Double-valve retainer for high-speed oil-lubricated ball bearing and high-speed oil-lubricated ball bearing

Abstract

A double-petal retainer for a high-speed oil lubrication ball bearing comprises two single-petal retainers, each single-petal retainer comprises a guide ring and a plurality of lintels, the two single-petal retainers and a rolling body are connected in a mutually-locked shape-locking mode, protruding blocks are arranged at the ends of the lintels of the single-petal retainers, and the protruding blocks are connected with the guide ring. Pits are formed in the corresponding positions of the guide rings of the oppositely-arranged single-petal retainers, and the sizes of the pits are larger than the sizes of the protruding blocks. The high-speed oil lubrication ball bearing comprises an inner ring, an outer ring, a rolling body arranged between the inner ring and the outer ring, and a bivalve retainer, a raceway is arranged on the inner circumferential surface of the outer ring, and the outline of the raceway is a continuous curved surface formed by a first circular arc with a smaller curvature radius and a second circular arc with a larger curvature radius in a tangent manner. The invention aims to solve the problems that a traditional bearing is prone to early failure under high-speed and inclined working conditions, and a retainer is damaged due to the fact that a rolling body and the retainer are not synchronous in speed.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of rolling bearing, in particular to a double-valve cage for high-speed oil-lubricated ball bearing and high-speed oil-lubricated ball bearing. BACKGROUND

[0002] With the development of industrial equipment towards high speed and high power, the working conditions of ball bearings are becoming increasingly severe. Under high speed, high temperature and heavy load conditions, the movement stability and mechanical durability of the cage, as the core component for guiding and isolating the rolling elements of the ball bearing, directly affect the overall performance and reliability of the bearing.

[0003] In the scenario of high-speed operation and asymmetric load, the outer ring and the inner ring of the bearing will produce relative tilt, causing the motion trajectory of the rolling element to change from a circle to an ellipse. This elliptical trajectory will generate additional constraint force, forming a strong impact on the cage, causing abnormal wear of the cage pocket, which is one of the reasons for the early failure of the bearing.

[0004] In addition, under high-speed rotation, the angular velocity of the rolling element and the rotation speed of the cage are difficult to synchronize, resulting in continuous and frequent collisions between the rolling element and the inner wall of the cage pocket. This interaction seriously damages the movement stability of the cage. The existing cage is difficult to effectively absorb and alleviate this impact energy due to its integrated structure (such as SNAP cage, riveted window type cage), and under the action of this unstable load for a long time, the cage pocket surface is prone to wear, plastic deformation or even fatigue peeling, and in severe cases, the cage will break. SUMMARY

[0005] The present application aims to provide a double-valve cage for high-speed oil-lubricated ball bearing and high-speed oil-lubricated ball bearing to improve the problem of early failure of traditional bearings under high-speed and inclined working conditions, and the problem of speed difference between the rolling element and the cage leading to damage of the cage.

[0006] In order to solve the above technical problems, the specific scheme adopted by the present application is: comprising two oppositely arranged single-petal retainers, each single-petal retainer comprises a guide ring and a plurality of uniformly spaced beams arranged circumferentially on the guide ring, one end of the beam is connected to the guide ring, the other end extends to the guide ring of the oppositely arranged single-petal retainer, the width of the beam gradually decreases first and then gradually increases along its extension direction, so that the adjacent beams of the two single-petal retainers form a ball pocket for installing the rolling body, the double-petal retainer installs the rolling body through the ball pocket and is constrained by the inner ring and the outer ring of the bearing, which can form a mutual locking form locking connection between the two single-petal retainers and the rolling body, the end of the beam of the single-petal retainer is provided with a protrusion, and the corresponding position of the guide ring of the oppositely arranged single-petal retainer is provided with a pit, the size of the pit is larger than the size of the protrusion, and the contact between the protrusion and the sidewall of the pit can provide deformation limiting for the double-petal retainer which is deformed by impact.

[0007] As a further optimization of the double-petal retainer for high-speed oil lubricated ball bearings: a composite lubrication module is provided on the single-petal retainer, the composite lubrication module comprises an outer spiral lubrication channel arranged outside the single-petal retainer body, an axial lubrication channel communicated with the outer spiral lubrication channel, and an inner spiral lubrication channel arranged inside the single-petal retainer body.

