Bearing structure, bearing assembly and motor assembly

Abstract

The embodiment of the utility model provides a kind of bearing structure, bearing assembly and motor assembly, wherein, bearing structure includes: coaxially arranged outer ring and inner ring, multiple rolling bodies are equipped between outer ring and inner ring, outer ring includes at least one wide body part and at least one narrow body part, the circumferential two sides of narrow body part are connected with wide body part respectively, and the minimum axial dimension of narrow body part is less than the maximum axial dimension of wide body part;Multiple grooves are set in at least one end of narrow body part in axial direction;Wherein, groove extends along the circumference of outer ring, and groove is recessed from the end surface of outer ring towards rolling body along axial direction.In the technical scheme of the utility model, face-to-face close fitting is realized, thereby significantly improving the uniformity and stability of pre-tightening force, reducing relative sliding, wear and heating during operation after assembly, prolonging the service life of waveform washer and bearing, and improving the running stability of entire motor system, reducing noise and vibration.

Description

Technical Field

[0001] This utility model relates to the field of bearing technology, and more specifically, to a bearing structure, a bearing assembly, and a motor assembly. Background Technology

[0002] Currently, to ensure the normal operation of a motor, bearings are usually installed inside. In related technologies, a certain preload is required before the bearing is used to eliminate internal clearance. This is usually achieved by using a wave-shaped elastic washer to press against the end face of the bearing. However, in the actual assembly process, the wave-shaped elastic washer is wavy with peaks and troughs. When applying preload to the bearing, it is usually impossible to ensure uniform force distribution, which causes relative sliding between the bearing and the washer, resulting in abnormal noise during motor operation. Utility Model Content

[0003] The present invention aims to at least solve the technical problem of limited preload force on bearings in the prior art or related technologies.

[0004] In view of this, an embodiment of the first aspect of the present invention provides a bearing structure.

[0005] A second aspect of this utility model provides a bearing assembly.

[0006] A third aspect of this utility model provides a motor assembly.

[0007] To achieve the above objectives, embodiments of this utility model provide a bearing structure, comprising: an outer ring and an inner ring coaxially arranged, with a plurality of rolling elements disposed between the outer ring and the inner ring; the outer ring includes at least one wide body portion and at least one narrow body portion, the circumferential sides of the narrow body portion being connected to the wide body portion respectively, and the minimum axial dimension of the narrow body portion being smaller than the maximum axial dimension of the wide body portion; a plurality of grooves disposed at at least one end of the narrow body portion in the axial direction; wherein the grooves extend circumferentially along the outer ring, and the grooves are recessed axially from the end face of the outer ring toward the rolling elements.

[0008] According to the bearing structure proposed in this utility model, an outer ring and an inner ring are arranged coaxially, with multiple rolling elements between the outer and inner rings. Multiple grooves are provided at least one end of the outer ring along its axial direction. These grooves extend circumferentially along the outer ring and are recessed axially from the end face of the outer ring towards the rolling elements. This structural design allows for a tight surface-to-surface fit when the bearing is engaged with a wave washer or wave spring, significantly improving the uniformity and stability of the preload, reducing relative sliding, wear, and heat generation during operation after assembly, extending the service life of the wave washer and bearing, and improving the overall smoothness of the motor system while reducing noise and vibration.

[0009] Understandably, this solution achieves a large-area, stable fit with the corrugated washer's arc surface by machining multiple circumferentially extending and axially recessed grooves on the end face of the outer ring. This eliminates localized stress concentration caused by traditional point / line contact. The grooves and the corrugated washer interlock to prevent circumferential slippage. The surface contact increases the coefficient of friction, reduces relative motion, decreases wear and heat generation, and maintains long-term stable performance. This, in turn, reduces noise and vibration, and improves the smoothness of motor operation.

[0010] It is important to emphasize that this design utilizes the wide body section to bear the main load, while the narrow body section features specially designed grooves to avoid weakening the overall structure during groove machining. The grooves in the narrow body section fit tightly against the wave-shaped washer, improving the uniform distribution and stability of the preload. The minimum axial dimension of the narrow body section is smaller than the maximum axial dimension of the wide body section, reducing bearing weight and meeting the compact design requirements of small motors.

[0011] In some technical solutions, optionally, it further includes: a first retaining ring and a second retaining ring, which are axially spaced between the outer ring and the inner ring, and a rolling element is disposed between the first retaining ring and the second retaining ring; wherein, on the cross-section of the outer ring, at least a portion of the projection of the first retaining ring coincides with the projection of at least a portion of the rolling element, and at least a portion of the projection of the second retaining ring coincides with the projection of at least a portion of the rolling element.

[0012] In this technical solution, the axial load is uniformly transmitted through surface contact. The retaining ring prevents the preload from being affected by changes in the position of the rolling element. The rolling element is fixed between the two retaining rings, reducing vibration and noise. The projection of the retaining ring coincides with the projection of the rolling element, ensuring that the retaining ring effectively bears and disperses the axial force of the rolling element, reducing local wear. The wave washer, the groove on the end face of the outer ring, and the retaining ring work together to reduce the risk of structural component wear and failure.

[0013] In some technical solutions, optionally, the outer ring includes a first end face and a second end face, the first retaining ring is disposed on the side of the rolling element facing the first end face, and the second retaining ring is disposed on the side of the rolling element facing the second end face; wherein, the groove is disposed on the first end face, and the lowest point of the groove is not lower than the surface of the first retaining ring facing the first end face; and / or the groove is disposed on the second end face, and the lowest point of the groove is not lower than the surface of the second retaining ring facing the second end face.

[0014] In this technical solution, the surface contact structure between the groove and the wave washer achieves uniform distribution and stable transmission of preload, avoiding local stress concentration, sliding wear and preload attenuation caused by point / line contact between the traditional wave spring and the bearing end face.

[0015] The first and second retaining rings respectively restrict the axial position of the two ends of the rolling element, preventing the rolling element from shifting axially due to vibration or load changes, and ensuring that the rolling element is always in the optimal working position.

