Plane thrust bearing retainer for high-speed rotation

Abstract

The invention discloses a plane thrust bearing retainer for high-speed rotation, and belongs to the field of plane thrust bearing retainers, the plane thrust bearing retainer comprises an outer ring wall, an inner ring wall and a bottom ring connecting the outer ring wall and the inner ring wall, the bottom ring is uniformly provided with a plurality of pockets for accommodating rolling bodies along the circumferential direction, and the inner side surface of the outer ring wall is provided with a plurality of pockets for accommodating rolling bodies. A plurality of first restraining parts and a plurality of first avoiding parts are alternately and continuously arranged in the circumferential direction of the first limiting part; a plurality of second restraining parts and a plurality of second avoiding parts are alternately and continuously arranged on the outer side face of the inner ring wall in the circumferential direction of the inner ring wall; the first restraining part corresponds to the second restraining part in position in the radial direction, and in the projection direction of the bearing axis, the projection contours of the first avoiding part and the second avoiding part are both located outside the projection contours of rolling bodies contained in the pocket holes. And the projection contours of the first restraining part and the second restraining part partially fall into the projection contours of the rolling bodies contained in the pockets.

Description

Technical Field

[0001] This application belongs to the field of planar thrust bearing cages, and particularly relates to a planar thrust bearing cage for high-speed rotation. Background Technology

[0002] Thrust bearings are key basic components in mechanical equipment used to bear axial loads. They are widely used in various high-speed rotation applications, and their performance is directly related to the stability, reliability, and lifespan of the entire transmission system.

[0003] In existing technology, the cage of a planar thrust bearing typically consists of an outer ring wall, an inner ring wall, and a bottom ring connecting the two. The bottom ring has pockets for accommodating the rolling elements. To prevent the rolling elements from dislodging under centrifugal force during high-speed operation, a common solution is to bend the upper inner part of the outer ring wall and the upper outer part of the inner ring wall towards the rolling elements, thereby forming an arc-shaped wrapping surface for the rolling elements. While this arc-shaped wrapping surface can provide effective axial restraint and ensure the running stability of the rolling elements within the track, its inherent defects also become apparent under actual high-speed operating conditions: Friction and temperature rise issues: The large contact area between the curved wrapping surface and the rolling element leads to a significant increase in sliding friction. This not only generates additional power loss but also exacerbates the temperature rise during operation.

[0004] Vibration and noise issues: Increased friction and unstable contact conditions can easily induce nonlinear vibration between the cage and the rolling elements, generating significant motion noise and affecting the equipment's operating accuracy and working environment.

[0005] Lubrication deterioration and early failure: Excessive contact area and friction can easily damage the lubricating oil film on the surface of the rolling elements, causing them to be in a state of boundary lubrication or even dry friction for a long time. This leads to rapid wear and scratches on the surface of the rolling elements and cage pockets, forming a vicious cycle of wear lubrication failure and more severe wear, resulting in bearing life far below design expectations.

[0006] Therefore, how to minimize the harmful contact area and friction between the cage and the rolling elements while ensuring reliable axial constraint on the rolling elements has become a technical problem that urgently needs to be solved to improve the performance of high-speed thrust bearings and extend their service life. Summary of the Invention

[0007] This invention provides a cage for a high-speed rotating planar thrust bearing, which solves the problems of existing planar thrust bearing cages having excessive contact between the arc-shaped wrapping surface and the balls, resulting in high friction, vibration and noise, damage to the oil film, and shortened lifespan.

