CN215762799U

CN215762799U - Thrust needle roller bearing suitable for eccentric condition

Info

Publication number: CN215762799U
Application number: CN202121695275.3U
Authority: CN
Inventors: 谷晓光; 邹玲红
Original assignee: Suzhou Bearing Factory Co ltd
Current assignee: Suzhou Bearing Factory Co ltd
Priority date: 2021-07-26
Filing date: 2021-07-26
Publication date: 2022-02-08
Anticipated expiration: 2031-07-26

Abstract

The utility model discloses a thrust needle roller bearing suitable for an eccentric condition, which comprises a shaft ring, a seat ring, a retainer and a rolling body, wherein the retainer is arranged between the shaft ring and the seat ring; the first gap is smaller than the eccentricity of the center of the retainer relative to the rotation center of the clutch, and the second gap is larger than the eccentricity. The clearance of the shaft ring guide retainer is small, so that the guide of the retainer to the rolling body is facilitated, the application of an eccentric working condition can be met without additionally performing strengthening treatment on the retainer, the eccentric working condition in the use process can be resisted, and the effective service life of the bearing is ensured; compared with the conventional design structure, the radial displacement of the rolling body is small, the sliding friction of the bearing is greatly reduced, and oil film lubrication is facilitated.

Description

Thrust needle roller bearing suitable for eccentric condition

Technical Field

The utility model belongs to a thrust needle roller bearing, and particularly relates to a thrust needle roller bearing suitable for an eccentric condition.

Background

The application conditions of the thrust needle roller bearing for the clutch system are that one end is a friction plate and a clutch gear ring, the other end is a piston, when the friction plate and the clutch gear ring are driven to rotate by driving force, a bearing shaft ring is driven to rotate, and the bearing shaft ring cannot rotate along the shaft center but rotates under the eccentric condition because a certain gap is inevitably formed between the clutch gear ring and an internal spline. The conventional integrated thrust needle roller bearing needs the strength of the retainer to have particularly high strength (more than 500 HV) under the working condition, and a sufficiently large gap needs to be designed between the retainer and the shaft ring and between the retainer and the race to eliminate the influence caused by eccentricity, the guidance of the shaft ring to the retainer is reduced due to the increase of the gap, the radial displacement of the needle roller is increased, the friction and the lubrication of the bearing are not facilitated, the manufacturing cost is high, and the conventional design does not have the function of preventing rotation (preventing slipping), so that the friction and the wear in the system are increased.

Disclosure of Invention

In view of the above technical problems, the present invention aims to: the thrust needle roller bearing suitable for the eccentric condition is provided, the clearance of the shaft ring guide retainer is small, the guide of the retainer to the rolling body is facilitated, the application of the eccentric working condition can be met without additionally strengthening the retainer, the eccentric working condition in the use process can be resisted, and the effective service life of the bearing is ensured; compared with the conventional design structure, the radial displacement of the rolling body is small, the sliding friction of the bearing is greatly reduced, and oil film lubrication is facilitated.

The technical scheme of the utility model is as follows:

the utility model discloses a thrust needle roller bearing suitable for an eccentric condition, which comprises a shaft ring, a seat ring, a retainer and a rolling body, wherein the retainer is arranged between the shaft ring and the seat ring;

wherein the first gap is smaller than the eccentricity of the center of the cage with respect to the center of rotation of the clutch and the second gap is larger than the eccentricity.

Preferably, the first gap is 0.1-0.3 mm.

Preferably, the second gap is greater than or equal to 0.6 mm.

Preferably, a plurality of convex tooth structures protruding outwards in the radial direction are arranged on the peripheral wall of the shaft ring at intervals in the circumferential direction, and the shaft ring is positioned through the convex tooth structures and the internal spline of the clutch gear ring.

Preferably, the cross section of the convex tooth structure is in a trapezoidal shape which is gradually reduced from inside to outside along the radial direction.

Preferably, the number of the convex tooth structures is four, and the four convex tooth structures are uniformly distributed at intervals along the circumferential direction.

Preferably, a plurality of salient points or salient balls which are arranged at intervals and protrude outwards along the radial direction are formed on the peripheral wall of the seat ring, and the seat ring is matched with a clamping groove in a piston hole of the piston through the salient points.

Preferably, the shaft ring and the seat ring are of a split structure.