[0016] In some technical solutions, the groove may be provided on the first end face, and the inner ring may protrude from the first end face; or the inner ring may be lower than the first end face.

[0017] In this technical solution, by setting the groove on the first end face and the inner ring protruding from the first end face, the corrugated washer and the outer ring groove surface fit together, which improves the uniformity and stability of the preload. The protruding end face of the inner ring provides precise axial positioning and support for the rolling elements and the first retaining ring, avoids interference between the corrugated washer and the inner ring end face, reduces wear and heat generation, and enhances the axial rigidity and overall stability of the bearing.

[0018] Alternatively, the inner ring can be positioned lower than the first end face, and the inner ring end face can be lower than the outer ring first end face. This ensures that the wave washer can be fully embedded in the groove without being obstructed by the inner ring end face, guaranteeing the integrity and effectiveness of the pre-tightening structure. The low-position design of the inner ring end face provides sufficient space for the wave washer and the groove, facilitating assembly and adjustment, and improving assembly flexibility and reliability.

[0019] In some technical solutions, the wide body portion may optionally include a first body portion and a protrusion connected along the axial direction, and the narrow body portion includes a second body portion, with the first body portion and the second body portion connected; wherein the protrusion is located at at least one end of the first body portion along the axial direction.

[0020] In this design, the groove is located in the narrow section, specifically in the second body section. The corrugated washer is embedded in the groove, ensuring uniform transmission of preload. The wide section serves as the main load-bearing component, guaranteeing the strength and rigidity of the entire outer ring and preventing the groove machining from weakening the structure.

[0021] In some technical solutions, optionally, the height of the radially inner side of the groove is the same as the height of the radially outer side of the groove.

[0022] In this technical solution, the radial inner and outer sides of the bottom of the groove are at the same height, forming a flat and uniform concave surface, which avoids tilting or unevenness at the bottom of the groove. When the arc-shaped surface of the corrugated washer fits with the bottom of the groove, the flatness of the bottom of the groove ensures that the corrugated washer is subjected to uniform force, avoiding localized force concentration or poor fit due to unevenness at the bottom of the groove.

[0023] In some technical solutions, the bottom of the groove may optionally be an arc surface.

[0024] In this technical solution, the arc-shaped groove bottom provides a continuous and uniform force-bearing surface, avoiding the uneven preload caused by traditional point-line contact.

[0025] In some technical solutions, optionally, multiple grooves are spaced apart along the circumference of the outer ring, and the multiple grooves are evenly distributed.

[0026] In this technical solution, grooves are evenly distributed around the outer ring in a periodic arrangement. The uniformly arranged grooves ensure that the preload load is evenly distributed around the bearing, reducing vibration and noise. The symmetrical and uniform arrangement of grooves forms a stable positioning structure, preventing the wave washer from shifting or rotating during operation.

[0027] A second aspect of this application provides a bearing assembly, including: a wave washer; and the aforementioned bearing structure, wherein the groove of the bearing structure fits into the wave washer.

[0028] The bearing assembly provided in this application includes a corrugated washer, typically a wave-shaped elastic washer, used to apply preload to the bearing. The arc-shaped surface design of the corrugated washer matches the groove on the outer ring of the bearing to achieve elastic compression and buffering.

[0029] Since the bearing assembly includes any of the above-mentioned bearing structures, it has the beneficial effects of any of the above-mentioned bearing structures, which will not be elaborated here.

[0030] A third aspect of this application provides a motor assembly, including: the aforementioned bearing assembly; and a rotor shaft that is connected to the inner ring of the bearing assembly.

[0031] The motor assembly provided in this application includes the aforementioned bearing assembly, which includes a wave washer and the aforementioned bearing structure that is in contact with it.

[0032] Since the motor structure includes any of the aforementioned bearing assemblies, it has the beneficial effects of any of the aforementioned bearing assemblies, which will not be elaborated further here.

[0033] Additional aspects and advantages of this invention will become apparent in the description that follows, or may be learned by practice of this invention. Attached Figure Description

[0034] Figure 1 A schematic diagram of a bearing structure according to an embodiment of the present invention is shown; Figure 2 A schematic diagram of a bearing structure according to an embodiment of the present invention is shown; Figure 3 A schematic diagram of a bearing structure according to an embodiment of the present invention is shown; Figure 4 A schematic diagram of a bearing structure according to an embodiment of the present invention is shown; Figure 5 A schematic diagram of a bearing structure according to an embodiment of the present invention is shown; Figure 6 A schematic diagram of the structure of a bearing assembly according to an embodiment of the present invention is shown; Figure 7A schematic diagram of the structure of a bearing assembly according to an embodiment of the present invention is shown; Figure 8 A schematic diagram of the structure of a motor assembly according to an embodiment of the present invention is shown.

[0035] Wherein, 100: bearing structure; 102: outer ring; 1022: first end face; 1024: second end face; 1026: wide body portion; 10261: first body portion; 10262: protrusion; 1028: narrow body portion; 10281: second body portion; 103: inner ring; 1032: rolling element; 1034: groove; 1036: first retaining ring; 1038: second retaining ring; 200: Bearing assembly; 202: Wave washer; 300: Motor assembly; 302: Rotor shaft. Detailed Implementation

[0036] To better understand the above-mentioned objectives, features, and advantages of the embodiments of this utility model, the embodiments of this utility model will be described in optional detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments can be combined with each other.

[0037] Many specific details are set forth in the following description in order to provide a full understanding of this application. However, embodiments of the present invention may also be implemented in other ways different from those described herein. Therefore, the scope of protection of this application is not limited to the specific embodiments disclosed below.

[0038] Currently, for deep groove ball bearings in motors, a preload is typically applied to achieve the following purposes: eliminating internal bearing clearance, increasing bearing rigidity, reducing vibration and noise levels, and improving fretting wear. For small motors (such as those with a power of less than 5kW), a corrugated washer (or simply corrugated washer) is usually required to press against the bearing end face to achieve this preload.

