Self-lubricating tapered roller bearing cage and bearing assembly

Abstract

The application provides a self-lubricating tapered roller bearing cage and a bearing assembly, and belongs to the technical field of bearings. The self-lubricating tapered roller bearing cage comprises a cage body, the cage body is provided with window beams which are distributed at intervals, and pockets which are suitable for accommodating roller bodies are formed between adjacent window beams; a pressure slope surface, a first non-pressure slope surface and a second non-pressure slope surface are formed on the window beam, and the pressure slope surface is suitable for embedding the roller body; wherein a bionic honeycomb groove is formed on the pressure slope surface, and the bionic honeycomb groove is filled with an anti-friction layer; and oil guide grooves are formed on the first non-pressure slope surface and the second non-pressure slope surface. The self-lubricating tapered roller bearing cage provided by the application is made of aluminum alloy, and the bionic honeycomb groove filled with the anti-friction layer is arranged on the pressure slope surface, and the oil guide grooves are arranged on the non-pressure slope surfaces, so that the solid lubrication and the liquid lubrication are coordinated, the friction coefficient and the wear amount are significantly reduced, and the service life and the running stability of the bearing are improved.

Description

Technical Field

[0001] This application belongs to the field of bearing technology, specifically relating to a self-lubricating tapered roller bearing cage and bearing assembly. Background Technology

[0002] As a core component of mechanical equipment, bearings directly determine the overall operating efficiency and lifespan of the machine. In the process of increasing the speed and weight of tapered roller bearings, the cage, as a key element guiding the rolling elements, is of paramount importance in terms of its performance.

[0003] While traditional copper alloy cages are widely used in medium-to-high speed and heavy-load conditions, their high density leads to a large moment of inertia and intense impact with the rollers. Simultaneously, the relatively low hardness of copper alloys makes the cuffs and beveled surfaces prone to wear and debris generation during high-speed operation, which accelerates overall bearing wear. With the increasing demands for bearing limiting speeds and lightweight design in high-end equipment such as new energy vehicles, copper alloy and traditional steel cages are no longer sufficient to meet the development needs of modern bearings. Summary of the Invention

[0004] To address at least one of the technical problems existing in the background art, this application provides a self-lubricating tapered roller bearing cage made of aluminum alloy. By setting biomimetic honeycomb grooves filled with anti-friction layers on the sloped surface and setting oil guide grooves on the non-sloped surface, the synergy of solid lubrication and liquid lubrication is achieved, which significantly reduces the coefficient of friction and wear, and improves the service life and operational stability of the bearing.

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

[0006] The technical solution adopted in this application is as follows: The first aspect of this application provides a self-lubricating tapered roller bearing cage, comprising: The cage body is provided with spaced window beams, and pockets suitable for accommodating the roller body are formed between adjacent window beams. The window beam has a sloped surface, a first non-sloped surface and a second non-sloped surface, and the sloped surface is suitable for fitting the roller body. Among them, a biomimetic honeycomb groove is formed on the slope surface, and the biomimetic honeycomb groove is filled with a wear-reducing layer; Oil guide grooves are formed on the first and second unpressurized slope surfaces.

