Miniature self-locking bearing cage

Abstract

The application discloses a micro self-locking bearing retainer which is composed of a ring body and a plurality of window beams which are uniformly distributed on the ring body, and a containing chamber for containing rolling elements is formed between adjacent window beams and is open on one side; a surface of the window beam facing the containing chamber is provided with an elastic deformation part which can independently deform relative to the window beam, and the elastic deformation part can independently deform relative to the window beam when an external force acts on the elastic deformation part; when the retainer is ovalized during operation, the elastic deformation parts on the adjacent window beams approach each other, at this time, the elastic deformation part first contacts the rolling elements (balls), and is self-adjusted according to the pressure applied by the balls, instead of directly transmitting the force to the balls like the traditional window beam, so that the radial thrust on the balls is buffered and reduced through the deformation of the elastic deformation part, and the pressure on the inner and outer rings of the bearing is also reduced correspondingly, thereby reducing the abrasion and damage caused by excessive contact stress.

Description

Technical Field

[0001] This application belongs to the field of bearing cages, and particularly relates to a miniature self-locking bearing cage. Background Technology

[0002] Harmonic reducers, as core transmission components in industrial robotic arms, humanoid robots, and other fields, mainly consist of wave generators, flexible bearings, flex wheels, and rigid wheels. Their working principle involves generating harmonic motion through the controllable elastic deformation of the flexible bearings and flex wheels, achieving high transmission ratio speed changes. Among these, the flexible bearings and flex wheels, as key flexible components, are crucial to the transmission function but are also vulnerable points prone to failure.

[0003] Flexible bearings have a unique structure with extremely thin inner and outer ring walls to meet operational requirements. During the operation of a harmonic reducer, the wave generator is embedded in the inner ring of the flexible bearing, deforming it into a non-circular profile and creating a long axis and a short axis. When the flexible bearing deforms into an ellipse, the cage deforms accordingly: at the long axis point, the distance between the inner surfaces of the beams on both sides of the pocket shortens while the distance between the outer surfaces lengthens, generating a radial force pushing the rolling elements outward; at the short axis point, the distance between the inner and outer surfaces of the beams on both sides of the pocket lengthens, generating a radial force pushing the rolling elements inward. This periodic action increases the contact stress between the inner and outer rings of the bearing and the rolling elements. Over long-term action, the contact surface material fatigues, forming micro-cracks that expand into pitting corrosion, leading to accelerated wear, affecting the life and performance of the flexible bearing, and ultimately threatening the normal operation of the harmonic reducer and the entire equipment.

[0004] Currently, to meet the requirements of elastic deformation, harmonic reducer retainers mostly use elastic materials such as nylon, and the window opening is on one side only. This design reduces the contact area between the window beam and the balls, lowers the degree of constraint and frictional resistance, and can reduce energy loss and heat generation under high-speed operation or frequent deformation conditions, ensuring stable operation. However, this design leaves the window opening without axial restraint on the balls, and at the position of the major axis of the flexible bearing ellipse, the balls are prone to significant axial movement. If the balls near both major axes move significantly, it will cause cage instability, wobbling and displacement, affecting transmission accuracy, and even damaging the bearing and related components. If the window opening is designed with an axial restraint structure, although it can limit the axial movement of the balls, it will increase the contact area and frictional resistance, leading to increased energy loss, aggravated bearing heat generation, and affecting overall performance and service life. Therefore, the existing technology needs further improvement and enhancement. Utility Model Content

[0005] This invention provides a miniature self-locking bearing cage to at least solve or alleviate one or more technical problems in the prior art, or to at least provide a beneficial alternative.

[0006] To achieve the above objectives, the present invention provides the following technical solution:

[0007] A miniature self-locking bearing cage consists of an annular body and multiple window beams evenly distributed on the annular body. The adjacent window beams enclose a receiving chamber for accommodating rolling elements, and one side of the receiving chamber is open.

