JP2006170370A - Thrust roller bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce a sliding friction between a cage and a bearing ring and to reduce a torque with respect to a thrust roller bearing using a roller such as a needle roller as a rolling element and supporting a thrust load acting on a shaft. .
SOLUTION: An end of a raceway ring 13 provided with a cage 11 made of an annular plate member having a plurality of pockets 18 at predetermined intervals in the circumferential direction and rollers 12 accommodated in the pockets 18 to which the rollers 12 are in rolling contact. A flange 22 that is bent in the axial direction is formed at the edge, and a guide piece 24 that is bent in the axial direction is formed at the end edge of the cage 11, and the guide piece 24 is guided by abutting against the flange 22. In the thrust roller bearing 10, the axial cross section of the outer diameter surface 25 of the guide piece 24 is a convex curved surface and the axial cross section of the inner diameter surface 23 of the flange 22 is on the opposing surfaces where the guide piece 24 and the flange 22 contact each other. It becomes a concave curved surface.
[Selection] Figure 1

Description

  The present invention relates to a thrust roller bearing that uses a roller such as a needle roller as a rolling element and supports a thrust load acting on a shaft.

  Conventionally, for example, in a swash plate compressor used in an air conditioner of an automobile, a thrust roller bearing that supports a thrust load acting on a shaft has been used (see Patent Document 1).

  FIG. 6 shows an example of a conventional thrust roller bearing. The thrust roller bearing 30 is provided with a cage 31 rotatably between a pair of race rings 34 and 35, and each roller 33 is accommodated in a plurality of pockets 32 formed at predetermined intervals in the circumferential direction of the cage 31. (For example, refer patent document 2).

  The cage 31 is made of an annular pressed steel plate formed by pressing a single steel plate, and in order to prevent the rollers 33 from jumping out of the pocket 32, the steel plate is axially moved in the radial direction (left-right direction in the figure). It is formed by bending a plurality of times in the vertical direction in the figure.

  The thrust roller bearing 30 is installed, for example, between a housing and a shaft of a swash plate compressor in a state where the rollers 33 housed in the pockets 32 are sandwiched between the race rings 34 and 35, and supports the thrust load.

The thrust roller bearing 30 rotates at the inner diameter end and the outer diameter end while the retainer 31 contacts and guides the race rings 34 and 35 while the roller 33 rolls on the raceway surface. The thrust roller bearing 30 is supplied with lubricating oil for smoothly rotating.
JP-A-11-351245 JP 2000-192965 A

  FIG. 7 is a sectional view of the thrust roller bearing 30 on the outer diameter side. The cage 31 bends the outer diameter surface 39 of the bent piece 36 bent in the axial direction in the axial direction to the edge of the race ring 34. The oil film 40 is formed between the outer diameter surface 39 of the bent piece 36 and the inner diameter surface 38 of the flange 37 and is guided by contact with the inner diameter surface 38 of the flange 37 formed as described above, thereby reducing the frictional resistance. It has been.

  However, the bent piece 36 and the flange 37 are parallel to each other in the axial direction, and the outer diameter surface 39 of the bent piece 36 and the inner diameter surface 38 of the flange 37 are opposed to each other on a flat surface. For this reason, the outer diameter surface 39 of the bent piece 36 and the inner diameter surface 38 of the flange 37 abut each other between the flat surfaces during rotation, and it is difficult for the oil film 40 to be formed between the outer diameter surface 39 and the inner diameter surface 38. There was a problem that the friction increased and the torque increased.

  Accordingly, an object of the present invention is to reduce sliding friction between the cage and the raceway and reduce torque.

  The present invention includes a cage made of an annular plate member having a plurality of pockets at predetermined intervals in the circumferential direction, and rollers accommodated in the respective pockets, and is bent in the axial direction at the edge of the race ring to which the rollers roll. In a thrust roller bearing in which a flange is formed and a guide piece bent in the axial direction is formed at the end edge of the cage, and the guide piece is guided by contact with the flange, the guide piece and the flange are In the opposing surfaces that come into contact with each other, the axial cross section of the opposing surface of the guide piece is a convex curved surface, and the axial cross section of the opposing surface of the flange is a concave curved surface.