[0008] To achieve the above objectives, the present invention provides the following technical solution: A high-speed rotating planar thrust bearing cage includes an outer ring wall, an inner ring wall, and a bottom ring connecting the outer ring wall and the inner ring wall. The bottom ring has a plurality of pockets evenly distributed along the circumference to accommodate rolling elements. On the inner side of the outer ring wall, a plurality of first constraint portions and a plurality of first clearance portions are alternately and continuously arranged along the circumference. On the outer side of the inner ring wall, a plurality of second constraint portions and a plurality of second clearance portions are alternately and continuously arranged along the circumference. The first constraint portion corresponds to the position of the second constraint portion in the radial direction, and the first clearance portion corresponds to the position of the second clearance portion in the radial direction, with the pocket opening directly opposite both of them; In the projection direction along the bearing axis, the projection outlines of the first clearance portion and the second clearance portion are both outside the projection outline of the rolling element contained in the pocket; the projection outlines of the first constraint portion and the second constraint portion partially fall within the projection outline of the rolling element contained in the pocket.

[0009] In a preferred embodiment, the first constraint portion is a section of the outer ring wall that is partially inclined toward the bearing axis; the first clearance portion is a section of the outer ring wall that is parallel to the bearing axis; the second constraint portion is a section of the inner ring wall that is partially inclined away from the bearing axis; and the second clearance portion is a section of the inner ring wall that is parallel to the bearing axis.

[0010] In a preferred implementation, the radial distance between the first clearance portion and its radially corresponding second clearance portion is greater than the diameter of the rolling element, and the minimum distance between the first constraint portion and its directly opposite second constraint portion is less than the diameter of the rolling element accommodated in the pocket.

[0011] In a preferred embodiment, the inclined starting position of the first constraint part is located in the axial middle or upper part of the outer ring wall, such that the outer ring wall has a first upright root section parallel to the bearing axis at its axial bottom; the inclined starting position of the second constraint part is located in the axial middle or upper part of the inner ring wall, such that the inner ring wall has a second upright root section parallel to the bearing axis at its axial bottom.

[0012] In a preferred embodiment, the first constraint portion and the first clearance portion on the outer ring wall are integrally formed continuous structures; the second constraint portion and the second clearance portion on the inner ring wall are integrally formed continuous structures.

[0013] In a preferred embodiment, the interface between the first constraint portion and the adjacent first clearance portion has a first rounded transition surface on the side facing the rolling element; the interface between the second constraint portion and the adjacent second clearance portion has a second rounded transition surface on the side facing the rolling element.

[0014] In a preferred embodiment, the interface between the first constraint portion and the adjacent first clearance portion has a third rounded transition surface on the side facing away from the rolling element, and the interface between the second constraint portion and the adjacent second clearance portion has a fourth rounded transition surface on the side facing away from the rolling element.

[0015] In a preferred embodiment, the inner surface of the window beam between two adjacent pockets facing the pockets is an arc-shaped guide surface. The radius of curvature of the arc-shaped guide surface is greater than the radius of the rolling element contained in the pocket. When the rolling element is installed in the pocket, the arc-shaped guide surface is in partial contact with the rolling element.

[0016] In a preferred embodiment, the window beam is an arched structure formed by the upward bulge of the bottom ring. The cross-sectional profile of the arched structure along the bearing circumference is an arc that is high in the middle and low at both ends. The highest point of the arched structure is lower than the top of the outer ring wall and the top of the inner ring wall in the bearing axial direction.

[0017] In a preferred embodiment, a first oil storage area is formed between the lower end of the arched structure and the inner side of the outer ring wall, and a second oil storage area is formed between the lower end of the arched structure and the outer side of the inner ring wall.

[0018] The above structure has the following beneficial effects: 1. The high-speed rotating planar thrust bearing cage of this application has its first and second clearance portions projected entirely outside the rolling element's projection contour, with no axial contact with the rolling element, thus completely eliminating unnecessary sliding friction between this portion of the wall and the rolling element in traditional designs. The projection portions of the first and second constraint portions fall within the rolling element's projection contour, fulfilling the necessary axial constraint. While ensuring that the high-speed running stability of the rolling element is not reduced, the overall contact area between the cage and the rolling element is reduced, suppressing frictional heat generation and surface damage from the source.