[0008] As a further optimization of the double-petal retainer for high-speed oil lubricated ball bearings: the cross section of the outer spiral lubrication channel is a trapezoidal shape that gradually narrows towards the outer surface of the single-petal retainer, and the cross section of the inner spiral lubrication channel is a semicircular shape.

[0009] As a further optimization of the double-petal retainer for high-speed oil lubricated ball bearings: the composite lubrication module further comprises an inner lubrication channel arranged inside the single-petal retainer, the inlet end of the inner lubrication channel is arranged on the end face of the guide ring of the single-petal retainer away from the beam, the outlet end of the inner lubrication channel is arranged on the wall surface of the ball pocket on both sides of the beam in contact with the rolling body, and the inner lubrication channel as a whole has an inclination angle towards the outer surface of the single-petal retainer.

[0010] As a further optimization of the double-petal retainer for high-speed oil lubricated ball bearings: a spring is arranged between the two outlet ends of the inner lubrication channel inside the single-petal retainer, and a sealing ball is connected to both ends of the spring, which is pressed against the corresponding outlet end under the pre-tightening force of the spring.

[0011] As a further optimization of the double-petal retainer for high-speed oil lubricated ball bearings: the inlet end of the inner lubrication channel is a tapered inlet with a large opening area, and the outlet end of the inner lubrication channel is matched with the outer contour of the rolling body.

[0012] As a further optimization of the double-petal retainer for high-speed oil lubricated ball bearings: the end face of the guide ring where the inlet end of the inner lubrication channel is located is an inclined flow guide surface, which is configured to guide the lubricating oil to the inlet end of the inner lubrication channel by means of the centrifugal force generated by the operation of the bearing.

[0013] Further optimization of double-lobe retainer for high-speed oil-lubricated ball bearing: the ball pocket includes a straight pocket segment close to the outer surface of the single-lobe retainer and a round pocket segment close to the inner surface of the single-lobe retainer, the straight pocket segment provides a guide path for the assembly of rolling elements, and the round pocket segment is used to accommodate and constrain the rolling elements.

[0014] Specific scheme of high-speed oil-lubricated ball bearing: including an inner ring, an outer ring, rolling elements arranged between the inner ring and the outer ring, and a retainer for guiding and isolating the rolling elements, the inner circumferential surface of the outer ring is provided with a raceway, and the profile of the raceway is a continuous curved surface formed by the tangency of a first circular arc with a smaller curvature radius and a second circular arc with a larger curvature radius, by arranging the first circular arc and the second circular arc in tangency, the rolling elements subjected to inclined load can be smoothly transitioned from the contact area with the first circular arc to the contact area with the second circular arc, so as to weaken the impact force generated by the ellipticalization of the rolling elements' revolution track caused by the inclined load.

[0015] Further optimization of high-speed oil-lubricated ball bearing: the profile of the outer ring raceway is a continuous curved surface formed by the tangency of a first circular arc, a second circular arc and a third circular arc with increasing curvature radii, and the second circular arc and the third circular arc are distributed on both sides of the first circular arc.

[0016] Beneficial effects: the rolling elements are loaded into the ball pocket formed by the lintels of the two single-lobe retainers to complete the preliminary assembly. The assembled retainer and rolling elements are placed together in the raceway between the inner and outer rings of the bearing. At this time, the raceways of the inner and outer rings constrain the rolling elements, allowing them to roll only within the raceway, while the lintels of the retainer, which vary in width, hold the rolling elements. This mutual restraint relationship causes the constrained rolling elements to in turn prevent the two single-lobe retainers from separating, thereby forming a form-locking structure. This form-locking structure ensures that the relative positions of the components remain unchanged while not depriving the double-lobe retainer of its ability to deform slightly. This deformation characteristic enables the double-lobe retainer to effectively absorb and buffer the impact force generated by the asynchronization of the rolling elements and the retainer in rotation.

[0017] In order to further control the deformation amplitude of the double-lobe retainer, the protrusions at the ends of the lintels cooperate with the recesses on the guide ring to form a deformation cutoff mechanism. When the rolling elements collide with the double-lobe retainer, causing the two single-lobe retainers to rotate relative to each other, the protrusions can move within the recesses to provide a buffer space. If the relative rotation is too large, the side walls of the protrusions will come into close contact with the side walls of the recesses, thereby preventing further displacement and effectively preventing secondary collisions between the retainer and the rolling elements caused by excessive deformation, thereby avoiding damage to the retainer. The design of the form-locking structure of the double-lobe retainer and the protrusions and recesses improves the problem of damage to the retainer caused by the asynchronization of the rolling elements and the retainer in high-speed operation.