  According to the thrust roller bearing of the present invention, the opposing surface of the guide piece and the flange of the bearing ring that are in contact with each other are formed in a convex curved surface in the axial cross section, and the opposing surface of the flange is the shaft. Since the directional cross section is formed as a concave curved surface, a space for storing lubricating oil is formed on the concave curved surface, and an oil film is easily formed between the opposing surfaces.

  According to the present invention, sliding friction between the cage and the race can be reduced, and torque can be reduced.

  The best embodiment of the present invention will be described with reference to FIGS.

  1 is a partial sectional view of a thrust roller bearing, FIG. 2 is a partial plan view of a cage of a thrust roller bearing, FIG. 3 is a partial sectional view of a cage of a thrust roller bearing, and FIG. 4 is a partially enlarged sectional view of a thrust roller bearing. FIG. 5 is a process chart of the thrust roller bearing cage.

  The thrust roller bearing 10 is configured by incorporating a plurality of rollers 12 held by a cage 11 between a pair of race rings 13 and 14.

  The races 13 and 14 are made of an annular thin steel plate and are formed by drawing with a press. Further, a hardened surface layer is formed on the raceway surface by carbonitriding or carburizing and quenching. On the outer diameter side of the thrust roller bearing 10, a flange 22 is formed by bending the end edge of the race 13 in the axial direction.

  The cage 11 is made of an annular pressed steel plate formed by pressing a single steel plate. The retainer 11 is bent in the axial direction a plurality of times in the radial direction, and has an inner diameter portion 15, an outer diameter portion 16, and an inner diameter portion 15. The intermediate portion 17 is formed between the outer diameter portion 16 and the intermediate portion 17. That is, the inner diameter portion 15 is bent at the tip bent in one axial direction inwardly in the radial direction, and the outer diameter portion 16 is bent at the tip bent in one axial direction outward in the radial direction, and further on the other side in the axial direction. The intermediate portion 17 is formed in a trapezoidal cross section that protrudes in the same direction as the bending direction of the inner diameter portion 15 and the outer diameter portion 16.

  A plurality of pockets 18 are formed in the intermediate portion 17 at a predetermined interval in the circumferential direction by punching with a press. Roller stopper protrusions 19, 20, 21 are formed on the inner peripheral surface of the pocket 18 to prevent the stored roller 12 from jumping out. The roller 12 is prevented from coming off on one side of the retainer 11 by a central roller-locking projection 19, and the retainer 11 on both sides is prevented from coming off on the other side of the cage 11. Is done.

  The thrust roller bearing 10 is installed, for example, between a housing and a shaft of a swash plate compressor in a state where the rollers 12 accommodated in the pockets 18 are sandwiched between the race rings 13 and 14, and supports the thrust load.

  The cage 11 rotates while being guided by contacting the outer diameter surface 25 of the guide piece 24 with the inner diameter surface 23 of the flange 22 of the raceway ring 13. As shown in FIG. 4, the outer diameter surface 25 of the guide piece 24 is formed as a convex curved surface having an arc cross section in the axial direction. Further, the inner diameter surface 23 of the flange 22 is formed in a concave curved surface having an arc cross section in the axial direction. The curvature radius R1 of the convex curved surface 25 of the guide piece 24 and the curvature radius R2 of the concave curved surface 23 of the flange 22 satisfy the relationship of R1 <R2.

  The guide piece 24 of the cage 11 is processed as shown in FIG. First, as shown in FIG. 5A, the tip of the cage 11 is pressed by a press machine 28 using a mold 27. As shown in FIG. 5B, the tip of the cage 11 is bent along the curved end surface of the mold 27. Further, as shown in FIG. 5C, the tip of the bent cage 11 is pressed by the press machine 28 in the direction of the curved end surface of the mold 27. By such press working, a guide piece 24 having a curved outer diameter surface 25 is formed.