[0008] The surface of the window beam facing the receiving chamber is provided with an elastic deformation part that can deform independently relative to the window beam. A deformation buffer area is reserved between the side of the elastic deformation part away from the receiving chamber and the window beam. When the cage undergoes elliptical deformation during operation, the elastic deformation units on adjacent window beams will approach each other and abut against the rolling element. Under the pressure applied by the rolling element, the elastic deformation unit will undergo adaptive deformation in the direction of the deformation buffer area, thereby reducing the contact stress of the rolling element on the inner or outer ring of the bearing.

[0009] The miniature self-locking bearing cage of this application features an elastic deformation section on the surface of the window beam facing the receiving chamber, which can deform independently relative to the window beam. This elastic deformation section can deform independently of the window beam when subjected to external forces, unlike traditional window beams which rigidly compress the rolling balls. When the cage undergoes elliptical deformation during operation, the elastic deformation sections on adjacent window beams will approach each other. At this time, the elastic deformation section first contacts the rolling element (balls) and self-adjusts according to the pressure applied by the balls, instead of directly transmitting force to the balls as in traditional window beams. When the elastic deformation section contacts the balls and is subjected to pressure, it adaptively deforms towards the deformation buffer area, buffering and reducing the radial thrust on the balls through its own deformation. As the radial thrust on the balls decreases, the pressure on the inner and outer rings of the bearing also decreases accordingly. This reduces wear and damage caused by excessive contact stress. This will help improve the transmission accuracy and stability of industrial robotic arms, humanoid robots, and other equipment, reduce maintenance costs and failure rates, and provide a more reliable transmission solution for the development of related fields.

[0010] In a preferred embodiment, the window beam is provided with elastic deformation parts near the inner and outer rings of the receiving cavity surface. The elastic deformation part of the elliptical variable axis of the retainer near the inner ring moves toward the deformation buffer area, and the elastic deformation part near the outer ring at the short axis moves toward the deformation buffer area.

[0011] In a preferred embodiment, the surface of the elastically deformable portion facing the receiving cavity and the surface of the window beam without the elastically deformable portion facing the receiving cavity together constitute the contact surface of the rolling element and are adapted to the curvature of the rolling element.

[0012] In a preferred embodiment, radial grooves are provided on the inner and outer walls of the window beam, and a connecting groove is provided on the surface of the window beam facing the receiving cavity. The connecting groove is connected to the groove, and the window beam portion above the groove forms an elastic deformation section.

[0013] In a preferred embodiment, a connecting part is provided between the elastic deformation parts on the inner and outer sides of the window beam, and the connecting part cuts the grooves on both sides of the window beam.

[0014] In a preferred embodiment, the connecting groove extends radially to the connecting portion or extends radially from the inside of the window beam to the outside.

[0015] In a preferred implementation, the window beam includes a first window beam, a second window beam, and a third window beam;

[0016] The first window beam and the second window beam are arranged adjacent to each other and have a mirror-symmetric structure, and together they form a set of window beam units. The third window beam is arranged between the adjacent window beam units.

[0017] An arc-shaped window opening with an upper opening is formed between the first window beam and the second window beam, which is adapted to the ball bearing. The upper side of both the first window beam and the second window beam is provided with an ear structure that bends toward the arc-shaped window opening. The ear structure can axially limit the ball bearing.

[0018] The third window beam, together with the first and second window beams on the two adjacent sides, forms a columnar window opening with an upper opening, and the radial projection of the third window beam falls at the center of the arc-shaped window opening.

[0019] In the preferred implementation, the ear structure has a platform on the side away from the arc-shaped window opening, and the height of the platform is lower than the height of the third window beam.

[0020] In a preferred implementation, the total height of the ear structure and the first or second window beam is equal to the height of the third window beam.