[0007] According to the self-lubricating tapered roller bearing cage provided in the first aspect of this application, by constructing biomimetic honeycomb grooves on the sloped surface of the window beam and filling them with a friction-reducing layer, and simultaneously setting oil guide grooves on the non-sloped surface, the solid lubrication and fluid lubrication mechanisms are integrated, achieving efficient friction reduction and wear resistance of the bearing under all working conditions. As the part that directly contacts the roller body and bears the main load, the biomimetic honeycomb groove structure on the sloped surface provides microscopic "anchor points" for the friction-reducing layer (such as polytetrafluoroethylene filler). Utilizing the mechanical interlocking effect of the inverted conical structure, the bonding strength between the friction-reducing layer and the aluminum alloy substrate is significantly enhanced, preventing peeling under high-speed centrifugal force and impact load. The friction-reducing layer filled therein can form a transfer film on the contact surface under boundary lubrication or dry start conditions through its own low shear strength, effectively reducing the coefficient of friction and preventing adhesive wear. Meanwhile, the oil guide grooves on the first and second non-pressure slopes act as "microchannels" for lubricating oil. Under the centrifugal force and capillary action generated by the bearing rotation, they continuously guide external lubricating oil from the oil reservoir to the contact area of ​​the friction pair on the pressure slope. This replenishes the lubricating medium and removes frictional heat. Furthermore, it forms a mixed lubrication state of "oil film + solid" with the solid anti-friction layer on the pressure slope, greatly improving the redundancy and reliability of the lubrication system. Based on this synergistic effect, not only is the frictional torque between the roller body and the pocket significantly reduced during bearing startup, avoiding the high wear risk during the running-in period of traditional single solid lubrication, but the anti-friction layer can also provide effective emergency lubrication protection under high speed, heavy load, or extreme conditions, preventing bearing seizure or jamming. In addition, the diversion effect of the oil guide grooves can effectively discharge wear-generated debris, preventing its accumulation in the contact area and causing secondary wear. This significantly improves the bearing's limiting speed, operational stability, and service life, making it particularly suitable for high-end transmission systems such as new energy vehicle reducers that have stringent requirements for lightweight, high speed, and long service life.

[0008] According to one embodiment of this application, the sidewalls of the biomimetic honeycomb cell are arranged in a converging posture along the direction from the bottom of the cell to the opening of the cell, so that the biomimetic honeycomb cell forms an inverted cone-shaped structure.

[0009] According to one embodiment of this application, the cross-section from the bottom to the opening of the biomimetic honeycomb cell is hexagonal; The inner diameter of the biomimetic honeycomb cell ranges from 100μm to 120μm, the depth of the biomimetic honeycomb cell ranges from 60μm to 80μm, the center-to-center distance between two adjacent biomimetic honeycomb cells ranges from 150μm to 200μm, and the inverted cone angle of the biomimetic honeycomb cell ranges from 5° to 15°.

[0010] According to one embodiment of this application, the friction-reducing layer comprises polytetrafluoroethylene filler.

[0011] According to one embodiment of this application, the depth of the oil guide groove ranges from 100μm to 150μm, and the width ranges from 150μm to 200μm.

[0012] According to one embodiment of this application, on the first non-pressurized slope surface, the grooves of the oil guide grooves are all oriented towards the roller body.

[0013] According to one embodiment of this application, the oil guide grooves are distributed in a cross shape on the second unpressurized slope surface.

[0014] According to one embodiment of this application, the spacing between adjacent oil guide grooves is 1 mm to 2 mm.

[0015] A second aspect of this application provides a bearing assembly, including: The roller body; and, As described above, in any embodiment of the first aspect, the self-lubricating tapered roller bearing cage has the roller body disposed within a pocket of the self-lubricating tapered roller bearing cage.

[0016] According to one embodiment of this application, it also includes: An inner ring and an outer ring, wherein the inner ring is coaxially disposed within the outer ring, and an annular raceway is formed between the outer circumferential surface of the inner ring and the inner circumferential surface of the outer ring; The roller body and the self-lubricating tapered roller bearing cage are disposed within the annular raceway. Attached Figure Description

[0017] The accompanying drawings, which are included to provide a further understanding of this application and form part of this application, illustrate exemplary embodiments and are used to explain this application, but do not constitute an undue limitation of this application. In the drawings: Figure 1 A schematic diagram of the structure of a self-lubricating tapered roller bearing cage provided in an embodiment of this application; Figure 2 for Figure 1 The diagram shows an enlarged view of the structure at point A of the self-lubricating tapered roller bearing cage.

[0018] in, 11. Cage body; 12. Window beam; 121. Sloping surface; 1211. Bionic honeycomb groove; 122. First non-sloping surface; 123. Second non-sloping surface; 1231. Oil guide groove; 13. Pocket. Detailed Implementation

[0019] To more clearly illustrate the overall concept of this application, a detailed explanation is provided below with reference to the accompanying drawings.

[0020] Many specific details are set forth in the following description to provide a thorough understanding of this application. However, this application 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. It should be noted that, unless otherwise specified, the embodiments of this application and the features thereof can be combined with each other.