[0019] 2. The high-speed rotating planar thrust bearing cage of this application sets the inclined starting position of the first and second constraint wall sections in the middle or upper part of the axial direction. This can ensure effective axial constraint of the rolling elements while avoiding unnecessary constraint forces in the bottom area. This allows the constraint wall sections to play a major role in the key positions where the rolling elements need to be constrained. Through reasonable inclination angle and length, the axial movement of the rolling elements is precisely constrained, preventing them from deviating from the normal movement track and ensuring the stability and reliability of the bearing during high-speed rotation.

[0020] 3. The high-speed rotating planar thrust bearing cage of this application has a double-sided stress-relieving structure formed by the combined action of the back fillet and the front fillet. This means that the connection area between the restraint part and the clearance part achieves smooth stress diffusion, whether on the front side bearing the contact pressure from the rolling element or on the back side bearing the reaction force from its own inertia and installation constraints, thus avoiding the bidirectional stress concentration effect.

[0021] 4. The high-speed rotating planar thrust bearing cage of this application has a gap between the large-curvature guide surface and the rolling element surface that naturally widens from the contact point to both sides. When the rolling elements move relative to the cage, the lubricating oil is actively drawn into this area, generating a significant hydrodynamic pressure effect, thereby making it easier to form and maintain a load-bearing oil film in the contact area. It allows the lubricating oil to flow freely, carrying away the frictional heat generated at the contact point, while bringing in new cooling lubricant, achieving a good self-cooling effect. Attached Figure Description

[0022] The accompanying drawings, which are included to provide a further understanding of the invention and form part of this invention, illustrate exemplary embodiments of the invention and, together with their description, serve to explain this application and do not constitute an undue limitation of the invention. In the drawings: Figure 1 A schematic three-dimensional structural diagram of one embodiment of the planar thrust bearing cage for high-speed rotation according to this application is shown. Figure 2 The illustration shows a three-dimensional structural diagram of one embodiment of the high-speed rotating planar thrust bearing cage of this application after the rolling elements are installed; Figure 3 A schematic top view of one embodiment of the planar thrust bearing cage for high-speed rotation according to this application is shown. Figure 4 It is illustrated Figure 3 A schematic cross-sectional view of one embodiment of AA; Figure 5 It is illustrated Figure 3 A schematic cross-sectional view of a possible embodiment of BB; Figure 6 A partially enlarged schematic diagram of one embodiment of the high-speed rotating planar thrust bearing cage of this application after the rolling elements are mounted is shown. Label Explanation: 1. Outer ring wall; 10. First constraint part; 11. First clearance part; 12. First upright root section; 13. First rounded transition surface; 14. Third rounded transition surface; 2. Inner ring wall; 20. Second constraint part; 21. Second clearance part; 22. Second upright root section; 23. Second rounded transition surface; 24. Fourth rounded transition surface; 3. Bottom ring; 30. Pocket; 31. Window beam; 310. Arc-shaped guide surface; 32. First oil storage area; 33. Second oil storage area; 4. Rolling element. Detailed Implementation

[0023] In the following description, only certain exemplary embodiments are briefly described. As those skilled in the art will recognize, the described embodiments can be modified in various ways without departing from the spirit and scope of the invention. Therefore, the drawings and description are considered to be exemplary in nature and not restrictive.

[0024] The present invention will now be described with reference to the accompanying drawings.

[0025] The specific solution adopted is as follows: like Figure 1-6 As shown, the present invention provides a high-speed rotating planar thrust bearing cage, including an outer ring wall 1, an inner ring wall 2, and a bottom ring 3 connecting the outer ring wall 1 and the inner ring wall 2. The bottom ring 3 has a plurality of pockets 30 evenly provided along the circumference for accommodating rolling elements 4. On the inner side of the outer ring wall 1, a plurality of first constraint portions 10 and a plurality of first clearance portions 11 are alternately and continuously provided along its circumference. On the outer side of the inner ring wall 2, a plurality of second constraint portions 20 and a plurality of second clearance portions 21 are alternately and continuously provided along its circumference. The first constraint part 10 is radially aligned with the position of the second constraint part 20, and the first clearance part 11 is radially aligned with the position of the second clearance part 21, with the pocket 30 opening directly opposite both of them; In the projection direction along the bearing axis, the projection outlines of the first clearance portion 11 and the second clearance portion 21 are both outside the projection outline of the rolling element 4 contained in the pocket 30; the projection outlines of the first constraint portion 10 and the second constraint portion 20 partially fall within the projection outline of the rolling element 4 contained in the pocket 30.