[0021] In a preferred embodiment, the first and second window beams facing the columnar window openings, as well as the third window beam facing both sides of the columnar window beams, are provided with arc-shaped contact surfaces adapted to the ball bearings. Attached Figure Description

[0022] The accompanying drawings, which are included to provide a further understanding of the present invention and constitute a part of this invention, illustrate exemplary embodiments of the present invention and, together with the description thereof, serve to explain this application and do not constitute an undue limitation of the present invention. In the drawings:

[0023] Figure 1 A schematic three-dimensional structural diagram of one embodiment of the miniature self-locking bearing cage of this application is shown;

[0024] Figure 2 This application is illustrated. Figure 1 An enlarged structural schematic diagram of one embodiment of part A in the diagram;

[0025] Figure 3The diagram illustrates a schematic embodiment of the fit between the long axis position of the miniature self-locking bearing cage and the balls in this application.

[0026] Figure 4 The diagram illustrates a schematic embodiment of the fit between the short shaft position of the miniature self-locking bearing cage and the balls in this application.

[0027] Label Explanation:

[0028] 1. Ring-shaped body; 2. Window beam; 20. First window beam; 21. Second window beam; 22. Third window beam; 23. Ear structure; 24. Platform; 25. Elastic deformation section; 26. Deformation buffer area; 27. Sink; 28. Connecting groove; 29. ​​Connecting part; 3. Receiving chamber; 4. Bearing outer ring; 5. Bearing inner ring. Detailed Implementation

[0029] In the following description, only certain exemplary embodiments are briefly described. As those skilled in the art will recognize, the described embodiments can be modified in various ways without departing from the spirit and scope of this invention. Therefore, the drawings and description are considered exemplary in nature and not restrictive.

[0030] First, the technical concept of the technical solution disclosed in this utility model will be explained.

[0031] Given the unique working characteristics and structural features of flexible rolling bearings, when the flexible bearing deforms into an elliptical shape, the cage will also deform accordingly. Specifically, at the major axis point, the distance between the inner surfaces of the beams on both sides of the pocket shortens, while the distance between the outer surfaces lengthens, which generates a radial pushing force towards the outer ring of the rolling elements. Conversely, at the minor axis point, the distance between the inner and outer surfaces of the beams on both sides of the pocket lengthens, resulting in a radial pushing force towards the inner ring of the rolling elements. This periodic radial pushing effect significantly increases the contact stress between the inner and outer rings of the bearing and the rolling elements. Under prolonged high contact stress, the contact surface material will gradually exhibit fatigue, forming micro-cracks. As operating time increases, these micro-cracks continue to expand and propagate, eventually developing into pitting corrosion. The appearance of pitting corrosion further damages the smoothness of the contact surface, leading to accelerated wear and severely affecting the service life and performance stability of the flexible bearing, thus adversely affecting the normal operation of the entire harmonic reducer and even industrial robotic arms and humanoid robots.

[0032] Traditional retainers lack an effective elastic cushioning structure. When the retainer deforms, the window beams on both sides of the pocket directly compress the ball bearings. Since the window beams themselves have limited elastic deformation capacity, they cannot fully adapt to the force generated by this compression, thus applying a large radial thrust to the ball bearings.

[0033] This radial thrust is transmitted to the inner and outer rings of the bearing through the balls. According to the principle of force interaction, after being subjected to radial thrust, the balls will contact the inner and outer rings with greater pressure, resulting in a significant increase in the contact stress between the balls and the bearing's inner and outer rings. Under this high contact stress state for a long time, the contact surface material between the bearing's inner and outer rings and the balls is prone to fatigue, forming micro-cracks that gradually expand into pitting, thereby accelerating wear, seriously affecting the life and performance of the flexible bearing, and ultimately threatening the normal operation of the harmonic reducer and the entire equipment.

