Tapered roller bearing assembly for disc harrow hub

Abstract

The invention discloses a tapered roller bearing assembly for a disc harrow hub. The tapered roller bearing assembly comprises a main shaft, the cover body is arranged at the front end of the main shaft in a sleeving manner and is provided with a cylindrical base body and a convex disc part which is arranged at the front end of the base body and protrudes outwards in the radial direction; the main shaft is coaxially sleeved with the outer shell, and a step face extending inwards in the radial direction is arranged in an inner hole in the front end of the outer shell; an annular accommodating cavity is formed between the convex disc part of the cover body and the step surface of the outer shell, the accommodating cavity is communicated with a bearing mounting area between the main shaft and the outer shell, and a tapered roller bearing is mounted in the bearing mounting area; the sealing mechanism is arranged in the accommodating cavity; the lubricating channel penetrates into the main shaft in the axial direction and is communicated with the lubricating area of the bearing mounting area through a radial branch hole which penetrates through the main shaft in the radial direction, it is guaranteed that the harrow blade still keeps rotating accurately under the high-impact and high-overturning working conditions of the rugged earth surface, and the service life of the bearing and the service life of the whole machine are remarkably prolonged.

Description

Technical Field

[0001] The invention relates to the technical field of bearings, in particular to a tapered roller bearing assembly for a disc harrow hub. Background Art

[0002] Existing agricultural disc harrows operate in harsh environments, with wheel hub bearings simultaneously enduring radial impact, axial thrust, and high-frequency vibration, as well as corrosion from multiple contaminants such as mud, straw debris, and chemicals. Traditional solutions often utilize double-row deep-groove ball bearings or simple double-row angular contact ball bearings. These bearings exhibit high contact stress between the rolling elements and raceways, resulting in a low load safety factor and prone to premature fatigue spalling under eccentric or impact loads. Furthermore, traditional single-layer lip seals are susceptible to permanent deformation under the impact of gravel, creating channels for impurities to enter. Simple labyrinth seals, with their short sealing paths and large gaps, are unable to effectively intercept high-speed splashing particulate impurities and corrosive media. Impurities can easily penetrate the sealing interface and enter the bearing area, leading to lubrication failure, channel spalling, and premature fatigue, significantly reducing overall machine reliability. Furthermore, existing disc harrow wheel hub bearings generally lack reliable lubrication methods, making timely grease replenishment impossible. On-site maintenance requires disassembly of the wheel hub, resulting in inefficient and labor-intensive lubrication.

[0003] There is an urgent need for a new bearing assembly that integrates a high-load tapered roller structure, direct relubrication and multi-stage gradient sealing to meet the high-efficiency and low-maintenance operation requirements of modern agriculture. Summary of the Invention

[0004] To solve the above technical problems, the present invention relates to a tapered roller bearing assembly for a disc harrow hub. The tapered roller bearing assembly has a simple and reliable structure, effectively solves the above technical problems, and is suitable for widespread use. To achieve the above purpose, the present invention is implemented through the following technical solutions: A tapered roller bearing assembly for a disc harrow hub, comprising spindle; A cover body sleeved on the front end of the main shaft, the cover body having a cylindrical base and a radially outwardly protruding flange portion provided on the front end of the base; An outer shell is coaxially sleeved on the main shaft, and the inner hole at the front end of the outer shell is provided with a step surface extending radially inward; An annular accommodating cavity is formed between the convex disc portion of the cover and the stepped surface of the outer shell. The accommodating cavity is communicated with the bearing installation area between the main shaft and the outer shell. A tapered roller bearing is installed in the bearing installation area. a sealing mechanism disposed in the accommodating cavity; A lubrication channel extends axially through the main shaft, the lubrication channel is connected to the lubrication area of ​​the bearing installation area through a radial branch hole radially penetrating the main shaft, and the lubrication channel is used to introduce grease into the bearing installation area.

[0005] On the basis of the above scheme and as a preferred scheme of the above scheme: there are two groups of tapered roller bearings, and both are single-row tapered roller bearings, and the tapered rollers of the two groups are installed face to face and symmetrically in the bearing installation area with the large ends facing outwards and the small ends facing each other.