[0026] Traditional curved wrapping surfaces, in order to solve constraint problems, are forced to bear the cost of large-area friction. In this invention, the avoidance parts (first and second avoidance parts 21) are projected entirely outside the projected outline of the rolling element 4, and have no axial contact with the rolling element 4, completely eliminating the unnecessary sliding friction between this part of the wall surface and the rolling element 4 in traditional designs. The constraint parts (first and second constraint parts 20) are projected within the projected outline of the rolling element 4, fulfilling the necessary axial constraint. While ensuring that the high-speed running stability of the rolling element 4 is not reduced, the overall contact area between the cage and the rolling element 4 is reduced, suppressing frictional heat generation and surface damage from the source.

[0027] The significant reduction in friction and optimization of contact conditions directly lower the probability of cage-rolling element collisions, resulting in smoother operation. Nonlinear vibrations and the resulting harsh noises are effectively suppressed, improving the overall performance of the machine. The minimized contact area and reduced high-stress contact points make it easier for the lubricating oil film to form and remain in the contact area, avoiding the continuous rupture of the oil film caused by large-area scraping in traditional structures. The reduction in frictional heat generation directly leads to a lower internal operating temperature of the bearing. This not only helps maintain the viscosity and performance of the lubricating oil but also reduces the risk of material softening due to high temperatures, thus making the bearing more reliable under the same operating conditions or able to operate safely at higher speeds.

[0028] In a preferred embodiment of this application, the first constraint part 10 is a section of the outer ring wall 1 that is partially inclined toward the bearing axis; the first clearance part 11 is a section of the outer ring wall 1 that is parallel to the bearing axis; the second constraint part 20 is a section of the inner ring wall 2 that is partially inclined away from the bearing axis; and the second clearance part 21 is a section of the inner ring wall 2 that is parallel to the bearing axis. This is achieved not by adding extra materials or complex attachments, but by optimizing the existing wall geometry to divide the area into two functionally different regions: the "constraint part" and the "clearance part".

[0029] Specifically, the portions of the outer ring wall 1 and inner ring wall 2 directly opposite the rolling element 4 are designed as vertical wall sections parallel to the bearing axis. This ensures that, in the axial projection direction of the bearing, these sections are completely outside the projected contour of the rolling element 4, achieving zero axial contact between the rolling element 4 and the outer and inner ring walls 1 and 2 during operation. This eliminates the undesirable sliding friction and wear that is unavoidable in this area in traditional designs, and the constraint function is located in a specific inclined section on the wall. This inclination is not a traditional large-area wrapping, but rather a cut-in at a specific angle towards or away from the axis, so that its end falls exactly within the contour of the rolling element 4 in projection. This optimizes the constraint function from surface constraint to line constraint or even point constraint. The significant reduction in contact area directly reduces frictional resistance, frictional heat, and shearing force on the oil film, while the efficiency and necessity of the constraint are not lost.

[0030] Minimize contact where it is necessary and completely eliminate contact where it is not necessary, thereby fundamentally solving a series of chain problems caused by excessive contact area at high speeds, such as temperature rise, vibration, lubrication failure, and premature wear.

[0031] Furthermore, the radial distance between the first clearance portion 11 and its radially corresponding second clearance portion 21 is greater than the diameter of the rolling element 4, and the minimum distance between the first constraint portion 10 and its directly opposite second constraint portion 20 is less than the diameter of the rolling element 4 accommodated in the pocket 30.

