A fast-lubricating rake blade hub bearing assembly

Abstract

This utility model discloses a fast-lubricating rake blade hub bearing assembly, including a main shaft; a cover sleeved on the front end of the main shaft, the cover having a cylindrical base and a radially outwardly protruding cam portion at the front end of the base; an outer housing coaxially sleeved on the main shaft, the front end of which has a radially inwardly extending stepped surface; an annular receiving cavity is formed between the cam portion of the cover and the stepped surface of the outer housing, the receiving cavity communicating with the bearing mounting area between the main shaft and the outer housing, a tapered roller bearing being installed in the bearing mounting area; a sealing assembly disposed in the receiving cavity; a lubrication channel radially penetrating the outer wall of the outer rotating body and communicating with the bearing mounting area, the lubrication channel being used to introduce grease into the bearing mounting area, ensuring that the rake blade maintains accurate rotation under high impact and high overturning conditions on rough surfaces, significantly extending the service life of the bearing and the entire machine.

Description

Technical Field

[0001] This utility model relates to the field of bearing technology, specifically to a fast-lubricating rake blade hub bearing assembly. Background Technology

[0002] The operating environment of existing disc harrows is harsh. The hub bearings must simultaneously withstand radial impact, axial thrust, and high-frequency vibration, while also facing corrosion from multiple pollutants such as mud, straw debris, and chemicals. Traditional solutions often use double-row deep groove ball bearings or simple double-row angular contact ball bearings. These bearings have high contact stress between the rolling elements and raceways, low load-bearing safety factors, and are prone to early fatigue spalling under eccentric or impact loads. In addition, traditional single-layer lip seal structures are prone to permanent deformation under gravel impact, creating channels for impurities to enter. Simple labyrinth seal structures have short sealing paths and large gaps, which cannot effectively intercept high-speed splashed particulate impurities and corrosive media. Impurities can easily penetrate the sealing interface and enter the bearing area, leading to lubrication failure, raceway spalling, and early fatigue, significantly reducing the overall reliability of the machine. Furthermore, existing disc harrow hub bearings generally lack reliable lubrication methods, making timely grease replenishment impossible. On-site maintenance requires disassembling the hub, resulting in low lubrication efficiency and high labor intensity.

[0003] There is an urgent need for a new type of bearing assembly that integrates a high-load-bearing 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-mentioned technical problems, this utility model relates to a quick-lubricating rake blade hub bearing assembly. This structure is simple and reliable, effectively solving the aforementioned technical problems and is suitable for widespread use. To achieve the above objectives, this utility model is implemented through the following technical solution:

[0005] A quick-lubricating rake blade hub bearing assembly, including

[0006] spindle;

[0007] A cover fitted onto the front end of the main shaft, the cover having a cylindrical base and a radially outwardly protruding cam portion located at the front end of the base;

[0008] The outer housing is coaxially fitted outside the main shaft, and its front end inner hole has a stepped surface that extends radially inward;

[0009] An annular receiving cavity is formed between the convex portion of the cover and the stepped surface of the outer shell. The receiving cavity is connected to the bearing mounting area between the main shaft and the outer shell. A tapered roller bearing is installed in the bearing mounting area.

[0010] A sealing assembly disposed within the receiving cavity;

[0011] A lubrication channel is provided, which radially penetrates the outer wall of the outer rotating body and communicates with the bearing mounting area. The lubrication channel is used to introduce grease into the bearing mounting area.

[0012] Based on the above scheme and as a preferred embodiment of the above scheme: there are two sets of tapered roller bearings, both of which are single-row tapered roller bearings, and the tapered rollers of the two sets are symmetrically installed face to face in the bearing mounting area with the large ends facing outwards and the small ends facing each other.

[0013] Based on the above scheme and as a preferred embodiment: the inner circumferential surface of the outer shell is provided with a radially inwardly protruding platform, the two ends of the platform abutting against 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 radially outwardly protruding flange; the outer circumference of the main shaft is also provided with a limiting ring located between the two outer rings; the end face of the limiting ring abuts axially against the inner rings of the two bearings; the flange and the cover axially clamp the inner rings of the two tapered roller bearings to form an inner ring axial limit; the platform is provided with an oil outlet hole corresponding to the lubrication channel; the oil outlet hole is located between the two tapered rollers.