[0039] The corrugated pad is wavy, and the contact area between it and the bearing end face is small, only the trough or crest of the "wave". This may result in uneven preload applied to the bearing end face. Furthermore, when the motor is running and the bearing is rotating, the friction between the corrugated pad and the bearing end face is insufficient, leading to relative sliding, wear, and heat generation between the corrugated pad and the bearing in the circumferential direction. This severely reduces the life of the corrugated pad, affects the bearing preload, and causes malfunctions such as abnormal motor noise.

[0040] The following reference Figures 1 to 8 Some embodiments according to the present invention are described.

[0041] like Figure 1 and Figure 2As shown, this embodiment provides a bearing structure 100, which adopts an outer ring 102 and an inner ring 103 arranged coaxially, as... Figure 5 As shown, a plurality of rolling elements 1032 are provided between the outer ring 102 and the inner ring 103, and a plurality of grooves 1034 are provided at least one end of the outer ring 102 in the axial direction. These grooves 1034 extend circumferentially along the outer ring 102 and are recessed axially from the end face of the outer ring 102 toward the rolling elements 1032. Through this structural design, a tight surface-to-surface fit can be achieved when the bearing is engaged with the wave washer 202 or the wave spring, thereby significantly improving the uniformity and stability of the preload, reducing relative sliding, wear and heat generation during operation after assembly, extending the service life of the wave washer 202 and the bearing, and improving the smooth operation of the entire motor system, reducing noise and vibration.

[0042] It is understood that the groove 1034 matches the arc surface of the corrugated washer 202, forming a large-area contact and avoiding local stress concentration caused by point / line contact. Optionally, the shape of the groove 1034 interlocks with the arc surface of the corrugated washer 202 to prevent the corrugated washer 202 from sliding circumferentially on the end face of the outer ring 102. The surface contact increases the coefficient of friction, reducing the relative movement between the end faces of the corrugated washer 202 and the outer ring 102 during operation, thereby reducing wear on the end faces of the corrugated washer 202 and the outer ring 102 and maintaining a long-term stable preload. In addition, this solution can also reduce vibration and noise levels, reduce fretting wear, and improve running smoothness.

[0043] Specifically, the bearing structure 100 includes an outer ring 102, an inner ring 103, rolling elements 1032, and a groove 1034. The outer ring 102 is located outside the bearing, and the inner ring 103 is located inside the outer ring 102. The central axes of the two coincide, i.e., they are coaxially arranged. The outer ring 102 and the inner ring 103 are supported and rolled together by multiple rolling elements 1032 to form a structure that can rotate relative to each other.

[0044] To ensure the basic functions of the bearing, namely reducing friction during rotation, supporting the shaft system, and ensuring rotational balance through coaxial arrangement, thereby reducing eccentricity and vibration during operation. At the same time, the outer ring 102 and inner ring 103 also provide a stable geometric reference for the fit between the groove 1034 and the wave washer 202, ensuring that the preload is applied to the correct axial position.

[0045] Multiple rolling elements 1032 are located in the annular space between the outer ring 102 and the inner ring 103, and are evenly distributed circumferentially. The rolling elements 1032 are in contact with the raceways of the outer ring 102 and the inner ring 103, and transmit load by rolling, reducing friction and ensuring low-friction rotation between the outer ring 102 and the inner ring 103. The evenly distributed rolling elements 1032 transmit axial and radial loads, ensuring that the bearing can still operate smoothly under preload.

[0046] In this design, the position of the rolling element 1032 determines the maximum depth of the groove 1034 recessed along the axial direction, ensuring that the groove 1034 does not interfere with the normal operation of the rolling element 1032.

[0047] A groove 1034 is located at at least one axial end of the outer ring 102, i.e., at the end face of the outer ring 102. The groove 1034 is directly machined onto the end face of the outer ring 102, forming an integral structure with the outer ring 102. The groove 1034 provides a matching embedding space for the curved surface of the wave washer 202 or wave spring, achieving surface-to-surface contact. Multiple grooves 1034 are distributed circumferentially, corresponding to the crests / troughs of the wave washer 202, ensuring uniform preload in the circumferential direction. The groove 1034 increases the contact area, reduces the pressure per unit area, and minimizes localized wear. Simultaneously, the groove 1034 also forms a positioning structure, preventing the wave washer 202 from sliding in the circumferential direction, thus improving friction and stability.

[0048] Optionally, the extension direction of each groove 1034 is consistent with the circumferential direction of the outer ring 102, and they are distributed around the circumference of the outer ring 102. The shape of the groove 1034 matches the arc surface of the wave washer 202 to form a continuous contact surface, ensuring that the crests or troughs of the wave washer 202 can be completely embedded in the groove 1034 in the circumferential direction, without poor contact or local gaps.

[0049] It is understood that the groove 1034 extends circumferentially along the outer ring 102, providing a continuous support surface to prevent the corrugated washer 202 from deforming or tilting under stress. At the same time, the circumferentially extending groove 1034 helps to disperse axial loads, so that the preload is evenly distributed across the end face of the entire outer ring 102.

[0050] The groove 1034 extends axially from the end face of the outer ring 102 into the outer ring 102 (in the direction of the rolling element 1032). The depth and shape of the groove 1034 match the arc height and curvature of the wave washer 202 to ensure tight embedding. By partially embedding the wave washer 202 into the end face of the outer ring 102, a stable axial positioning is formed, making it difficult to detach or misalign. The axial recess increases the contact area, enhances friction, and prevents slippage during operation. Through the recessed structure, the load of the wave washer 202 can be directly transferred to the outer ring 102, reducing deformation and energy loss of the intermediate contact surface, and ensuring that sufficient preload is maintained without interfering with the normal operation of the rolling element 1032.