[0021] Furthermore, it should be understood in the description of this application that the terms "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0022] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a communication connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0023] In this application, unless otherwise expressly specified and limited, the "above" or "below" of the second feature can mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediate medium. In the description of this specification, references to terms such as "an embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. 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 can be combined in any suitable manner in one or more embodiments or examples.

[0024] like Figures 1 to 2 As shown, a first aspect of this application provides a self-lubricating tapered roller bearing cage, comprising: The cage body 11 is provided with spaced window beams 12, and pockets 13 suitable for accommodating the roller body are formed between adjacent window beams 12. A sloped surface 121, a first non-sloped surface 122 and a second non-sloped surface 123 are formed on the window beam 12. The sloped surface 121 is suitable for fitting the roller body. Among them, a biomimetic honeycomb groove 1211 is formed on the slope surface 121, and the biomimetic honeycomb groove 1211 is filled with a wear-reducing layer. Oil guide grooves 1231 are formed on the first unpressurized slope 122 and the second unpressurized slope 123.

[0025] The cage body 11 serves as an integral support structure, with multiple spaced window beams 12. Adjacent window beams 12 form pockets 13 for accommodating the roller bodies, enabling positioning and guidance of the roller bodies. The surfaces of the window beams 12 facing the roller bodies are divided into a pressure-sloping surface 121, a first non-pressure-sloping surface 122, and a second non-pressure-sloping surface 123 according to the stress state. The pressure-sloping surface 121 is the working surface that directly contacts the roller body and bears the main load, responsible for fitting and guiding the movement of the roller body. To improve lubrication performance, biomimetic honeycomb grooves 1211 are machined on the pressure-sloping surface 121, filled with a friction-reducing layer (such as polytetrafluoroethylene filler) to reduce the coefficient of friction. Oil guide grooves 1231 are provided on the first non-pressure-sloping surface 122 and the second non-pressure-sloping surface 123, which do not directly bear loads. These oil guide grooves 1231 serve as lubricating oil delivery channels, continuously guiding lubricating oil into the friction area during bearing operation through capillary action and centrifugal effect, achieving replenishment and maintenance of hydrodynamic lubrication. The biomimetic honeycomb grooves 1211 of the sloped surface 121 and the oil guide grooves 1231 of the non-sloped surface work together to construct a composite lubrication system of "solid lubrication + fluid lubrication".

[0026] According to the self-lubricating tapered roller bearing cage provided in the first aspect of this application, by constructing a biomimetic honeycomb groove 1211 on the sloped surface 121 of the window beam 12 and filling it with a friction-reducing layer, and simultaneously setting an oil guide groove 1231 on the non-sloped surface, the solid lubrication and fluid lubrication mechanisms are integrated, achieving efficient friction reduction and wear resistance of the bearing under all working conditions. The sloped surface 121, as the part that directly contacts the roller body and bears the main load, has a biomimetic honeycomb groove 1211 structure on its surface that provides microscopic "anchor points" for the friction-reducing layer (such as polytetrafluoroethylene filler). Utilizing the mechanical interlocking effect of the inverted conical structure, the bonding strength between the friction-reducing layer and the aluminum alloy substrate is significantly enhanced, preventing peeling under high-speed centrifugal force and impact load. The friction-reducing layer filled therein can form a transfer film on the contact surface under boundary lubrication or dry start conditions through its own low shear strength, effectively reducing the coefficient of friction and preventing adhesive wear. Meanwhile, the oil guide grooves 1231 set on the first non-pressure slope 122 and the second non-pressure slope 123 are "microchannels" for lubricating oil. Under the centrifugal force and capillary action generated by the rotation of the bearing, external lubricating oil can be continuously guided from the oil storage area to the friction pair contact area of ​​the pressure slope 121. On the one hand, it replenishes the lubricating medium and carries away the frictional heat. On the other hand, it forms a mixed lubrication state of "oil film + solid" with the solid anti-friction layer on the pressure slope 121, which greatly improves the redundancy and reliability of the lubrication system. Based on the above synergistic effect, not only is the frictional torque between the roller body and the pocket 13 significantly reduced during bearing startup, avoiding the high wear risk during the running-in period of traditional single solid lubrication, but the anti-friction layer can still provide effective emergency lubrication protection under high speed, heavy load or extreme working conditions, preventing bearing seizure or jamming; in addition, the diversion effect of the oil guide groove 1231 can effectively discharge the micro-debris generated by wear, preventing it from accumulating in the contact area and causing secondary wear, thereby significantly improving the bearing's limiting speed, running stability and service life, and is particularly suitable for high-end transmission systems such as new energy vehicle reducers that have strict requirements for lightweight, high speed and long service life.