[0014] Based on the above scheme and as a preferred embodiment of the above scheme: the outer end of the lubrication channel is provided with a detachable grease nipple, the grease nipple 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 grease backflow.

[0015] Based on the above scheme and as a preferred embodiment of the above scheme: the outer peripheral surface of the outer shell is provided with a flange, and several bolt holes are evenly distributed along the circumference of the flange for direct bolt connection with the spokes of the rake wheel hub, so as to realize the rigid integrated installation of the bearing assembly and the hub.

[0016] Based on the above solution and as a preferred embodiment of the above solution: the sealing assembly includes at least three layers of sealing rings spaced apart along the axial direction, and a support assembly for supporting the sealing rings, the support assembly including a first support body and a second support body;

[0017] The first support body is a ring structure with a concave cross-section. It has a connecting plate that fits with the inner hole surface of the outer shell, an inner side plate and an outer side plate that bend inward from both ends of the connecting plate, wherein the inner side plate abuts against the stepped surface of the outer shell, and a first axial gap is formed between the outer side plate and the cylindrical base of the cover body.

[0018] The second support body is sleeved on the outside of the base of the cover body. It has an outer ring body that mates with the base 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 side plate and the outer side plate of the first support body, and a second axial gap is formed between the partition plate and the connecting plate.

[0019] The outer side plate and the cover protrusion form a first radial channel, the outer side plate and the partition plate form a second radial channel, and the partition plate and the inner side plate form a third radial channel. The first axial gap connects the first radial channel and the second radial channel, and the second axial gap connects the second radial channel and the third radial channel, forming a continuous zigzag sealing path. The sealing ring is used to establish a gradient sealing barrier in the zigzag sealing path.

[0020] Based on the above scheme and as a preferred embodiment of the above scheme: each layer of sealing ring surface is provided with protruding ribs, and several protruding ribs are spaced apart along the length direction of the sealing ring.

[0021] Based on the above scheme and as a preferred embodiment of the above scheme: the sealing ring is divided into

[0022] The first sealing ring is fixed to the end face of the outer side plate of the first support body facing the cover plate, and its protruding rib extends into the first radial channel and blocks the radial through path.

[0023] The second sealing ring is fixed to the end face of the second support body partition near the outer side plate, and its protruding ribs extend into the second radial channel to block the radial through path;

[0024] The third sealing ring is fixed to the axial end face of the partition plate near the inner side plate, and its protruding ribs extend into the third radial channel to block the radial through path.

[0025] Based on the above scheme and as a preferred option: each protruding rib undergoes directional bending deformation under axial assembly pre-tightening, with the bending direction pointing towards the pollutant inflow end of its channel, forming a hook-shaped sealing structure opposite to the direction of media intrusion.

[0026] The outstanding and beneficial technical effects of this utility model compared to the prior art are:

[0027] 1. Tapered roller bearings, with their line contact structure between the rollers and raceways, disperse the point contact stress of traditional ball bearings into a wider contact band. Under the same external dimensions, they can significantly improve the ability to withstand combined radial and axial loads. Their tapered geometry causes the load to generate a self-balancing axial component along the axial direction, allowing them to bear heavy loads and impact loads without the need for additional thrust bearings. This makes the overall structure more compact and lighter. Two rows of single-row tapered roller bearings arranged face-to-face achieve precise preload through the inner convex platform of the housing, the main shaft flange, and the limiting ring, further amplifying rigidity and ensuring that the rake blades maintain precise rotation under high impact and high overturning conditions on rough surfaces, significantly extending the service life of the bearings and the entire machine.

[0028] 2. With the lubrication channel located on the outer wall of the housing, the lubricating grease enters from the outer wall and only needs to pass through the outer ring wall thickness to reach the bearing area for lubrication. This allows for rapid grease injection. The grease reaches the raceway directly via the shortest radial path, significantly reducing the flow distance and instantly and evenly covering the two rows of tapered rollers, achieving efficient and zero-dead-angle lubrication. The externally detachable grease nozzle integrates a one-way valve to prevent grease backflow and the intrusion of external impurities, greatly shortening maintenance time and reducing labor intensity.