[0051] In summary, this solution achieves a large-area, stable fit with the arc surface of the wave washer 202 by machining multiple circumferentially extending and axially recessed grooves 1034 on the end face of the outer ring 102. This eliminates localized stress concentration caused by traditional point / line contact. The grooves 1034 and the wave washer 202 interlock to prevent circumferential slippage. The surface contact increases the coefficient of friction, reduces relative motion, reduces wear and heat generation, and maintains long-term stable performance. This, in turn, reduces noise and vibration, and improves the smoothness of motor operation.

[0052] It should be added that, in some embodiments, optionally, such as Figure 2 As shown, the outer ring 102 is divided into different structural regions along the axial direction, including at least one wider portion (i.e., the wide body portion 1026) and at least one narrower portion (i.e., the narrow body portion 1028). The narrow body portion 1028 is connected to the wide body portion 1026 on both circumferential sides, meaning that the narrow body portion 1028 is located between or on one side of the wide body portion 1026, and the two are connected to form an integral outer ring 102 structure. The wide body portion 1026 and the narrow body portion 1028 have different axial dimensions, with the axial dimension of the narrow body portion 1028 being significantly smaller than that of the wide body portion 1026. A groove 1034 is machined onto the narrow body portion 1028 of the outer ring 102, extending circumferentially and being axially recessed.

[0053] Due to its larger axial dimension, the wide body portion 1026 provides greater structural rigidity and load-bearing area. As the main load-bearing part of the outer ring 102, it ensures the overall strength and rigidity of the bearing. The wide body portion 1026 provides a stable support surface for the retaining ring, raceway, and other key components, reducing the deformation of the outer ring 102 caused by load and vibration, and ensuring the normal operation of the rolling elements 1032 and the inner ring 103.

[0054] The narrow body portion 1028 has a smaller axial dimension, providing a dedicated area for machining the groove 1034. By limiting the size of the narrow body portion 1028, the depth and shape of the groove 1034 can be precisely controlled, preventing the groove 1034 from being too deep and affecting the overall strength of the outer ring 102. The groove 1034 is located in the narrow body portion 1028, preventing the main load-bearing area of ​​the wide body portion 1026 from being weakened, and ensuring the structural integrity of the outer ring 102. The narrow body portion 1028 serves as the mating surface between the wave washer 202 and the groove 1034, ensuring the uniform transmission and stable fit of the preload.

[0055] The narrow body portion 1028 is connected to the wide body portion 1026 on both sides of its circumference, ensuring a rigid connection between the narrow body portion 1028 and the wide body portion 1026, maintaining the integrity of the overall structure of the outer ring 102, and ensuring that the outer ring 102 still has sufficient strength and rigidity to resist loads while forming a groove 1034 locally.

[0056] It is understandable that the transition design at the connection point helps to distribute stress evenly and avoid stress concentration that could lead to fatigue or fracture.

[0057] The groove 1034 is confined to the narrow body portion 1028, making the shape and size of the groove 1034 controllable, which is conducive to achieving precise surface fit with the wave washer 202. The groove 1034 is not provided in the wide body portion 1026 to avoid weakening the key load-bearing area and to ensure the strength and rigidity of the outer ring 102.

[0058] The narrow body portion 1028, where the groove 1034 is located, carries the preload force transmission of the wave washer 202, ensuring that the preload force is uniform and stable.

[0059] In summary, the wide body 1026 bears the main load, while the narrow body 1028 has a specially designed groove 1034 to prevent the machining of the groove 1034 from weakening the overall structure. The groove 1034 fits tightly with the wave washer 202 in the narrow body 1028, improving the uniform distribution and stability of the preload. The axial dimension of the narrow body 1028 is smaller than that of the wide body 1026, reducing the bearing weight and meeting the compact design requirements of small motors.

[0060] In some embodiments, optionally, based on the original coaxially arranged outer ring 102 and inner ring 103, multiple grooves 1034, and multiple rolling elements 1032, such as Figure 3 and Figure 4 As shown, a first retaining ring 1036 and a second retaining ring 1038 are added and are axially spaced between the outer ring 102 and the inner ring 103. The rolling element 1032 is located between the first retaining ring 1036 and the second retaining ring 1038. Furthermore, on the cross-section of the outer ring 102, at least a portion of the projection of the first retaining ring 1036 coincides with at least a portion of the projection of the rolling element 1032, and at least a portion of the projection of the second retaining ring 1038 coincides with at least a portion of the projection of the rolling element 1032.

[0061] With this structure, while ensuring that the wave washer 202 fits against the groove 1034, the retaining ring can axially limit and protect the rolling element 1032, control the axial position and range of motion of the rolling element 1032, prevent the rolling element 1032 from dislodging or generating abnormal friction, and further improve the operating stability and life of the bearing.

[0062] The first retaining ring 1036 and the second retaining ring 1038 form a double limiting mechanism, keeping the rolling element 1032 in the correct position between them and reducing clearance variations. The projected relationship between the retaining rings and the rolling element 1032 ensures stable contact support under load, reducing abnormal friction between the rolling element 1032 and the cage or other components.

[0063] Multiple rolling elements 1032 are located in the annular space between the outer ring 102 and the inner ring 103, and are evenly distributed in the circumferential direction. The rolling elements 1032 are in contact with the raceways of the outer ring 102 and the inner ring 103, transmitting load and reducing friction. The rolling elements 1032 are located between the first retaining ring 1036 and the second retaining ring 1038, and are axially limited by the two retaining rings to prevent them from moving.

[0064] It should be added that the first retaining ring 1036 is located axially on one side of the rolling element 1032, between the outer ring 102 and the inner ring 103. The structure of the first retaining ring 1036 matches that of the outer ring 102 and the inner ring 103, forming an annular limiting element to restrict the axial displacement of the rolling element 1032 in one direction. On the cross-section of the outer ring 102, at least a portion of the projection of the first retaining ring 1036 coincides with at least a portion of the projection of the rolling element 1032. The retaining ring is in the same area as the rolling element 1032 in the radial direction, ensuring that the retaining ring can effectively block the axial movement of the rolling element 1032, prevent the rolling element 1032 from dislodging or shifting, and ensure that the rolling element 1032 is in the correct working position.