[0027] In some embodiments of this application, the sidewalls of the biomimetic honeycomb groove 1211 are in a converging posture along the direction from the bottom of the groove to the opening of the groove, so that the biomimetic honeycomb groove 1211 forms an inverted cone-shaped structure.

[0028] When the wear-reducing layer material is filled into the inverted conical groove, the groove wall forms a strong lateral constraint and bottom support for the wear-reducing layer, which greatly increases the contact area and mechanical interlocking force between the filling material and the substrate, effectively overcoming the defects of traditional straight-walled or flared grooves where the filling material is easy to loosen and fall off when subjected to alternating loads.

[0029] This inverted conical structure significantly enhances the bonding strength between the friction-reducing layer and the cage substrate. Even under harsh conditions such as the enormous centrifugal force generated by the high-speed operation of the bearing and the frequent impacts of the roller body, it ensures that the friction-reducing layer is firmly anchored in the groove, preventing premature peeling or failure of the lubricating medium. At the same time, this structure ensures the continuity and stability of the lubricating film on the surface of the friction pair, thereby greatly extending the self-lubricating life of the cage and improving the reliability of bearing operation.

[0030] like Figures 1 to 2 As shown, in some embodiments of this application, the cross-section from the bottom to the opening of the biomimetic honeycomb groove 1211 is hexagonal; The inner diameter of the bionic honeycomb cell 1211 ranges from 100μm to 120μm, the depth of the bionic honeycomb cell 1211 ranges from 60μm to 80μm, the distance between the centers of two adjacent bionic honeycomb cells 1211 ranges from 150μm to 200μm, and the inverted cone angle of the bionic honeycomb cell 1211 ranges from 5° to 15°.

[0031] This specific hexagonal honeycomb structure, combined with the aforementioned micron-level dimensional proportions, creates an optimal surface texture density, preventing a decrease in matrix strength due to excessively dense slots or insufficient lubrication due to excessively sparse slots. Simultaneously, the 5° to 15° inverted taper angle ensures sufficient mechanical interlocking force and shear resistance in the friction-reducing layer filler material, while avoiding stress concentration caused by excessively large angles or processing difficulties and insufficient bonding force due to excessively small angles. Through this series of optimized microscopic parameter combinations, an optimal balance between the surface friction performance and structural performance of the cage is achieved, significantly improving the bearing's fatigue wear resistance under mixed lubrication conditions and ensuring long-term operational stability.

[0032] In one specific embodiment of this application, the cross-section from the bottom to the opening of the biomimetic honeycomb groove 1211 is a regular hexagon with an inscribed circle diameter of 110 μm and a groove depth of 70 μm. The center-to-center distance between two adjacent biomimetic honeycomb grooves 1211 is fixed at 175 μm, and the inverted cone angle formed by the groove walls converging along the direction from the bottom to the opening is precisely controlled at 10°. The 110 μm inscribed circle diameter combined with the 70 μm groove depth provides a suitable microcavity volume while avoiding weakening of the matrix strength due to excessive groove depth. The 175 μm center-to-center distance ensures the formation of a high-density lubrication lattice within a unit area, guaranteeing full coverage of the friction interface. The 10° inverted cone angle is within the optimal range of mechanical locking effect, giving the friction-reducing layer extremely strong resistance to shearing and centrifugal force detachment, while avoiding the risk of processing stress concentration. This specific combination of parameters maximizes the synergy between the tribological properties of the cage surface and the structural integrity, significantly improving the oil film carrying capacity and fatigue wear resistance of the bearing under mixed lubrication conditions.

