A high speed ball bearing cage and a high speed ball bearing comprising the same

Abstract

The utility model relates to mechanical transmission component field especially, more particularly to a kind of high-speed ball bearing retainer and the high-speed ball bearing containing this retainer.The present application provides a kind of retainer for high-speed ball bearing, technical scheme is as follows: a kind of retainer for high-speed ball bearing, including retainer and the pocket hole for separating steel ball along the circumferential direction even arrangement and to the same side opening, the material of retainer is the composite material containing glass fiber reinforced polyamide or carbon fiber reinforced polyamide;It is characterized by: the inner diameter surface of the connecting part between adjacent pocket hole is provided with groove, and the groove is through the closed side and the opening side of retainer.This scheme has the advantages of improving torsional stiffness, inhibiting centrifugal deformation and prolonging service life.

Description

Technical Field

[0001] This utility model relates to the field of mechanical transmission components, and in particular to a high-speed ball bearing cage and a high-speed ball bearing containing the cage. Background Technology

[0002] Ball bearings are fundamental components widely used in rotating mechanisms. Their main functions are to support rotating shafts, reduce friction, and bear loads. A typical ball bearing set usually consists of an inner ring, an outer ring, multiple balls located between the raceways of the inner and outer rings, and a cage to separate and guide the balls.

[0003] Among various types of cages, engineering plastic cages are favored in high-speed applications due to their advantages such as light weight, low coefficient of friction, good self-lubrication, and ease of molding. Cages made from glass fiber reinforced polyamide materials through injection molding are particularly common. To facilitate injection molding and subsequent bearing assembly, these plastic cages are typically designed with pockets opening to one side.

[0004] However, this asymmetrical opening structure presents challenges under high-speed operating conditions. When the bearing rotates at high speed, the cage itself is subjected to enormous centrifugal force, causing it to expand and deform towards the opening side, severely affecting rotational stability. To address this problem, a common solution is to remove some material from the cage to reduce weight. For example, Chinese utility model patents with authorization publication numbers CN216951304U and CN218440255U both disclose plastic cages with some material removed from the pocket connection area on the non-opening side of the cage. Chinese utility model patent with authorization publication number CN223190843U describes a solution that simultaneously removes some material from both the pocket connection area on the non-opening side of the cage and the outer diameter surface of the cage to achieve weight reduction.

[0005] However, while reducing weight, such existing weight-reduction designs also significantly weaken the overall stiffness of the cage structure, especially its torsional stiffness along its sides. During high-speed bearing rotation, the balls generate push-pull forces due to their different rotational speeds. When the distance between adjacent balls decreases, a thrust is generated, pushing the cage; when the distance increases, a pull is generated, pulling the cage. This periodically changing push-pull force creates alternating torsional stress. If the cage's torsional stiffness is insufficient due to weight reduction, it will undergo torsional deformation under this alternating stress, potentially causing the entire cage to detach from the bearing and resulting in premature bearing failure. Therefore, existing weight-reduction schemes struggle to simultaneously achieve low centrifugal deformation and high torsional stiffness under high-speed operating conditions.

[0006] Therefore, there is an urgent need in this field for an innovative cage design that can effectively reduce weight to control centrifugal deformation while ensuring that the cage has sufficiently high torsional stiffness to meet the stringent requirements of modern equipment for high-speed and high-reliability operation of bearings. Summary of the Invention

[0007] To address the aforementioned problems, the present invention aims to provide a high-speed ball bearing cage and a high-speed ball bearing containing the cage, which has the advantages of improving torsional stiffness, suppressing centrifugal deformation, and extending service life.

[0008] To achieve the above objectives, the present invention adopts the following technical solution:

[0009] This application provides a cage for a high-speed ball bearing, the technical solution of which is as follows: A cage for a high-speed ball bearing includes a cage and pockets evenly arranged circumferentially and opening to the same side for separating steel balls. The material of the cage is a composite material containing glass fiber reinforced polyamide or carbon fiber reinforced polyamide. The characteristic feature is that a groove is provided on the inner diameter surface of the connection part between adjacent pockets, and the groove penetrates the closed side and the open side of the cage.