[0032] The radial distance between the first clearance wall section and the radially corresponding second clearance wall section is greater than the diameter of the rolling element 4 accommodated in the pocket 30. This significantly reduces the contact opportunity between the rolling element 4 and the clearance wall section of the cage during high-speed bearing rotation. The significant reduction in contact area directly leads to a decrease in friction, thereby reducing the heat generated by friction. Simultaneously, the reduction in friction effectively reduces wear on the cage and the rolling element 4, extending the service life of the components. The minimum distance between the first constraint wall section and its directly opposite second constraint wall section is less than the diameter of the rolling element 4 accommodated in the pocket 30, forming an effective constraint mechanism for the rolling element 4. During high-speed bearing rotation, even if the rolling element 4 is subjected to centrifugal force or other forces, it is difficult for it to detach from the cage's movement track. The constraint wall sections reliably limit the range of motion of the rolling element 4, preventing bearing failure due to accidental detachment and ensuring the stability and safety of the bearing during high-speed operation.

[0033] In a preferred embodiment of this application, the inclined starting position of the first constraint part 10 is located in the axial middle or upper part of the outer ring wall 1, such that the outer ring wall 1 has a first upright root section 12 parallel to the bearing axis at its axial bottom; the inclined starting position of the second constraint part 20 is located in the axial middle or upper part of the inner ring wall 2, such that the inner ring wall 2 has a second upright root section 22 parallel to the bearing axis at its axial bottom.

[0034] If the restraint section starts tilting directly from the junction of the ring wall and the bottom ring 3 (i.e., the root), a sharp geometric notch and extremely high stress concentration will form at this turning point. Under high-speed cyclic loading, fatigue cracks are very likely to initiate at this point, becoming a fatal weakness for cage fracture. This invention, by setting an upright root section, moves the tilting starting point upwards, allowing the root to maintain a straight and robust shape, resulting in a more gradual stress distribution. This significantly improves the cage's fatigue resistance and overall structural reliability under harsh operating conditions. The upright root section and the bottom ring 3 together form a more direct and robust support frame for the bottom of the pocket 30. This enhances the cage's resistance to radial impact and centrifugal force-induced deformation of the rolling elements 4, ensuring the stability of the pocket 30's geometric accuracy during long-term operation and avoiding motion interference or uneven load distribution caused by deformation.

[0035] The inner wall of the upright root section, together with the plane of the bottom ring 3, forms a flared oil reservoir with a larger radial dimension at the axial bottom of the pocket 30. Compared with the traditional design that slopes from the root, the spatial volume of this area is substantially increased, allowing for the storage of more lubricating oil. Under the centrifugal force generated by high-speed rotation, the lubricating oil is thrown towards the periphery of the pocket 30, precisely on the path of lubricating oil migration. This effectively captures and stores the lubricating oil, ensuring that even in cases of momentary insufficient oil supply or increased oil splashing due to high temperature, the oil reservoir always maintains lubricating medium near the contact area between the rolling element 4 and the pocket 30, preventing dry friction and greatly improving the bearing's survivability under extreme operating conditions.

[0036] In a preferred embodiment of this application, the first constraint portion 10 and the first clearance portion 11 on the outer ring wall 1 are integrally formed continuous structures; the second constraint portion 20 and the second clearance portion 21 on the inner ring wall 2 are integrally formed continuous structures.

[0037] The one-piece continuous structure eliminates any gaps or weak points between the first constraint part 10 and the first clearance part 11, and between the second constraint part 20 and the second clearance part 21. During bearing operation, it can withstand greater loads and impacts, and is less prone to structural failures due to loosening or breakage of connections, significantly improving the overall structural strength and reliability of the cage. A one-piece casting process can be used, manufacturing multiple wall sections simultaneously in a single operation. Materials can be metal or engineering plastics, eliminating the need for separate processing and assembly of multiple components. This greatly simplifies the production process, reduces production steps and equipment investment, improves production efficiency, and lowers production costs. Alternatively, a step-by-step processing method can be used, first machining ordinary outer ring wall 1 and inner ring wall 2, and then stamping locally inclined constraint sections onto the walls.