[0033] In some embodiments of this application, the anti-friction layer includes polytetrafluoroethylene (PTFE) filler. PTFE possesses an extremely low coefficient of friction and excellent self-lubricating properties, while also exhibiting excellent resistance to high and low temperatures (long-term use within a range of -196°C to 260°C), resistance to strong acids, alkalis, and various organic solvents, as well as excellent electrical insulation and physiological inertness. Filling the biomimetic honeycomb groove 1211 with PTFE as an anti-friction layer can significantly reduce the frictional resistance between the cage and the roller body contact surface, effectively preventing adhesive wear on the metal surface under high-speed or heavy-load conditions. Simultaneously, due to the chemical stability and weather resistance of PTFE, this anti-friction layer can maintain stable performance in harsh lubrication environments or corrosive media, ensuring a long-lasting and reliable solid lubrication effect, thereby significantly extending the bearing's service life and improving its operational reliability under extreme conditions.

[0034] In some embodiments of this application, the depth of the oil guide groove 1231 ranges from 100μm to 150μm, and the width ranges from 150μm to 200μm.

[0035] The specific depth-to-width ratio ensures that the oil guide groove 1231 has sufficient volume to store and guide lubricating oil, so that under the action of centrifugal force generated by the bearing operation, it can overcome fluid resistance and continuously and stably guide the lubricating oil from the oil storage area to the key friction contact area, effectively replenishing the oil film.

[0036] This micron-level oil guide groove 1231 avoids weakening the structural strength of the cage window beam 12 due to excessive groove depth, and also prevents the problem of oil flow obstruction due to excessively narrow groove width or insufficient capillary suction due to excessively wide groove width. Thus, while ensuring the overall rigidity of the cage, it maximizes the auxiliary effect of hydrodynamic lubrication, significantly reduces the temperature rise and oil churning loss of the bearing during high-speed operation, and improves the smoothness of operation.

[0037] In one specific embodiment of this application, the depth of the oil guide groove 1231 is set to 120 μm, and the width is controlled at 175 μm. The 120 μm depth ensures that the oil guide microchannel has sufficient volume to store lubricating oil, enabling it to overcome fluid resistance under the centrifugal force generated by the high-speed operation of the bearing. The 175 μm width avoids both obstruction of oil flow or insufficient capillary suction due to excessively narrow groove width, and weakening of the effective support area of ​​the non-load-bearing surface of the cage due to excessively wide groove width. While ensuring the structural rigidity and strength of the cage body 11, the auxiliary efficiency of hydrodynamic lubrication is maximized, ensuring that the lubricating oil stored in the non-load-bearing area can be efficiently and continuously guided to the critical friction contact area, thereby significantly reducing the temperature rise and oil churning loss of the bearing during high-speed operation, and improving the overall operational stability and reliability.

[0038] In some embodiments of this application, the openings of the oil guide grooves 1231 on the first non-pressure slope 122 all face the roller body. When the cage rotates at high speed with the roller body, the lubricating oil, under the combined action of centrifugal force and fluid shear force, flows smoothly along the openings of these oil guide grooves 1231 facing the roller body, forming a directional oil flow pointing towards the contact area of ​​the friction pair. This directional flow design reduces the disorderly retention or backflow of lubricating oil in the grooves, ensuring that the lubricating oil stored on the non-load-bearing surface can be efficiently and accurately "pumped" to the potential contact area between the roller body and the window beam 12, thereby quickly establishing and maintaining a stable hydrodynamic oil film between the roller body and the cage. This not only greatly improves the utilization efficiency of the lubricant, but also effectively avoids local dry friction caused by oil supply lag, significantly reducing the risk of operating temperature rise and wear.

[0039] like Figures 1 to 2 As shown, in some embodiments of this application, the oil guide grooves 1231 are distributed in a cross shape on the second unpressurized slope 123. This constructs a mesh-like flow guiding network. Unlike unidirectional parallel grooves, the cross-shaped structure breaks the single-direction limitation of lubricating oil flow, allowing the lubricating medium to achieve free horizontal and vertical communication and rapid redistribution within the grooves.

