High-rotating-speed bearing retainer for electric drive

Abstract

The high-rotating-speed bearing retainer comprises an end ring and window beams, the window beams are distributed on one side of the end ring at intervals, pocket holes with one ends open are defined between the adjacent window beams, the thickness of the retainer is gradually increased from the ends of the window beams to the end ring, the light weight of the upper portion of the retainer is achieved, the light weight design is beneficial to reducing rotational inertia, and the service life of the retainer is prolonged. The method is crucial for improving the response speed and the stability of the bearing at a high rotating speed; by increasing the thickness gradient from the window beam to the end ring, the structural strength of the bottom of the pocket is enhanced, complex stress and deformation generated during high-speed operation can be resisted, and therefore the risk of breakage of the bottom of the pocket is reduced; a groove is formed in the other side of the end ring and corresponds to a window beam, so that the mass center position of the retainer can be adjusted, the retainer is closer to the rotating center section of a ball, additional torque generated by centrifugal force is reduced, stress concentration generated by high-frequency swing and distortion of the bottom of a pocket is reduced, the fracture risk is reduced, and the operation stability of the bearing is improved.

Description

Technical Field

[0001] This application belongs to the field of bearing cages, and particularly relates to a high-speed bearing cage for electric drive. Background Art

[0002] A high-speed bearing cage for electric drive refers to a cage specifically designed for high-speed bearings in an electric drive system. In the field of new energy vehicles, the drive motors in new energy vehicles need to operate at high speeds, and at the same time, low noise and high stability are required. The high-speed bearing cage can effectively support and guide the rolling elements, reduce friction and wear, and improve the rotational accuracy and service life of the bearing. Therefore, in the drive motors of new energy vehicles, the high-speed bearing cage is an indispensable component. New energy vehicles have relatively high requirements for the lightweight of components. The crowned deep groove ball bearing cage is made of engineering plastics, which has a lighter mass compared to traditional steel cages, helps to reduce the weight of the whole vehicle, improve energy efficiency. It not only has a light mass but also has low friction performance, can meet the requirements of high-speed operation of new energy vehicles, and at the same time reduce friction losses and energy consumption.

[0003] However, due to the single-sided opening design of the crowned plastic cage, the centroid is not located on the central cross-section of the steel ball's rotation. Under high-speed operation, affected by centrifugal force and the change of contact angle, complex motions such as differential motion, spin, and gyroscopic effect will occur between the steel balls and the raceways. These motions will have a strong impact on the cage, further exacerbating its wear, heat generation, and deformation. At the same time, these motions will also cause high-frequency swinging and twisting at the bottom of the cage pockets. Considering that the bottom of the cage pockets is relatively weak and the material will soften at high temperatures, this high-frequency swinging and twisting will cause the bottom of the cage pockets to break, resulting in bearing failure. It can be seen that the existing technology needs to be further improved. Summary of the Utility Model

[0004] The utility model provides a high-speed bearing cage for electric drive, which solves problems such as centroid offset encountered by the crowned plastic cage during high-speed operation, wear, heat generation, and deformation caused by complex motions, and fracture caused by high-frequency swinging and twisting at the bottom of the cage pockets.

[0005] To achieve the above object, the utility model provides the following technical solutions:

[0006] A high-speed bearing cage for electric drive includes end rings and window beams. The window beams are spaced apart on one side of the end ring. The adjacent window beams enclose a pocket with one end open. The thickness of the cage gradually increases from the end of the window beam to the end ring, realizing lightweight of the upper part of the cage to reduce the moment of inertia and enhancing the structural strength of the bottom of the pocket to improve the anti-deformation ability. On the other side of the end ring, grooves are provided at positions corresponding to the window beams to adjust the centroid position close to the central cross-section of the ball rotation, reduce the risk of fracture at the bottom of the pocket, and improve the operating stability of the bearing.

[0007] The high-speed bearing retainer for electric drive of the present application has a retainer whose thickness gradually increases from the end of the window beam to the end ring, thereby achieving lightweighting of the upper part of the retainer. The lightweight design helps to reduce the moment of inertia, which is crucial for improving the response speed and stability of the bearing at high speeds; by increasing the thickness gradient from the window beam to the end ring, the structural strength of the bottom of the pocket is enhanced, which helps to resist the complex stress and deformation generated during high-speed operation, thereby reducing the risk of fracture at the bottom of the pocket; on the other side of the end ring, a groove is provided corresponding to the window beam position, which can adjust the center of mass position of the retainer to make it closer to the central cross-section of the ball rotation, reduce the additional torque generated by centrifugal force, and reduce the stress concentration caused by high-frequency swinging and twisting at the bottom of the pocket, thereby reducing the vibration and noise of the retainer during high-speed operation, further reducing the risk of fracture, and improving the operating stability of the bearing.