Compared with the prior art, the utility model has the advantages that:

according to the thrust needle roller bearing suitable for the eccentric condition, the clearance of the shaft ring guide retainer is small (the clearance between the retainer and the shaft ring is 0.1-0.3 mm), the guide of the retainer to a rolling body is facilitated, the application of the eccentric working condition can be met without additionally performing strengthening treatment on the retainer (the strength only needs 380 HV), the eccentric working condition in the use process can be resisted, and the effective service life of the bearing is ensured; compared with the conventional design structure, the radial displacement of the rolling body is small, the sliding friction of the bearing is greatly reduced, and oil film lubrication is facilitated. The shaft ring and the clutch gear ring are positioned through the convex tooth structure, so that the shaft ring and the clutch gear ring can synchronously rotate, relative sliding cannot be generated, the effects of preventing rotation and slipping are achieved, and friction and abrasion are reduced.

Drawings

The utility model is further described with reference to the following figures and examples:

FIG. 1 is a sectional view of a needle thrust bearing adapted for an eccentric condition according to an embodiment of the present invention;

FIG. 2 is an enlarged partial view of the thrust needle bearing adapted for the eccentric condition of FIG. 1 at location A;

FIG. 3 is a schematic diagram of a collar of a thrust needle bearing adapted for an eccentric condition according to an embodiment of the present invention;

FIG. 4 is a cross-sectional view of a race of a thrust needle bearing adapted for an eccentric condition in accordance with an embodiment of the present invention;

fig. 5 is a partially enlarged view of the thrust needle bearing B suitable for the eccentric condition of fig. 4.

Wherein: 1. a shaft ring; 11. a convex tooth structure; 2. a seat ring; 21. bumps (convex balls); 3. a holder; 4. a rolling body; 5. a first gap; 6. a second gap.

Detailed Description

In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be described in further detail with reference to the accompanying drawings in conjunction with the following detailed description. It should be understood that the description is intended to be exemplary only, and is not intended to limit the scope of the present invention. Moreover, in the following description, descriptions of well-known structures and techniques are omitted so as to not unnecessarily obscure the concepts of the present invention.

Example (b):

referring to fig. 1 to 5, a thrust needle roller bearing adapted to an eccentric condition according to an embodiment of the present invention includes a race 1, a race 2, a cage 3, and rolling elements 4. A cage 3 is provided between the race 1 and the race 2, and rolling elements 4 are mounted in the cage 3. A first gap 5 is formed between the inner peripheral wall of the retainer 3 and the shaft ring 1, and a second gap 6 is formed between the outer peripheral wall of the retainer 3 and the race 2. Wherein the first clearance 5 is smaller than the eccentricity of the center of the cage 3 with respect to the center of rotation of the clutch and the second clearance 6 is larger than the eccentricity. The structure can meet the application of eccentric working conditions without additionally strengthening the retainer 3 (the strength of the retainer 3 in the embodiment of the utility model is 380 HV), so that the production cost is obviously reduced; the eccentric working condition in the use process can be resisted, and the effective service life of the bearing is ensured. The clearance of the shaft ring 1 for guiding the retainer 3 is small, the guide of the retainer 3 to the rolling body 4 is facilitated, the structure is better than that of the conventional design, the radial displacement of the roller pin is small, the sliding friction of the bearing is greatly reduced, and oil film lubrication is facilitated.

Preferably, the first gap 5 is 0.1-03 mm. More preferably 0.2 mm. The second gap 6 is greater than or equal to 0.6 mm. Compared with the gap (0.6 mm or more) between the cage 3, the collar 1, and the race 2 of the conventional thrust needle bearing for a clutch system, the gap between the cage 3 and the collar 1 is smaller in the collar 1 of the present embodiment, and the cage 3 contributes to the guide of the rolling elements 4.

Preferably, a plurality of convex tooth structures 11 protruding outwards in the radial direction are arranged on the outer peripheral wall of the shaft ring 1 at intervals along the circumferential direction, and the shaft ring 1 is positioned with the internal spline of the clutch gear ring through the convex tooth structures 11. As shown in fig. 3, the cross section of the tooth structure 11 is in a trapezoidal shape that tapers from inside to outside in the radial direction. Preferably, the cross section of the tooth structure 11 is an isosceles trapezoid. As shown in fig. 3, the number of the tooth structures 11 is four, and four tooth structures 11 are uniformly distributed at intervals in the circumferential direction. I.e. the angle between two adjacent tooth structures 11 is 90 deg.. The outer diameter tooth profile design of the shaft ring 1 can ensure that the shaft ring and the clutch gear ring rotate synchronously without relative sliding, thereby playing the roles of preventing rotation and slipping and reducing friction and wear.

