Thrust joint bearing

Abstract

The utility model discloses a kind of thrust joint bearings, including seat ring, axle ring and cage, and the pocket hole of installing ball is equipped on cage, the side of pocket hole towards axle ring is equipped with first limit baffle, the side of towards seat ring is equipped with second limit baffle, both are protruded along cage axial and asymmetric design, the axial protruding height of first limit baffle and the contact package angle of inner side with ball are all greater than second limit baffle, make the stress side of ball be in first limit baffle side, and lubricating medium flows in favor, the curvature center of the spherical surface section of first limit baffle, second limit baffle inner wall and ball adaptation is separated along cage axial, and make the instantaneous rotation axis of ball deviate first limit baffle side, optimize movement guide, the utility model improves the stress and movement control of ball.

Description

Technical Field

[0001] This utility model belongs to the field of bearing technology, and in particular relates to a thrust joint bearing. Background Technology

[0002] Thrust spherical plain bearings are rolling bearings that primarily bear axial loads and are widely used in mechanical transmission systems, such as machine tool spindles, automotive transmissions, and large vertical water pumps. They are used to transmit thrust and ensure rotational accuracy. They typically consist of a shaft ring, a housing ring, a cage, and balls. The cage isolates and guides the balls. However, in existing technologies, the constraint on the balls from both sides of the pockets on the cage is often symmetrically designed, making it difficult to optimize the force and motion guidance in the main thrust direction. As a result, when the balls are subjected to a unidirectional main thrust, the contact stress distribution and motion trajectory are not guided and controlled most effectively. Utility Model Content

[0003] The purpose of this invention is to solve the above-mentioned technical problems existing in the prior art and to provide a thrust joint bearing that can optimize the force distribution and motion guidance of the balls through an asymmetrical limiting flange design.

[0004] To solve the above-mentioned technical problems, the present invention adopts the following technical solution: A thrust spherical plain bearing includes a housing ring and a shaft ring, with a cage between the housing ring and the shaft ring. The cage has a pocket for mounting balls. A first limiting flange is provided on the side of the pocket facing the shaft ring, and a second limiting flange is provided on the side facing the housing ring. Both the first and second limiting flanges protrude axially. The axial protrusion height of the first limiting flange is greater than that of the second limiting flange, and the contact wrap angle between the inner limiting surface of the first limiting flange and the ball is greater than that between the inner limiting surface of the second limiting flange and the ball. This results in the bearing force of the balls being biased towards the first limiting flange side, and facilitates the flow of lubricating medium from the second limiting flange side to the ball contact area.

[0005] Furthermore, the section of the inner wall of the first limiting stop that adapts to the outer surface of the ball is the first spherical section, and the section of the inner wall of the second limiting stop that adapts to the outer surface of the ball is the second spherical section. The curvature centers of the first spherical section and the second spherical section are separated from each other along the axial direction of the cage, thereby causing the contact pressure centers of the ball and the first and second spherical sections to shift axially.

[0006] Furthermore, the axial distance from the curvature center of the first spherical segment to the center of the ball is less than the axial distance from the curvature center of the second spherical segment to the center of the ball, thereby causing the instantaneous rotation axis of the ball to be biased towards the first limiting stop side.

[0007] Furthermore, an oil guide groove is provided on the opening side of the pocket, which extends into the pocket and smoothly transitions to the inner wall of the pocket.

[0008] Furthermore, the cage has weight-reducing holes located between two adjacent pockets.

[0009] Furthermore, the weight reduction hole is an axial through hole, and its inner wall is provided with reinforcing ribs connecting the edge of the hole.

[0010] Furthermore, the inner wall of the cage's shaft hole is provided with at least one oil reservoir.

[0011] Furthermore, the radial width of the first and second limiting stops gradually narrows from their root towards their free end.

