A planar thrust segment retainer
Patent Information
- Application Number
- CN202522632919.9
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-12-11
- Publication Date
- 2026-10-20
- Estimated Expiration
- 2035-12-11
AI Technical Summary
[0004]本实用新型提供了一种平面推力分段保持架，解决在大型高速工况下，现有平面分段式保持架的动态润滑保障系统失效，薄弱部位出现早期破坏的问题
本申请的平面推力分段保持架在承受最大离心力的区域外圈部，设置朝向背离轴承轴线方向倾斜，导油斜面覆盖滚动体端面，直接作用于润滑油的流动路径。当轴承高速旋转时，被甩向保持架外缘的润滑油首先撞击到轴向加高的弧形外圈部，对油液的径向向外飞溅构成了第一道物理屏障。润滑油沿外圈部的径向内壁面流动时，必须爬上导油斜面，这过程会消耗油的动能，减缓其向外流动的速度，阻滞了润滑油的快速流失，在油堆积在外侧区域减速后又能顺着导油斜面回到滚动体和保持架接触区域进行润滑，润滑得到保障后，滚动体与保持架之间的油膜缓冲作用恢复，能有效吸收和阻尼碰撞冲击力，从而大幅降低窗梁和拐角处的交变冲击应力，抑制微观裂纹的萌生。通过保障润滑和降低冲击，直接解决了分段式保持架在高速下的早期失效问题，延长轴承整体寿命。弧形外圈部波峰与波谷的交替排列，形成了一个“波浪形”轮廓。当轴承高速旋转时，离心力会将部分油液甩向外圈端面区域。此时，传统的平面端面会使油液跨过平面端面而难以在跨回端面。而本设计的波谷部其最低点正对滚动体端面区域，润滑油甩到外侧时可以在波谷聚集，加上导油斜面的作用，部分润滑油回流至滚动体端面及兜孔区域，进行润滑，极大地延长了关键摩擦副在极端工况下的油荒耐受时间，轴承内部能维持基本润滑。
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Figure CN224871700U_ABST
Abstract
Description
Technical Field
[0001] This application belongs to the field of thrust bearing cages, and particularly relates to a planar thrust segmented cage. Background Technology
[0002] Thrust bearings are critical mechanical components specifically designed to withstand axial loads, widely used in heavy machinery, wind turbine yaw and pitch systems, and large slewing bearings. The cage, as the core component of the bearing, functions to evenly isolate and guide the rolling elements, preventing them from colliding. It has a decisive impact on the bearing's operational stability, load-bearing capacity, and service life. For large and even ultra-large thrust bearings, the cage dimensions are enormous. Traditional integral cages have many drawbacks, such as complex manufacturing processes; any localized damage can lead to the scrapping of the entire expensive cage or even the bearing, resulting in high maintenance costs. To overcome these shortcomings, segmented cages have emerged. This design divides the integral cage into multiple independent arc-shaped segments, each of which can be manufactured and installed independently. This reduces the difficulty and cost of single-piece machining. Furthermore, during maintenance, only damaged sections can be replaced, achieving modular maintenance and significantly improving economic efficiency.
[0003] However, in practical applications, especially in large, high-speed, or complex thrust bearings, existing segmented cages, due to their large bearing size and high cage linear velocity, struggle to overcome the centrifugal force guiding the lubricating grease or oil to the outer edge of the cage, failing to effectively return to the contact interface between the rolling elements and the cage, and to the pockets. This results in insufficient lubrication in critical friction areas, leading to localized oil deficiency or dry friction. Under poor lubrication conditions, the impact force between the rolling elements and the cage increases significantly. These concentrated impact forces, particularly those repeatedly acting at the corners of the segmented arched walls of the cage's window beam, easily induce micro-cracks. Ultimately, this leads to premature failure of the entire bearing, causing significant economic losses and safety hazards. Therefore, existing technology requires further improvement and enhancement. Utility Model Content
[0004] This invention provides a planar thrust segmented cage, which solves the problem of failure of the dynamic lubrication protection system and premature damage to weak parts in existing planar segmented cages under large-scale high-speed operating conditions.