[0018] The application provides a sliding buffer interval for rolling bodies under inclined load by setting the raceway of the bearing outer ring as a curved surface tangent to circular arcs with different curvature radii, so as to weaken the impact force caused by the elliptical orbit of the rolling bodies under inclined load, and to improve the problem of early failure of the conventional bearing under high-speed and inclined working conditions. BRIEF DESCRIPTION OF DRAWINGS

[0019] Figure 1 a single-petal retainer according to the application; Figure 2 a double-petal retainer according to the application; Figure 3 a top view of a single-petal retainer according to the application; Figure 4 a side view of a single-petal retainer according to the application; Figure 5 a schematic view of the structure of a sealing ball and a spring at the outlet end of an inner lubricating channel according to the application; Figure 6 a schematic view of the cross section of a ball pocket according to the application; Figure 7 a schematic view of a high-speed oil lubricated ball bearing according to the application; Figure 8 a schematic view of the raceway of the outer ring of a high-speed oil lubricated ball bearing according to the application; Figure 9 a schematic view of the raceway of the outer ring of a double-row ball bearing according to the application; Figure 10 a schematic view of another matching form of the raceway of the outer ring of a double-row ball bearing according to the application; Figure 11 a schematic view of the size relationship of the curvature radii R1, R2 and R3 according to the application; Markings in the figure: 1, guide ring, 2, lintel, 3, composite lubricating module, 301, axial lubricating channel, 302, outer spiral lubricating channel, 303, inner spiral lubricating channel, 304, inner lubricating channel, 4, protruding block, 5, single-petal retainer, 6, pit, 7, rolling body, 8, outlet end, 9, inlet end, 10, spring, 11, sealing ball, 12, outer ring, 13, retainer, 14, inner ring, 15, ball pocket, 16, double-petal retainer, 17, straight pocket segment, 18, round pocket segment, 19, raceway, 20, first circular arc, 21, second circular arc, 22, third circular arc. DETAILED DESCRIPTION

[0020] Example 1 As Figure 7As shown, a high-speed oil-lubricated ball bearing includes an inner ring 14, an outer ring 12, rolling elements 7 disposed between the inner ring 14 and the outer ring 12, and a cage 13 for guiding and isolating the rolling elements 7. The cage 13 is a double-lobed cage 16 for the high-speed oil-lubricated ball bearing of the present invention. The outer ring 12 and the inner ring 14 are used to constrain the rolling elements 7 so that they can only roll in the raceway 19 between the outer ring 12 and the inner ring 14. The rolling elements 7 roll between the inner ring 14 and the outer ring 12, converting sliding friction into rolling friction.

[0021] like Figure 8 As shown, a raceway 19 is provided on the inner circumferential surface of the outer ring 12. The outline of the raceway 19 is a continuous curved surface formed by the tangency of a first circular arc 20 with a smaller radius of curvature and a second circular arc 21 with a larger radius of curvature. R1 is the radius corresponding to the first circular arc 20, and R2 is the radius corresponding to the second circular arc 21. The two radii are tangentially transitioned to form a continuous curved surface. R1 is adapted to non-tilting conditions, and its size design matches the radius of the raceway 19 of a traditional deep groove ball bearing, ensuring that the bearing can operate smoothly in a non-tilting, normal installation state. R2 is adapted to tilting conditions. When the rolling element 7 is subjected to tilting load, it smoothly transitions from the contact area of ​​the first circular arc 20 to the contact area of ​​the second circular arc 21 to weaken the impact force caused by the ellipticization of the orbital trajectory of the rolling element 7 due to the tilting load. In this embodiment, R2 is 1.5 times that of R1 and is located on both sides of the R1 raceway 19 area.