[0065] Similarly, the second retaining ring 1038 is located axially on the other side of the rolling element 1032, opposite to the first retaining ring 1036. On the cross-section of the outer ring 102, at least part of the projection of the second retaining ring 1038 coincides with at least part of the projection of the rolling element 1032, ensuring that the retaining ring is effectively aligned with the rolling element 1032 in the radial direction. The second retaining ring 1038 and the first retaining ring 1036 cooperate to form a bidirectional limiting on both sides, so that the rolling element 1032 is always kept in the working range between the two retaining rings.

[0066] The first retaining ring 1036 and the second retaining ring 1038 are located on both sides of the rolling element 1032, separated by a certain distance along the axial direction. The two retaining rings, together with the outer ring 102 and the inner ring 103, form an axial constraint space for the rolling element 1032, forming a closed working area for the rolling element 1032. This prevents the rolling element 1032 from axially drifting due to vibration or impact, ensuring that the rolling element 1032 always operates in the optimal position, and reducing rolling resistance and abnormal wear.

[0067] In summary, this solution transmits axial load uniformly through surface contact. The retaining ring prevents the preload from being affected by changes in the position of the rolling element 1032. The rolling element 1032 is fixed between the two retaining rings, reducing vibration and noise. The projection of the retaining ring coincides with the projection of the rolling element 1032, ensuring that the retaining ring effectively bears and disperses the axial force of the rolling element 1032, reducing local wear. The wave washer 202, the end face groove 1034 of the outer ring 102, and the retaining ring work together to reduce the risk of structural component wear and failure.

[0068] In some embodiments, the rolling elements 1032 at both ends of the bearing are optionally axially limited by the first retaining ring 1036 and the second retaining ring 1038, respectively, to ensure the stable positioning of the rolling elements 1032 between the outer ring 102 and the inner ring 103 and to prevent axial displacement or dislocation. The groove 1034 is provided on the end face of the outer ring 102 (first end face 1022 and / or second end face 1024), and the lowest point of the groove 1034 (i.e. the deepest recess) is not lower than the surface of the corresponding retaining ring facing that end face, to ensure that the groove 1034 does not affect the support function of the retaining ring, and also to ensure that the wave washer 202 can form a good "face-to-face" fit with the groove 1034.

[0069] The surface contact structure between the groove 1034 and the wave washer 202 achieves uniform distribution and stable transmission of preload, avoiding local stress concentration, sliding wear and preload attenuation caused by point / line contact between the traditional wave spring and the bearing end face.

[0070] The first retaining ring 1036 and the second retaining ring 1038 respectively restrict the axial position of the two ends of the rolling element 1032, preventing the rolling element 1032 from shifting axially due to vibration or load changes, and ensuring that the rolling element 1032 is always in the optimal working position.

[0071] The height relationship between the lowest point of the groove 1034 and the surface of the retaining ring ensures the structural integrity and functional effectiveness of the retaining ring, while not hindering the tight fit between the wave washer 202 and the groove 1034, thus improving the rigidity and stability of the overall structure.

[0072] Overall, this solution effectively solves problems such as uneven preload distribution in deep groove ball bearings for small motors, sliding wear between the wave washer 202 and the bearing end face, preload attenuation, and abnormal noise and vibration in the motor, significantly improving the performance stability and service life of the bearing.

[0073] Specifically, the outer ring 102 is annular and has two opposing end faces, such as... Figure 2 As shown, the first end face 1022 and the second end face 1024 are respectively distributed along the axial direction. The first end face 1022 and the second end face 1024 serve as the two end interfaces of the outer ring 102 of the bearing, respectively bearing the mating surface with the wave washer 202 and the mounting reference of the retaining ring.

[0074] The first retaining ring 1036 is axially disposed on the side of the rolling element 1032 near the first end face 1022, located between the outer ring 102 and the inner ring 103, surrounding the rolling element 1032. The first retaining ring 1036 cooperates with the outer ring 102 and the inner ring 103 to form an axial limiting structure for the rolling element 1032. Under the action of the first retaining ring 1036, the movement of the rolling element 1032 axially toward the first end face 1022 can be restricted, preventing the rolling element 1032 from detaching or excessively moving, providing support and positioning for the rolling element 1032, ensuring that the rolling element 1032 maintains a stable position during operation, reducing abnormal contact between the rolling element 1032 and the cage or other components, avoiding localized wear, and ensuring that the structural integrity of the retaining ring is not weakened by the groove 1034 through its height relationship with the lowest point of the groove 1034.

[0075] Similarly, the second retaining ring 1038 restricts the movement of the rolling element 1032 axially toward the second end face 1024, preventing the rolling element 1032 from dislodging. It cooperates with the first retaining ring 1036 to form a bidirectional axial limit, ensuring that the rolling element 1032 operates stably between the two retaining rings, protecting the rolling element 1032 from excessive axial load, reducing abnormal wear and vibration. The lowest point of the groove 1034 is not lower than the surface of the second retaining ring 1038 facing the second end face 1024, ensuring the integrity and support function of the retaining ring.

[0076] Grooves 1034 are machined on the first end face 1022 and / or the second end face 1024 of the outer ring 102, extending circumferentially and recessed axially. Grooves 1034 are integrally formed with the end face of the outer ring 102 and form a surface fit with the arc surface of the wave washer 202. By increasing the contact area between the wave washer 202 and the end face of the bearing outer ring 102, a stable "surface-to-surface" fit is achieved. The circumferential extension of grooves 1034 allows the crests / troughs of the wave washer 202 to be fully embedded, ensuring a uniform distribution of preload. The axial recess ensures the embedding depth of the wave washer 202, increasing friction and reducing slippage.

