Asymmetric tapered roller bearing for wind power transmission system

Abstract

The invention discloses an asymmetric tapered roller bearing for a wind power transmission system, the asymmetric tapered roller bearing comprises an inner ring, a first outer ring and a second outer ring, a first raceway is obliquely arranged between the inner ring and the first outer ring, a second raceway is arranged between the inner ring and the second outer ring, a spacer ring is arranged between the first outer ring and the second outer ring, and the spacer ring is arranged between the first outer ring and the second outer ring. An annular groove is formed in the upper edge of the outer circumferential wall of the spacer ring, oil holes are formed in the annular groove at intervals, a hub end roller is arranged in the first roller path, a motor end roller is arranged in the second roller path in a matched mode, retainers are arranged on the motor end roller and the hub end bearing respectively, the length of the motor end roller is larger than that of the hub end roller, and the motor end roller and the hub end bearing are arranged in a matched mode. The retainers extend towards the spacer ring to form protrusions, the protrusions are arranged at intervals, and the protrusions on the two retainers are arranged in a staggered mode. The structure is simple, the layout is reasonable, the bearing capacity and the rigidity support of the bearing are effectively improved, the abnormal sound is effectively reduced, and the use effect is good.

Description

Technical Field

[0001] The present invention relates to an asymmetric tapered roller bearing for a wind power transmission system. Background Art

[0002] In a wind power transmission chain system, the performance of core components directly determines the stability and efficiency of wind power generation equipment. As one of the key components, the asymmetric tapered roller bearing of the wind power transmission system is usually installed at the motor side end of the output shaft of the wind power high-speed shaft, and its working state directly affects the operation quality of the entire transmission system. Under normal working conditions, the hub blades rotate clockwise. Through the force transmission of the planetary gearbox gears, the axial force generated by the gear on the high-speed shaft is directed from the hub end to the motor end; while when the system reverses, the axial force direction instantly changes to be directed from the motor end to the hub end. Such a complex and changeable stress environment poses strict requirements on the performance of the bearing. Traditionally, two sets of single-row tapered roller bearings are mostly used to support the wind power high-speed shaft. However, due to the mutual independence of the two sets of bearings, the support stiffness of the bearings is greatly reduced. During actual operation, the low support stiffness not only makes it difficult for the bearings to maintain stability when bearing axial force and radial force, but also causes vibration and noise, exacerbates the wear of internal parts of the bearings, and thus significantly shortens the service life of the bearings. With the development of the wind power industry towards high power and high reliability, the traditional bearing design has been difficult to meet the increasing performance requirements. Summary of the Invention

[0003] Aiming at the deficiencies of the prior art, the present invention provides an asymmetric tapered roller bearing for a wind power transmission system, which has a simple structure, reasonable layout, effectively improves the bearing capacity and stiffness support of the bearing, effectively reduces abnormal noise, and has good use effects.

[0004] To achieve the above object, the present invention provides an asymmetric tapered roller bearing for a wind power transmission system, including an inner ring, a first outer ring and a second outer ring. A first raceway is inclined between the inner ring and the first outer ring, a second raceway is provided between the inner ring and the second outer ring, a spacer ring is provided between the first outer ring and the second outer ring. An annular groove is provided along the outer peripheral wall of the spacer ring, and oil holes are spaced in the middle of the annular groove. Hub end rollers are arranged in the first raceway, motor end rollers are fitted in the second raceway. Cage are respectively arranged on the motor end rollers and the hub end bearings. The length of the motor end rollers is greater than that of the hub end rollers. The cage extends towards the spacer ring with protrusions, the protrusions are spaced, and the protrusions on the two cages are arranged staggeredly.