[0029] 3. A serpentine folding sealing channel is formed, which, together with a three-layer sealing ring with reverse hook-shaped protrusions, constructs a multi-level gradient barrier from the outside to the inside; the pre-tightening bending direction of the protrusions always opposes the flow of pollutants to intercept impurities, significantly improving sealing reliability and ensuring long-term stable operation of the bearing in harsh field environments. Attached Figure Description

[0030] Figure 1 This is a schematic diagram of the internal cross-section of the bearing assembly;

[0031] Figure 2 This is a schematic diagram of the three-dimensional structure of the bearing assembly. Detailed Implementation

[0032] 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 with reference to the accompanying drawings. However, the specific implementation methods and embodiments described below are for illustrative purposes only and are not intended to limit the present invention.

[0033] In the description of this utility model, it should be understood that the terms "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the appendix. Figure 1 The directions or positional relationships shown are for the purpose of describing this utility model only, and are not intended to indicate or imply that the device or component 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 utility model.

[0034] In the description of this application, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated.

[0035] To solve the above technical problems, such as Figure 1-2 As shown, this utility model designs a fast-lubricating rake blade hub bearing assembly, including...

[0036] Main shaft 1, which is the torque input end, serves as the assembly reference for the entire bearing structure and provides a coaxial reference for the subsequent cover 2 and outer shell 3.

[0037] A cover 2 is fitted onto the front end of the main shaft 1. The cover 2 has a cylindrical base 22 and a radially outward protruding convex portion 21 located at the front end of the base 22. A gap is left between the convex portion 21 and the inner hole of the outer shell 3.

[0038] The outer housing 3, which is coaxially sleeved outside the main shaft 1, has a stepped surface extending radially inward in its front end inner hole;

[0039] The convex portion 21 of the cover 2 forms a baffle in the axial direction, which not only blocks the direct splashing of mud and significantly reduces the kinetic energy of impurities, but also forms an annular receiving cavity with the stepped surface of the outer shell 3. The cavity volume provides sufficient space for the sealing mechanism 6 to allow for multi-level protection. The receiving 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 advantages of using this type of bearing are that it has a large line contact load capacity, can withstand radial and axial combined loads at the same time, has high rigidity, and is impact resistant, making it suitable for heavy-duty agricultural machinery working conditions.

[0040] A sealing mechanism 6 is disposed within the receiving cavity. The sealing mechanism 6 includes at least three layers of sealing rings spaced apart along the axial direction, and a support assembly supporting the sealing rings. The sealing rings and the support assembly form a gradient progressive sealing structure. By utilizing multiple layers of sealing rings for step-by-step protection, external contaminant particles are gradually weakened, preventing them from ultimately reaching the raceway. This achieves gradient filtration from the surface inwards, which is significantly superior to traditional single-stage sealing methods, extending bearing life and improving its reliability.

[0041] The lubrication channel 7 penetrates the outer wall of the housing 3 radially and communicates with the bearing mounting area. The lubrication channel 7 is used to introduce grease into the bearing mounting area 6. After entering from the outer wall, the grease can reach the bearing area by passing through only the outer ring wall thickness to achieve lubrication. This allows for rapid grease injection. The grease reaches the raceway directly through the shortest radial path, greatly shortening the flow distance and instantly and evenly covering the two rows of tapered rollers, achieving efficient and zero-dead-angle lubrication.

[0042] In this embodiment, it is further preferred that there are two sets of tapered roller bearings 5, both of which are single-row tapered roller bearings 5. The tapered rollers of the two sets are symmetrically installed face-to-face in the bearing mounting 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 cage. The tapered geometry of the tapered rollers 51 themselves causes the radial load to be automatically decomposed into a radial component and a pair of axial components in opposite directions. When arranged face-to-face, the axial components of the two sets of bearings cancel each other out internally, forming a self-balancing axial force closed loop. It can withstand bidirectional axial loads without additional thrust bearings. The overall load-bearing capacity is significantly improved compared with traditional double-row ball bearings. The face-to-face symmetrical arrangement also forms a self-balancing axial force closed loop. It can cope with the huge impact of the harrow blades entering the soil without additional thrust bearings, so that the whole machine can obtain greater load redundancy in a compact space and meet the long service life requirements of heavy-duty farmland operations.