[0077] Of course, it can also be set on the first end face 1022 and the second end face 1024 at the same time to adapt to different motor design requirements and flexibly adjust the preload structure.

[0078] The recess depth of the groove 1034 on the first end face 1022 is controlled such that the lowest point is not lower than the surface height of the first retaining ring 1036 facing the first end face 1022. This ensures that the groove 1034 does not weaken the axial support surface of the retaining ring, guarantees that the first retaining ring 1036 fully supports the rolling element 1032, and prevents the structural strength of the retaining ring from decreasing due to excessively deep groove 1034. This also ensures that the groove 1034 and the retaining ring form a reasonable axial height relationship, guaranteeing that when the wave washer 202 fits the groove 1034, the retaining ring can still effectively limit the rolling element 1032, preventing stress concentration in the retaining ring due to excessively deep groove 1034 and avoiding structural damage.

[0079] Similarly, the recess depth of the groove 1034 on the second end face 1024 is controlled so that the lowest point is not lower than the surface of the second retaining ring 1038 facing the second end face 1024. This also ensures the integrity of the axial support surface of the second retaining ring 1038, ensuring that the effective axial limiting function of the second retaining ring 1038 is not affected by the depth of the groove 1034, maintaining the strength and performance of the retaining ring, preventing the retaining ring from failing due to the processing of the groove 1034, and ensuring the stability and safety of the overall bearing structure 100.

[0080] In some embodiments, the groove 1034 is located on the first end face 1022 of the outer ring 102, extends circumferentially and is axially recessed, and the inner ring 103 protrudes outward in the axial direction relative to the first end face 1022 of the outer ring 102, that is, the end face of the inner ring 103 is located at or beyond the first end face 1022 of the outer ring 102.

[0081] The groove 1034 is located on the first end face 1022 of the outer ring 102, and the recessed direction is axially recessed from the first end face 1022 towards the inner ring 103, forming a groove 1034 structure that matches the arc-shaped surface of the wave washer 202. The groove 1034 is integrally formed with the end face of the outer ring 102, serving as the mating surface between the wave washer 202 and the outer ring 102. This increases the contact area between the end face of the wave washer 202 and the outer ring 102, achieving a "surface-to-surface" fit, improving the uniformity and stability of the preload. The axial recess of the groove 1034 allows the wave washer 202 to be partially embedded, preventing the wave washer 202 from sliding or wearing during operation.

[0082] The end face of the inner ring 103 is located at or beyond the first end face 1022 of the outer ring 102, and protrudes axially from the end face. The inner ring 103 protrudes outward relative to the first end face 1022 of the outer ring 102, forming an end face protrusion structure of the inner ring 103. This protrusion portion forms a spatial fit relationship with components such as the rolling element 1032, the first retaining ring 1036, and the wave washer 202. The protruding end face formed by the inner ring 103 protruding from the first end face 1022 can serve as a positioning reference for the rolling element 1032 and the first retaining ring 1036, ensuring the accurate position of the rolling element 1032 and the retaining ring.

[0083] In addition, the protruding end face of the inner ring 103 and the first end face 1022 of the outer ring 102 form a certain axial clearance and fitting space, which improves the overall axial rigidity and stability of the bearing.

[0084] In summary, by setting the groove 1034 on the first end face 1022 and having the inner ring 103 protrude from the first end face 1022, the wave washer 202 fits against the surface of the groove 1034 of the outer ring 102, improving the uniformity and stability of the preload. The protruding end face of the inner ring 103 provides precise axial positioning and support for the rolling element 1032 and the first retaining ring 1036, avoiding interference between the end faces of the wave washer 202 and the inner ring 103, reducing wear and heat generation, and enhancing the axial rigidity and overall stability of the bearing.

[0085] Alternatively, the inner ring 103 is lower than the first end face 1022, that is, the end face of the inner ring 103 is located further in the axial direction relative to the first end face 1022 of the outer ring 102, that is, the end face of the inner ring 103 is located "below" or "inside" the first end face 1022 of the outer ring 102.

[0086] The end face of the inner ring 103 is located inside the axial position of the first end face 1022 of the outer ring 102. That is, the end face of the inner ring 103 is not flush with the first end face 1022 of the outer ring 102, but is relatively concave. The first end face 1022 of the outer ring 102 is provided with a groove 1034. The groove 1034 is concave from the first end face 1022 toward the inner ring 103 along the axial direction. The end face of the inner ring 103 is lower than the first end face 1022 and the concave direction of the groove 1034 is consistent.

[0087] The axial position of the end face of the inner ring 103 is lower than the first end face 1022 of the outer ring 102, forming a structure in which the end faces of the inner and outer rings are staggered. The wave washer 202 is embedded in the groove 1034 on the first end face 1022 of the outer ring 102 and fits against the arc-shaped bottom surface of the groove 1034. The end face of the inner ring 103 does not interfere with the mating area between the wave washer 202 and the groove 1034.

[0088] The end face of the inner ring 103 is lower than the first end face 1022 of the outer ring 102, ensuring that the wave washer 202 can be fully embedded in the groove 1034 without being obstructed by the end face of the inner ring 103, thus guaranteeing the integrity and effectiveness of the pre-tightening structure. The low-position design of the end face of the inner ring 103 provides sufficient space for the wave washer 202 and the groove 1034, facilitating assembly and adjustment and improving assembly flexibility and reliability.

[0089] In some embodiments, the wide body portion 1026 may optionally consist of two parts, specifically a first body portion 10261 and a protrusion 10262, which are connected in the axial direction. The protrusion 10262 is located at one or both ends of the first body portion 10261 in the axial direction. The first body portion 10261 serves as the main body of the wide body portion 1026 and is connected to the second body portion 10281, which serves as the main body of the narrow body portion 1028, to form an integral outer ring structure.