[0034] Furthermore, existing harmonic reducer retainers are mostly made of materials with a certain degree of elasticity, such as nylon, to meet the requirements of elastic deformation. Moreover, to achieve better elastic deformation, the retainer typically employs a single-sided opening design for the aperture. This design means the aperture does not axially restrict the balls, reducing the contact area between the aperture beam and the balls, thus lowering the constraint on the balls and effectively reducing the frictional resistance experienced by the balls during movement. On the other hand, when the flexible bearing is operating at high speed or undergoing frequent deformation, this low-friction design can significantly reduce energy loss, lower bearing heat generation, and ensure stable bearing operation. However, during the operation of the flexible bearing, especially at the major axis of the ellipse, due to the large deformation of the flexible bearing, the balls are very likely to experience significant axial movement. If the balls near both major axes experience significant axial movement, it can lead to cage instability, causing the cage to wobble and shift during movement, resulting in changes in its position. This not only affects the transmission accuracy of the harmonic reducer but may also damage the bearings and other related components. However, if all the windows of the cage are designed with axial constraints, although the axial movement of the balls can be effectively restricted, the contact area and frictional resistance between the window beam and the balls will be greatly increased, resulting in increased energy loss, aggravated bearing heating, and affecting the overall performance and service life of the flexible bearing.

[0035] In view of the aforementioned problems, this utility model provides a miniature self-locking bearing cage. The utility model will now be described in conjunction with the accompanying drawings.

[0036] The specific solution adopted is as follows:

[0037] like Figure 1-4 As shown, this utility model provides a miniature self-locking bearing cage, which consists of an annular body 1 and a plurality of window beams 2 evenly distributed on the annular body 1. The adjacent window beams 2 enclose a receiving chamber 3 for receiving rolling elements, and the receiving chamber 3 has an opening on one side.

[0038] The surface of the window beam 2 facing the receiving chamber 3 is provided with an elastic deformation part 25 that can deform independently relative to the window beam 2. A deformation buffer area 26 is reserved between the side of the elastic deformation part 25 facing away from the receiving chamber 3 and the window beam 2. When the cage undergoes elliptical deformation during operation, the elastic deformation units on adjacent window beams 2 will approach each other and abut against the rolling element. Under the pressure applied by the rolling element, the elastic deformation unit will undergo adaptive deformation in the direction of the deformation buffer area 26, thereby reducing the contact stress of the rolling element on the inner or outer ring of the bearing.

[0039] By employing the miniature self-locking bearing cage of this application, an elastic deformation portion 25, which can deform independently relative to the window beam 2, is provided on the surface of the window beam 2 facing the receiving chamber 3. This elastic deformation portion 25 can deform independently of the window beam 2 when subjected to external force, instead of rigidly compressing the balls as a whole like a traditional window beam 2. When the cage undergoes elliptical deformation during operation, the elastic deformation portions 25 on adjacent window beams 2 will approach each other. At this time, the elastic deformation portion 25 first contacts the rolling element (ball) and self-adjusts according to the pressure applied by the ball, instead of directly transmitting force to the ball as in a traditional window beam 2. When the elastic deformation portion 25 contacts the ball and is subjected to pressure, it will adaptively deform towards the deformation buffer area 26, buffering and reducing the radial thrust on the ball through its own deformation. When the radial thrust on the ball decreases, the pressure on the inner and outer rings of the bearing also decreases accordingly. This reduces wear and damage caused by excessive contact stress. This will help improve the transmission accuracy and stability of industrial robotic arms, humanoid robots and other equipment, reduce maintenance costs and failure rates, and provide more reliable transmission solutions for the development of related fields.

[0040] In a preferred embodiment of this application, the window beam 2 is provided with elastic deformation portions near the inner and outer rings on the side facing the receiving chamber 3. The elastic deformation portion of the elliptical variable axis of the retainer near the inner ring moves toward the deformation buffer area, and the elastic deformation portion near the outer ring at the short axis moves toward the deformation buffer area.

[0041] For details, see Figure 3 When the cage undergoes elliptical deformation, at the major axis position, due to the action of the wave generator, the inner ring 5 of the flexible bearing will undergo a significant outward expansion deformation. At this time, the elastically deformed portions near the inner ring will approach each other as the window beam 2 deforms, gradually approaching the balls in the receiving chamber 3. Due to the expansion of the inner ring, an outward radial force will be generated on the balls, causing the balls to tend to move outward and squeeze the outer ring.