[0022] like Figure 2 As shown, the high-speed oil-lubricated ball bearing includes two opposing single-lobed retainers 5. Each single-lobed retainer 5 includes a guide ring 1, which is the basic frame of the single-lobed retainer 5 and the connection basis for components such as the crossbeams 2 and the recesses 6. The guide ring 1 is provided with multiple crossbeams 2 evenly spaced around its circumference. One end of the crossbeam 2 is connected to the guide ring 1, and the other end extends toward the guide ring 1 of the opposing single-lobed retainer 5. The crossbeams 2 cooperate with the crossbeams 2 of the opposing single-lobed retainer 5 to form a ball pocket 15 for mounting the rolling element 7. The double-lobed retainer 16 mounts the rolling element 7 through the ball pocket 15 and constrains the rolling element 7 with the help of the inner ring 14 and outer ring 12 of the bearing, so that the two single-lobed retainers 5 and the rolling element 7 can form a mutually locking form-locking connection. The width of the crossbeam 2 gradually decreases and then gradually increases along its extension direction. The crossbeam 2 with varying width can completely hold the rolling element 7, ensuring the stability of the form-locking connection. In this embodiment, the double-lobed retainer 16 is made of high-performance plastics such as PAI (polyamide-imide). PAI plastic has excellent high temperature resistance, high strength, high rigidity, good wear resistance and corrosion resistance, which can meet the bearing's usage requirements under different working conditions. In particular, it exhibits better performance in high temperature, high speed and corrosive environments.

[0023] like Figure 3As shown, the end of the crossbeam 2 of the single-lobed retainer 5 is provided with a protrusion 4, and the corresponding position of the guide ring 1 of the oppositely arranged single-lobed retainer 5 is provided with a recess 6. The size of the recess 6 is larger than the size of the protrusion 4. The protrusion 4 at the end of the crossbeam 2 and the recess 6 on the guide ring 1 cooperate to form a deformation cutoff mechanism. When the rolling element 7 collides with the double-lobed retainer 16, causing the two single-lobed retainers 5 to rotate relative to each other, the protrusion 4 can move within the recess 6 to provide buffer space. If the relative rotation is too large, the sidewall of the protrusion 4 will be in close contact with the sidewall of the recess 6, thereby preventing the displacement from expanding further. This effectively prevents secondary collisions between the retainer and the rolling element 7 caused by excessive deformation, and avoids damage to the retainer.

[0024] like Figure 1 As shown, the single-lobe retainer 5 is equipped with a composite lubrication module 3, which is an integrated module on the single-lobe retainer 5 that provides guidance for lubricating oil. The composite lubrication module 3 includes an outer spiral lubrication channel 302 located on the outside of the single-lobe retainer 5 body, an axial lubrication channel 301 communicating with the outer spiral lubrication channel 302, and an inner spiral lubrication channel 303 located on the inside of the single-lobe retainer 5 body. The outer spiral lubrication channel 302 and the axial lubrication channel 301 together constitute a lubrication channel acting on the outer surface of the single-lobe retainer 5. The outer spiral lubrication channel 302 has a spiral helix angle of 5°. The helix angle design can utilize the centrifugal force generated when the bearing rotates at high speed to provide strong guiding force for the lubricating oil, causing the lubricating oil to flow smoothly along the outer spiral lubrication channel 302. The axial lubrication channel 301 crosses the outer spiral lubrication channel 302 to ensure that the lubricating oil is evenly delivered to all positions of the single-lobe retainer 5.

[0025] The cross-section of the external spiral lubrication channel 302 is a trapezoid that gradually narrows towards the outer surface of the single-lobe retainer 5. Compared with the traditional rectangular or semi-circular cross-section, the trapezoidal cross-section reduces the possibility of lubricating oil being thrown out under the action of centrifugal force. During the operation of the bearing, the stored lubricating oil can continuously and stably provide lubrication to the contact area, avoiding the problem of lubrication failure due to insufficient lubricating oil supply. Especially when the lubricating oil is not replenished in time, the lubricating oil stored in the trapezoidal cross-section can effectively extend the oilless lubrication time of the bearing and improve the reliability of the bearing.

[0026] The inner spiral lubrication channel 303 forms a lubrication channel acting on the inner surface of the single-lobe retainer 5. It works in conjunction with the outer spiral lubrication channel 302 and the axial lubrication channel 301 to achieve comprehensive lubrication of both the inner and outer surfaces of the single-lobe retainer 5. The inner spiral lubrication channel 303 has a semi-circular cross-section. When the bearing operates at high speed, the lubricating oil on the surface of the inner spiral lubrication channel 303 is smoothly collected into the semi-circular oil storage channel and flows along the spiral lubrication channel under the drive of centrifugal force. Ultimately, it is delivered to the contact areas between the rolling element 7 and the single-lobe retainer 5, and between the rolling element 7 and the bearing raceway 19, ensuring that the lubrication requirements of the inner area of ​​the single-lobe retainer 5 are met.