[0010] This technical solution resolves the conflict between centrifugal deformation and torsional stiffness of the cage under high-speed conditions through the synergistic effect of material selection and structural design. First, glass fiber or carbon fiber reinforced polyamide composites are used to improve material strength while ensuring lightweight design, providing a foundation for subsequent weight reduction. Second, while the pockets are evenly arranged circumferentially and open to the same side, meeting the requirements of injection molding, the open structure is prone to centrifugal expansion. To address this, a groove is created on the inner diameter surface of the connection between adjacent pockets, connecting the closed and open sides. Weight reduction is achieved by removing material from the inner diameter surface connection, reducing expansion deformation under centrifugal force. Simultaneously, the groove's connection to both sides avoids localized stress concentration, allowing the cage to maintain overall torsional stiffness through the continuous distribution of the remaining structure after weight reduction. Furthermore, the groove is located on the inner diameter surface rather than the outer diameter surface, minimizing weakening of the external load-bearing area while reducing weight, further balancing stiffness and weight reduction requirements.

[0011] Furthermore, this application proposes that the cross-sectional size of the groove gradually tapers from the closed side to the open side of the cage. This technical solution achieves a balance between weight reduction and torsional stiffness by designing the groove with a gradually tapering cross-section. Specifically, the structure of the groove cross-section gradually tapering from the closed side to the open side allows for a larger groove cross-section on the closed side to provide sufficient material removal for weight reduction, while the gradually narrowing groove on the open side retains more material to maintain the torsional stiffness of the connection. This gradually tapering cross-section design optimizes stress distribution, reducing expansion deformation caused by centrifugal force during high-speed rotation, and resisting torsional stress caused by alternating push-pull forces through the solid structure retained on the open side, thus meeting the dual requirements of lightweighting and torsional stiffness.

[0012] Furthermore, this application proposes that, from the axial view of the cage, the cross-sectional profile of the groove is trapezoidal, and the width of this trapezoid gradually decreases from its opening on the inner diameter surface to the bottom of the groove. By designing the cross-sectional profile of the groove as trapezoidal with a gradually narrowing opening towards the bottom, a gradient transition in material distribution is achieved. Compared to conventional shapes such as rectangles or triangles, the trapezoidal cross-section can create a better load transfer path while maintaining weight reduction: the larger width at the opening reduces local stress peaks, while the gradually narrowing shape towards the bottom enhances the shear resistance of the connection points. This geometric gradient feature avoids stress concentration caused by abrupt changes in cross-section and enhances the structure's resistance to torsional stress through the inclination angle of the trapezoidal sidewalls, enabling the cage to effectively suppress centrifugal expansion deformation and maintain sufficient torsional stiffness under high-speed alternating loads.

[0013] Furthermore, this application proposes that the corners on both sides of the trapezoidal groove bottom be rounded. This technical solution effectively improves the stress distribution characteristics of the groove structure by providing rounded corners at the corners of the trapezoidal groove bottom. The corners of the trapezoidal groove bottom, as locations of geometric abrupt changes, are prone to stress concentration points under alternating torsional stress. The rounded corner structure can smoothly transition the geometric contour of this area, significantly reducing local stress peaks and thus inhibiting the initiation and propagation of microcracks. This design, while maintaining the weight-reduction function of the groove, enhances the fatigue resistance of the structure by optimizing local geometric features, enabling the cage to maintain sufficient torsional stiffness under high-speed alternating loads.

[0014] Furthermore, this application proposes that, from the axial perspective of the cage, the cross-sectional profile of the groove is arc-shaped, thus giving the groove an overall semi-frustum shape. This technical solution optimizes the structural mechanical properties of the cage by designing the cross-sectional profile of the groove to be arc-shaped. From the axial perspective, the arc-shaped cross-section can effectively disperse the torsional stress borne by the adjacent pocket connection parts during high-speed rotation, avoiding stress concentration caused by the groove's sharp corners. Compared to other cross-sectional shapes, the arc-shaped profile has a more uniform stress transmission path, which can maintain the torsional stiffness of the groove area while reducing weight, thereby suppressing the cage's tendency to twist under alternating loads. In addition, the arc-shaped cross-section also reduces the material flow resistance caused by sharp corners during injection molding, which is beneficial to improving the stability of the manufacturing process.

[0015] Furthermore, this application proposes that, in a cross-section passing through the cage axis, the semi-cone angle C between the sidewall of the groove and the rotation center axis of the cage is 10° to 20°. This technical solution optimizes the mechanical properties of the groove structure by limiting the range of the semi-cone angle between the sidewall of the groove and the rotation center axis. Controlling the semi-cone angle C between 10° and 20° results in the groove sidewall forming an inclined surface at a specific angle. This inclination angle ensures that the groove has sufficient structural depth to achieve effective weight reduction, while avoiding an excessively large angle leading to an insufficient sidewall support area.