[0038] In addition, the tilt angle range of the first constraint part 10 is set to 5°-10°, and the tilt angle range of the second constraint part 20 is the same as that of the first constraint wall section.

[0039] If the tilt angle is too small, such as less than 5°, the constraint force of the restraining wall section on the rolling element 4 in the axial direction will be significantly insufficient. When the bearing is running at high speed, the rolling element 4 may tend to move axially under stress. An excessively small tilt angle cannot provide sufficient reaction force to prevent this movement, and the rolling element 4 may easily deviate from its normal motion track, leading to bearing failure, such as rolling element 4 jamming or increased bearing vibration, which seriously affects the normal use and life of the bearing. A tilt angle range of 5° to 10° can generate a more suitable constraint force, effectively limiting excessive axial movement of the rolling element 4 and ensuring stable operation of the rolling element 4 within the pocket 30.

[0040] When the tilt angle is too large, such as exceeding 10°, the axial restriction of the rolling element 4 by the constraint wall section becomes too strict. The rolling element 4 requires a certain axial clearance during operation to allow for flexible rolling and position adjustment. An excessively large tilt angle will significantly compress this clearance space, severely restricting the movement of the rolling element 4. This will lead to a sharp increase in friction between the rolling element 4 and the constraint wall, which will not only accelerate component wear but also generate a large amount of heat, reducing bearing operating efficiency and potentially damaging the bearing due to overheating. A tilt angle range of 5° to 10°, however, can ensure effective constraint while maintaining appropriate axial clearance for the rolling element 4, allowing it to roll smoothly.

[0041] In a preferred embodiment of this application, the interface between the first constraint portion 10 and the adjacent first clearance portion 11 has a first rounded transition surface 13 on the side facing the rolling body 4; the interface between the second constraint portion 20 and the adjacent second clearance portion 21 has a second rounded transition surface 23 on the side facing the rolling body 4.

[0042] Without a rounded transition, a sharp geometric step or ridge would form between the inclined constraint section and the upright clearance section. When the rolling element 4 moves relative to the cage under centrifugal force or load, its surface contacts this ridge, resulting in extremely high contact stress and making it highly susceptible to scratching. The rounded transition surface eliminates this harmful geometric discontinuity. The contact force between the rolling element 4 and the cage can be smoothly established and released according to the curvature of the surface, avoiding sudden increases and decreases in stress and greatly reducing the risk of impact wear at the contact edge. The rounded surface provides a continuous guide surface, making the movement trajectory of the rolling element 4 more controllable and stable, thereby suppressing abnormal vibrations and noise and improving operational smoothness. Sharp edges have a strong "shearing" and "scraping" destructive effect on the lubricating oil film. The rounded transition surface greatly alleviates this damage. Its smooth and continuous contour allows the lubricating oil film to pass more smoothly through the contact area, reducing the probability of the oil film being locally squeezed or cut off.

[0043] Furthermore, the interface between the first constraint part 10 and the adjacent first clearance part 11 has a third rounded transition surface 14 on the side facing away from the rolling body 4, and the interface between the second constraint part 20 and the adjacent second clearance part 21 has a fourth rounded transition surface 24 on the side facing away from the rolling body 4.

[0044] Similar to the side facing the rolling element 4, if the constraint and clearance sections lack rounded corners at their back junction, a geometrical sharp angle will also form. During high-speed rotation, the cage bears complex cyclic stresses, and this sharp angle can become a dangerous stress peak point, easily initiating fatigue cracks. The rounded transition surface on the back effectively eliminates this potential crack initiation point, allowing stress to transition smoothly in this area, significantly improving the cage's fatigue life and structural reliability under alternating loads. The back rounded corners, together with the front rounded corners, form a double-sided stress-relieving structure. This means that the connection area between the constraint and clearance sections achieves smooth stress diffusion, whether on the front side bearing the contact pressure from the rolling element 4 or on the back side bearing the reaction force from its own inertia and installation constraints, avoiding a two-way stress concentration effect.