[0027] like Figure 4 As shown, the composite lubrication module 3 also includes an inner lubrication channel 304 located inside the single-lobed retainer 5. The inlet end 9 of the inner lubrication channel 304 is located on the end face of the guide ring 1 of the single-lobed retainer 5 away from the guide beam 2, and the outlet end 8 of the inner lubrication channel 304 is located on the wall surface of the ball pocket 15 on both sides of the guide beam 2 that contacts the rolling elements 7. If only the outer spiral lubrication channel 302 and the inner spiral lubrication channel 303 are used to guide and transport the lubricating oil, it is difficult for the lubricating oil to penetrate into the contact surface between the rolling elements 7 and the inner wall of the ball pocket 15 in a timely and sufficient manner. The design of the inner lubrication channel 304 can more accurately transport the lubricating oil to the contact area between the rolling elements 7 and the inner wall of the ball pocket 15, avoiding lubrication blind spots in the contact area between the rolling elements 7 and the inner wall of the ball pocket 15, and ensuring the lubrication effect. The inner lubrication channel 304 has an overall inclination angle towards the outside of the single-lobed retainer 5. The inclination angle design can accelerate the flow speed of the lubricating oil under the action of centrifugal force, so that the lubricating oil flows out smoothly from the outlet end 8.

[0028] like Figure 5 As shown, a spring 10 is provided between the two outlet ends 8 of the inner lubrication channel 304 inside the single-lobe retainer 5. Both ends of the spring 10 are connected to sealing balls 11. Under the preload of the spring 10, the sealing balls 11 are pressed against the corresponding outlet ends 8, which can form a good sealing effect on the outlet ends 8, so that the lubricating oil in the inner lubrication channel 304 can be prevented from leaking from the outlet ends 8 when the bearing is stopped rotating. When the bearing rotates, the rolling element 7 will exert pressure on the sealing ball 11. This pressure will cause the spring 10 to undergo slight compression deformation, thereby promoting the flow of lubricating oil from the outlet ends 8, ensuring that the lubricating oil can be continuously and stably delivered to the target area.

[0029] The guide ring 1, where the inlet end 9 of the inner lubrication channel 304 is located, has an inclined guide surface. This is configured to guide lubricating oil to the inlet end 9 of the inner lubrication channel 304 using the centrifugal force generated by the bearing's operation. Under the action of centrifugal force, the inclined guide surface guides the lubricating oil to the inlet of the inner lubrication channel 304. The inlet end 9 of the inner lubrication channel 304 is a conical inlet with a large opening area, effectively collecting lubricating oil on the end face of the guide ring 1 of the single-lobe retainer 5. The outlet end 8 of the inner lubrication channel 304 is adapted to the outer contour of the rolling element 7, ensuring that the lubricating oil flowing from the outlet end 8 is more evenly distributed on the surface of the rolling element 7. Simultaneously, the adapted outlet end 8 also guides and positions the rolling element 7.

[0030] like Figure 6 As shown, the ball pocket 15 includes a straight pocket section 17 near the outer surface of the single-lobed cage 5 and a round pocket section 18 near the inner surface of the single-lobed cage 5. The straight pocket section 17 provides a guiding path for the assembly of the rolling elements 7, and the round pocket section 18 is used to accommodate and constrain the rolling elements 7. The contour of the round pocket section 18 is adapted to the outer contour of the rolling elements 7, which allows the force exerted by the rolling elements 7 on the double-lobed cage 16 to act perpendicularly on the inner wall of the ball pocket 15 during high-speed operation of the bearing. This reduces the sliding friction between the rolling elements 7 and the inner wall of the ball pocket 15, reduces the heat generated by friction, and avoids performance degradation of the bearing due to excessive temperature during high-speed operation. At the same time, the perpendicular driving force enables the rolling elements 7 to maintain a stable motion state within the ball pocket 15, reduces the runout and offset of the rolling elements 7, and improves the adaptability of the bearing to high-speed operation. The contact area between the round pocket section 18 and the rolling elements 7 is adjusted according to the actual rotational speed of the bearing. The higher the actual rotational speed of the bearing, the larger the contact area between the round pocket section 18 and the rolling elements 7.