[0016] Furthermore, this application proposes that the outer diameter surface of the cage on the opening side be provided with a slope, making the outer diameter surface conical with a larger bottom and a smaller top. This technical solution forms a conical structure with a larger bottom and a smaller top by setting a slope with specific geometric features on the outer diameter surface of the cage opening side. The choice of setting a slope on the outer diameter surface of the opening side directly optimizes the structure of the opening side region where centrifugal force is greatest during high-speed rotation. This effectively reduces the mass of this region to decrease the centrifugal expansion tendency, while also enhancing the bending stiffness of this region by utilizing the geometric characteristics of the conical structure. The conical structure with a larger bottom and a smaller top changes the stress distribution path of the outer diameter surface, allowing the tensile stress generated during centrifugal force to be uniformly transmitted along the conical surface, avoiding the stress concentration phenomenon that occurs in traditional straight-walled structures after weight reduction. This asymmetrical conical design achieves a balance between weight reduction and enhanced stiffness, particularly strengthening the structure of the opening side, the key area most prone to expansion deformation, thereby improving torsional performance without significantly increasing the overall mass.

[0017] Furthermore, this application proposes that, on the cross-section passing through the cage axis, the angle B between the inner wall of the groove and the rotation center axis of the cage is 10° to 20°; and the angle A between the inclined surface and the rotation center axis of the cage is 10° to 20°. This technical solution optimizes the key structure of the cage through a dual-angle constraint mechanism. First, the angle B between the inner wall of the groove and the rotation axis is limited to 10° to 20°. This angle range ensures that the groove structure retains sufficient sidewall support area during weight reduction, avoiding weakening of the torsional section due to excessive tilting, and also guides the centrifugal force to be evenly transmitted along the groove wall through the tilt angle. Second, the angle A between the outer diameter surface and the rotation axis is limited to 10° to 20°. This angle range allows the inclined surface to form a progressive transition structure to disperse stress concentration while reducing the mass on the opening side. In particular, by simultaneously controlling the two key angles within the same numerical range, the composite weight-reducing structure formed by the groove and the slope has mechanical symmetry in spatial distribution, thereby reducing centrifugal deformation while ensuring the stability of the overall torsional stiffness of the cage.

[0018] Furthermore, this application proposes that angles A and B be equal, ensuring that the inner and outer walls of the groove are parallel and that the groove wall thickness is uniform. This solution achieves this by setting the angle between the outer diameter surface of the cage opening and the inner wall of the groove relative to the axis of rotation to be equal, thus creating a parallel structure between the inner and outer walls of the groove and guaranteeing uniform wall thickness. This design optimizes the stress distribution of the groove through geometric symmetry, reducing weight while avoiding localized stress concentration caused by uneven wall thickness. The parallel structure of the inner and outer walls enhances the torsional stiffness of the groove region, enabling the cage to uniformly transmit torsional stress when subjected to alternating push-pull forces during high-speed rotation, suppressing torsional deformation caused by periodic loads. Uniform wall thickness further improves the structural stability of the groove, ensuring that the weight-reduced cage still has sufficient deformation resistance under dynamic conditions, thereby addressing both the requirements of centrifugal deformation control and torsional stiffness.

[0019] Furthermore, this application also proposes a high-speed ball bearing, comprising a steel outer ring, an inner ring, steel balls disposed between the outer ring and the inner ring, and a cage for separating the steel balls, characterized in that: the cage is the aforementioned cage.

[0020] As can be seen from the above, the cage for high-speed ball bearings and the high-speed ball bearing including the cage provided in this application effectively enhance the torsional stiffness of the cage by providing a groove that runs through the closed side and the open side on the inner diameter surface of the adjacent pocket connection part, suppressing centrifugal deformation and torsion caused by alternating stress during high-speed operation, and has the advantages of improving structural stability and extending service life. Attached Figure Description

[0021] Figure 1This is a three-dimensional schematic diagram of the first structure of the cage described in Example 1.

[0022] Figure 2 This is a schematic diagram of the top surface of the first structure of the cage described in Example 1.

[0023] Figure 3 This is a schematic diagram of the bottom surface of the first structure of the cage described in Example 1.

[0024] Figure 4 This is a side view of the first structure of the cage described in Example 1.

[0025] Figure 5 This is a side cross-sectional view of the first structure of the cage described in Example 1.