[0005] To achieve the above objectives, the present invention provides the following technical solution: A planar thrust segmented cage includes an arc-shaped outer ring extending circumferentially and an arc-shaped inner ring concentrically arranged thereon, and a plurality of window beams circumferentially spaced between the arc-shaped outer ring and the arc-shaped inner ring. Adjacent window beams form pockets for accommodating rolling elements. The axial height of both the arc-shaped outer ring and the arc-shaped inner ring is greater than the axial height of the window beams. The radially inner side of the arc-shaped outer ring facing the pocket is an oil-guiding slope inclined in a direction away from the bearing axis. The oil-guiding slope is provided on the radially inner wall of the arc-shaped outer ring with an axial height higher than that of the window beams. The oil-guiding slope at least partially covers the end face of the rolling element accommodated in the pocket. The oil-guiding slope is used to impede the radial outward flow of lubricating oil under centrifugal force when the bearing rotates and to guide the lubricating oil to converge towards the pocket area.
[0006] In a preferred embodiment, the arc-shaped outer ring portion has two end faces in the axial direction with alternating circumferentially arranged crests and troughs. The circumferential position of the troughs corresponds to the pocket, the circumferential position of the crests corresponds to the window beam, and the lowest point of the troughs corresponds radially to the end face region of the rolling element accommodated by the pocket.
[0007] In a preferred implementation, the bottom surface of the trough is an oil return slope that is inclined in a direction away from the bearing axis.
[0008] In a preferred embodiment, on the outer arc-shaped portion and the inner arc-shaped portion, in the region facing the radially inner side of the pocket and located at the same height as the window beam axis, a raised guide portion is provided. The guide portion corresponds to the central region of the trough portion and is used to form a guide contact with the corresponding end face of the rolling element in the pocket. The two sides of the guide portion are recessed oil storage portions, forming an oil passage gap between them and the corresponding end face of the rolling element.
[0009] In a preferred implementation, in the circumferential region corresponding to the pocket, the outer wall of the arc-shaped inner ring is recessed inward and the inner wall is convex outward, resulting in a relatively reduced wall thickness in the region; in the circumferential region connected to the window beam, the outer wall of the arc-shaped inner ring is convex outward and the inner wall is recessed inward, resulting in a relatively increased wall thickness in the region.
[0010] In a preferred implementation, the wall thickness of the arc-shaped inner ring at a position where its axial direction is equal to the height of the window beam is a first thickness; the wall thickness at a position where its axial direction exceeds the height of the window beam is a second thickness; wherein the first thickness is greater than the second thickness.
[0011] In a preferred implementation, at the radial inner wall surface at both ends of the arc-shaped outer ring portion where the axial height is higher than the end face of the window beam, a first radial reinforcement portion is provided corresponding to the circumferential position of each window beam. The first radial reinforcement portion connects the window beam and the inner wall surface of the arc-shaped outer ring portion, and the first radial reinforcement portion has an inclined surface that is inclined in the direction away from the bearing axis.
[0012] In a preferred implementation, at one end of the arc-shaped inner ring, where the axial height is higher than the radial inner wall of the window beam end face, a second radial reinforcement is provided corresponding to the circumferential position of each window beam. The second radial reinforcement connects the window beam and the inner wall of the arc-shaped inner ring. The other end face of the arc-shaped inner ring is flush with the window beam end face and is provided with a third radial reinforcement, which connects the window beam and the axial end face of the arc-shaped inner ring.
[0013] In the preferred implementation, the end of the arc-shaped inner ring with an axial height higher than the end face of the window beam is higher than the end face of the highest point of the crest portion, and the end face of the third radial reinforcement portion is flush with the end face of the crest portion.
[0014] In a preferred embodiment, the end face of the arc-shaped inner ring between adjacent third radial reinforcing portions is further provided with a reinforcing protrusion.