[0008] In a preferred implementation, the end of the window beam is provided with two arc-shaped claws bent toward the pocket to hold the ball and prevent it from escaping from the pocket. The thickness of the claws is less than the thickness of the window beam to reduce the contact area between the claws and the ball.

[0009] The thickness of the jaws is designed to be smaller, and the contact area with the ball is correspondingly reduced, which helps to reduce friction and wear during high-speed operation.

[0010] In a preferred implementation, an oil-passing gap is provided between the two arc-shaped claw portions, and a supporting portion is provided in the oil-passing gap. The supporting portion abuts against the bottom end of the claw portion to enhance the structural strength of the claw portion.

[0011] The presence of the support portion can significantly enhance the structural strength of the jaw portion, preventing it from being deformed or creeping due to the squeezing and friction of the ball during high-speed operation.

[0012] In a preferred implementation, a weight-reducing groove is provided in the middle of the oil-passing gap.

[0013] In a preferred implementation, a weight-reducing hole is provided in the middle of the oil-passing gap, and the weight-reducing hole is connected to the groove.

[0014] In a preferred implementation, the groove cavity of the groove extends to the middle area of the window beam to reduce the weight of the retaining frame and increase the grease capacity.

[0015] In a preferred implementation, a through-hole groove is provided on the side of the end ring facing the inner ring or the outer ring, and the through-hole groove directly penetrates the groove to form a grease flow channel.

[0016] In a preferred implementation, the inner surface of the pocket is provided with a symmetrical oil-passing portion, which has no contact with the ball so as to reduce the contact area between the ball and the inner surface of the pocket.

[0017] In a preferred implementation, both the window beam facing the inner circumferential surface and the outer circumferential surface are arc-shaped surfaces curved towards the center of the circle, so as to enhance its ability to resist the outward folding caused by the centrifugal force. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The drawings described herein are used to provide a further understanding of the present utility model and form a part of the present utility model. The schematic embodiments of the present utility model and their descriptions are used to explain the present application and do not constitute an improper limitation to the present utility model. In the drawings:

[0019] Figure 1 A schematic three-dimensional structural diagram of a schematic embodiment of the high-speed bearing cage for electric drive of the present application is shown;

[0020] Figure 2 A schematic structural diagram of a schematic embodiment of the groove of the present application is shown;

[0021] Figure 3 A schematic three-dimensional structural diagram of an embodiment of the high-speed bearing cage for electric drive of the present application is shown;

[0022] Figure 4 A structural diagram of another embodiment of the high-speed bearing cage for electric drive of the present application is shown;

[0023] Reference Numeral Description:

[0024] 1 - end ring; 2 - window beam; 20 - arc-shaped surface; 3 - pocket; 4 - groove; 5 - claw portion; 6 - support portion; 7 - through-hole groove; 8 - oil passage portion; 9 - weight reduction groove; 10 - weight reduction hole. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0025] In the following, only some exemplary embodiments are simply described. As those skilled in the art can recognize, the described embodiments can be modified in various different ways without departing from the spirit and scope of the present utility model. Therefore, the drawings and the description are considered to be exemplary in nature rather than restrictive.

[0026] In the description of the present utility model, it should be understood that the orientation or positional relationship indicated by terms such as "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation to the present utility model. In the present utility model, unless otherwise clearly specified and defined, the first feature being "above" or "below" the second feature may be that the first and second features are in direct contact, or the first and second features are indirectly in contact through an intermediate medium.

[0027] In the present utility model, unless otherwise clearly specified and defined, terms such as "installation", "connection", "connection", "fixation", etc. should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or integrated; it may be directly connected, or indirectly connected through an intermediate medium, and it may be the communication inside two elements or the interaction relationship between two elements. However, indicating a direct connection means that there is no connection relationship constructed through an excessive structure between the two connected main bodies, and they are only connected through the connection structure to form a whole. For those of ordinary skill in the art, the specific meanings of the above terms in the present utility model can be understood according to specific circumstances.

[0028] In the present utility model, descriptions such as "first", "second", etc. are only for descriptive purposes and should not be understood as indicating or implying their relative importance or implicitly indicating the quantity of the indicated technical features. Thus, features defined with "first" and "second" may explicitly or implicitly include at least one of such features.

[0029] The present utility model will be described below in conjunction with the accompanying drawings of the specification.