[0031] The invention relates to a double-lobed cage for a high-speed oil-lubricated ball bearing and a method for using the bearing: First, the rolling elements 7 are placed one by one between two opposing single-lobed cages 5, with the ball pockets 15 formed by the cage's crossbeams 2 providing initial support. Then, the combination of the double-lobed cage 16 and the rolling elements 7 is inserted between the outer ring 12 and the inner ring 14 of the bearing. At this point, the constraint of the rolling elements 7 by the inner and outer rings 12 and the locking design of the cage crossbeams 2 securely lock the entire assembly into a single unit. During use, lubricating oil is injected into the inner ring 14 and the outer ring 12 of the bearing. During high-speed operation, the composite lubrication module 3 of the double-lobed cage 16 automatically and efficiently delivers the lubricating oil to the critical area between the rolling elements 7 and the double-lobed cage 16 using centrifugal force. When the rolling element 7 collides with the double-lobed cage 16, the double-lobed cage 16 absorbs energy through its own slight deformation, while the protrusion 4 and the recess 6 cooperate to prevent the double-lobed cage 16 from deforming excessively. When the bearing is subjected to a tilting load, the rolling element 7 smoothly transitions from the contact area of ​​the first arc 20 to the contact area with the second arc 21, so as to weaken the impact force caused by the ellipticization of the orbital trajectory of the rolling element 7 due to the tilting load.

[0032] Example 2 This embodiment is an optimization based on Embodiment 1.

[0033] The raceway profile of the outer ring 12 is a continuous curved surface formed by the tangency of a first circular arc 20, a second circular arc 21, and a third circular arc 22, whose radii of curvature increase sequentially. The second circular arc 21 and the third circular arc 22 are distributed on both sides of the first circular arc 20. The raceway profile with three tangent circular arcs in this embodiment is mainly used in double-row ball bearings, and the continuous profile with three tangent circular arcs can withstand a larger bidirectional overturning moment.

[0034] like Figure 11 As shown, R1 is the radius corresponding to the first arc 20, R2 is the radius corresponding to the second arc 21, and R3 is the radius corresponding to the third arc 22. The second arc 21 and the third arc 22 of the two rows in the double-row ball bearing are arranged symmetrically. R1 has the same function as in Example 1, which is adapted to non-tilting working conditions. The values ​​of R2 and R3 are 1.5 times and 2 times that of R1, respectively.

[0035] When a double-row ball bearing is subjected to a lateral overturning moment, the rolling elements 7 inside the double-row ball bearing will shift outward toward the raceway 19. For example... Figure 9 As shown, when the second arc 21 and the third arc 22 of the double-row ball bearing are installed as illustrated, the second arc 21 corresponding to R2 is on the outermost side of the raceway 19. That is, the second arc 21 serves as the main area for the sliding of the rolling element 7, allowing the bearing to withstand a relatively large lateral overturning moment. This installation method is suitable for applications with large overturning moments. Figure 10As shown, when the second arc 21 and the third arc 22 of the double-row ball bearing are installed as shown, the third arc 22 corresponding to R3 is on the outermost side of the raceway 19. That is, the third arc 22 is the main area for the sliding of the rolling element 7, and the bearing can withstand a relatively larger lateral overturning moment. This installation method is suitable for working conditions with a larger overturning moment.

Claims

1. A double-lobe cage for a high-speed oil-lubricated ball bearing, comprising two opposing single-lobe cages (5), characterized in that: Each single-lobed retainer (5) includes a guide ring (1) and a plurality of evenly spaced transoms (2) arranged circumferentially on the guide ring (1). One end of the transom (2) is connected to the guide ring (1), and the other end extends toward the guide ring (1) of the opposite single-lobed retainer (5). The width of the transom (2) gradually decreases and then gradually increases along its extension direction, so that a ball pocket (15) for mounting the rolling element (7) is formed between the adjacent transoms (2) of two single-lobed retainers (5). The double-lobed retainer (16) mounts the rolling element (7) through the ball pocket (15) and uses the ball pocket (15) to mount the rolling element (7). The inner ring (14) and outer ring (12) of the auxiliary bearing constrain the rolling element (7), enabling the two single-lobed retainers (5) to form a locking connection with the rolling element (7). The end of the beam (2) of the single-lobed retainer (5) is provided with a protrusion (4), and the guide ring (1) of the oppositely arranged single-lobed retainer (5) is provided with a corresponding recess (6). The size of the recess (6) is larger than the size of the protrusion (4). Through the contact between the protrusion (4) and the side wall of the recess (6), the double-lobed retainer (16) that is deformed by impact can be provided with deformation limit.