[0042] The elastic deformation portion near the inner ring moves towards the deformation buffer area after being subjected to pressure transmitted from the balls. This elastic deformation portion can freely undergo elastic compression and deformation without being rigidly restricted by the window beam 2. This reduces the radial thrust on the balls, effectively reducing the rigid compression of the balls directly by the window beam 2, and consequently reducing the pressure of the balls on the outer ring 4, thereby reducing the contact stress between the balls and the outer ring. This helps reduce the risk of fatigue damage to the contact surface materials, reduces pitting and wear, and extends the service life of the outer ring 4.

[0043] See Figure 4 At the short axis position of the elliptical deformation of the cage, the expansion of the inner ring 5 of the flexible bearing is relatively small, while the outer ring, due to overall deformation and internal stress, will generate an inward radial force on the balls. At this time, the elastically deformed parts near the outer ring will move away from each other as the window beam 2 deforms, but due to the inward radial force of the outer ring, the balls will be squeezed and tend to move inward.

[0044] The elastically deformable portion near the outer ring, after being subjected to inward pressure transmitted from the balls, will also move towards the deformation buffer area, thus reducing the actual inward radial force on the balls. The pressure of the balls on the inner ring 5 of the bearing also decreases, thereby reducing the contact stress between the balls and the inner ring. This also helps to reduce the risk of fatigue damage to the contact surface materials, reduce pitting and wear, and extend the service life of the inner ring 5 of the bearing.

[0045] This design effectively adjusts the complex forces acting on the balls during elliptical deformation. Overall, it balances the contact stress between the balls and the inner and outer rings, preventing premature damage caused by localized stress concentration. Compared to traditional cages, this design significantly improves the reliability and lifespan of flexible bearings, thereby enhancing the performance of harmonic reducers in industrial robotic arms, humanoid robots, and other fields, while reducing equipment maintenance costs and failure rates.

[0046] In a preferred embodiment of this application, when the surface of the elastically deformable portion facing the receiving chamber 3 and the surface of the window beam 2 without the elastically deformable portion facing the receiving chamber 3 together constitute the contact surface of the rolling element (such as a ball) and are adapted to the curvature of the rolling element, the contact surface adapted to the curvature of the rolling element can make the contact between the rolling element and the cage more uniform. During the operation of the bearing, the load on the rolling element can be more evenly distributed on the contact surface, avoiding excessive local pressure.

[0047] See Figure 1 and Figure 2The inner and outer walls of the window beam 2 are respectively provided with radial grooves 27. A connecting groove 28 is provided on the side of the window beam 2 facing the receiving chamber 3. The connecting groove 28 is connected to the grooves 27 and has two sections. Thus, the portion of the window beam 2 above the grooves 27 forms an independently deformable elastic deformation section 25. Due to the presence of the grooves 27, the material thickness of this portion of the window beam 2 in the radial direction is relatively thin, resulting in better elasticity and deformation capacity compared to other parts of the window beam 2. When subjected to external forces, it can more easily undergo elastic deformation to adapt to changes in the force on the rolling elements. The grooves 27 form a deformation buffer area. The grooves 27 have a certain depth and space in the radial direction. When the elastic deformation section 25 deforms, it can move into the deformation buffer area formed by the grooves 27, thereby providing sufficient space and buffer for the deformation of the elastic deformation section 25.

[0048] In a preferred embodiment of this application, a connecting portion 29 is provided between the elastic deformation portions 25 on the inner and outer sides of the window beam 2, and the connecting portion 29 divides the recesses 27 on both sides of the window beam 2.

[0049] Elastic deformation sections 25 are provided on the inner and outer sides of the window beam 2, and a connecting section 29 is provided between the elastic deformation sections 25 on the inner and outer sides of the window beam 2. The connecting section 29 divides the grooves 27 on both sides of the window beam 2. After the grooves 27 are divided by the connecting section 29, relatively independent deformation spaces are formed on the inner and outer sides of the window beam 2. Each elastic deformation section 25 has its corresponding local groove 27 area as a deformation buffer area. The inner elastic deformation section 25 is mainly affected by the deformation of the inner ring and the inward or outward squeezing of the rolling element, while the outer elastic deformation section 25 is more affected by the force of the outer ring. Due to the difference in the force on both sides, the two elastic deformation sections 25 will deform independently according to their respective force conditions.