[0030] The specific solution adopted is as follows:

[0031] As Figures 1-4 shown, the present utility model provides a high-speed bearing cage for electric drive, including an end ring 1 and window beams 2. The window beams 2 are spaced apart on one side of the end ring. The adjacent window beams enclose a pocket with one end open. The thickness of the cage gradually increases from the end of the window beam to the end ring, realizing lightweight of the upper part of the cage to reduce the moment of inertia and enhancing the structural strength of the bottom of the pocket 3 to improve the anti-deformation ability. On the other side of the end ring, a groove 4 is provided corresponding to the position of the window beam to adjust the centroid position close to the cross-section of the center of rotation of the ball, reduce the risk of fracture at the bottom of the pocket, and improve the operating stability of the bearing.

[0032] In the above structure, the thickness of the retainer gradually increases from the end of the window beam to the end ring, thereby achieving lightweighting of the upper part of the retainer. The lightweight design helps to reduce the moment of inertia, which is crucial for improving the response speed and stability of the bearing at high speeds; by increasing the thickness gradient from the window beam to the end ring, the structural strength of the bottom of the pocket is enhanced, which helps to resist the complex stress and deformation generated during high-speed operation, thereby reducing the risk of fracture at the bottom of the pocket; on the other side of the end ring, a groove is provided corresponding to the window beam position, which can adjust the center of mass position of the retainer to make it closer to the central section of the ball rotation, reduce the additional torque generated by centrifugal force, and reduce the stress concentration caused by high-frequency swing and twisting at the bottom of the pocket, thereby reducing the vibration and noise of the retainer during high-speed operation, further reducing the risk of fracture, and improving the operating stability of the bearing.

[0033] As a preferred embodiment of the present application, the end of the window beam is provided with two arc-shaped claw portions 5 bent toward the pocket to hold the ball and prevent it from escaping from the pocket. The thickness of the claw portion 5 is less than the thickness of the window beam 2 to reduce the contact area between the claw portion and the ball.

[0034] When installing a ball, place it into the pocket through the upper opening. When the ball contacts the upper end of the jaws, the jaws are subjected to an outward bending force. As the ball continues to fall, the jaws continue to bend outward until the ball is completely inserted into the pocket and reaches the desired position. At this point, the jaws naturally return to their original position, tightly gripping the upper portion of the ball. The inner curvature of the jaws closely conforms to the surface of the ball, effectively preventing the ball from falling out of the upper opening. The jaws are designed to be thinner, reducing the contact area with the ball, which helps reduce friction and wear during high-speed operation.

[0035] Furthermore, there is an oil gap between the two arc-shaped claw parts, and the oil gap is provided with a support part, which abuts against the bottom end of the claw part to enhance the structural strength of the claw part. The presence of the support part 6 can significantly enhance the structural strength of the claw part, preventing it from being deformed or creeping due to the squeezing and friction of the ball during high-speed operation, which is crucial for maintaining stable operation of the bearing.

[0036] To achieve a further lightweight design, as a preferred embodiment of the present application, a weight-reducing groove 9 is provided in the middle of the oil gap to reduce the overall weight of the cage, thereby reducing the moment of inertia of the bearing and improving the response speed and energy efficiency of the electric drive system. Figure 4 The weight-reducing groove is located in the middle of the oil gap, which neither interferes with the flow of lubricating oil nor weakens the structural strength of the cage. Its shape can be customized according to actual needs, such as circular, oval, rectangular or irregular shapes, to maximize the weight reduction effect while maintaining structural integrity.

[0037] With the assistance of the support part, the structural strength of the claw mouth part is effectively enhanced, and even with the weight reduction groove, it can still maintain a stable limit on the ball.

[0038] As the second preferred embodiment of the present application, a weight reduction hole 10 is provided in the middle of the oil passing gap, and the weight reduction hole is communicated with the groove. The design of the weight reduction hole reduces the material usage of the cage, thus achieving lightweight. At the same time, the connected design of the weight reduction hole and the groove provides an additional flow channel for lubricating oil or lubricant, which helps to ensure sufficient lubrication inside the bearing, reduce friction and wear, and improve the operating efficiency and life of the bearing.

[0039] As a preferred embodiment of the present application, the cavity of the groove 4 extends to the middle area of the window beam 2 to reduce the weight of the cage and increase the grease storage space. Extending the cavity of the groove to the middle area of the window beam can significantly reduce the material usage of the window beam part, achieve lightweight design, help reduce the moment of inertia of the bearing, and improve the response speed and energy efficiency of the electric drive system; the extended groove cavity provides a larger storage space for lubricating oil or lubricant, which helps to ensure continuous lubrication of the bearing during operation; the increased grease storage space also helps to improve the thermal management performance of the bearing. During high-speed operation, the bearing generates heat, and the lubricating oil or lubricant can absorb and disperse this heat, thereby reducing the working temperature of the bearing.

[0040] In addition, by extending the cavity of the groove, the centroid position of the cage can be adjusted to be closer to the rotation center of the ball. The optimized distribution of the centroid can also improve the operating stability of the bearing, extend the durability and service life of the bearing.