[0026] Figure 6 This is a three-dimensional schematic diagram of the second type of cage structure described in Example 1.

[0027] Figure 7 This is a schematic diagram of the top surface of the second type of cage structure described in Example 1.

[0028] Figure 8 This is a schematic diagram of the bottom surface of the second type of cage structure described in Example 1.

[0029] Figure 9 This is a side cross-sectional view of the second type of cage structure described in Example 1.

[0030] Figure 10 This is a schematic diagram of the high-speed ball bearing described in Example 2. Detailed Implementation

[0031] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain this utility model, and should not be construed as limiting this utility model.

[0032] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "clockwise", "counterclockwise", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They 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. Therefore, they should not be construed as limitations on this utility model.

[0033] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this utility model, unless otherwise stated, "a plurality of" means two or more, unless otherwise expressly defined.

[0034] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0035] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0036] In existing technologies, ball bearing cages are generally made of engineering plastics to achieve lightweighting, with glass fiber reinforced polyamide being widely used due to its ease of molding. To accommodate injection molding processes, cages are typically designed as pocket structures with openings on one side. However, under high-speed rotation, this structure is prone to expansion deformation on the open side due to centrifugal force. Existing weight reduction solutions reduce mass by removing material from the non-opening side, but this design significantly weakens the cage's torsional stiffness, leading to the risk of torsional deformation under alternating stress.

[0037] To address the aforementioned issues, researchers noted a conflict between stiffness and weight reduction in existing weight-reduction solutions. Analysis of the cage's stress state revealed that centrifugal force primarily acts on the open side, while alternating torsional stress concentrates at the connection points. Based on this, the research focus shifted to selecting areas that achieve weight reduction without compromising torsional stiffness. Further investigation revealed that removing material from the inner diameter surface reduces centrifugal expansion while preserving the integrity of the outer diameter surface structure to maintain stiffness. Finite element simulations verified that the through-groove design effectively disperses stress concentration, thus forming a technical approach that balances weight reduction and stiffness.

[0038] Example 1:

[0039] like Figure 1-9 As shown, this application proposes a cage 4 for high-speed ball bearings, made of glass fiber or carbon fiber reinforced polyamide composite material. The glass fiber reinforced polyamide composite material refers to an engineering plastic with polyamide as the matrix and glass fiber as the reinforcing phase. Specifically, it can be processed into the main structure of the cage 4 through injection molding, and the strength in a specific direction can be improved by controlling the fiber orientation.

[0040] The cage 4 includes circumferentially evenly arranged pockets 5, each open on one side. A groove 7, penetrating the closed side 10 and the open side 11, is provided on the inner diameter surface 6 at the connection point of adjacent pockets 5. The penetrating groove 7 refers to a groove structure that runs along the axis of the cage 4 through the closed side 10 and the open side 11. Specifically, it can be designed with a trapezoidal or arc-shaped cross-section and can be achieved through CNC machining or mold forming. Its penetrating characteristic avoids localized stress concentration. The groove 7 on the inner diameter surface 6 means that the groove is located on the inner surface of the cage 4 near the rotation center axis. Specifically, it can be located in the middle region at the connection point of adjacent pockets 5, reducing the mass distribution under the action of rotational centrifugal force by removing material from the inner diameter surface 6.

[0041] Specifically, during high-speed rotation, the open side 11 of the cage 4 tends to expand due to centrifugal force. By setting a through groove 7 on the inner diameter surface 6, the mass distribution in this area is effectively reduced, thereby reducing the tensile effect of centrifugal force on the open side 11. Simultaneously, the through design of the groove 7 creates a continuous structure in the material removal area, avoiding stress concentration caused by traditional isolated grooves. Since the groove 7 is located on the inner diameter surface 6, the outer diameter surface 8 structure remains intact, ensuring that the cage 4 has sufficient torsional stiffness when subjected to the ball's push-pull force. The reinforcing fibers in the composite material are distributed circumferentially, further strengthening the deformation resistance of the connection parts. This solution chooses to set a through groove 7 on the inner diameter surface 6, which reduces the centrifugal expansion effect and maintains torsional stiffness by preserving the continuous structure of the outer diameter surface 8. In the prior art, isolated grooves easily lead to stress concentration, while the through design allows the load to be uniformly transmitted along the axial direction, significantly improving structural reliability. Through the above technical solution, this application precisely selects the inner diameter surface 6 as the material removal area during the weight reduction process of the cage 4, optimizes the centrifugal force distribution through the design of the through-groove 7, and achieves a balance between reducing centrifugal deformation and maintaining torsional stiffness by utilizing the properties of composite materials and the structural integrity of the outer diameter surface 8. This solution effectively solves the problem of insufficient torsional stiffness of the cage 4 due to weight reduction under high-speed conditions and avoids the risk of torsional deformation caused by alternating stress.