[0006] On the basis of the above scheme and as a preferred scheme of the above scheme: the inner circumferential surface of the outer shell is provided with a platform protruding radially inward, and the axial ends of the platform respectively abut the outer ring end faces of the two tapered roller bearings to form an outer ring limit, and the end of the main shaft extending into the outer shell is provided with a flange portion protruding radially outward, and the outer periphery of the main shaft is also provided with a limit ring located between the two outer rings, the end face of the limit ring axially abuts against the inner rings of the two bearings, and the flange portion and the cover body axially clamp the inner rings of the two tapered roller bearings to form an inner ring axial limit.

[0007] On the basis of the above scheme and as a preferred scheme of the above scheme: the limiting ring is provided with an outflow hole corresponding to the radial branch hole, and the grease passes through the radial branch hole and directly reaches the bearing installation area through the outflow hole.

[0008] On the basis of the above scheme and as a preferred scheme of the above scheme: a detachable oil nozzle is provided at the outer end of the lubrication channel, the oil nozzle is threadedly connected to the end of the lubrication channel and has a built-in one-way valve, and the one-way valve is used to prevent the grease from flowing back.

[0009] On the basis of the above scheme and as a preferred scheme of the above scheme: the outer peripheral surface of the outer shell is provided with a flange, and a plurality of bolt holes are evenly distributed along the circumference of the flange for direct bolt connection with the spoke plate of the rake wheel hub, thereby realizing the rigid integrated installation of the bearing assembly and the wheel hub.

[0010] Based on the above solution and as a preferred solution of the above solution: the sealing assembly includes at least three layers of sealing rings distributed in an axial direction at intervals, and a support assembly supporting the sealing rings, the support assembly including a first support body and a second support body; The first support body is an annular structure with a concave cross-section, comprising a connecting plate that fits in contact with the inner hole surface of the outer shell, and inner and outer plates that bend inwardly from both ends of the connecting plate, wherein the inner plate fits against the stepped surface of the outer shell, and a first axial gap is formed between the outer plate and the cylindrical base of the cover body; The second support body is sleeved on the outside of the base body of the cover body, and comprises an outer ring body that cooperates with the base body of the cover body, and a partition plate that extends radially outward from the front end of the outer ring body. The partition plate is inserted between the inner plate and the outer plate of the first support body, and a second axial gap is formed between the partition plate and the connecting plate. The outer plate and the cover body convex disc constitute a first radial channel, the outer plate and the partition constitute a second radial channel, the partition and the inner plate constitute a third radial channel, the first axial gap connects the first radial channel and the second radial channel, the second axial gap connects the second radial channel and the third radial channel, and the whole forms a continuously folded serpentine sealing path, and the sealing ring is used to establish a gradient sealing barrier in the serpentine sealing path.

[0011] On the basis of the above solution and as a preferred solution of the above solution: each layer of the sealing ring is provided with ribs on its surface, and a plurality of ribs are arranged at intervals along the length direction of the sealing ring.

[0012] On the basis of the above solution and as a preferred solution of the above solution: the sealing ring is divided into A first sealing ring is fixed to the end surface of the outer plate of the first support body facing the cover body flange, and its protruding rib extends into the first radial channel and blocks the radial through path; A second sealing ring is fixed to the end surface of the second support body partition close to the outer plate, and its protruding rib extends into the second radial channel to block the radial through path; The third sealing ring is fixed to the axial end surface of the partition close to the inner plate, and the protruding rib of the third sealing ring extends into the third radial channel to block the radial through path.

[0013] On the basis of the above scheme and as a preferred scheme of the above scheme: each rib undergoes directionally bending deformation under the action of axial assembly pre-tightening, and the bending direction points to the pollutant inflow end of the channel in which it is located, forming a hook-shaped sealing structure in the opposite direction of the medium intrusion direction.