[0015] The above structure has the following beneficial effects: The planar thrust segmented cage of this application is inclined in the outer ring portion, which bears the maximum centrifugal force, away from the bearing axis. The oil guide ramp covers the end faces of the rolling elements, directly acting on the flow path of the lubricating oil. When the bearing rotates at high speed, the lubricating oil thrown towards the outer edge of the cage first impacts the axially raised arc-shaped outer ring portion, forming the first physical barrier against radial outward splashing of the oil. As the lubricating oil flows along the radial inner wall of the outer ring portion, it must climb the oil guide ramp. This process consumes the kinetic energy of the oil, slowing its outward flow speed and hindering rapid oil loss. After the oil accumulates and slows down in the outer area, it can return to the contact area between the rolling elements and the cage along the oil guide ramp for lubrication. With lubrication guaranteed, the oil film buffering effect between the rolling elements and the cage is restored, effectively absorbing and damping the impact force, thereby significantly reducing the alternating impact stress at the beams and corners and inhibiting the initiation of microcracks. By ensuring lubrication and reducing impact, the early failure problem of segmented cages at high speeds is directly solved, extending the overall life of the bearing. The alternating crests and troughs of the curved outer ring create a "wave-shaped" profile. When the bearing rotates at high speed, centrifugal force throws some oil towards the outer ring end face area. In a traditional flat end face, the oil would cross over and have difficulty returning. However, in this design, the lowest point of the troughs faces the rolling element end face area. When lubricating oil is thrown to the outside, it can accumulate in the troughs. Combined with the effect of the guide slope, some lubricating oil flows back to the rolling element end face and the pocket area for lubrication, greatly extending the oil shortage tolerance time of critical friction pairs under extreme operating conditions, and maintaining basic lubrication inside the bearing. Attached Figure Description
[0016] The accompanying drawings, which are included to provide a further understanding of the present invention and constitute a part of this invention, illustrate exemplary embodiments of the present invention and, together with the description thereof, serve to explain this application and do not constitute an undue limitation of the present invention. In the drawings: Figure 1 A schematic three-dimensional structural diagram of a planar thrust segmented cage of this application is shown from a first perspective. Figure 2 A schematic three-dimensional structural diagram of a planar thrust segmented cage according to a second perspective is shown; Figure 3 A schematic three-dimensional structural diagram of a planar thrust segmented cage of this application is shown from a third perspective. Label Explanation: 1. Arc-shaped outer ring; 10. Oil guide slope; 11. Crest; 12. Trough; 120. Oil return slope; 13. First radial reinforcement; 14. Guide high part; 15. Oil storage low part; 2. Arc-shaped inner ring; 20. Second radial reinforcement; 21. Third radial reinforcement; 22. Reinforcing protrusion; 3. Window beam; 4. Pocket. Detailed Implementation
[0017] 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 this invention. Therefore, the drawings and description are considered exemplary in nature and not restrictive.
[0018] In the description of this utility model, it should be understood that the terms "center," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "axial," "radial," and "circumferential," etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the accompanying drawings and are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model. In this utility model, unless otherwise expressly specified and limited, the first feature being "upper" or "lower" than the second feature can mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediate medium.
[0019] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral unit; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. However, specifying a direct connection indicates that the two main bodies at the connection point are not connected by an intermediate structure, but are simply connected to form a whole through a connecting structure. For those skilled in the art, the specific meaning of the above terms in this utility model can be understood according to the specific circumstances.
[0020] In this utility model, descriptions involving "first," "second," etc., are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of that feature.
[0021] The present invention will now be described with reference to the accompanying drawings.
[0022] The specific solution adopted is as follows: like Figure 1-3As shown, this utility model provides a planar thrust segmented retainer, including an arc-shaped outer ring 1 extending circumferentially and an arc-shaped inner ring 2 concentrically arranged with the arc-shaped outer ring 1, and a plurality of window beams 3 circumferentially spaced between the arc-shaped outer ring 1 and the arc-shaped inner ring 2. Adjacent window beams 3 form pockets 4 for accommodating rolling elements. The axial height of the arc-shaped outer ring 1 and the arc-shaped inner ring 2 is greater than the axial height of the window beams 3. The radially inner side of the arc-shaped outer ring 1 facing the pocket 4 is an oil guiding slope 10 inclined in a direction away from the bearing axis. The oil guiding slope 10 is provided on the radially inner wall of the arc-shaped outer ring 1 with an axial height higher than that of the window beams 3. The oil guiding slope 10 at least partially covers the end face of the rolling element accommodated in the pocket 4. The oil guiding slope 10 is used to block the radial outward flow of lubricating oil under the action of centrifugal force when the bearing rotates, and to guide the lubricating oil to converge in the pocket 4 area.