[0042] In a further preferred embodiment, the cross-sectional size of the groove 7 gradually tapers from the closed side 10 of the cage 4 to the open side 11. This gradual taper means that the cross-sectional area of ​​the groove 7 continuously decreases along the direction from the closed side 10 to the open side 11. This can be achieved using a trapezoidal or conical cross-section structure. The larger cross-section of the groove 7 on the closed side 10 allows for the removal of more material to reduce mass, while the gradually narrowing groove 7 on the open side 11 retains more solid material to maintain the structural integrity of the connection. Specifically, when the cage 4 rotates at high speed, the closed side 10 experiences significant expansion stress due to centrifugal force. Increasing the cross-section of the groove 7 in this area effectively reduces mass and alleviates centrifugal deformation. The open side 11 requires higher torsional stiffness due to the alternating push-pull forces from adjacent steel balls; shrinking the cross-section of the groove 7 retains more material to enhance torsional resistance. This gradually tapering cross-section design optimizes the closed side 10 and the open side 11 for centrifugal deformation and torsional stress respectively, achieving a balance between weight reduction and stiffness. Through the above technical solution, this application can simultaneously reduce the centrifugal expansion deformation of the cage 4 and improve its torsional stiffness under high-speed rotation conditions, thereby effectively preventing torsional failure caused by alternating stress and ensuring the stability and reliability of bearing operation.

[0043] like Figure 1-5 In the first embodiment shown, the cross-sectional profile of the groove 7 is trapezoidal when viewed from the axial perspective of the cage 4, and the width of the trapezoid gradually decreases from its opening on the inner diameter surface 6 to the bottom of the groove.

[0044] The trapezoidal cross-sectional profile refers to the quadrilateral shape projected onto the plane perpendicular to the axis of the retainer 4, where the quadrilateral has two parallel sides, with the side length at the opening being greater than that at the bottom of the groove. This can be achieved using a trapezoidal protrusion structure in the injection mold, with the slope of the trapezoidal sidewalls controlled by adjusting the mold's tilt angle. The gradually decreasing width refers to a continuous reduction in size of the trapezoidal cross-section from the opening towards the bottom of the groove. This can be achieved by controlling the tilt angles of the two trapezoidal sidewalls. Specifically, the larger width at the opening of the trapezoidal cross-section disperses the stress distribution at the connection points of adjacent pockets 5, avoiding localized stress concentration; the gradually tapering structure towards the bottom of the groove creates a gradient transition in the material within the groove 7 region, enhancing the shear resistance of the connection points under torsional loads. The tilt angle of the trapezoidal sidewalls optimizes the load transfer path, allowing the alternating torsional stress acting on the retainer 4 to be evenly transferred along the sidewalls to the surrounding structure, thereby increasing overall torsional stiffness while reducing weight.

[0045] Furthermore, a rounded corner 12 structure is incorporated at the two corners of the bottom of the trapezoidal groove 7. The rounded corner 12 refers to replacing the sharp corners with rounded transitions, specifically using a curved surface with a radius ranging from 0.1 mm to 0.5 mm. This curved surface smoothly connects to the sidewalls and bottom of the groove 7. The rounded corner 12 structure eliminates stress concentration in areas of geometric abrupt change, thereby reducing the risk of crack initiation. Specifically, when the cage 4 is subjected to cyclic torsional stress, the corner areas at the bottom of the groove 7 are prone to localized stress peaks due to abrupt changes in cross-section. The rounded corner 12 structure increases the radius of curvature in this area, making the stress distribution more uniform and preventing excessive stress accumulation at the corners. Therefore, under high-speed alternating loads, the fatigue resistance of the bottom of the groove 7 is improved without affecting its weight reduction function. This solution, by introducing the rounded corner 12 structure, significantly improves the crack resistance of the bottom of the groove 7 while maintaining the overall torsional stiffness of the cage 4, achieving the same weight reduction effect.