[0014] Compared with the prior art, the present invention has the following outstanding and beneficial technical effects: 1. Tapered roller bearings, with their line contact structure between rollers and raceways, disperse the point contact stress of traditional ball bearings into a wider contact zone. This significantly improves the combined radial and axial load-bearing capacity within the same overall dimensions. Their tapered geometry generates a self-balancing axial component of load along the axis, allowing them to bear heavy and impact loads without the need for additional thrust bearings. This makes the overall machine more compact and lighter. The two single-row tapered roller bearings, arranged face-to-face, are precisely preloaded through the convex platform within the housing, the spindle flange, and the limit ring, further enhancing rigidity and ensuring the harrow blade maintains precise rotation even under high-impact and high-overturning conditions on rugged terrain, significantly extending the service life of the bearings and the entire machine.

[0015] 2. The axial lubrication channel running through the main shaft is combined with radial branch holes and limit ring outflow holes to achieve direct injection lubrication of the axis. Grease can be added online without removing the wheel hub. The external detachable oil nozzle is integrated with a one-way valve to prevent grease backflow and external impurities from intruding, greatly shortening maintenance time and reducing labor intensity.

[0016] 3. A serpentine return sealing channel is formed, and three layers of sealing rings with reverse hook-shaped ribs are used to build a multi-level gradient barrier from the outside to the inside. The pre-tightened bending direction of the ribs is always opposite to the flow of pollutants to intercept impurities, significantly improving sealing reliability and ensuring long-term stable operation of the bearing in harsh field environments. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 is a schematic cross-sectional view of the interior of the bearing assembly; Figure 2 It is a schematic diagram of the three-dimensional structure of the bearing assembly. DETAILED DESCRIPTION

[0018] In order to make the objectives, technical solutions and advantages of this application clearer, the technical solutions in the embodiments will be clearly and completely described below in conjunction with the drawings in the embodiments. However, the specific implementation methods and embodiments described below are only for illustrative purposes and are not intended to limit the present invention.

[0019] In the description of the present invention, it should be understood that the terms "longitudinal", "transverse", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside" and the like indicate directions or positional relationships based on the attached Figure 1 The directions or positional relationships shown are only for the convenience of describing the present invention, and do not indicate or imply that the devices or components referred to must have a specific orientation, be constructed and operate in a specific orientation. Therefore, they should not be understood as limiting the present invention.

[0020] In the description of this application, the terms "first", "second", etc. are used for descriptive purposes only and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features.

[0021] In order to solve the above technical problems, Figure 1-2 As shown, the present invention designs a tapered roller bearing assembly for a disc harrow hub, comprising The main shaft 1 is the torque input end and the assembly reference of the entire bearing structure, providing a coaxial reference for the subsequent cover body 2 and outer shell 3; The cover 2 is sleeved on the front end of the main shaft 1. The cover 2 has a cylindrical base 22 and a radially outwardly protruding flange portion 21 provided at the front end of the base 22. A gap is left between the flange portion 21 and the inner hole of the outer shell 3. The outer housing 3 is coaxially sleeved on the main shaft 1, and the inner hole at the front end thereof is provided with a stepped surface extending radially inward; The convex disc portion 21 of the cover body 2 forms a retaining wall in the axial direction, which not only blocks the direct splashing mud and significantly reduces the kinetic energy of impurities, but also forms an annular accommodating cavity with the step surface of the outer shell 3. The cavity volume provides sufficient arrangement space for the sealing mechanism 6 to allow multi-level protection. The accommodating cavity is connected to the bearing mounting area 4 between the main shaft 1 and the outer shell 3. A tapered roller bearing 5 is installed in the bearing mounting area 4. The advantage of using this type of bearing is that it has a large line contact load, can withstand radial and axial combined loads at the same time, has high rigidity and impact resistance, and is suitable for heavy-load agricultural machinery working conditions.