[0043] In this embodiment, it is further preferred that the inner circumferential surface of the outer shell 3 is provided with a radially inwardly protruding platform 31. The two ends of the platform 31 abut against 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 that extends into the outer shell 3 is provided with a radially outwardly protruding flange 11. The outer circumference of the main shaft 1 is also provided with a limiting ring 9 located between the two outer rings 52. The end face of the limiting ring 9 abuts axially with the inner rings 53 of the two bearings. The flange 11 and the cover 2 axially clamp the inner rings 53 of the two tapered roller bearings 5 ​​to form an inner ring 53 axial limit. After assembly, a stable preload is established immediately to achieve precise axial locking of the outer rings 52 and inner rings 53, preventing them from moving. Assembly and maintenance are faster, and the bearings are kept in the theoretical contact position under heavy load impact, avoiding roller overload and raceway peeling, significantly improving overall reliability and service life.

[0044] The platform 31 is provided with an oil outlet corresponding to the lubrication channel 7. The oil outlet is located between two tapered rollers. After the grease enters from the lubrication channel on the outer wall, it is directly sprayed into the intersection area of ​​the two bearings through the oil outlet of the platform. The path is the shortest and without turning. The grease spreads instantly in the space between the two rows of rollers. In addition, since the roller axis naturally tilts towards the center line of the main shaft 1, the small end is close to the oil outlet of the limiting ring 9. The grease can fall directly into the contact area between the roller and the raceway after being sprayed out of the oil outlet. Then it spreads along the tapered surface to the large end, forming a "near first and then far" self-guiding lubrication path. It can cover the entire rolling surface without the need for an additional oil guiding structure, which significantly improves the lubrication efficiency.

[0045] In this embodiment, it is further preferred that the outer end of the lubrication channel 7 is provided with a detachable grease nipple 10, which 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 downtime for maintenance. In addition, the grease nipple 10 is provided with a one-way valve, which is used to prevent grease backflow and allows one-way flow during grease injection.

[0046] In this embodiment, it is further preferred that the outer peripheral surface of the outer shell 3 is provided with a flange 32, and a plurality of bolt holes 33 are evenly distributed along the circumference of the flange 32 for direct bolt connection with the spokes of the rake wheel hub, so as to realize the rigid integrated installation of the bearing assembly and the hub, which is convenient for disassembly and assembly. In addition, the integrated flange has no relative slippage when transmitting torque, eliminating fretting wear and improving transmission efficiency.

[0047] In this embodiment, it is further preferred that the support component includes a first support body 61 and a second support body 62;

[0048] The first support 61 is a ring structure with a concave cross-section. It has a connecting plate 611 that fits against the inner hole surface of the outer shell 3, an inner side plate 612 and an outer side plate 613 that bend inward from both ends of the connecting plate 611. The inner side plate 612 is attached to the stepped surface of the outer shell 3, and the outer side plate 613 forms a first axial gap with the cylindrical base of the cover 2. The first support 61 forms a rigid constraint in both the radial and axial directions through the continuous bending of the connecting plate 611, the outer side plate 613 and the inner side plate 612. This provides a reference mounting surface for the sealing ring and initially divides the cavity into two-stage reflux zones, so that large particles of impurities will undergo inertial separation during the first reflux.

[0049] The second support 62 is sleeved on the outside of the base of the cover 2. It has an outer ring 621 that mates with the base of the cover 2 and a partition 622 that extends radially outward from the front end of the outer ring 621. The partition 622 is inserted between the inner side plate 612 and the outer side plate 613 of the first support 61. 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 61, it splits the single path into two parallel and opposite sub-channels, so that the medium flow must undergo a second reversal before it can continue to penetrate. This structure achieves a geometric increase in path length while maintaining a compact axial dimension.