[0090] The first body portion 10261 is the main part of the wide body portion 1026, and undertakes the main load-bearing and support functions. The first body portion 10261 is connected to the protrusion 10262 along the axial direction to form the wide body portion 1026 as a whole. The protrusion 10262 is provided at least one end of the first body portion 10261 along the axial direction and protrudes outward or inward. Under the action of the protrusion 10262, the local structural size can be increased and the local rigidity can be strengthened. At the same time, the position of the groove 1034 can be restricted by the protrusion 10262 to facilitate assembly and processing.

[0091] The second body portion 10281 serves as the main structure of the narrow body portion 1028 and is directly connected to the first body portion 10261, forming a narrow body region on the outer ring.

[0092] The first body part 10261 and the second body part 10281 can have the same axial dimensions, resulting in a balanced axial structure, reduced stress concentration, simplified manufacturing and assembly processes, improved production efficiency, and ensured the integrity and uniform stress distribution of the groove 1034 and the pre-tightening structure of the wave washer.

[0093] Alternatively, the axial dimension of the first body part 10261 is greater than the axial dimension of the second body part 10281. The larger axial dimension of the first body part 10261 provides sufficient assembly space and positioning surface, improving assembly accuracy and product consistency. The smaller size of the second body part 10281 simplifies the machining of the groove 1034 and reduces manufacturing difficulty.

[0094] The first body portion 10261 and the second body portion 10281 are adjacent to each other along the axial direction and connected to form a continuous outer ring structure. The protrusion 10262 extends from the first body portion 10261 and forms a partial protrusion of the wide body portion 1026. The narrow body portion 1028 is adjacent to the wide body portion 1026 and is provided with a groove 1034.

[0095] The wide body portion 1026 consists of a first body portion 10261 and a protrusion portion 10262. The protrusion portion 10262 enhances the local strength of the wide body portion 1026 by locally thickening or protruding, resisting load concentration and fatigue failure. The narrow body portion 1028 has a small axial dimension, providing space for the groove 1034 and ensuring that the depth and shape of the groove 1034 do not affect the strength of the wide body portion 1026.

[0096] It is understood that the groove 1034 is located in the narrow body portion 1028, specifically in the second body portion 10281. The wave washer is embedded in the groove 1034, and the preload is transmitted evenly. The wide body portion 1026 serves as the main load-bearing component, ensuring the strength and rigidity of the entire outer ring and preventing the groove 1034 from weakening the structure during processing. In some embodiments, optionally, the height of the radially inner side of the groove 1034 is the same as the height of the radially outer side of the groove 1034, that is, the height of the groove 1034 is consistent on both sides in the radial direction (from the axial center outward direction). The height of the bottom of the groove 1034 remains flush or equal on the radially inner and radially outer sides. The groove 1034 is located in the narrow body portion 1028 (or end face) of the outer ring 102, and its bottom maintains the same height plane on the radially inner side (near the axial direction) and the radially outer side (away from the axial direction), without tilting or step changes. The bottom of the groove 1034 is integrally formed with the outer ring 102, and the height of the inner and outer edges of the groove 1034 is consistent, forming a uniform concave surface.

[0097] The inner and outer sides of the bottom of the groove 1034 are at the same height, forming a flat and uniform concave surface. This prevents the bottom of the groove 1034 from tilting or becoming uneven. When the arc-shaped surface of the wave washer 202 fits against the bottom of the groove 1034, the flatness of the bottom of the groove 1034 ensures that the wave washer 202 is subjected to uniform force, preventing localized force concentration or poor fit due to unevenness at the bottom of the groove 1034.

[0098] In addition, the uniformly spaced grooves at the bottom of the 1034 reduce stress concentration points on the structure, thereby reducing the risk of material fatigue and early damage caused by uneven stress.

[0099] Of course, the flat bottom of the groove 1034 simplifies the processing technology, makes it easier to control the size and shape of the groove 1034, and ensures the consistency of mass production.

[0100] In some embodiments, the groove bottom of the groove 1034, i.e. the bottom of the groove 1034, is not a plane, but a continuous arc-shaped surface formed along a certain curvature. The groove 1034 is located in the narrow body portion 1028 or end face of the outer ring 102, and its bottom presents a continuous arc-shaped surface in the radial or axial direction, rather than a plane or a stepped shape. The arc-shaped groove bottom is integrally formed with the outer ring 102 to form a matching surface with the arc-shaped surface of the wave washer 202.

[0101] The wave washer 202 itself is a wave-shaped or arc-shaped spring, and its contact surface is arc-shaped. The bottom of the groove 1034 is arc-shaped, which can achieve a tight fit with the surface of the wave washer 202, increase the contact area, and avoid local contact stress concentration.

[0102] It should be added that the curved groove bottom provides a continuous and uniform force-bearing surface, avoiding the uneven preload caused by traditional point-line contact.

[0103] In some embodiments, the grooves 1034 are not continuously arranged, but are distributed in the circumferential direction of the outer ring 102. There are gaps between the grooves 1034. These grooves 1034 are evenly distributed in the circumferential direction of the outer ring 102 to ensure that the number and position of the grooves 1034 are evenly distributed on the end face of the outer ring 102.

[0104] The groove 1034 is integrally formed with the outer ring 102. The spaced area provides structural continuity and rigid support. The multiple grooves 1034 are distributed at intervals so that the peaks or troughs of the wave washer 202 correspond to the positions of the grooves 1034, ensuring that the preload is evenly distributed in the circumference and avoiding local overload.

[0105] The spacer area, acting as a raised portion, maintains the overall rigidity and strength of the end face of the outer ring 102, preventing strength reduction caused by the continuity of the groove 1034. The uniformly distributed grooves 1034 and spacer area help to make the stress distribution more uniform and reduce the risk of fatigue.

[0106] The grooves 1034 are evenly distributed around the outer ring 102, forming a periodic arrangement. The uniformly arranged grooves 1034 make the preload load evenly distributed around the bearing, reducing vibration and noise. The symmetrical and uniform arrangement of the grooves 1034 forms a stable positioning structure, preventing the wave washer 202 from shifting or rotating during operation.