[0046] like Figure 6-9 In the second embodiment shown, from the axial perspective of the retainer 4, the cross-sectional profile of the groove 7 on the inner diameter surface 6 of the connection between adjacent pockets 5 is arc-shaped. Here, "arc-shaped cross-sectional profile of the groove 7" means that the cross-sectional shape of the groove 7 on the plane perpendicular to the axis of the retainer 4 is a continuous arc curve. It can be a non-closed arc, such as a semicircle or a semi-elliptical arc. Specifically, it can be achieved by designing an arc-shaped mold cavity during injection molding. This shape can avoid stress concentration caused by sharp edges.

[0047] Specifically, during high-speed rotation, adjacent steel balls exert periodic pushing and pulling forces on the cage 4, causing the connection to bear alternating torsional stress. By designing the groove 7 with a circular arc cross-section, the stress is transmitted tangentially along the surface of the arc contour, avoiding local stress peaks at the corners of right-angled or trapezoidal cross-sections. The circular arc cross-section makes the material distribution more uniform, forming a smooth transition geometry in the weight-reducing area, which not only reduces the mass effect caused by centrifugal force but also maintains the torsional stiffness of the connection through continuous curvature changes. In addition, the circular arc contour reduces the flow resistance of molten material during injection molding, reducing the risk of internal defects caused by uneven filling, thereby improving structural integrity.

[0048] Compared to existing technologies, conventional cage 4 weight reduction methods remove material by setting rectangular or trapezoidal grooves 7 at the connection points. However, the sharp angles of such cross-sections easily cause stress concentration, leading to a decrease in torsional stiffness. In contrast, the arc-shaped cross-section grooves 7 eliminate sharp angles, resulting in a more uniform stress distribution and significantly improving torsional resistance under the same weight reduction conditions. This also avoids fatigue crack propagation caused by stress concentration. Through the above technical solution, this application can effectively suppress torsional deformation caused by alternating torsional stress during high-speed rotation while reducing the weight of the cage 4, ensuring the structural stability of the cage 4 under high-speed operating conditions and reducing the difficulty of the injection molding process.

[0049] In a further embodiment, the semi-cone angle between the sidewall of the groove 7 and the rotation center axis of the cage 4 on the cross-section along the axis of the cage 4 is 10° to 20°. The semi-cone angle refers to the inclination angle formed between the sidewall of the groove 7 and the rotation center axis, which can be achieved by adjusting the cavity contour angle of the injection mold. This angle range balances the weight reduction effect of the groove 7 with the sidewall support area. The rotation center axis refers to the geometric center line around which the cage 4 rotates, which can be ensured by the coaxiality machining accuracy of the inner diameter surface 6 and the outer diameter surface 8 of the cage 4. This axis serves as a reference for determining the inclination direction of the sidewall of the groove 7.

[0050] Specifically, when the semi-cone angle is within the range of 10° to 20°, for example, 10°, the sidewall of groove 7 forms a support surface with a specific inclination angle. During high-speed rotation, when the pushing and pulling forces generated by adjacent steel balls are transmitted along the sidewall of groove 7, the inclination surface can decompose the force into axial and radial components, reducing the torsional moment on the connection. Simultaneously, this angle range allows groove 7 to maintain sufficient material thickness on the sidewall to resist alternating stress while retaining the necessary depth, preventing plastic deformation due to excessively thin sidewalls caused by excessive angle. Through the above technical solution, this application effectively suppresses the torsional deformation of cage 4 during high-speed rotation, solving the technical problem of insufficient torsional stiffness caused by weight reduction. The inclination angle of the sidewall of groove 7 enables the connection to withstand the torsional stress generated by cyclic pushing and pulling forces, avoiding structural failure caused by stress concentration, thereby ensuring the operational stability of cage 4 under high-speed conditions.

[0051] like Figure 4 and 5 As shown in Figure 9, an inclined surface 9 is provided on the outer diameter surface 8 on the opening side of the retainer 4, so that the outer diameter surface 8 is a cone shape with a larger bottom and a smaller top.