[0050] The outer side plate 613 and the convex plate of the cover 2 form a first radial channel 66, the outer side plate 613 and the partition plate 622 form a second radial channel 67, and the partition plate 622 and the inner side plate 612 form 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 zigzag sealing path. The continuous zigzag path, consisting of the first radial channel 66, the first axial gap, the second radial channel 67, the second axial gap, and the third radial channel 68 connected in series, allows pollutants to undergo multiple directional reversals within a limited space. The centrifugal separation and turbulent dissipation caused by the sudden change in direction work together to form a natural settling zone, reducing the load on the subsequent sealing ring.

[0051] The sealing ring can establish a gradient sealing barrier in the serpentine sealing path, with its sealing strength increasing from the outside to the inside. Through spatial misalignment and functional sharing, the wear risk of a single sealing surface is dispersed to multiple levels, so that the wear originally concentrated on a single sealing surface is absorbed by multiple levels in a coordinated manner, significantly extending the overall sealing life.

[0052] In this embodiment, it is further preferred that each sealing ring surface is provided with protruding ribs 69. The protruding ribs 69 are actually distributed in a ring shape in the three-dimensional structure. Several protruding ribs 69 are spaced apart along the length of the sealing ring, which actually forms multiple parallel ring ridges. This arrangement significantly increases the contact area with the medium and the turbulence damping without increasing the thickness of the sealing ring, so that impurities are reflected, decelerated and deposited multiple times between adjacent ring ridges, thus weakening their kinetic energy in advance.

[0053] In this embodiment, it is further preferred that the sealing ring is divided into a first sealing ring 63, which is fixed to the end face of the outer side plate 613 of the first support body 61 facing the convex disk of the cover body 2, and its protrusion 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 plate 622 of the second support body 62 near the outer side plate 613, and its protrusion extends into the second radial channel 67 to block the radial through path; and a third sealing ring 65, which is fixed to the axial end face of the partition plate 622 near the inner side plate 612, and its protrusion extends into the third radial channel 68 to block the radial through path. Furthermore, preferably, each protruding rib 69 undergoes directional bending deformation under axial assembly pre-tightening, with the bending direction pointing towards the pollutant inflow end of its channel, forming a hook-shaped sealing structure opposite to the direction of media intrusion. Through the precise layout of the three sealing rings in the serpentine channel and the reverse hook-shaped bending design of the protruding ribs 69, a multi-level linkage dynamic pollution interception system is constructed. The first sealing ring 63 and protruding rib 69 block external direct-flow impurities, the second sealing ring 64 and protruding rib 69 intercept diverted migrating particles, and the third sealing ring 65 and protruding rib 69 seal the final infiltration channel. Under the action of assembly pre-tightening force, each protruding rib 69 bends directionally to form a hook-shaped sealing lip, with its bending direction always opposite to the pollutant flow direction, so that various pollutants settle step by step in the three-level return channel, completely eliminating the problem of rapid bearing damage caused by the failure of a single barrier in traditional seals, and achieving long-term sealing protection for agricultural machinery wheel hub bearings under extreme working conditions.

[0054] The rib 69 and the sealing ring body are integrally vulcanized and molded. The material can be 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 can maintain low wear and long service life even when rotating at high speed.

[0055] In addition, the outer edge of each sealing ring is further bent toward the axial gap area to form a covering wing. This wing is also vulcanized to form continuous protrusions. Under assembly pre-tightening, the bent wing is tightly attached to the gap sidewall, and the protrusions are bent in the opposite direction into a hook shape, directly blocking the potential leakage channel of the axial gap, achieving radial and axial double interception, so that impurities are intercepted a second time before entering the next channel, and the redundancy and reliability of the overall sealing link are improved again.

[0056] The above embodiments are merely preferred embodiments of this utility model and are not intended to limit the scope of protection of this utility model. Therefore, all equivalent changes made by those skilled in the art based on the structure, shape, and principle of this utility model should be included within the scope of protection of this utility model.