[0107] like Figure 6 and Figure 7 As shown, an embodiment of the second aspect of this application provides a bearing assembly 200, which includes a wave washer 202, also known as a wave spring, typically a wavy elastic washer, used to apply preload to the bearing. The arc-shaped surface design of the wave washer 202 matches the groove 1034 on the outer ring 102 of the bearing to achieve elastic compression and buffering.

[0108] The arc-shaped groove bottom of the groove 1034 and the arc-shaped spring surface of the wave washer 202 achieve a "face-to-face" tight fit, forming a stable contact surface. The fit ensures that the preload is evenly distributed, avoiding local stress concentration caused by traditional point / line contact, effectively preventing the wave washer 202 from sliding relative to the bearing end face, and reducing wear and heat generation.

[0109] Since the bearing assembly 200 includes any of the above-mentioned bearing structures 100, it has the beneficial effects of any of the above-mentioned bearing structures 100, which will not be elaborated here.

[0110] like Figure 8As shown, an embodiment of the third aspect of this application provides a motor assembly 300, including the aforementioned bearing assembly 200. The bearing assembly 200 includes a wave washer 202 and the aforementioned bearing structure 100 that is fitted therewith. The rotor shaft 302 is connected to the inner ring 103 of the bearing assembly 200, serving as a support shaft for the motor rotor. The inner ring 103 enables stable rotation and radial and axial positioning of the rotor shaft 302.

[0111] The rotor shaft 302 is inserted into or connected to the inner ring 103 of the bearing assembly 200 to ensure that the rotational movement of the rotor shaft 302 is supported by the bearing.

[0112] Optionally, the motor assembly 300 effectively reduces abnormal noise and fretting wear, with a power of less than 5kW.

[0113] Since the motor structure includes any of the aforementioned bearing assemblies 200, it has the beneficial effects of any of the aforementioned bearing assemblies 200, which will not be elaborated further here.

[0114] In one specific embodiment, a bearing is provided, including: an outer ring; an inner ring; and other standard components, including seals, a cage, steel balls, etc. The outer ring has a widened side, and an arc-shaped groove / recess is formed on the end face of that side by machining.

[0115] The bearing has an outer ring that is widened on one side, allowing for a margin in the outer ring. This is then machined to form an arc-shaped groove / slot. This groove / slot can form a tight "face-to-face" fit with the arc-shaped surface of the wave washer (also known as a "wave spring").

[0116] This structure: 1) enables the bearing to obtain a more stable and reliable preload; 2) suppresses the relative slippage between the bearing outer ring and the wave washer, which can improve failures such as bearing outer ring slippage; 3) improves the noise performance of the entire equipment or system.

[0117] In this utility model, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance; the term "multiple" refers to two or more unless otherwise explicitly defined. The terms "install," "connect," "join," and "fix" should be interpreted broadly. For example, "connect" can be a fixed connection, a detachable connection, or an integral connection; "join" can be a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0118] In the description of this utility model, it should be understood that the terms "upper", "lower", "left", "right", "front", "rear", 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 unit 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.

[0119] In the description of this specification, the terms "one embodiment," "some embodiments," "specific embodiment," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which 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.

[0120] The above are merely preferred embodiments of this utility model and are not intended to limit the scope of this utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A bearing structure, characterized in that, include: An outer ring and an inner ring are coaxially arranged, and a plurality of rolling elements are provided between the outer ring and the inner ring. The outer ring includes at least one wide body portion and at least one narrow body portion. The two circumferential sides of the narrow body portion are respectively connected to the wide body portion. The minimum axial dimension of the narrow body portion is smaller than the maximum axial dimension of the wide body portion. Multiple grooves are provided at at least one end of the narrow body portion in the axial direction; The groove extends circumferentially along the outer ring, and the groove is recessed along the axial direction from the end face of the outer ring toward the rolling element.

2. The bearing structure according to claim 1, characterized in that, Also includes: The first retaining ring and the second retaining ring are spaced apart along the axial direction between the outer ring and the inner ring, and the rolling element is disposed between the first retaining ring and the second retaining ring; Wherein, on the cross-section of the outer ring, at least a portion of the projection of the first retaining ring coincides with at least a portion of the projection of the rolling element, and at least a portion of the projection of the second retaining ring coincides with at least a portion of the projection of the rolling element.

3. The bearing structure according to claim 2, characterized in that, The outer ring includes a first end face and a second end face that are opposite each other. The first retaining ring is disposed on the side of the rolling element facing the first end face, and the second retaining ring is disposed on the side of the rolling element facing the second end face. Wherein, the groove is provided on the first end face, and the lowest point of the groove is not lower than the surface of the first retaining ring facing the first end face; and / or the groove is provided on the second end face, and the lowest point of the groove is not lower than the surface of the second retaining ring facing the second end face.

4. The bearing structure according to claim 3, characterized in that, The groove is provided on the first end face, and the inner ring protrudes from the first end face; or the inner ring is lower than the first end face.

5. The bearing structure according to claim 1, characterized in that, The wide body portion specifically includes a first body portion and a protrusion portion connected along the axial direction, and the narrow body portion includes a second body portion, with the first body portion and the second body portion connected together. The protrusion is located at at least one end of the first body portion in the axial direction.

6. The bearing structure according to claim 1, characterized in that, The height of the radially inner side of the groove is the same as the height of the radially outer side of the groove.

7. The bearing structure according to claim 1, characterized in that, The bottom of the groove is an arc surface.

8. The bearing structure according to claim 1, characterized in that, The plurality of grooves are spaced apart along the circumference of the outer ring, and the plurality of grooves are evenly distributed.

9. A bearing assembly, characterized in that, include: Wave-shaped washers; The bearing structure according to any one of claims 1 to 8, wherein the groove of the bearing structure fits against the wave washer.

10. A motor assembly, characterized in that, include: The bearing assembly as described in claim 9; The rotor shaft is connected to the inner ring of the bearing assembly.

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