Preferably, as shown in fig. 1, 4 and 5, the outer peripheral wall of the seat ring 2 is formed with a plurality of protruding points or balls which are arranged at intervals and protrude outwards in the radial direction, and the seat ring 2 is matched with the clamping groove in the piston hole of the piston through the protruding points. The outer diameter salient point design of the seat ring 2 can not fall off from the piston after assembly, and the host machine is convenient to assemble.

Preferably, the collar 1 and the race 2 are of a split construction. Is convenient for assembling, disassembling, maintaining and replacing parts.

According to the thrust needle roller bearing suitable for the eccentric condition, the bearing is designed in a split type structure with the shaft ring 1 and the seat ring 2. The shaft ring 1 and the internal spline are positioned, and the outer diameter adopts a tooth-shaped design, so that the shaft ring 1 and the gear ring are prevented from sliding relatively. Seat circle 2 is fixed a position with the piston hole to 2 design salient points of seat circle prevent with the cooperation of piston hole draw-in groove to drop, the host computer assembly of being convenient for. The guiding mode of the retainer 3 is inner guiding, namely the inner diameter of the retainer 3 and the shaft ring 1 are designed by a first gap 5 (small gap, smaller than eccentricity), and the outer diameter of the retainer 3 and the seat ring 2 are designed by a second gap 6 (large gap, far larger than eccentricity).

It is to be understood that the above-described embodiments of the present invention are merely illustrative of or explaining the principles of the utility model and are not to be construed as limiting the utility model. Therefore, any modification, equivalent replacement, improvement and the like made without departing from the spirit and scope of the present invention should be included in the protection scope of the present invention. Further, it is intended that the appended claims cover all such variations and modifications as fall within the scope and boundaries of the appended claims or the equivalents of such scope and boundaries.

Claims

1. A thrust needle roller bearing suitable for an eccentric condition, comprising a shaft ring (1), a race (2), a cage (3) and rolling bodies (4), wherein the cage (3) is arranged between the shaft ring (1) and the race (2), and the rolling bodies (4) are installed in the cage (3), characterized in that a first clearance (5) is formed between the inner peripheral wall of the cage (3) and the shaft ring (1), and a second clearance (6) is formed between the outer peripheral wall of the cage (3) and the race (2);

wherein the first clearance (5) is smaller than the eccentricity of the center of the retainer (3) relative to the center of rotation of the clutch and the second clearance (6) is larger than the eccentricity.

2. Thrust needle bearing adapted to the eccentric condition, according to claim 1, characterized in that said first clearance (5) is 0.1-0.3 mm.

3. Thrust needle bearing adapted for the eccentric condition, according to claim 1, characterized in that said second clearance (6) is greater than or equal to 0.6 mm.

4. The thrust needle roller bearing suitable for the eccentric condition of claim 1, characterized in that a plurality of convex tooth structures (11) protruding outwards in the radial direction are arranged on the outer circumferential wall of the shaft ring (1) at intervals along the circumferential direction, and the shaft ring (1) is positioned with the internal spline of the clutch ring gear through the convex tooth structures (11).

5. Thrust needle roller bearing adapted to the eccentric condition according to claim 4, characterized in that the cross section of the lobe structure (11) is trapezoidal in shape that tapers from inside to outside in the radial direction.

6. Thrust needle bearing adapted to an eccentric condition, according to claim 4, characterized in that said tooth structure (11) comprises four, four tooth structures (11) evenly spaced in the circumferential direction.

7. The needle thrust bearing adapted for the eccentric condition of claim 1, wherein a plurality of protrusions or balls are formed on the outer peripheral wall of the race (2) at intervals and protrude outward in the radial direction, and the race (2) is engaged with a locking groove in the piston hole of the piston through the protrusions.

8. Thrust needle bearing adapted for the eccentric condition, according to any of claims 1-7, characterized in that said collar (1) and said race (2) are of a split structure.