[0012] This utility model, by adopting the above-mentioned technical solution, has the following beneficial effects: 1. In this utility model, by adopting an asymmetrical limiting stop design with different axial protrusion height and contact wrap angle, the axial constraint force and contact stress of the ball are actively focused on the first limiting stop (shaft ring side) bearing the main thrust load. At the same time, in combination with the design of the curvature centers of the first and second spherical sections being separated axially and offset by a specific amount, the instantaneous rotation axis of the ball is naturally biased towards the main load-bearing side, optimizing the contact stress distribution and motion trajectory control of the ball when bearing unidirectional thrust, and improving the stability of power transmission; 2. In this utility model, the asymmetrical flange structure reserves a relatively loose space in the second limiting flange (seat ring side). Combined with the setting of the wedge-shaped oil guide groove, it can guide the lubricating medium to flow more smoothly and more concentratedly into the area that needs lubrication, ensuring sufficient lubrication, effectively reducing friction and temperature rise, thereby extending the service life of the bearing. 3. In this utility model, an axially penetrating weight-reducing hole is provided on the cage to effectively reduce the weight and inertia of the cage. At the same time, reinforcing ribs are provided on the inner wall of the weight-reducing hole to enhance the bending and deformation stiffness of the cage and ensure the stability and reliability of the overall structure of the cage. Attached Figure Description

[0013] The present invention will be further described below with reference to the accompanying drawings: Figure 1 This is a front view of a thrust joint bearing according to the present invention; Figure 2 This is a front view of the cage in this utility model; Figure 3 This is a front sectional view of the cage in this utility model; Figure 4 This is a side view of the cage in this utility model; Figure 5 for Figure 3 Enlarged schematic diagram of a local structure at point A; Figure 6 for Figure 4Enlarged schematic diagram of the local structure at point B.

[0014] In the figure: 1-Seat ring; 2-Shaft ring; 3-Cage; 4-Pocket; 5-Ball; 6-First limiting stop; 7-Second limiting stop; 8-First spherical section; 9-Second spherical section; 10-Oil guide groove; 11-Weight reduction hole; 12-Reinforcing rib; 13-Oil reservoir. Detailed Implementation

[0015] like Figures 1 to 6 As shown, this utility model discloses a thrust spherical bearing, comprising a seat ring 1 and a shaft ring 2 coaxially arranged, with a retainer 3 disposed between the seat ring 1 and the shaft ring 2. Both the seat ring 1 and the shaft ring 2 have annular grooves on their opposing surfaces, collectively forming a raceway for accommodating balls 5. The retainer 3 has an annular structure with a central hole for mounting a rotating shaft, and multiple pockets 4 for mounting balls 5 evenly distributed circumferentially on the outer side of the hole.

[0016] A first limiting flange 6 is formed on the side of the pocket 4 facing the shaft ring 2, and a second limiting flange 7 is formed on the side facing the seat ring 1. Both limiting flanges protrude axially outward from the body of the cage 3, working together to restrict the axial movement of the ball 5. The first limiting flange 6 and the second limiting flange 7 are asymmetrically designed: the axial protrusion height of the first limiting flange 6 is greater than the axial protrusion height of the second limiting flange 7.

[0017] The inner side of the first limiting flange 6 is used to contact the limiting surface of the ball 5, and its contact wrap angle with the ball 5 is also greater than the contact wrap angle between the inner limiting surface of the second limiting flange 7 and the ball 5. This asymmetrical structure means that when the ball 5 is running, the axial restraint force and contact stress it experiences are more distributed on the side of the first limiting flange 6, i.e., the side of the shaft ring 2. The relatively loose space on the side of the second limiting flange 7 allows lubricating oil or grease to flow more smoothly from its outer side into the core contact area between the ball 5 and the raceway.

[0018] The inner wall area of ​​the first limiting flange 6 in contact with the ball 5 is constructed as the first spherical segment 8, and the corresponding inner wall area of ​​the second limiting flange 7 is constructed as the second spherical segment 9. These two spherical segments are not concentric, and their centers of curvature are separated from each other along the axial direction of the cage 3. This causes the contact pressure centers of the ball 5 with the two spherical segments to no longer coincide axially when rolling, resulting in an offset that is beneficial to power transmission. The axial distance from the center of curvature of the first spherical segment 8 to the geometric center of the ball 5 is designed to be smaller than the axial distance from the center of curvature of the second spherical segment 9 to the center of the ball 5. This geometric relationship guides the instantaneous rotation axis of the ball 5 during operation to naturally deviate towards the first limiting flange 6, thereby providing more direct and stable support and guidance when bearing the main thrust load from the shaft ring 2.