[0022] The sealing mechanism 6 provided in the accommodating cavity comprises at least three layers of sealing rings spaced apart in the axial direction, and a supporting assembly for supporting the sealing rings. The sealing rings and the supporting assembly form a gradient progressive sealing structure. The multi-layer sealing rings provide step-by-step protection, so that external pollutant particles and impurities are gradually weakened to prevent them from eventually reaching the raceway, thus achieving gradient filtration from the outside to the inside. This is significantly superior to the traditional single-stage sealing method, can extend the bearing life, and improve its reliability. A lubrication channel 7 extends axially through the interior of the main shaft 1, and the lubrication channel 7 is connected to the lubrication area of ​​the bearing mounting area 4 through a radial branch hole 8 radially penetrating the main shaft 1. The center-through lubrication channel 7 cooperates with the radial branch hole 8 to introduce grease into the bearing mounting area 4, so that the grease injection channel is completely hidden inside the rotating shaft system. The high-rigidity wall of the main shaft 1 forms a natural protection for the oil channel, and it will not become unstable due to deformation even under heavy load impact, ensuring the long-term reliability of the oil circuit. The axially penetrating and radially branching flow path is short, and the grease can be evenly sprayed to the entire raceway width of the tapered roller through the radial branch hole 8 in a short time, achieving coverage without dead angles, significantly reducing early wear caused by local grease deficiency, and the centrifugal force generated when the main shaft 1 rotates further promotes the grease to diffuse outward, forming a continuously circulating oil film, which not only improves the lubrication efficiency but also avoids grease deposition and aging. This design can avoid uneven lubrication and dead angles, and achieve fast, uniform, and online relubrication.

[0023] It is further preferred in this embodiment that there are two groups of tapered roller bearings 5, and both are single-row tapered roller bearings 5. The tapered rollers of the two groups are symmetrically installed face to face in the bearing installation area 4 with the large ends facing outward and the small ends facing each other. The tapered rollers 51 are fixed between the outer ring 52 and the inner ring 53 by a retaining frame. The conical geometry of the tapered rollers 51 themselves automatically decomposes the radial load into a radial component and a pair of axial components in opposite directions. When arranged face to face, the axial components of the two groups of bearings offset each other internally to form a self-balancing axial force closed loop, which can withstand bidirectional axial loads without the need for additional thrust bearings. The overall load-bearing capacity is significantly improved compared to traditional double-row ball bearings. The face-to-face symmetrical arrangement forms a self-balancing axial force closed loop, which can cope with the huge impact of the harrow blade entering the soil at the moment without the need for additional thrust bearings, so that the whole machine obtains greater load redundancy in a compact space and meets the long life requirements of heavy-load operations in farmland.

[0024] In this embodiment, it is further preferred that the inner circumference of the outer shell 3 is provided with a platform 31 protruding radially inward, and the axial ends of the platform 31 respectively abut the end faces of the outer rings 52 of the two tapered roller bearings 5 ​​to form an outer ring 52 limit. The end of the main shaft 1 extending into the outer shell 3 is provided with a flange portion 11 protruding radially outward. The outer periphery of the main shaft 1 is also provided with a limit ring 9 located between the two outer rings 52, and the end face of the limit ring 9 axially abuts the inner rings 53 of the two bearings. The flange portion 11 and the cover body 2 axially clamp the inner rings 53 of the two tapered roller bearings 5 ​​to form an axial limit of the inner ring 53. After assembly, stable preload is established immediately to achieve precise axial locking of the outer ring 52 and the inner ring 53 to prevent them from moving, making assembly and maintenance faster, and keeping the bearings in the theoretical contact position at all times under heavy load impact to avoid roller overload and channel peeling, thereby significantly improving overall reliability and service life.

[0025] It is further preferred in this embodiment that the limit ring 9 is provided with an outflow hole corresponding to the radial branch hole 8. The grease passes through the radial branch hole 8 and directly reaches the bearing mounting area 4 through the outflow hole. Since the roller axis is naturally inclined toward the center line of the main shaft 1, the small end is close to the oil outlet hole of the limit ring 9. The grease is sprayed from the radial branch hole 8 and can directly fall on the contact area between the roller and the raceway, and then diffuses along the cone surface to the large end, forming a "near first and then far" self-guiding lubrication path, which can cover the entire rolling surface without the need for an additional oil guide structure, thereby significantly improving the lubrication efficiency.