[0045] As a preferred embodiment of this application, see [link to application]. Figure 6 The inner surface of the window beam 31 between two adjacent pockets 30 is an arc-shaped guide surface 310 facing the pocket 30. The radius of curvature of the arc-shaped guide surface 310 is greater than the radius of the rolling element 4 contained in the pocket 30. When the rolling element 4 is installed in the pocket 30, the arc-shaped guide surface 310 is in partial contact with the rolling element 4.

[0046] The radius of curvature of the arc-shaped guide surface 310 is larger than that of the rolling element 4. The contact area is concentrated in a very small area near the equator of the rolling element 4. The sharp reduction in the contact area directly leads to a proportional and significant decrease in the frictional force between the two. The large curvature design ensures that, except for the central contact point, there is a uniform gap between the upper and lower parts of the rolling element 4 and the surface of the window beam 31. This completely avoids accidental and harmful scratching and interference between the non-equatorial area of ​​the rolling element 4 and the edge of the window beam 31 during movement. Such interference is a significant source of vibration and wear at high speeds.

[0047] The gap between the high-curvature guide surface and the surface of the rolling element 4 naturally widens from the contact point to both sides. When the rolling element 4 moves relative to the cage, the lubricating oil is actively drawn into this area, generating a significant hydrodynamic pressure effect. This makes it easier to form and maintain a load-bearing oil film in the contact area. It allows the lubricating oil to flow freely, carrying away the frictional heat generated at the contact point, while bringing in new cooling lubricant, achieving a good self-cooling effect.

[0048] Furthermore, the window beam 31 is an arched structure formed by the upward bulge of the bottom ring 3. The cross-sectional profile of the arched structure along the circumference of the bearing is an arc with a high center and low ends. The highest point of the arched structure is lower than the top of the outer ring wall 1 and the top of the inner ring wall 2 in the bearing axial direction. When the window beam 31 on the bottom ring 3 is flat, the bottom of the rolling element 4 does not reach the higher position of the ball when it contacts it, and the circumferential restriction effect on the rolling element 4 is small, making it easy for the rolling element 4 to circumferentially disengage from the pocket 30. However, after the window beam 31 bulges to form an arched structure, the axial restriction height increases, which is equivalent to providing a higher "fence" for the rolling element 4. When the rolling element 4 moves circumferentially, it needs to overcome a greater height difference to disengage from the pocket 30, thereby effectively restricting the circumferential movement of the rolling element 4 and ensuring the normal operation of the bearing.

[0049] Furthermore, the two bottom ends of the arched window beam 31 do not extend to both ends of the bottom ring 3, but leave a certain space. When the window beam 31 is between the outer ring wall 1 and the inner ring wall 2, the space between the bottom end of the arched structure and the inner side of the outer ring wall 1 naturally forms the first oil storage area 32, and the space between the bottom end of the arched structure and the outer side of the inner ring wall 2 forms the second oil storage area. The existence of the oil storage area allows the bearing to hold more lubricating oil. More lubricating oil can reduce the friction and wear between the rolling element 4 and the window beam 31, and the inner and outer ring walls 1, thereby improving the reliability of the bearing.

[0050] For any parts not mentioned in this invention, existing technologies can be used or referenced.