[0005] The beneficial effect of such a setting is that, as a preferred embodiment, the bearing is composed of an inner ring, a first outer ring, and a second outer ring to form a basic frame, wherein the inner ring is innovatively designed to have two raceways, one at the hub end and the other at the motor end, and the length of the raceway on the hub side is less than that on the motor side. This asymmetric raceway layout is based on the characteristic that the axial force of wind power equipment is mostly directed from the hub end to the motor end when the equipment is running. Through differentiated design, the bearing capacity of the raceways on both sides is more uniform, which greatly improves the stability of the bearing in a complex stress environment and effectively avoids premature wear and failure caused by local overload. In addition, the two rows of raceways adopt different shaping methods to further optimize the contact state between the rollers and the raceways, reduce stress concentration, and significantly enhance the overall bearing performance of the bearing. The annular groove and the oil hole on the outer peripheral wall of the spacer ring constitute an efficient lubrication channel. After the oil filling part is set at the corresponding position of the equipment, the lubricating oil can be accurately injected into the bearing through the oil hole of the annular groove. At the same time, the two retaining frames have protrusions extending toward the spacer rings, which are arranged in a staggered manner. The staggered arrangement here refers to the staggered adjacent protrusions on the two retaining frames, and a certain height difference is formed to avoid mutual interference between the structures during use, ensure the smooth operation of the structure, and form a unique lubricating oil guiding and diverting structure. When the lubricating oil enters the bearing, the protruding structure can effectively guide the oil to evenly cover the rollers at the hub end and the rollers at the motor end, achieving full lubrication in all directions and without dead ends. This design greatly reduces the friction between the rollers and the raceways, and between the rollers and the retaining frames, which not only reduces the abnormal noise caused by dry friction, but also reduces operating energy consumption, extends the service life of the bearings, and ensures the smooth and efficient operation of the wind power transmission system.

[0006] As a further configuration of the present invention, first guide grooves are respectively provided on the protrusions of the retaining frame, second guide grooves are respectively provided on the outer walls of the retaining frame, and the first guide grooves and the second guide grooves are connected to each other.

[0007] The beneficial effect of this arrangement is that the first guide groove on the protrusion and the second guide groove on the outer wall of the two retainers are interconnected to build a more precise lubricating oil guiding network. When the lubricating oil is injected into the bearing through the oil hole of the spacer ring, the first guide groove can accurately guide the oil to flow along the protrusion structure and transport the lubricating oil to the key area where the roller contacts the raceway; while the second guide groove cooperates with the first guide groove to further disperse the lubricating liquid to various parts of the roller. This double guide groove design ensures that the lubricating liquid can evenly and efficiently cover the hub end roller and the motor end roller, effectively reducing the friction resistance when the roller moves. It not only significantly reduces the degree of wear of the bearing during operation, but also avoids local overheating caused by uneven lubrication, further prolongs the service life of the bearing, and comprehensively improves the operating stability and reliability of the wind power transmission system.

[0008] As a further configuration of the present invention, an oil seepage hole is provided in the first guide groove.

[0009] The beneficial effect of this arrangement is that, with this arrangement, traditional bearing lubrication often cannot fully take into account hidden areas such as the back of the raised structure, while the presence of the oil seepage hole allows the oil to break through the conventional path and enter the back of the raised structure. When the lubricating oil flows along the guide groove, part of the oil can penetrate through the oil seepage hole to the back of the raised structure, filling the lubrication blind area and achieving all-round lubrication of the roller and cage. This design effectively reduces the wear caused by insufficient local lubrication, reduces abnormal friction during bearing operation, further enhances the stability of the bearing under complex working conditions, and extends the service life of the bearing.

[0010] As a further configuration of the present invention, a boss is provided on the outer peripheral wall of the inner ring between the first raceway and the second raceway, an oil separation groove is provided on the end surface of the boss along the circumferential direction, and a plurality of branch grooves are provided on both sides of the oil separation groove.

