a roller length along an axis line (X) of each tapered roller (4) is (dm), the radial dimension of the inner ring (2) at an intersection of the inner ring raceway (2a) and a perpendicular line (v) extending from a position of the pitch circle diameter in a direction perpendicular to the axis line is the thickness (Hi) of the inner ring, a cross-sectional center diameter of the roller bearing is (dh), the length of the tapered roller (4) is the length (L) of the tapered roller, and a half of the sum of the large diameter dimension and the small diameter dimension of the tapered roller (4) is the diameter (Dw) of the tapered roller.

Abstract: A spherical roller bearing having a flanged disk designed as a hollow body, formed from a straight pipe section that is bent to form a ting having two ring ends that are joined. The ring is shaped into a flanged disk with a desired axial section geometry in a pressing device with a contour tool in a single pass.

Abstract: A radial roller bearing, in particular a single-track ball roller bearing, which has an outer bearing ring with an inner groove track, an inner bearing ring with an outer groove track and ball rollers, which are disposed parallel to one another and held in a peripheral direction at even distances from one another by a plastic bearing cage, that roll between the bearing rings in the groove tracks. Each roller has two lateral surfaces that are flattened symmetrically from a spherical base form and a defined axial tilting clearance. The cage has two axially separated, pocketed cage halves which can be assembled in a positive-fitted, form-locked or integral fashion by opposing connecting elements.

Abstract: A tapered roller bearing includes an outer ring, an inner ring, a plurality of tapered rollers interposed between the outer ring and the inner ring, and a cage for the tapered rollers. Ra is smaller than Rb where Ra represents a radius of curvature of a large end face of the tapered roller and Rb represents a radius of curvature of an end face of a large rib portion of the inner ring.

Abstract: A ball roller bearing which has an outer and inner bearing ring and ball rollers arranged between the rings, which roll in groove-shaped tracks in the rings and are held at a uniform distance to one another by a window cage. The cage has two lateral angle ribs, pocket bridges, which connect the ribs and cage pockets separated by the pocket bridges. The pockets have a cross-shaped hole formed from a contour perpendicular to the circumferential direction and a cross-sectional contour of a ball roller arranged longitudinally to the circumferential direction. The side edges are formed from the pocket bridges, which have radii of arch-shaped guide surfaces corresponding to the running surfaces of two ball rollers. The pocket bridges have additional material profiling between the side edges and on the guide surfaces for axial stiffening of the cage and damping bearing noise.

Abstract: A method for producing a bearing ring for a roiling bearing, the bearing ring comprising a raceway for a rolling member as well as at least one lateral rim for axially guiding the rolling member. In one step of said method, a notch is introduced into a running surface of the bearing ring which faces the rolling member. The final contour of the bearing ring is created by means of a hard turning process.

Abstract: A double row roller bearing which has an outer and inner bearing ring and ball rollers, which have lateral faces and are arranged next to each other in rows, arranged between the bearing rings. The rollers roll in raceways incorporated into the inner face of the outer bearing ring and outer face of the inner hearing ring. The raceways run in parallel and have pressure angle axes that are pitched at a pressure angle relative to a bearing radial axis. The rollers have a distance relative to each other which excludes mutual frictional contacts. For this purpose, the distance of the pressure angle axes of the raceways is enlarged and both rows of rollers are guided in separate bearing cages, while the raceway of the rollers of the row with the larger reference circle arranged on the inner bearing ring has a one-sided axial extension using the distance.

Abstract: A radial bearing configured as a single-row spherical roller bearing is provided that includes an inner and outer bearing ring, and rollers arranged between the bearing rings. The rollers have two side faces which are flattened symmetrically from a spherical base shape, and roll in two groove-shaped raceways which are defined by two axial rims. The width of the rollers between their side faces is at least 70% of the diameter of the spherical base shape and is greater than the distance between the axial rims. The rollers are in full linear contact with their running faces in the bearing rings at an operational pressure angle of up to 25° on both sides of the bearing longitudinal axis. The distance between radially opposite axial rims when the bearing rings are arranged eccentrically to each other is less than the diameter of the spherical base shape of the rollers.

Abstract: A roller bearing includes: an inner ring having an inner ring raceway; an outer ring having an outer ring raceway; and a plurality of rollers interposed between the inner ring raceway and an outer ring raceway, wherein a crowning is formed on at least one of the inner ring raceway, the outer ring raceway, and a roller rolling contact surface, wherein an optimal value of a drop amount of the crowning at an end of an effective length is determined, from a diameter of a roller and an effective length of the roller, and wherein drop amounts of the crowning at a plurality of positions in a bus-line direction of the crowning are within an allowable range set forth in a specific table.