[0050] Furthermore, the connecting groove 28 extends radially to the connecting portion 29 or extends radially from the inner side of the window beam 2 to the outer side.

[0051] In the first embodiment, when the elastic deformation portion 25 on the inner or outer side of the window beam 2 is subjected to the force of the rolling element, the force is transmitted to the vicinity of the connecting portion 29 through the connecting groove 28. Since the connecting groove 28 only extends to the connecting portion 29 and does not completely penetrate the window beam 2, the connecting portion 29 plays a role in isolating and dispersing the force to a certain extent. It can locally buffer and disperse the force transmitted from one side, preventing the force from being directly transmitted to the elastic deformation portion 25 on the other side, thereby ensuring that the elastic deformation portions 25 on both sides can independently undergo elastic deformation according to their respective force conditions.

[0052] In the second embodiment, since the connecting groove 28 penetrates the window beam 2, the entire structure of the window beam 2 forms a seesaw-like mechanical system. When the force on one side changes, it triggers a response in the opposite direction on the other side. When the ball applies force towards the inner wall of the outer ring, the inner elastic deformation part 25 moves towards the groove 27. This reduces the radial thrust on the ball towards the inner wall of the outer ring. At the same time, the outer elastic deformation part contacts the ball and applies a radial thrust towards the inner ring, further reducing the force exerted by the ball on the outer ring. This bidirectional force adjustment mechanism makes the force on the ball more uniform and stable at the long axis position, improving the bearing's operating performance. The adjustment mechanism in the short axis direction is the same and will not be described in detail.

[0053] In both the first and second embodiments, lubricating oil is present in the settling tank 27, covering the inner wall of the settling tank 27 and the lower surface of the elastic deformation part 25. When the elastic deformation part 25 deforms, its lower side is supported by the lubricating oil. The lubricating oil has a certain viscosity and fluidity, and it can form a lubricating film between the elastic deformation part 25 and the bottom of the settling tank 27. This lubricating film can play a buffering and supporting role, reducing the direct contact and friction between the elastic deformation part 25 and the bottom of the settling tank 27.

[0054] The solutions involved in this application include two combinations of the elastic deformation part and the cage. In the first method, the elastic deformation part and the cage body are an integral structure, meaning they are formed simultaneously during manufacturing using the same process, such as injection molding or casting. This eliminates any splicing or connecting gaps between the elastic deformation part and the cage body, ensuring the integrity of the overall structure and the uniformity of mechanical properties. This facilitates the coordinated deformation of the elastic deformation part and the cage body under stress, achieving the intended function. The second method involves separately setting and installing the elastic deformation part on the cage. Specifically, an independent elastic deformation part with a specific shape and size is first manufactured to meet the cage's installation requirements. Then, the elastic deformation part is fixedly installed in a predetermined position on the cage using suitable installation methods such as snap-fit ​​connections, bolt connections, or welding. This ensures that the elastic deformation part can work stably after installation and can independently deform according to actual stress conditions. Both of these structural solutions regarding the elastic deformation part and the cage achieve the technical objectives of this application and are therefore covered within the scope of protection of this application.

[0055] In a preferred embodiment of this application, the window beam 2 includes a first window beam 20, a second window beam 21, and a third window beam 22;

[0056] The first window beam 20 and the second window beam 21 are arranged adjacently and have a mirror-symmetric structure, and together they form a set of window beam 2 units. The third window beam 22 is arranged between the adjacent window beam 2 units.

[0057] The first window beam 20 and the second window beam 21 form an arc-shaped window hole that is adapted to the ball and has an opening on the upper side. The upper side of the first window beam 20 and the second window beam 21 is provided with an ear structure 23 that bends toward the arc-shaped window hole. The ear structure 23 can axially limit the ball.