[0052] The inclined surface 9 refers to the inclined structure formed on the outer diameter surface 8 of the opening side 11 of the cage 4 through machining or injection molding. Specifically, it can be achieved by cutting or molding. This feature, the outer diameter surface 8, removes material to form a conical transition or is directly injection molded into a conical transition. Specifically, the weight reduction design in this area directly acts on the opening side 11 where the centrifugal force is greatest, effectively reducing the mass inertia of this part. The construction of the conical inclined surface 9 changes the stress transmission path of the outer diameter surface 8, so that the tensile stress generated under the action of centrifugal force is evenly distributed along the conical surface, avoiding the local stress concentration phenomenon that occurs in traditional straight-wall structures after weight reduction. The geometric continuity of the conical surface enhances the structural integrity of the edge of the opening side 11, forming continuous support in the material removal area and improving the bending stiffness of this part. Through the above technical solution, this application effectively reduces the mass of the opening side 11 of the cage 4, reduces the tendency of centrifugal expansion deformation during high-speed rotation, and at the same time enhances the bending stiffness of this area through the geometric construction of the conical outer diameter surface 8, achieving a balance between weight reduction and structural strength. The stress dispersion characteristics of the conical structure avoid the stress concentration problem caused by traditional weight reduction designs, and improve the deformation resistance of the cage 4 under alternating torsional stress. The position of the inclined surface 9 matches the area of ​​the largest expansion deformation on the opening side 11, so that the structural optimization effect directly affects the part that needs improvement the most.

[0053] Furthermore, in the cross-section passing through the axis of the cage 4, the angle B between the inner wall of the groove 7 and the rotation center axis of the cage 4 is 10° to 20°; the angle A between the inclined surface 9 and the rotation center axis of the cage 4 in the cross-section is 10° to 20°. Here, the angle B between the inner wall of the groove 7 and the rotation center axis refers to the inclination angle of the groove 7 structure in the axial cross-section. This angle range allows the sidewall of the groove 7 to retain sufficient support area during weight reduction, avoiding excessive weakening of the torsional section. Here, the angle A between the inclined surface 9 and the rotation center axis refers to the inclination angle of the inclined surface 9 structure on the outer diameter surface 8. This angle range allows the inclined surface 9 to form a gradually transitioning conical surface when removing material from the opening side 11, dispersing stress concentration areas.

[0054] Specifically, the inclination angle of the inner wall of trench 7 is controlled within the range of 10° to 20°, ensuring that while maintaining the weight reduction effect, the sidewalls of trench 7 can still form an effective support surface to resist the shear force generated by alternating torsional stress. The inclination angles of the outer diameter surface 8 and the inclined surface 9 are simultaneously controlled within the same range, resulting in a spatially symmetrical distribution of the inclined surface 9 structure and the inner wall of trench 7. This symmetrical design allows centrifugal force to be uniformly transmitted along the wall of trench 7, while the conical structure of the inclined surface 9 disperses local stress to adjacent areas, avoiding structural fatigue caused by stress concentration. The combined effect of these two angular constraints creates a mechanical balance between the weight reduction area and the support area of ​​the cage 4, both reducing the mass of the open side 11 to suppress centrifugal expansion and enhancing torsional stiffness through the symmetrical inclined structure. This scheme, through dual angular constraints, creates a spatially symmetrical layout between the weight reduction structure and the support structure, establishing a mechanical transmission path between the material removal area and the retention area, maintaining the weight reduction effect while compensating for the loss of torsional stiffness through the support of the inclined sidewalls. Through the above technical solution, this application reduces the weight of the cage 4 opening side 11, and through the symmetrically distributed tilt angle design, the groove 7 and the inclined surface 9 structure work together to enhance the torsional section stiffness, effectively resisting the alternating torsional stress generated by the ball push-pull force during high-speed rotation, and avoiding the risk of torsion deformation and dislodgement of the cage 4 due to insufficient torsional stiffness.

[0055] In the optimal design, angles A and B are equal, ensuring that the inner and outer walls of groove 7 are parallel and have uniform wall thickness. Uniform wall thickness means that the material thickness between the inner and outer walls of groove 7 remains consistent; this design eliminates areas of localized stress concentration. Specifically, when angles A and B are equal, the inner wall of groove 7 forms a symmetrical inclination angle with the inclined surface 9 of the outer diameter surface 8, making the inner and outer walls of groove 7 parallel in the axial section. This parallel structure ensures that the wall thickness of groove 7 is uniformly distributed circumferentially and axially, thus avoiding thin-walled areas during weight reduction. Under high-speed rotation conditions, the alternating torsional stress generated by the ball bearing push-pull force is dispersed and transferred to the entire cage 4 through the uniform wall thickness structure, rather than concentrating at a weak point. The parallel groove 7 walls further enhance the flexural section modulus of this region, enabling the cage 4 to effectively resist torsional deformation under cyclic loads. This solution achieves uniform wall thickness in groove 7 through symmetrical angle settings, significantly improving torsional stiffness in the groove 7 region while avoiding the risk of localized deformation due to stress concentration, all while maintaining the same weight reduction effect. Through this technical solution, this application addresses the problem of insufficient torsional stiffness in the high-speed ball bearing cage 4 after weight reduction. The uniform wall thickness structure suppresses torsional deformation under alternating stress, preventing the cage 4 from becoming unstable and dislodging under periodic loads, thereby extending the bearing's service life under high-speed conditions.