Abstract: A ball roller bearing and to a method for the installation thereof. The ball roller bearing has an outer bearing race, and an inner bearing race, and a plurality of ball rollers, which are disposed between the bearing races and are held at equal distances to each other by a bearing cage. For this purpose, the ball rollers have a width of approximately 70% of the diameter of a spherical shape thereof, and roll with bearing surfaces thereof in two groove-shaped raceways, the depth of which is smaller than the distance between the outer and inner bearing race. The cage pockets of the bearing cage have a cross-sectional contour of a ball roller disposed in the longitudinal and transverse directions to the circumferential direction. The method for installation of the ball roller bearing is a cross/oblique pivot mount between the inner and outer bearing races and the ball rollers.

Abstract: A double-row angular contact bearing and which has outer and inner bearing rings with two rows of rolling elements disposed between the bearing rings that are held by two bearing cages interspaced at even distances. At least one row is configured as balls with parallel lateral faces that are symmetrically flattened. Both rows of rolling elements roll in adjacent races machined into the inner face of the outer ring and the outer face of the inner ring. The contact angle axes are pitched towards each other in an O-arrangement or X-arrangement and the races are axially delimited only on one side by shoulders. Additional clearance and supporting contours are formed at axial edge sections, opposite the shoulders, onto the races. The contours can be used to fit the balls into angular contact by axially inserting them into the clearance between the bearing rings and then tilting them into the races.

Abstract: A roller for a rolling bearing has an outer surface revolving about an axis of symmetry and a lateral face arranged on either side of the outer surface. The roller is intended to rotate in the bearing about the axis of symmetry while bearing on the outer surface. The roller has two recesses produced respectively on one lateral face extending along the axis of symmetry. The recesses have an opening formed on the lateral face and are separated axially by a material bridge. The recesses are defined by a lateral revolving surface, the shape whereof is divergent tapered from the opening to the material bridge.

Abstract: In a tapered roller bearing assembly, a crowning profile formed portion of the roller rolling surface is made up of a contact area crowned portion (7), which is held in contact with an inner ring raceway surface (1a), and a non-contact area crowned portion (8) which is held in non-contact with the inner ring raceway surface (1a). The contact area crowned portion (7) and the non-contact area crowned portion (8) have their generatrices extending in an axial direction of a roller (3), which generatrices are represented by corresponding continuous lines represented by different functions and continued smoothly at a point of connection, and the curvature of the generatrix of the non-contact area crowned portion (8) in the vicinity of the connection point is chosen to be smaller than the curvature of the generatrix of the contact area crowned portion (7).

Abstract: A gear unit having at least one shaft supported by a bearing in the gear unit housing, the spatial region of a bearing of a shaft situated in a cutout of the gear unit housing being limited at least partially towards the interior of the gear unit by a limiting device, in particular one that has a cutout for a shaft supported in the bearing, the lowest point of the cutout effecting a minimum oil level in the spatial region of the bearing.

Abstract: A tandem roller bearing having circumferential inner and outer races each having first and second contact surfaces with convex profiles is provided. Rolling elements are arranged between the inner and outer races, each of the rolling elements having a concave profile corresponding to the convex profiles of a respective pairing of the first contact surfaces of the inner and outer races or of the second contact surfaces of the inner and outer races. A cage is arranged between the inner and outer races that separates and is guided by the rolling elements. The rolling elements include first and second sets of rolling elements having first and second axes of rotation that are arranged between the first and second contact surfaces of the inner and outer races, respectively. The first and second axes of rotation are inclined in a same direction with respect to a central axis of the inner race.

Abstract: The angular contact roller bearing has an outer bearing ring, an inner bearing ring, a plurality of ball rollers arranged between the rings, and a bearing cage. The ball rollers in the two adjacent rows have pressure angle axes extending parallel to one another and are arranged directly one next to the other with their side faces point toward one another. Adjacent ball rollers in the two rows are arranged on a common rotational axis. The ball rollers have diameters and widths which are dimensioned in such a way that envelope cones which form tangents with all the ball rollers at their diameters are arranged with their cone tips precisely at the intersection point of the common rotational axes of the bearing longitudinal axis.

Abstract: A radial anti friction bearing (1) which is configured as a single-row spherical roller bearing, which includes an outer bearing ring (2), an inner bearing ring (3) and a plurality of spherical rollers (5) that are arranged between the bearing rings (2, 3). The spherical rollers have respectively two side faces (6, 7) which are flattened symmetrically from a spherical base shape, are retained with uniform spacing to each other a bearing cage (4) and roll with their running faces (8) in two groove-shaped raceways (11, 12) which are defined, respectively, by two axial rims (13, 14 and 15, 16). The width (bK) of the spherical rollers (5) between their side faces (6, 7) is smaller than the distance (aB) between the radially opposing axial rims (13, 15 and 14, 16), such that the spherical rollers (5) can be in the space therebetween via the axial mounting method in the radial anti friction bearing.