[0019] To enhance lubrication, an oil guide groove 10 is provided on the opening side of the pocket 4 on the cage 3. The oil guide groove 10 gradually extends into the pocket 4 and smoothly transitions to the inner wall of the pocket 4 without sharp angles, forming a wedge-shaped drainage channel, which can more effectively gather external lubricant and guide it to the contact area of ​​the ball 5 that needs lubrication.

[0020] A weight-reducing hole 11 is provided on the cage 3 at the position between two adjacent pockets 4, and the weight-reducing hole 11 completely penetrates the cage 3 along the axial direction.

[0021] To enhance the rigidity of this area, a reinforcing rib 12 is provided on the inner wall of the weight reduction hole 11, and the reinforcing rib 12 is connected to the hole edges of the weight reduction hole 11 on both sides in the axial direction.

[0022] In addition, two annular oil reservoirs 13 are machined on the inner wall of the shaft hole of the cage 3. The oil reservoirs 13 can be used to store a small amount of grease for auxiliary lubrication when the cage 3 slides relative to the related parts.

[0023] The radial width of the first limiting stop 6 and the second limiting stop 7, that is, the dimension from the root to the free end, gradually narrows from the root to the free end, which helps to optimize the contact and friction state between the ball 5 and the limiting stop.

[0024] The above are merely specific embodiments of this utility model, but the technical features of this utility model are not limited thereto. Any simple changes, equivalent substitutions, or modifications made based on this utility model to solve essentially the same technical problems and achieve essentially the same technical effects are all covered within the protection scope of this utility model.

Claims

1. A thrust spherical plain bearing, comprising a housing ring and a shaft ring, wherein a cage is provided between the housing ring and the shaft ring, and the cage is provided with pockets for mounting balls, characterized in that: A first limiting stop is provided on the side of the pocket facing the shaft ring, and a second limiting stop is provided on the side facing the seat ring. Both the first and second limiting stops protrude along the axial direction of the cage. The axial protrusion height of the first limiting stop is greater than that of the second limiting stop, and the contact wrap angle between the inner limiting surface of the first limiting stop and the ball is greater than that between the inner limiting surface of the second limiting stop and the ball. This results in the bearing force of the ball being biased towards the first limiting stop side, and the lubricating medium can flow from the second limiting stop side to the ball contact area.

2. A thrust joint bearing according to claim 1, characterized in that: The section of the inner wall of the first limiting stop that adapts to the outer surface of the ball is a first spherical section, and the section of the inner wall of the second limiting stop that adapts to the outer surface of the ball is a second spherical section. The curvature centers of the first spherical section and the second spherical section are separated from each other along the axial direction of the cage, thereby causing the contact pressure centers of the ball with the first spherical section and the second spherical section to shift along the axial direction of the cage.

3. A thrust joint bearing according to claim 2, characterized in that: The axial distance from the curvature center of the first spherical segment to the center of the ball is less than the axial distance from the curvature center of the second spherical segment to the center of the ball, thereby causing the instantaneous rotation axis of the ball to be biased toward the first limiting stop side.

4. A thrust joint bearing according to claim 1, characterized in that: The opening side of the pocket is provided with an oil guide groove, which extends into the pocket and smoothly transitions to the inner wall of the pocket.

5. A thrust joint bearing according to claim 1, characterized in that: The retainer has a weight-reducing hole between two adjacent pockets.

6. A thrust joint bearing according to claim 5, characterized in that: The weight-reducing hole is an axial through hole, and its inner wall is provided with reinforcing ribs connecting the edge of the hole.

7. A thrust joint bearing according to claim 1, characterized in that: The inner wall of the shaft hole of the cage is provided with at least one oil reservoir.

8. A thrust joint bearing according to claim 1, characterized in that: The radial width of the first limiting stop and the second limiting stop gradually narrows from their root to their free end.

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