[0040] This mesh structure greatly improves the uniformity of lubricant coverage on non-load-bearing surfaces. When the bearing is subjected to complex loads or uneven loads that cause changes in the flow direction of the lubricating oil, the intersecting grooves can quickly respond and guide the oil to the oil-deficient area, acting as a "reservoir" for regulation. At the same time, this structure can also effectively disrupt the laminar boundary of the surface oil film, increase the disturbance and mixing of the oil, and promote heat dissipation. Thus, while ensuring comprehensive lubrication, it further reduces the operating temperature of the cage and improves the overall thermal stability of the bearing system.

[0041] In some embodiments of this application, the spacing between adjacent oil guide grooves 1231 is 1 mm to 2 mm. On the one hand, this ensures that the oil guide grooves 1231 have a reasonable distribution density on the non-sloping surface, forming a sufficiently dense micro "oil reservoir" and flow guiding network to ensure that the lubricating oil can cover the friction pair surface in a timely and uniform manner, avoiding localized oil supply lag or lubrication blind spots due to excessive spacing. On the other hand, this spacing range strictly avoids the risk of excessively weakening the effective load-bearing cross-sectional area of ​​the window beam 12 due to excessively small groove spacing, thereby ensuring that the cage body 11 still has sufficient mechanical strength and rigidity when subjected to high-speed centrifugal force and complex alternating loads, preventing fatigue fracture or plastic deformation. Under the premise of ensuring structural safety, the fluid lubrication efficiency is maximized, significantly improving the operational reliability and service life of the bearing system.

[0042] In one specific embodiment of this application, the spacing between adjacent oil guide grooves 1231 is set to 1.5 mm. On the one hand, the 1.5 mm spacing ensures that the oil guide microchannels have a reasonable distribution density on the non-pressure slope surface of the cage, forming a sufficiently dense micro oil reservoir array. This ensures that the lubricating oil can cover the friction pair surface in a timely and uniform manner during operation, effectively eliminating local dry friction blind spots caused by delayed oil supply or uneven distribution. On the other hand, this spacing strictly avoids the hidden danger of excessively weakening the effective load-bearing cross-sectional area of ​​the window beam 12 due to excessively small groove spacing. This ensures that the cage body 11 retains sufficient solid matrix material to provide reliable mechanical support when subjected to the huge centrifugal force generated by high-speed rotation and complex alternating loads. This not only eliminates the risk of fatigue fracture or plastic deformation of the cage but also maximizes the hydrodynamic lubrication efficiency, thereby significantly improving the overall operational stability and service life of the bearing assembly.

[0043] A second aspect of this application provides a bearing assembly, including: The roller body; and, In any embodiment of the first aspect described above, the self-lubricating tapered roller bearing cage has roller bodies disposed within the pockets 13 of the self-lubricating tapered roller bearing cage.

[0044] According to the bearing assembly provided in the second aspect of this application, the roller body is integrated into the cage pocket 13 of the self-lubricating tapered roller bearing of any of the first aspects described above. The micro-texture on the cage constructs a stable self-lubricating circulation system between the contact interface of the roller body and the pocket 13. Even under extreme working conditions such as high speed, heavy load or lack of lubricating medium, the lubricant can be continuously supplied through the pumping effect of the micro-grooves, which significantly reduces the coefficient of friction and wear rate between the end face of the roller body and the pocket 13. This greatly improves the limiting speed and fatigue life of the bearing assembly, ensuring the operating accuracy and reliability of mechanical equipment under complex working conditions.

[0045] In some embodiments of this application, the bearing assembly further includes: The inner ring and the outer ring are coaxially arranged inside the outer ring, and an annular raceway is formed between the outer circumferential surface of the inner ring and the inner circumferential surface of the outer ring. The roller body and the self-lubricating tapered roller bearing cage are housed within an annular raceway.

[0046] The bearing assembly further integrates coaxial inner and outer rings, defining an annular raceway between them to house the self-lubricating tapered roller bearing cage and roller body, thus constructing a complete self-lubricating rolling bearing system. By systematically integrating the inner and outer rings with the aforementioned biomimetic microtextured self-lubricating cage, a closed-loop precision load-bearing and lubrication system is formed.