2. The double-lobe cage for a high-speed oil-lubricated ball bearing according to claim 1, characterized in that: The single-petal retainer (5) is provided with a composite lubrication module (3). The composite lubrication module (3) includes an outer spiral lubrication channel (302) located on the outside of the single-petal retainer (5) body, an axial lubrication channel (301) connected to the outer spiral lubrication channel (302), and an inner spiral lubrication channel (303) located on the inside of the single-petal retainer (5) body.

3. A double-lobe cage for a high-speed oil-lubricated ball bearing according to claim 2, characterized in that: The cross-section of the outer spiral lubrication channel (302) is a trapezoid that gradually narrows towards the outer surface of the single-lobe retainer (5), and the cross-section of the inner spiral lubrication channel (303) is a semi-circle.

4. A double-lobe cage for a high-speed oil-lubricated ball bearing according to claim 2, characterized in that: The composite lubrication module (3) also includes an inner lubrication channel (304) located inside the single-lobe retainer (5). The inlet end (9) of the inner lubrication channel (304) is located on the end face of the guide ring (1) of the single-lobe retainer (5) away from the crossbeam (2). The outlet end (8) of the inner lubrication channel (304) is located on the wall surface of the ball pocket (15) on both sides of the crossbeam (2) that contacts the rolling element (7). The inner lubrication channel (304) as a whole has an inclination angle toward the outer surface of the single-lobe retainer (5).

5. A double-lobe cage for a high-speed oil-lubricated ball bearing according to claim 4, characterized in that: A spring (10) is provided between the two outlet ends (8) of the internal lubrication channel (304) inside the single-lobe retainer (5). Both ends of the spring (10) are connected to sealing balls (11). The sealing balls (11) are pressed against the corresponding outlet ends (8) under the pre-tightening force of the spring (10).

6. A double-lobe cage for a high-speed oil-lubricated ball bearing according to claim 4, characterized in that: The inlet end (9) of the internal lubrication channel (304) is a conical inlet with a large opening area, and the outlet end (8) of the internal lubrication channel (304) is adapted to the outer contour of the rolling element (7).

7. A double-lobe cage for a high-speed oil-lubricated ball bearing according to claim 4, characterized in that: The end face of the guide ring (1) where the inlet end (9) of the inner lubrication channel (304) is located is an inclined guide surface, which is configured to guide the lubricating oil to the inlet end (9) of the inner lubrication channel (304) by means of the centrifugal force generated by the operation of the bearing.

8. A double-lobe cage for a high-speed oil-lubricated ball bearing according to claim 1, characterized in that: The ball pocket (15) includes a straight pocket section (17) near the outer surface of the single-lobe retainer (5) and a round pocket section (18) near the inner surface of the single-lobe retainer (5). The straight pocket section (17) provides a guide path for the assembly of the rolling element (7), and the round pocket section (18) is used to accommodate and constrain the rolling element (7).

9. A high-speed oil-lubricated ball bearing, comprising an inner ring (14), an outer ring (12), rolling elements (7) disposed between the inner ring (14) and the outer ring (12), and a cage (13) for guiding and isolating the rolling elements (7), characterized in that: The cage (13) is a double-lobed cage for any high-speed oil-lubricated ball bearing as described in claims 1-8. The inner circumferential surface of the outer ring (12) is provided with a raceway (19). The outline of the raceway (19) is a continuous curved surface formed by the tangency of a first circular arc (20) with a smaller radius of curvature and a second circular arc (21) with a larger radius of curvature. By setting the tangent first circular arc (20) and second circular arc (21), the rolling element (7) subjected to tilt load can smoothly transition from the contact area with the first circular arc (20) to the contact area with the second circular arc (21), thereby weakening the impact force generated by the ellipticization of the orbital trajectory of the rolling element (7) caused by the tilt load.

10. A high-speed oil-lubricated ball bearing according to claim 9, characterized in that: The outline of the raceway (19) of the outer ring (12) is a continuous curved surface formed by the tangency of the first circular arc (20), the second circular arc (21) and the third circular arc (22) with the radius of curvature increasing sequentially. The second circular arc (21) and the third circular arc (22) are distributed on both sides of the first circular arc (20).

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