[0041] As a preferred embodiment of the present application, a through-hole groove 7 is provided on one side of the end ring facing the inner ring or the outer ring, and the through-hole groove directly penetrates the groove to form a grease flow channel. As the grease flow channel, the through-hole groove can ensure that the lubricating oil or grease is continuously and evenly distributed between the ball and the raceway during the operation of the bearing. As the bearing rotates, when the bearing rotates at high speed, the grease in the through-hole groove will be affected by the centrifugal force and spread to the periphery of the bearing, which helps to ensure that the lubrication requirements of each part of the bearing are met and also helps to dissipate the heat of the bearing. The flowing grease can absorb and carry away this heat, thereby reducing the working temperature of the bearing.

[0042] As a preferred embodiment of the present application, symmetric oil passing parts 8 are provided on the inner surface of the pocket hole. The oil passing parts are not in contact with the ball to reduce the contact area between the ball and the inner surface of the pocket hole. As the grease channel, the oil passing parts can ensure that the lubricating oil or grease flows smoothly through the gap between the ball and the pocket hole during the operation of the bearing. This helps to form a uniform lubricating film, reduce the direct contact between the ball and the inner surface of the pocket hole, and thus reduce friction and wear.

[0043] As a preferred embodiment of the present application, both the inner circumferential surface and the outer circumferential surface of the window beam are arc-shaped surfaces 20 that are curved towards the center of the circle, so as to enhance its ability to resist the outward folding caused by the centrifugal force.

[0044] By designing the inner circumferential surface and the outer circumferential surface of the window beam as arc-shaped surfaces that are curved towards the center of the circle, the structural rigidity of these surfaces when bearing the centrifugal force can be increased, enabling the window beam to better resist the outward folding force generated by the high-speed rotation of the ball bearings, thereby maintaining the stability and integrity of the bearing.

[0045] What is not described in this utility model can be realized by adopting or referring to the existing technology.

[0046] The above is only the specific embodiment of the present utility model, but the protection scope of the present utility model is not limited thereto. Any person skilled in the art within the technical scope disclosed by the present utility model can easily think of various changes or substitutions, and these should all be covered within the protection scope of the present utility model. Therefore, the protection scope of the present utility model shall be subject to the protection scope of the claims.

Claims

1. A high-speed bearing cage for electric drive, comprising end rings and window beams. The window beams are spaced apart on one side of the end ring, and a pocket with one open end is formed between adjacent window beams. It is characterized in that, The thickness of the cage gradually increases from the end of the window beam to the end ring, making the upper part of the cage lightweight to reduce the moment of inertia and enhancing the structural strength of the bottom of the pocket to improve its anti-deformation ability. On the other side of the end ring, a groove is provided corresponding to the window beam position to adjust the center of mass position close to the cross-section of the ball rotation center, reducing the risk of fracture at the bottom of the pocket and improving the stability of the bearing operation.

2. The cage of the high-speed bearing for electric drive according to claim 1, characterized in that, The end of the window beam is provided with two arc-shaped claws bent toward the pocket to hold the ball and restrict it from leaving the pocket. The thickness of the claws is less than the thickness of the window beam to reduce the contact area between the claws and the ball.

3. The cage of the high-speed bearing for electric drive according to claim 2, characterized in that An oil-passing gap is provided between the two arc-shaped claw mouths, and a supporting portion is provided in the oil-passing gap. The supporting portion abuts against the bottom end of the claw mouth to enhance the structural strength of the claw mouth.

4. The cage of the high-speed bearing for electric drive according to claim 3, characterized in that, A weight-reducing groove is provided in the middle of the oil-passing gap.

5. The cage for a high-speed bearing for electric drive according to claim 3, characterized in that, A weight-reducing hole is provided in the middle of the oil-passing gap, and the weight-reducing hole is connected to the groove.

6. The cage of the high-speed bearing for electric drive according to claim 1, characterized in that The groove cavity of the groove extends to the middle area of the window beam, so as to reduce the weight of the retaining frame and increase the grease capacity space.

7. The cage of the high-speed bearing for electric drive according to claim 1, wherein A through hole groove is provided on the side of the end ring facing the inner ring or the outer ring, and the through hole groove directly penetrates the groove to form a grease flow channel.

8. The cage of the high-speed bearing for electric drive according to claim 1, characterized in that, The inner surface of the pocket is provided with a symmetrical oil-passing portion, which has no contact with the ball so as to reduce the contact area between the ball and the inner surface of the pocket.

9. The cage of the high-speed bearing for electric drive according to claim 1, characterized in that, The inner and outer surfaces of the window beam are both arc-shaped surfaces bent toward the center of the circle, so as to enhance its ability to resist outward folding caused by centrifugal force.

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