[0026] It is further preferred in this embodiment that a detachable oil nozzle 10 is provided at the outer end of the lubrication channel 7, and the oil nozzle 10 is threadedly connected to the end of the lubrication channel 7. The threaded connection forms a quick-change interface, which can be disassembled and assembled without tools, significantly shortening the downtime for maintenance. In addition, a one-way valve is provided in the oil nozzle 10, which is used to prevent the backflow of grease and can achieve one-way flow during grease injection.

[0027] In this embodiment, it is further preferred that a flange 32 is provided on the outer circumferential surface of the outer shell 3, and a plurality of bolt holes 33 are evenly distributed along the circumference of the flange 32 for direct bolt connection with the spoke plate of the harrow blade hub, thereby realizing a rigid integrated installation of the bearing assembly and the hub, and facilitating assembly and disassembly. In addition, the integrated flange transmits torque without relative slippage, thereby eliminating micro-wear and improving transmission efficiency.

[0028] It is further preferred in this embodiment that the support assembly includes a first support body 61 and a second support body 62; The first support body 61 is an annular structure with a concave cross-section, comprising a connecting plate 611 that fits against the inner hole surface of the outer shell 3, and an inner plate 612 and an outer plate 613 that bend inwardly from both ends of the connecting plate 611. The inner plate 612 abuts against the stepped surface of the outer shell 3, and a first axial gap is formed between the outer plate 613 and the cylindrical base of the cover body 2. The first support body 61 forms a rigid constraint in both the radial and axial directions through the continuous bending of the connecting plate 611, the outer plate 613, and the inner plate 612. This not only provides a reference mounting surface for the sealing ring, but also preliminarily divides the accommodating cavity into two-stage recirculation zones, so that large particles of impurities are inertially separated upon their first return. The second support body 62 is sleeved on the outside of the base of the cover body 2, and has an outer ring body 621 that cooperates with the base of the cover body 2, and a partition 622 extending radially outward from the front end of the outer ring body 621. The partition 622 is inserted between the inner plate 612 and the outer plate 613 of the first support body 61, and a second axial gap is formed between the partition 622 and the connecting plate 611. After the partition 622 is radially inserted into the groove of the first support body 61, the single path is split into two parallel and opposite sub-channels, so that the medium flow must undergo a second return before continuing to go deeper; this structure achieves a geometric multiplication of the path length while maintaining a compact axial size.

[0029] The outer plate 613 and the convex disc of the cover body 2 constitute a first radial channel 66, the outer plate 613 and the partition 622 constitute a second radial channel 67, and the partition 622 and the inner plate 612 constitute a third radial channel 68. The first axial gap connects the first and second radial channels 67, and the second axial gap connects the second and third radial channels 68, forming a continuous folding serpentine sealing path as a whole. The continuous folding path formed by the first radial channel 66, the first axial gap, the second radial channel 67, the second axial gap, and the third radial channel 68 in series in sequence enables the pollutants to complete multiple direction reversals in a limited space. The centrifugal separation caused by the sudden change of direction and the turbulent dissipation work together to form a natural sedimentation area, which reduces the load on the subsequent sealing ring.

[0030] The sealing ring can establish a gradient sealing barrier in the serpentine sealing path, and its sealing strength increases from the outside to the inside. Through spatial dislocation and functional sharing, the wear risk of a single sealing surface is dispersed to multiple levels, so that the wear originally concentrated on the single-stage sealing surface is absorbed by multiple levels in a coordinated manner, significantly extending the overall sealing life.

[0031] It is further preferred in this embodiment that each layer of the sealing ring is provided with a protruding rib 69 on its surface. The protruding rib 69 is actually distributed in a ring shape in the three-dimensional structure. Several protruding ribs 69 are arranged at intervals along the length direction of the sealing ring, which actually forms a plurality of parallel annular ridges. This arrangement significantly increases the contact area with the medium and the turbulent damping without increasing the thickness of the sealing ring, so that impurities are reflected, decelerated and deposited multiple times between adjacent annular ridges, thereby weakening their kinetic energy in advance.