[0051] The above are merely specific embodiments of the present invention, but the scope of protection of the present invention is not limited thereto. Any person skilled in the art can easily conceive of various variations or substitutions within the technical scope disclosed in the present invention, and these should all be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. A cage for a high-speed rotating planar thrust bearing, comprising an outer ring wall, an inner ring wall, and a bottom ring connecting the outer ring wall and the inner ring wall, wherein the bottom ring has a plurality of pockets evenly distributed circumferentially for accommodating rolling elements, characterized in that, On the inner surface of the outer ring wall, a plurality of first constraint parts and a plurality of first clearance parts are alternately and continuously provided along its circumference; on the outer surface of the inner ring wall, a plurality of second constraint parts and a plurality of second clearance parts are alternately and continuously provided along its circumference. The first constraint portion corresponds to the position of the second constraint portion in the radial direction, and the first clearance portion corresponds to the position of the second clearance portion in the radial direction, with the pocket opening directly opposite both of them; In the projection direction along the bearing axis, the projection outlines of the first clearance portion and the second clearance portion are both outside the projection outline of the rolling element contained in the pocket; the projection outlines of the first constraint portion and the second constraint portion partially fall within the projection outline of the rolling element contained in the pocket.

2. The high-speed rotating planar thrust bearing cage according to claim 1, characterized in that, The first constraint portion is a section of the outer ring wall that is inclined toward the bearing axis; the first clearance portion is a section of the outer ring wall that is parallel to the bearing axis; the second constraint portion is a section of the inner ring wall that is inclined away from the bearing axis; and the second clearance portion is a section of the inner ring wall that is parallel to the bearing axis.

3. The high-speed rotating planar thrust bearing cage according to claim 2, characterized in that, The radial distance between the first clearance portion and its radially corresponding second clearance portion is greater than the diameter of the rolling element, and the minimum distance between the first constraint portion and its directly opposite second constraint portion is less than the diameter of the rolling element accommodated in the pocket.

4. The high-speed rotating planar thrust bearing cage according to claim 2, characterized in that, The first constraint portion is inclined at the middle or upper part of the outer ring wall in the axial direction, such that the outer ring wall has a first upright root section at its axial bottom that is parallel to the bearing axis; the second constraint portion is inclined at the middle or upper part of the inner ring wall in the axial direction, such that the inner ring wall has a second upright root section at its axial bottom that is parallel to the bearing axis.

5. The high-speed rotating planar thrust bearing cage according to claim 1, characterized in that, The first constraint portion and the first clearance portion on the outer ring wall are integrally formed continuous structures; the second constraint portion and the second clearance portion on the inner ring wall are integrally formed continuous structures.

6. The high-speed rotating planar thrust bearing cage according to claim 1, characterized in that, The interface between the first constraint part and the adjacent first clearance part has a first rounded transition surface on the side facing the rolling element; the interface between the second constraint part and the adjacent second clearance part has a second rounded transition surface on the side facing the rolling element.

7. The high-speed rotating planar thrust bearing cage according to claim 5, characterized in that, The interface between the first constraint part and the adjacent first clearance part has a third rounded transition surface on the side facing away from the rolling element, and the interface between the second constraint part and the adjacent second clearance part has a fourth rounded transition surface on the side facing away from the rolling element.

8. The high-speed rotating planar thrust bearing cage according to claim 1, characterized in that, The inner surface of the window beam between two adjacent pockets is an arc-shaped guide surface. The radius of curvature of the arc-shaped guide surface is greater than the radius of the rolling element contained in the pocket. When the rolling element is installed in the pocket, the arc-shaped guide surface is in partial contact with the rolling element.

9. The high-speed rotating planar thrust bearing cage according to claim 8, characterized in that, The window beam is an arched structure formed by the upward bulge of the bottom ring. The cross-sectional profile of the arched structure along the bearing circumference is an arc that is high in the middle and low at both ends. The highest point of the arched structure is lower than the top of the outer ring wall and the top of the inner ring wall in the bearing axial direction.

10. The high-speed rotating planar thrust bearing cage according to claim 9, characterized in that, A first oil storage area is formed between the lower end of the arched structure and the inner side of the outer ring wall, and a second oil storage area is formed between the lower end of the arched structure and the outer side of the inner ring wall.

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