Abstract: A friction plate is formed in such a manner that a plurality of friction material segments fixed to an annular core plate, wherein a passage extends through from an inner diameter side to an outer diameter side and is defined between the plurality of friction material segments, and a forming portion for retaining air is provided on a bottom surface of the passage.

Abstract: A friction plate is formed by annularly fixing a plurality of friction material segments to a substantially annular core plate, and a minute groove is formed on a surface of the friction material segment.

Abstract: A friction plate is formed in such a manner that a plurality of friction material segments fixed to an annular core plate, wherein a passage extends through from an inner diameter side to an outer diameter side and is defined between the plurality of friction material segments, and a forming portion for retaining air is provided on a bottom surface of the passage.

Abstract: A friction plate is formed by annularly fixing a plurality of friction material segments to a substantially annular core plate, and a minute groove is formed on a surface of the friction material segment.

Abstract: A toroidal-type continuously variable transmission, has: first and second disks; a plurality of trunnions; a plurality of displacement shafts respectively supported on associated trunnions; a plurality of power rollers respectively interposed between the first and second disks; and, a plurality of thrust bearings respectively interposed between the power rollers and trunnions, each of the thrust bearings including an outer ring, an inner raceway formed in the outer end face of the power roller, a plurality of rolling elements, and a circular-ring-shaped retainer, wherein, in case where the density of a retainer material constituting the retainer is ?d, the elastic modulus of the retainer material is Ed, the density of rolling element materials is ?c and the elastic modulus of the rolling element materials is Ec, { ( ? d · E d ) / ( ? c · E c ) } 1 2 ? 0.6 is satisfied.

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: When an information provision program is implemented, an input screen is displayed on a display section (step 101). A specific designation number is input (step 103), and one or plural bearing performance indexes are selected (step 107). When bearing performance indexes are selected, bearing service conditions which are required depending on the bearing performance indexes are input. Then, performance calculation programs corresponding to selected bearing performances are activated (steps 110-1, 110-2, . . .), and obtained calculation results are simultaneously displayed.

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 toroidal-type continuously variable transmission, has: first and second disks; a plurality of trunnions; a plurality of displacement shafts respectively supported on associated trunnions; a plurality of power rollers respectively interposed between the first and second disks; and, a plurality of thrust bearings respectively interposed between the power rollers and trunnions, each of the thrust bearings including an outer ring, an inner raceway formed in the outer end face of the power roller, a plurality of rolling elements, and a circular-ring-shaped retainer, wherein, in case where the density of a retainer material constituting the retainer is &rgr;d, the elastic modulus of the retainer material is Ed, the density of rolling element materials is &rgr;c and the elastic modulus of the rolling element materials is Ec, 1 { ( ρ d · E d ) / ( ρ c · E c ) } 1 2 ≤ 0.

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: The present invention provides a traction coefficient measurement device having a driving roller rotated around a driving shaft, a driven shaft is rotated together with a driven shaft, corresponding to the rotation of the driving roller, based on the engagement with the driving roller, and a load device for applying a resistance to the driven shaft against the rotation, wherein the driving shaft is fixed in position and the driven shaft is supported so as to move to and from the driving shaft, and a press apparatus is used to force the driven shaft to the driving shaft for measurement operation, and the driven shaft is positioned lower than the driving shaft in height, and the traction force acting on the engagement portion between the driving roller and the driven roller is directed in a direction to push the driven shaft downward.

Abstract: The present invention provides a traction coefficient measurement device having a driving roller rotated around a driving shaft, a driven shaft is rotated together with a driven shaft, corresponding to the rotation of the driving roller, based on the engagement with the driving roller, and a load device for applying a resistance to the driven shaft against the rotation, wherein the driving shaft is fixed in position and the driven shaft is supported so as to move to and from the driving shaft, and a press apparatus is used to force the driven shaft to the driving shaft for measurement operation, and the driven shaft is positioned lower than the driving shaft in height, and the traction force acting on the engagement portion between the driving roller and the driven roller is directed in a direction to push the driven shaft downward.

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

Abstract: A 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: The present invention provides a traction coefficient measurement device comprises a driving roller rotated around a driving shaft, a driven shaft is rotated together with a driven shaft, corresponding to the rotation of the driving roller, based on the engagement with the driving roller, and a load device for applying a resistance to the driven shaft against the rotation, wherein the driving shaft is fixed in position and the driven shaft is supported so as to move to and from the driving shaft, and a press apparatus is used to force the driven shaft to the driving shaft for measurement operation, and the driven shaft is positioned lower than the driving shaft in height, and the traction force acting on the engagement portion between the driving roller and the driven roller is directed in a direction to push the driven shaft downward.

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

Abstract: 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: When an information provision program is implemented, an input screen is displayed on a display section (step 101). A specific designation number is input (step 103), and one or plural bearing performance indexes are selected (step 107). When bearing performance indexes are selected, bearing service conditions which are required depending on the bearing performance indexes are input. Then, performance calculation programs corresponding to selected bearing performances are activated (steps 110-1, 110-2, . . .), and obtained calculation results are simultaneously displayed.

Abstract: In the roller bearing, between an outer ring (1) and an inner ring (2), there are interposed a plurality of tapered rollers (3) in a freely rollable manner. A flange portion (4) is formed in the side portion of the inner ring (2). The undercut allowance ratios of a contact ellipse formed due to mutual contact between the flange portion (4) and the end face of the roller (3) is set in the range of −0.6≦(h−b−c)/b≦2, where a grinding undercut dimension on the flange portion (4) is expressed as c, a contact point height between the flange portion (4) and the end face of the roller (3) is expressed as h, and the minor radius of a contact ellipse formed due to contact between the flange portion (4) and the end face of the roller (3) is expressed as b.

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.