  As for the processing of the flange 22 of the bearing ring 13, the inner diameter surface 23 is formed into a concave curved surface by pressing as in the case of the guide piece 24 of the cage 11. The outer diameter surface of the flange 22 is appropriately flattened by cutting. Alternatively, the concave inner diameter surface 23 may be formed by cutting using a tool such as a cutting tool.

  According to the thrust roller bearing 10 configured in this manner, the outer diameter surface 25 of the guide piece 24 is a convex curved surface, and the inner diameter surface 23 of the flange 22 is a concave curved surface, so that the lubricating oil 26 is formed between the opposing surfaces. easy. As a result, sliding friction during rotation can be reduced, torque can be reduced, wear resistance and seizure resistance can be improved, bearing functions can be stabilized and the life can be extended.

  The curvature radius R1 of the convex curved surface 25 of the guide piece 24 and the curvature radius R2 of the concave curved surface 23 of the flange 22 satisfy the relationship of R1 <R2, but R1 = R2 may be satisfied. Moreover, the outer diameter surface 25 of the guide piece 24 should just be a convex curved surface, and the inner diameter surface 23 of the flange 22 should just be a concave curved surface, and is not restricted circular arc shape like the said embodiment.

  The above embodiment relates to the outer diameter surface 25 of the guide piece 24 and the inner diameter surface 23 of the flange 22 of the bearing ring 13 on the outer diameter side of the bearing, but the same configuration may be adopted on the inner diameter side of the bearing. Good. That is, a guide piece bent in the axial direction is formed on the inner peripheral edge of the cage 10, the axial cross section of the inner diameter surface of the guide piece is formed in a convex shape, and the outside of the flange formed on the edge of the raceway ring 14 is formed. The axial cross section of the radial surface may be concave and the guide piece may be guided by contacting the inner diameter surface of the guide piece with the outer diameter surface of the flange.

  Furthermore, the cross-sectional shape of the cage 11 is not limited to the cross-sectional shape as in the above embodiment. Furthermore, the material of the cage 11 is not limited to the steel plate, but may be made of, for example, reinforced resin and formed by casting.

  INDUSTRIAL APPLICABILITY The present invention is useful as a thrust roller bearing in a swash plate type compressor used for an air conditioner of an automobile, a transmission such as MT, AT, and CVT.

Partial sectional view of a thrust roller bearing in an embodiment of the present invention The fragmentary top view of the cage | basket of the thrust roller bearing in embodiment of this invention The fragmentary sectional view of the cage | basket of the thrust roller bearing in embodiment of this invention The partial expanded sectional view of the thrust roller bearing in embodiment of this invention Processing diagram of cage of thrust roller bearing in embodiment of the present invention Partial sectional view of a conventional thrust roller bearing Partial enlarged sectional view of a conventional thrust roller bearing

Explanation of symbols

10 Thrust roller bearing 11 Cage 12 Rollers 13 and 14 Race ring 18 Pocket 22 Flange 23 Inner diameter surface (opposing surface)
24 guide piece 25 outer diameter surface (opposite surface)
40 Oil film

Claims (2)

A cage made of an annular plate having a plurality of pockets at predetermined intervals in the circumferential direction, and rollers stored in each of the pockets,
A flange formed by bending in the axial direction is formed at an end edge of the raceway to which the rollers make rolling contact, and a guide piece formed by bending in the axial direction is formed at an end edge of the cage. In thrust roller bearings that are guided against the flange,
In the opposing surfaces where the guide piece and the flange contact each other, the axial cross section of the opposing surface of the guide piece is a convex curved surface, and the axial cross section of the opposing surface of the flange is a concave curved surface. Thrust roller bearing. The flange is formed on the edge of the bearing ring on the outer diameter side of the bearing, and the guide piece is formed on the outer peripheral edge of the cage,
2. The thrust roller bearing according to claim 1, wherein an axial section of the outer diameter surface of the guide piece is a convex curved surface, and an axial section of the inner diameter surface of the flange is a concave curved surface.

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