[0032] It is further preferred in this embodiment that the sealing ring is divided into a first sealing ring 63, which is fixed to the end face of the outer plate 613 of the first support body 61 facing the convex disc of the cover body 2, and its protruding rib extends into the first radial channel 66 and blocks the radial through-path; a second sealing ring 64, which is fixed to the end face of the partition 622 of the second support body 62 close to the outer plate 613, and its protruding rib extends into the second radial channel 67 to block the radial through-path; a third sealing ring 65, which is fixed to the axial end face of the partition 622 close to the inner plate 612, and its protruding rib extends into the third radial channel 68 to block the radial through-path. In addition, it is preferred that each rib 69 undergoes directionally bent deformation under the action of axial assembly preload, and the bending direction points to the pollutant inflow end of the channel in which it is located, forming a hook-shaped sealing structure opposite to the medium intrusion direction. Through the precise layout of the three-layer sealing ring in the serpentine channel and the reverse hook-shaped bending design of the rib 69, a multi-stage linkage dynamic pollution interception system is constructed. The first sealing ring 63 rib 69 blocks external direct impurities, the second sealing ring 64 rib 69 intercepts the redirected migrating particles, and the third sealing ring 65 rib 69 blocks the terminal infiltration channel. Each rib 69 is directionally bent under the action of the assembly preload to form a hook-shaped sealing lip, and its bending direction is always opposite to the pollutant flow direction, so that various types of pollutants and impurities are gradually settled in the three-stage return channel, completely eliminating the problem of rapid bearing damage caused by the failure of a single barrier in traditional seals, and realizing long-term sealing protection of agricultural machinery wheel hub bearings under extreme working conditions.

[0033] The rib 69 and the sealing ring body are integrally vulcanized and the material department selects hydrogenated nitrile rubber. At the same time, the surface of the rib 69 is covered with a wear-resistant coating to ensure that the sealing performance with low wear and long life can be maintained even at high-speed rotation.

[0034] In addition, the outer edge of each sealing ring is further bent toward the axial gap area to form a covering wing. The wing is also vulcanized to form a continuous rib. The bent wing is tightly attached to the side wall of the gap under assembly pre-tightening, and the rib is reversely bent into a hook shape, directly blocking the potential leakage channel of the axial gap, achieving radial and axial dual interception, so that impurities are retained for a second time before entering the next channel, and the redundancy and reliability of the overall sealing link are further improved.

[0035] The above embodiments are only preferred embodiments of the present invention and are not intended to limit the scope of protection of the present invention. Therefore, any equivalent changes made by technicians in the relevant technical field based on the structure, shape, and principle of the present invention should be included in the scope of protection of the present invention.

Claims

1. A tapered roller bearing assembly for a disc harrow hub, characterized in that: include spindle; A cover body sleeved on the front end of the main shaft, the cover body having a cylindrical base and a radially outwardly protruding flange portion provided on the front end of the base; An outer shell is coaxially sleeved on the main shaft, and the inner hole at the front end of the outer shell is provided with a step surface extending radially inward; An annular accommodating cavity is formed between the convex disc portion of the cover and the stepped surface of the outer shell. The accommodating cavity is communicated with the bearing installation area between the main shaft and the outer shell. A tapered roller bearing is installed in the bearing installation area. a sealing mechanism disposed in the accommodating cavity; A lubrication channel extends axially through the main shaft, the lubrication channel is connected to the lubrication area of ​​the bearing installation area through a radial branch hole radially penetrating the main shaft, and the lubrication channel is used to introduce grease into the bearing installation area.

2. A tapered roller bearing assembly for a disc harrow hub according to claim 1, characterized in that: There are two groups of tapered roller bearings, both of which are single-row tapered roller bearings. The tapered rollers of the two groups are symmetrically installed face to face in the bearing installation area with their large ends facing outwards and their small ends facing each other.