[0058] The third window beam 22, together with the first window beam 20 and the second window beam 21 on the two adjacent sides, forms a columnar window opening with an upper opening, and the radial projection of the third window beam 22 falls at the center of the arc-shaped window opening.

[0059] In the above structure, the arc-shaped window formed between the first window beam 20 and the second window beam 21 has an opening on the upper side and ear structures 23 on both sides that can axially limit the balls. During the operation of the flexible bearing, especially at the position of the major axis of the ellipse, when the balls tend to move axially, the ear structures 23 can block the axial movement of the balls and effectively limit the axial movement of the balls. The radial projection of the third window beam 22 falls at the center of the arc-shaped window, so that when the long axis of the flexible bearing deforms, there is always an axial limit on one side near the long axis position, and the situation where both sides lose their limit will not occur. This enhances the cage's control over the axial movement of the balls, avoids the problem of cage instability, shaking and displacement caused by large movement of the balls on both sides, ensures the transmission accuracy of the harmonic reducer, and also reduces the risk of damage to the bearings and other related components. The third window beam 22, together with the adjacent first window beam 20 and second window beam 21 on both sides, forms a cylindrical window opening with an upper opening. This cylindrical window opening maintains characteristics similar to the existing single-sided opening design of window openings, reducing the contact area between the window beam 2 and the ball bearings, and lowering the degree of constraint on the ball bearings, thereby effectively reducing the frictional resistance experienced by the ball bearings during movement. Under conditions of high-speed operation or frequent deformation of flexible bearings, this low-friction design can significantly reduce energy loss, reduce bearing heat generation, and ensure stable bearing operation.

[0060] Furthermore, the ear structure 23 has a platform 24 on the side opposite to the arched window opening, and the height of the platform 24 is lower than the height of the third window beam 22.

[0061] With the ear structure 23 positioned on the side opposite the arc-shaped window opening, and the height of the platform 24 being lower than the height of the third window beam 22, a structure with one side lower and the other higher is formed in the cylindrical window opening. The lower side further reduces the contact area between the rolling elements and the cage, which is crucial for reducing frictional resistance, as harmonic reducers are typically used in applications requiring high precision and efficiency, such as robot joints and aerospace equipment. Lower frictional resistance reduces energy loss, improves transmission efficiency, and enables the reducer to operate more stably and efficiently. This design also achieves a certain degree of weight reduction; reducing the weight of the cage reduces the inertia of the entire bearing system. The larger oil reservoir formed on the upper side of the platform 24 can store more lubricating oil. More lubricating oil ensures that the rolling elements are always adequately lubricated during movement, forming a good oil film, reducing direct contact between the rolling elements and the cage, as well as the inner and outer rings, further reducing frictional resistance and wear.

[0062] Furthermore, the total height of the ear structure 23 and the first window beam 20 or the second window beam 21 is equal to the height of the third window beam 22. This ensures a relatively uniform mass distribution across the cage during rotation. When the harmonic reducer is running, the cage rotates at high speed, and a uniform mass distribution ensures rotational stability, reduces centrifugal force differences caused by uneven mass, and thus maintains good dynamic balance. If the heights of the different window beams 2 are not uniform, it will lead to uneven mass distribution across the cage. During rotation, the parts with larger mass will generate larger centrifugal forces, while the parts with smaller mass will generate smaller centrifugal forces. This difference in centrifugal forces will cause the cage to sway and vibrate, disrupting its dynamic balance.

[0063] Furthermore, the first window beam 20 and the second window beam 21 facing the columnar window opening, as well as the third window beam 22 facing both sides of the columnar window beam 2, are all provided with arc-shaped contact surfaces adapted to accommodate the ball bearings. The shape of the arc-shaped contact surface is adapted to the outer contour of the ball bearings, enabling a closer fit between the ball bearings and the window beam 2. Compared to planar contact, this fitted arc-shaped contact can greatly reduce stress concentration on the contact area and lower the pressure per unit area, thereby effectively reducing the friction between the ball bearings and the window beam 2 during movement.