[0023] In this application, the planar thrust segmented cage features an axially protruding lubrication barrier with an inwardly inclined oil-guiding surface on the outer ring portion, which bears the maximum centrifugal force. This barrier is located radially inner to the raised portion of the outer ring and is inclined away from the bearing axis. The oil-guiding surface 10 covers the end face of the rolling element and directly acts on the flow path of the lubricating oil. When the bearing rotates at high speed, the lubricating oil thrown towards the outer edge of the cage first impacts the axially raised arc-shaped outer ring portion 1, forming the first physical barrier against radial outward splashing of the oil. As the lubricating oil flows along the radial inner wall of the outer ring portion, it must climb the oil-guiding surface 10. This process consumes the kinetic energy of the oil, slowing its outward flow speed and hindering rapid oil loss. After the oil accumulates and slows down in the outer area, it can return to the contact area between the rolling element and the cage along the oil-guiding surface 10 for lubrication.
[0024] With lubrication ensured, the oil film buffering effect between the rolling elements and the cage is restored, effectively absorbing and damping impact forces. This significantly reduces the alternating impact stress at the window beam 3 and corners, inhibiting the initiation of microcracks. By ensuring lubrication and reducing impact, the early failure problem of segmented cages at high speeds is directly solved, extending the overall bearing life.
[0025] Further, see Figure 1 and Figure 2The arc-shaped outer ring portion 1 has two circumferentially alternating crests 11 and troughs 12 on its two axial end faces. The circumferential position of the troughs 12 corresponds to the pocket 4, and the circumferential position of the crests 11 corresponds to the window beam 3. The lowest point of the troughs 12 corresponds radially to the end face area of the rolling element accommodated by the pocket 4. The alternating arrangement of crests and troughs first forms a "wave-shaped" profile. When the bearing rotates at high speed, centrifugal force will throw some oil towards the outer ring end face area. At this time, the conventional flat end face will cause the oil to cross the flat end face and have difficulty crossing back to the end face. However, the lowest point of the troughs 12 in this design is directly opposite the end face area of the rolling element. When the lubricating oil is thrown to the outside, it can accumulate in the trough. With the action of the oil guiding slope 10, some lubricating oil flows back to the end face of the rolling element and the pocket 4 area for lubrication, which greatly extends the oil shortage tolerance time of the key friction pair under extreme working conditions, and the bearing can maintain basic lubrication.
[0026] In a preferred embodiment of this invention, the bottom surface of the trough portion 12 is an oil return slope 120 that slopes away from the bearing axis. The oil return slope 120 ensures that the lubricating oil accumulated in the trough can be redirected to the friction area, preventing dry friction and thus extending the bearing life.
[0027] In a preferred embodiment of this application, a raised guide height 14 is provided on the radially inner side of the arc-shaped outer ring portion 1 and the arc-shaped inner ring portion 2, facing the pocket 4 and located in the region at the same height as the axial direction of the window beam 3. The guide height 14 corresponds to the central region of the trough portion 12 and is used to form a guide contact with the corresponding end face of the rolling element in the pocket 4. The two sides of the guide height 14 are recessed oil storage low portions 15, which form an oil passage gap with the corresponding end face of the rolling element.
[0028] The guide height 14 is the area that makes actual mechanical contact with the end face of the rolling element and performs guiding and limiting functions. Because it is convex, the contact area is deliberately reduced and precisely controlled. This reduces sliding friction and frictional heat, and ensures the positioning accuracy and operational stability of the rolling element in the pocket 4, preventing operational wobbling or impact caused by excessive lubrication clearance. On both sides of the guide height 14, recessed oil reservoirs 15 are designed. This creates an oil reservoir between the end face of the rolling element and the inner side of the cage in the non-contact area. This reservoir stores the lubricating oil collected from the guide slope 10 and the return slope 120, ensuring lubrication in the guide contact area.