3. The tapered roller bearing assembly for a disc harrow hub according to claim 2, characterized in that: The inner circumference of the outer shell is provided with a platform protruding radially inward, and the axial ends of the platform respectively abut the outer ring end faces of the two tapered roller bearings to form an outer ring limit. The end of the main shaft extending into the outer shell is provided with a flange portion protruding radially outward. The outer circumference of the main shaft is also provided with a limit ring located between the two outer rings. The end face of the limit ring axially abuts against the inner rings of the two bearings, and the flange portion and the cover body axially clamp the inner rings of the two tapered roller bearings to form an inner ring axial limit.

4. The tapered roller bearing assembly for a disc harrow hub according to claim 3, characterized in that: The limiting ring is provided with an outflow hole corresponding to and communicating with the radial branch hole. The grease passes through the radial branch hole and directly reaches the bearing installation area through the outflow hole.

5. The tapered roller bearing assembly for a disc harrow hub according to claim 4, characterized in that: A detachable oil nozzle is provided at the outer end of the lubrication channel. The oil nozzle is threadedly connected to the end of the lubrication channel and has a built-in one-way valve. The one-way valve is used to prevent the grease from flowing back.

6. The tapered roller bearing assembly for a disc harrow hub according to claim 1, characterized in that: The outer peripheral surface of the outer shell is provided with a flange, and a plurality of bolt holes are evenly distributed on the flange along the circumference for direct bolt connection with the spoke plate of the rake blade hub to achieve rigid integrated installation of the bearing assembly and the hub.

7. The tapered roller bearing assembly for a disc harrow hub according to claim 1, characterized in that: The sealing assembly comprises at least three layers of sealing rings spaced apart in the axial direction, and a supporting assembly for supporting the sealing rings, wherein the supporting assembly comprises a first supporting body and a second supporting body; The first support body is an annular structure with a concave cross-section, comprising a connecting plate that fits in contact with the inner hole surface of the outer shell, and inner and outer plates that bend inwardly from both ends of the connecting plate, wherein the inner plate fits against the stepped surface of the outer shell, and a first axial gap is formed between the outer plate and the cylindrical base of the cover body; The second support body is sleeved on the outside of the base body of the cover body, and comprises an outer ring body that cooperates with the base body of the cover body, and a partition plate that extends radially outward from the front end of the outer ring body. The partition plate is inserted between the inner plate and the outer plate of the first support body, and a second axial gap is formed between the partition plate and the connecting plate. The outer plate and the cover body convex disc constitute a first radial channel, the outer plate and the partition constitute a second radial channel, the partition and the inner plate constitute a third radial channel, the first axial gap connects the first radial channel and the second radial channel, the second axial gap connects the second radial channel and the third radial channel, and the whole forms a continuously folded serpentine sealing path, and the sealing ring is used to establish a gradient sealing barrier in the serpentine sealing path.

8. The tapered roller bearing assembly for a disc harrow hub according to claim 7, characterized in that: Each layer of sealing ring is provided with protruding ribs on its surface, and a plurality of protruding ribs are arranged at intervals along the length direction of the sealing ring.

9. The tapered roller bearing assembly for a disc harrow hub according to claim 8, characterized in that: The sealing ring is divided into A first sealing ring is fixed to the end surface of the outer plate of the first support body facing the cover body flange, and its protruding rib extends into the first radial channel and blocks the radial through path; A second sealing ring is fixed to the end surface of the second support body partition close to the outer plate, and its protruding rib extends into the second radial channel to block the radial through path; The third sealing ring is fixed to the axial end surface of the partition close to the inner plate, and the protruding rib of the third sealing ring extends into the third radial channel to block the radial through path.

10. The tapered roller bearing assembly for a disc harrow hub according to claim 9, characterized in that: Each rib undergoes directional bending deformation under the action of axial assembly pre-tightening, and the bending direction points to the pollutant inflow end of the channel where it is located, forming a hook-shaped sealing structure in the opposite direction of the medium intrusion direction.

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