[0047] This integrated design not only inherits the rigidity advantage of traditional tapered roller bearings in bearing high combined radial and axial loads, but also achieves long-term self-lubrication of the internal friction pairs of the bearing through the biomimetic oil storage and guiding mechanism inside the cage. In sealed and semi-sealed environments where grease is difficult to enter or is easily lost, this structure can continuously release the lubricating medium using microtexture, effectively preventing direct contact and scuffing between the raceway and the roller body surface, significantly reducing the starting torque and operating temperature rise of the bearing, thereby greatly improving the operational stability and reliability of the bearing assembly throughout its entire life cycle. It is particularly suitable for automated equipment and precision machinery fields with extremely high requirements for maintenance convenience.

[0048] For any parts not mentioned in this application, existing technologies may be used or referenced.

[0049] The various embodiments in this specification are described in a progressive manner. The same or similar parts between the various embodiments can be referred to each other. Each embodiment focuses on describing the differences from other embodiments.

[0050] The above description is merely an embodiment of this application and is not intended to limit this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A self-lubricating tapered roller bearing cage, characterized in that, include: The cage body (11) is provided with spaced window beams (12), and pockets (13) suitable for accommodating the roller body are formed between adjacent window beams (12). The window beam (12) has a pressure slope (121), a first non-pressure slope (122) and a second non-pressure slope (123) formed thereon, and the pressure slope (121) is adapted to fit the roller body; Among them, a biomimetic honeycomb groove (1211) is formed on the slope surface (121), and the biomimetic honeycomb groove (1211) is filled with a wear-reducing layer; Oil guide grooves (1231) are formed on the first unpressurized slope (122) and the second unpressurized slope (123).

2. The self-lubricating tapered roller bearing cage according to claim 1, characterized in that, Along the direction from the bottom of the groove to the opening of the groove, the sidewalls of the bionic honeycomb groove (1211) are in a converging posture so that the bionic honeycomb groove (1211) forms an inverted cone structure.

3. The self-lubricating tapered roller bearing cage according to claim 2, characterized in that, The cross-section from the bottom to the opening of the biomimetic honeycomb trough (1211) is hexagonal; The inner diameter of the bionic honeycomb cell (1211) ranges from 100μm to 120μm, the depth of the bionic honeycomb cell (1211) ranges from 60μm to 80μm, the center-to-center distance between two adjacent bionic honeycomb cells (1211) ranges from 150μm to 200μm, and the inverted cone angle of the bionic honeycomb cell (1211) ranges from 5° to 15°.

4. The self-lubricating tapered roller bearing cage according to claim 1, characterized in that, The friction-reducing layer includes polytetrafluoroethylene filler.

5. The self-lubricating tapered roller bearing cage according to claim 1, characterized in that, The depth of the oil guide groove (1231) ranges from 100μm to 150μm, and the width ranges from 150μm to 200μm.

6. The self-lubricating tapered roller bearing cage according to claim 5, characterized in that, On the first unpressurized slope (122), the grooves of the oil guide grooves (1231) are all oriented towards the roller body.

7. The self-lubricating tapered roller bearing cage according to claim 5, characterized in that, On the second unpressurized slope (123), the oil guide grooves (1231) are distributed in a cross shape.

8. The self-lubricating tapered roller bearing cage according to claim 5, characterized in that, The spacing between adjacent oil guide grooves (1231) is 1 mm to 2 mm.

9. A bearing assembly, characterized in that, include: Roller body; and, The self-lubricating tapered roller bearing cage according to any one of claims 1 to 8, wherein the roller body is disposed within the pocket (13) of the self-lubricating tapered roller bearing cage.

10. The bearing assembly according to claim 9, characterized in that, Also includes: An inner ring and an outer ring, wherein the inner ring is coaxially disposed within the outer ring, and an annular raceway is formed between the outer circumferential surface of the inner ring and the inner circumferential surface of the outer ring; The roller body and the self-lubricating tapered roller bearing cage are disposed within the annular raceway.

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