[0029] In a preferred embodiment of this application, in the circumferential region corresponding to the pocket 4, the outer wall of the arc-shaped inner ring 2 is concave inward and the inner wall is convex outward, resulting in a relatively reduced wall thickness in this region. This allows for appropriate weight reduction and a degree of lightweighting. In the circumferential region connected to the window beam 3, the outer wall of the arc-shaped inner ring 2 convexes outward and the inner wall is concave inward, resulting in a relatively increased wall thickness in this region. The window beam 3 and its connection to the inner and outer rings are areas of impact load and stress concentration. Increasing the wall thickness of the arc-shaped inner ring 2 in this region is equivalent to directly increasing the flexural modulus and stiffness of this section.
[0030] Furthermore, the wall thickness of the arc-shaped inner ring 2 at the position where it is equal to the height of the window beam 3 in the axial direction is the first thickness; the wall thickness at the position where it exceeds the height of the window beam 3 in the axial direction is the second thickness; wherein, the first thickness is greater than the second thickness, and the contact area between the end face of the rolling element and the cage is locally thickened to improve strength, thereby enhancing the fatigue resistance and impact resistance of the weak links of the segmented cage.
[0031] See Figure 2 At the radially inner wall surface where the axial height at both ends of the arc-shaped outer ring portion 1 is higher than the end face of the window beam 3, a first radial reinforcement portion 13 is provided corresponding to the circumferential position of each window beam 3. The first radial reinforcement portion 13 connects the window beam 3 and the inner wall surface of the arc-shaped outer ring portion 1, and the first radial reinforcement portion 13 has an inclined surface that is inclined away from the bearing axis. A robust triangular support structure is constructed at the connection of the window beams 3 in the outer ring portion. Through its inclined surface design, on the one hand, the impact load on the window beam 3 is efficiently distributed and transferred to the tough outer ring portion, significantly reducing the stress concentration at the root of the window beam 3 and greatly improving the impact resistance and fatigue resistance; on the other hand, the inclined surface itself, together with the aforementioned oil guiding inclined surface 10, can also guide the convergence and flow of lubricating oil.
[0032] Furthermore, at one end of the arc-shaped inner ring 2, where the axial height is higher than the radial inner wall of the end face of the window beam 3, a second radial reinforcement 20 is provided corresponding to the circumferential position of each window beam 3. The second radial reinforcement 20 connects the window beam 3 and the inner wall of the arc-shaped inner ring 2. The other end face of the arc-shaped inner ring 2 is flush with the end face of the window beam 3, and a third radial reinforcement 21 is provided. The third radial reinforcement 21 connects the window beam 3 and the axial end face of the arc-shaped inner ring 2.
[0033] The design of the second and third radial reinforcement sections 21 is to reinforce the connection area of the inner ring window beam 3, which greatly improves the structural integrity of this area under complex alternating stress and ensures the overall stability of the segmented structure.
[0034] See Figure 3The axial height of the inner arc-shaped part 2 is higher than that of the end face of the window beam 3, and the height of the end face of the crest part 11 is higher than that of the highest point of the crest part 11. The end face of the third radial reinforcement part 21 is flush with the end face of the crest part 11. The higher side of the inner arc-shaped part, as the highest point, forms a stable axial guiding and positioning contact with the bearing component. The fact that the end face of the third reinforcement part is flush with the end face of the crest part 11 ensures that the support on this side is uniform and continuous, forming a flat support together with the crest part 11.
[0035] As a preferred embodiment of this application, the end face of the arc-shaped inner ring portion 2 between adjacent third radial reinforcing portions 21 is also provided with a reinforcing protrusion 22, which improves the strength and deformation resistance of the inner ring portion, effectively resists the complex forces generated by the force transmission of the window beam 3, and improves the deformation resistance of the retainer.
[0036] For any parts not mentioned in this utility model, existing technologies can be used or referenced.
[0037] The above are merely specific embodiments of this utility model, but the protection scope of this utility model is not limited thereto. Any person skilled in the art can easily conceive of various variations or substitutions within the technical scope disclosed in this utility model, and these should all be included within the protection scope of this utility model. Therefore, the protection scope of this utility model should be determined by the scope of the claims.