[0064] For any parts not mentioned in this utility model, existing technologies can be used or referenced.

[0065] The above are merely specific embodiments of this utility model, but the protection scope of this utility model is not limited thereto. Any person skilled in the art can easily conceive of various variations or substitutions within the technical scope disclosed in this utility model, and these should all be included within the protection scope of this utility model. Therefore, the protection scope of this utility model should be determined by the scope of the claims.

Claims

1. A miniature self-locking bearing cage, characterized in that, It consists of a ring-shaped body and multiple window beams evenly distributed on the ring-shaped body. The adjacent window beams enclose a receiving chamber for accommodating the rolling element, and one side of the receiving chamber is open. The surface of the window beam facing the receiving chamber is provided with an elastic deformation part that can deform independently relative to the window beam. A deformation buffer area is reserved between the side of the elastic deformation part away from the receiving chamber and the window beam. When the cage undergoes elliptical deformation during operation, the elastic deformation units on adjacent window beams will approach each other and abut against the rolling element. Under the pressure applied by the rolling element, the elastic deformation unit will undergo adaptive deformation in the direction of the deformation buffer area, thereby reducing the contact stress of the rolling element on the inner or outer ring of the bearing.

2. The miniature self-locking bearing cage according to claim 1, characterized in that, The window beam is provided with elastic deformation parts near the inner and outer rings of the cavity surface. The elastic deformation part of the elliptical cage near the inner ring at the major axis position moves toward the deformation buffer area, and the elastic deformation part near the outer ring at the minor axis position moves toward the deformation buffer area.

3. The miniature self-locking bearing cage according to claim 1, characterized in that, The surface of the elastically deformable part facing the receiving cavity and the surface of the window beam without elastically deformable part facing the receiving cavity together constitute the contact surface of the rolling element and are adapted to the curvature of the rolling element.

4. The miniature self-locking bearing cage according to claim 1, characterized in that, The inner and outer walls of the window beam are respectively provided with radial grooves, and the window beam facing the receiving cavity is provided with a connecting groove. The connecting groove is connected to the groove, and the window beam part above the groove forms an elastic deformation part.

5. The miniature self-locking bearing cage according to claim 4, characterized in that, A connecting part is provided between the elastic deformation parts on the inner and outer sides of the window beam, and the connecting part cuts the grooves on both sides of the window beam.

6. The miniature self-locking bearing cage according to claim 5, characterized in that, The connecting groove extends radially to the connecting part or extends radially from the inside of the window beam to the outside.

7. The miniature self-locking bearing cage according to claim 1, characterized in that, The window beams include a first window beam, a second window beam, and a third window beam; The first window beam and the second window beam are arranged adjacent to each other and have a mirror-symmetric structure, and together they form a set of window beam units. The third window beam is arranged between the adjacent window beam units. An arc-shaped window opening with an upper opening is formed between the first window beam and the second window beam, which is adapted to the ball bearing. The upper side of both the first window beam and the second window beam is provided with an ear structure that bends toward the arc-shaped window opening. The ear structure can axially limit the ball bearing. The third window beam, together with the first and second window beams on the two adjacent sides, forms a columnar window opening with an upper opening, and the radial projection of the third window beam falls at the center of the arc-shaped window opening.

8. The miniature self-locking bearing cage according to claim 7, characterized in that, The ear structure has a platform on the side opposite to the arched window opening, and the height of the platform is lower than the height of the third window beam.

9. The miniature self-locking bearing cage according to claim 8, characterized in that, The total height of the ear structure and the first or second window beam is equal to the height of the third window beam.

10. The miniature self-locking bearing cage according to claim 7, characterized in that, The first and second window beams facing the columnar window openings, as well as the third window beam facing both sides of the columnar window beams, all have arc-shaped contact surfaces adapted for ball bearings.

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