Abstract: The radial rolling bearing has an outer bearing ring, an inner bearing ring, and spherical rollers arranged between bearing rings. The spherical rollers have two flat side faces arranged parallel to one another. The spherical rollers are retained with uniform spacing to one another in the peripheral direction by a bearing cage. The spherical rollers have a width between their side faces of approximately 70% of the diameter of their spherical basic shape. The running faces of the rollers roll in two groove-shaped raceways which are formed in the inner side of the outer bearing ring and in the outer side of the inner bearing ring. At least one of the axial rims which delimit the groove-shaped raceways is reduced in radial height such that the radial bearing can be equipped with an increased number of spherical rollers in an axial assembly process.

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: 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: The invention relates to a roller bearing comprising an inner ring that defines a bearing axis and an outer ring, said rings forming bearing races. Roller bodies are provided between the races, the geometry of the roller bodies and the races being adapted to one another in such a way that the roller bearing forms a barrel roller bearing that can be stressed on one side. Preferably the roller bodies lie against two osculation contact points lying outside the self-locking region on the races of the inner and outer rings.

Abstract: A radial rolling bearing, which has an outer bearing ring, an inner bearing ring, and rollers, which are arranged between the bearing rings and held at uniform distances from one another in a peripheral direction by a bearing cage in individual cage pockets. The rollers are spherical disks that have parallel lateral surfaces which are symmetrically flattened from a basic spherical shape and which roll in groove-type raceways with their faces. The raceways are incorporated into the inner face of the outer bearing ring and the outer face of the inner bearing ring. The rollers are axially guided between the bearing rings via two low-friction line contacts between lateral surfaces and the longitudinal webs of the cage pockets. The rollers are configured to have a defined degree of freedom for self-alignment to the pressure angle of the radial rolling bearing.

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: The radial antifriction bearing has an outer bearing ring, an inner bearing ring and roller bodies, which are arranged between the bearing rings, are held at uniform distances from one another in the peripheral direction by a bearing cage. The roller bodies are discs that each have two parallelly arranged lateral surfaces which are symmetrically flattened from a spherical basic shape. In order to prevent edge stresses between the discs and the raceways, at least the raceway in the inner bearing ring, on its outer edge areas, transition into a logarithmically decreasing profile.

Abstract: A radial roller bearing, which is a single-grooved ball bearing. The bearing bodies are spherical disks with two symmetrical, parallel lateral surfaces from a spherical base shape. The bearing has a larger contact surface of the spherical disk in relation to the bearing body tracks thereof, as well as, an increased number of bearing bodies. One part of the width of the disks, between the lateral surfaces thereof, is larger than the distance between the inner side of the external bearing ring and the external side of the inner bearing ring, but equal to or smaller than the width of the bearing body tracks. Also, the use of the disks in the bearing takes place according to an eccentric mounting method where the disks are arranged in a transversal manner in the bearing body tracks and are arranged on top of each other in relation to the lateral surfaces thereof.

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: The present invention provides a ball roller rolling member which can take crossing arrangement, conveyance including alignment and separation can be easily automated, lateral both sides of a rolling curved portion can be easily discriminated and the rolling curved portion thereof can be precisely ground. Such ball roller rolling member comprises a rolling curved portion having a circular-arc outer periphery and end spherical portions provided on both sides of the rolling curved portion so as to be spherically swelled outward, respectively, the rolling curved portion having a radius of the circular-arc portion larger than a radius of curvature of each of the end spherical portions.

Abstract: A radial anti friction bearing (1) which is configured as a single-row spherical roller bearing, which includes an outer bearing ring (2), an inner bearing ring (3) and a plurality of spherical rollers (5) that are arranged between the bearing rings (2, 3). The spherical rollers have respectively two side faces (6, 7) which are flattened symmetrically from a spherical base shape, are retained with uniform spacing to each other by a bearing cage (4) and roll with their running faces (8) in two groove-shaped raceways (11, 12) which are defined, respectively, by two axial rims (13, 14 and 15, 16). The width (bK) of the spherical rollers (5) between their side faces (6, 7) is at least 70% of the diameter (dK) of the spherical base shape and as a result, is greater than the distance (aB) between the axial rims (13, 15 and 14, 16) of the raceways (11, 12) in the bearing rings (2, 3).