[0056] Example 2:

[0057] like Figure 10As shown, this embodiment relates to a high-speed ball bearing, including a steel outer ring 1, an inner ring 2, steel balls 3 disposed between the outer ring 1 and the inner ring 2, and a cage 4 for separating the steel balls 3. The cage 4 is the cage 4 described in Embodiment 1.

[0058] Under high-speed rotation conditions, the glass fiber or carbon fiber reinforced composite matrix enhances the deformation resistance of the cage 4 through fiber orientation. The through-groove 7 reduces material usage while its cross-sectional contraction maintains torsional stiffness at the connection points, preventing stress concentration caused by excessive local material removal. The tapered slope 9 on the outer diameter surface 8 of the open side 11 suppresses centrifugal expansion by reducing the radial projected area, while the parallel structure of the inner and outer walls of the groove 7 ensures uniform stress transmission along the axial direction, eliminating the risk of torsional deformation caused by abrupt changes in wall thickness. The high specific stiffness of the composite material and the geometric constraints of the structural design create a synergistic effect, achieving lightweighting while constructing a stable torsional load-bearing system. Compared with existing technologies, this solution, through the combined design of the through-groove 7 and the tapered slope 9, forms a continuous material distribution gradient in the axial direction, effectively reducing mass while maintaining structural integrity. In existing technologies, the weight reduction area is concentrated on the non-open side 11, while this solution sets the tapered slope 9 on the open side 11, directly optimizing the structure in the area with the most significant centrifugal expansion, forming a technical path for actively suppressing deformation.

[0059] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0060] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention without departing from the principles and spirit of the present invention.

Claims

1. A high-speed ball bearing cage, comprising a cage (4) and pockets (5) evenly arranged circumferentially and opening to the same side for separating steel balls; characterized in that: A groove (7) is provided on the inner diameter surface (6) of the connection between adjacent pockets (5), and the groove (7) passes through the closed side (10) and the open side (11) of the retainer (4).

2. The high-speed ball bearing cage according to claim 1, characterized in that: The cross-sectional size of the groove (7) gradually decreases from the closed side (10) of the retainer (4) to the open side (11).

3. A high-speed ball bearing cage according to claim 2, characterized in that: Viewed from the axial perspective of the retainer (4), the cross-sectional profile of the groove (7) is trapezoidal, and the width of the trapezoid gradually decreases from its opening on the inner diameter surface (6) to the bottom of the groove.

4. A high-speed ball bearing cage according to claim 3, characterized in that: The trapezoidal groove bottom has rounded corners (12) on both sides.

5. A high-speed ball bearing cage according to claim 2, characterized in that: Viewed from the axial perspective of the cage (4), the cross-sectional profile of the groove (7) is arc-shaped.

6. A high-speed ball bearing cage according to claim 5, characterized in that: In a cross section passing through the axis of the retainer (4), the semi-cone angle C between the sidewall of the groove (7) and the rotation center axis of the retainer (4) is 10° to 20°.

7. A high-speed ball bearing cage according to claim 1, characterized in that: The outer diameter surface (8) on the opening side of the retainer (4) is provided with a slope (9), so that the outer diameter surface (8) is a cone shape with a larger bottom and a smaller top.

8. A high-speed ball bearing cage according to claim 7, characterized in that: In a cross section passing through the axis of the retainer (4), the angle B between the inner wall of the groove (7) and the rotation center axis of the retainer (4) is 10° to 20°; and the angle A between the inclined surface (9) and the rotation center axis of the retainer (4) in the cross section is 10° to 20°.

9. A high-speed ball bearing cage according to claim 8, characterized in that: The included angle A is equal to the included angle B, so that the inner and outer walls of the groove (7) are parallel to each other, and the wall thickness of the groove (7) is uniform.

10. A high-speed ball bearing, comprising a steel outer ring (1), an inner ring (2), steel balls (3) disposed between the outer ring (1) and the inner ring (2), and a cage (4) for separating the steel balls (3), characterized in that: The cage (4) is a high-speed ball bearing cage as described in any one of claims 1 to 9.

Images