Claims

1. A fast-lubricating rake blade hub bearing assembly, characterized in that: include spindle; A cover fitted onto the front end of the main shaft, the cover having a cylindrical base and a radially outwardly protruding cam portion located at the front end of the base; The outer housing is coaxially fitted outside the main shaft, and its front end inner hole has a stepped surface that extends radially inward; An annular receiving cavity is formed between the convex portion of the cover and the stepped surface of the outer shell. The receiving cavity is connected to the bearing mounting area between the main shaft and the outer shell. A tapered roller bearing is installed in the bearing mounting area. A sealing assembly disposed within the receiving cavity; A lubrication channel is provided, which radially penetrates the outer wall of the outer rotating body and communicates with the bearing mounting area. The lubrication channel is used to introduce grease into the bearing mounting area.

2. The fast-lubricating rake blade hub bearing assembly according to claim 1, characterized in that: There are two sets of tapered roller bearings, both of which are single-row tapered roller bearings. The tapered rollers of the two sets are symmetrically installed face-to-face in the bearing mounting area with the large ends facing outwards and the small ends facing each other.

3. The fast-lubricating rake blade hub bearing assembly according to claim 2, characterized in that: The inner circumferential surface of the outer casing is provided with a radially inwardly protruding platform. The two ends of the platform abut against 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 casing is provided with a radially outwardly protruding flange. The outer circumference of the main shaft is also provided with a limiting ring located between the two outer rings. The end face of the limiting ring abuts against the inner rings of the two bearings axially. The flange and the cover axially clamp the inner rings of the two tapered roller bearings to form an inner ring axial limit. The platform is provided with an oil outlet hole corresponding to the lubrication channel. The oil outlet hole is located between the two tapered rollers.

4. The fast-lubricating rake blade hub bearing assembly according to claim 3, characterized in that: The outer end of the lubrication channel is provided with a detachable grease nipple, which is threaded to the end of the lubrication channel and has a built-in one-way valve to prevent grease backflow.

5. The fast-lubricating rake blade hub bearing assembly according to claim 1, characterized in that: The outer circumferential surface of the outer shell is provided with a flange, and several bolt holes are evenly distributed along the circumference of the flange for direct bolt connection with the spokes of the rake wheel hub, so as to realize the rigid integrated installation of the bearing assembly and the hub.

6. The fast-lubricating rake blade hub bearing assembly according to claim 1, characterized in that: The sealing assembly includes at least three layers of sealing rings spaced apart along the axial direction, 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 a ring structure with a concave cross-section. It has a connecting plate that fits with the inner hole surface of the outer shell, an inner side plate and an outer side plate that bend inward from both ends of the connecting plate, wherein the inner side plate abuts against the stepped surface of the outer shell, and a first axial gap is formed between the outer side plate and the cylindrical base of the cover body. The second support body is sleeved on the outside of the base of the cover body. It has an outer ring body that mates with the base 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 side plate and the outer side plate of the first support body, and a second axial gap is formed between the partition plate and the connecting plate. The outer side plate and the cover protrusion form a first radial channel, the outer side plate and the partition plate form a second radial channel, and the partition plate and the inner side plate form a third radial channel. The first axial gap connects the first radial channel and the second radial channel, and the second axial gap connects the second radial channel and the third radial channel, forming a continuous zigzag sealing path. The sealing ring is used to establish a gradient sealing barrier in the zigzag sealing path.

7. A quick-lubricating rake blade hub bearing assembly according to claim 6, characterized in that: Each sealing ring surface is provided with protruding ribs, and several protruding ribs are spaced apart along the length of the sealing ring.

8. A fast-lubricating rake blade hub bearing assembly according to claim 7, characterized in that: The sealing ring is divided into The first sealing ring is fixed to the end face of the outer side plate of the first support body facing the cover plate, and its protruding rib extends into the first radial channel and blocks the radial through path. The second sealing ring is fixed to the end face of the second support body partition near the outer side plate, and its protruding ribs extend into the second radial channel to block the radial through path; The third sealing ring is fixed to the axial end face of the partition plate near the inner side plate, and its protruding ribs extend into the third radial channel to block the radial through path.

9. A quick-lubricating rake blade hub bearing assembly according to claim 8, characterized in that: Each rib undergoes directional bending deformation under axial assembly pre-tightening, with the bending direction pointing towards the pollutant inflow end of its channel, forming a hook-shaped sealing structure opposite to the direction of media intrusion.

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