Claims
1. A planar thrust segmented retainer, comprising an arcuate outer ring extending circumferentially and an arcuate inner ring concentrically arranged thereon, and a plurality of window beams circumferentially spaced between the arcuate outer ring and the arcuate inner ring, wherein pockets for accommodating rolling elements are formed between adjacent window beams, characterized in that, The axial height of both the arc-shaped outer ring and the arc-shaped inner ring is greater than the axial height of the window beam. The radially inner side of the arc-shaped outer ring facing the pocket is an oil guiding slope inclined in a direction away from the bearing axis. The oil guiding slope is provided on the radially inner wall of the arc-shaped outer ring with an axial height higher than that of the window beam. The oil guiding slope at least partially covers the end face of the rolling element contained in the pocket. The oil guiding slope is used to block the radial outward flow of lubricating oil under the action of centrifugal force when the bearing rotates and guide the lubricating oil to converge in the pocket area.
2. The planar thrust segmented retainer according to claim 1, characterized in that, The arc-shaped outer ring has two end faces in the axial direction with alternating circumferential crests and troughs. The circumferential position of the troughs corresponds to the pocket, the circumferential position of the crests corresponds to the window beam, and the lowest point of the troughs corresponds radially to the end face area of the rolling element accommodated by the pocket.
3. The planar thrust segmented retainer according to claim 2, characterized in that, The bottom surface of the trough is an oil return slope that is inclined in a direction away from the bearing axis.
4. The planar thrust segmented retainer according to claim 2, characterized in that, On the outer arc-shaped portion and the inner arc-shaped portion, in the region facing the radially inner side of the pocket and located at the same height as the window beam axis, there is a raised guide height. The guide height corresponds to the central region of the trough portion and is used to form a guide contact with the corresponding end face of the rolling element in the pocket. The two sides of the guide height are recessed oil storage low portions, which form an oil passage gap with the corresponding end face of the rolling element.
5. The planar thrust segmented retainer according to claim 1, characterized in that, In the circumferential region corresponding to the pocket, the outer wall of the arc-shaped inner ring is recessed inward and the inner wall is convex outward, resulting in a relatively reduced wall thickness in the region; in the circumferential region connected to the window beam, the outer wall of the arc-shaped inner ring is convex outward and the inner wall is recessed inward, resulting in a relatively increased wall thickness in the region.
6. The planar thrust segmented retainer according to claim 5, characterized in that, The wall thickness of the arc-shaped inner ring at a position where its axial direction is equal to the height of the window beam is the first thickness; the wall thickness at a position where its axial direction exceeds the height of the window beam is the second thickness; wherein the first thickness is greater than the second thickness.
7. The planar thrust segmented retainer according to claim 2, characterized in that, At the radial inner wall surface at both ends of the arc-shaped outer ring portion where the axial height is higher than the end face of the window beam, a first radial reinforcement portion is provided corresponding to the circumferential position of each window beam. The first radial reinforcement portion connects the window beam and the inner wall surface of the arc-shaped outer ring portion, and the first radial reinforcement portion has an inclined surface that is inclined in the direction away from the bearing axis.
8. The planar thrust segmented retainer according to claim 2, characterized in that, At one end of the arc-shaped inner ring, where the axial height is higher than the radial inner wall of the window beam end face, a second radial reinforcement is provided corresponding to the circumferential position of each window beam. The second radial reinforcement connects the window beam and the inner wall of the arc-shaped inner ring. The other end face of the arc-shaped inner ring is flush with the window beam end face and is provided with a third radial reinforcement. The third radial reinforcement connects the window beam and the axial end face of the arc-shaped inner ring.
9. The planar thrust segmented retainer according to claim 8, characterized in that, The end of the arc-shaped inner ring with an axial height higher than the end face of the window beam is higher than the highest point end face of the crest section, and the end face of the third radial reinforcement section is flush with the end face of the crest section.
10. The planar thrust segmented retainer according to claim 8, characterized in that, The inner arc-shaped end face between adjacent third radial reinforcements is also provided with a reinforcing protrusion.