[0011] The beneficial effect of this arrangement is that when distributing lubricating oil, traditional bearings often lack effective guide structures, which makes it difficult for the oil to evenly cover the raceway, resulting in uneven lubrication. When the lubricating oil drips from the spacer ring to the end face of the boss, the circumferentially arranged oil distribution groove begins to play a role, which can quickly disperse the concentrated lubricating oil evenly along the circumferential direction. Several branch grooves on both sides of the oil distribution groove accurately deliver the lubricating oil to the first raceway and the second raceway. This design allows the lubricating oil to quickly and evenly infiltrate the contact area between the roller and the raceway, effectively avoiding local dry friction and reducing the wear of the roller and the raceway. At the same time, through reasonable oil distribution path planning, the consumption of lubricating oil is reduced and the lubrication efficiency of the bearing is improved.

[0012] As a further configuration of the present invention, the cone angle of the roller at the hub end is greater than the cone angle of the roller at the motor end.

[0013] The beneficial effect of this arrangement is that with this arrangement, the raceway taper angles on both sides of the outer ring are also different. In order to ensure that the bearing has good rigidity and load-bearing capacity during operation, the roller taper angle at the hub end is greater than the roller taper angle at the motor end, so that the roller close to the motor end has a higher load-bearing capacity, ensuring the stability of the structure and having a good use effect.

[0014] As a further configuration of the present invention, ribs are provided on the edge of the inner ring corresponding to the positions of the first raceway and the second raceway.

[0015] The beneficial effect of this arrangement is that it can effectively limit the axial displacement of the roller and prevent it from leaving the raceway when running at high speed or when the force suddenly changes. This design enhances the stability of the bearing structure, reduces abnormal friction between the roller and the edge of the raceway, reduces the risk of wear caused by roller deviation, and ensures that the bearing maintains good performance during long-term operation. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1Schematic cross-sectional view of the overall structure of an embodiment of the present invention; Figure 2 Schematic cross-sectional view of the spacer structure in an embodiment of the present invention; Figure 3 Schematic view of the structure of the cage in an embodiment of the present invention. Detailed implementation manners

[0017] The present invention provides an embodiment of an asymmetric tapered roller bearing for a wind power transmission system, as Figures 1 to 3As shown, it includes an inner ring 1, a first outer ring 21 and a second outer ring 22, a first raceway is obliquely arranged between the inner ring 1 and the first outer ring 21, a second raceway is arranged between the inner ring 1 and the second outer ring 22, a spacer ring 5 is arranged between the first outer ring 21 and the second outer ring 22, an annular groove 51 is arranged on the outer peripheral wall of the spacer ring 5, oil holes 52 are arranged at intervals in the annular groove 51, a hub end roller 31 is arranged in the first raceway, a motor end roller 32 is matched in the second raceway, a retainer 4 is respectively arranged on the motor end roller 32 and the hub end bearing, the motor end roller 32 is longer than the hub end roller 31, the retainer 4 extends to the spacer ring 5 with a protrusion 41, the protrusion 41 is arranged at intervals, and the protrusions 41 on the two retainers 4 are staggered. The beneficial effect of such arrangement is as follows: as a preferred embodiment, the bearing is composed of an inner ring 1, a first outer ring 21, and a second outer ring 22 to form a basic frame, wherein the inner ring 1 is innovatively designed to have two raceways, one at the hub end and the other at the motor end, and the length of the raceway on the hub side is less than that on the motor side. This asymmetric raceway layout is based on the characteristic that the axial force of the wind power equipment is mostly directed from the hub end to the motor end when the wind power equipment is running. Through differentiated design, the bearing capacity of the raceways on both sides is more uniform, which greatly improves the stability of the bearing in a complex stress environment and effectively avoids premature wear and failure caused by local overload. In addition, the two rows of raceways adopt different shaping methods to further optimize the contact state between the rollers and the raceways, reduce stress concentration, and significantly enhance the overall bearing performance of the bearing. The annular groove 51 and the oil hole 52 on the outer peripheral wall of the spacer ring 5 constitute an efficient lubrication channel. After the oil replenishing part is set at the corresponding position of the equipment, the lubricating oil can be accurately injected into the bearing through the oil hole 52 of the annular groove 51. At the same time, the two retaining frames 4 have protrusions 41 extending toward the spacer ring 5, which are arranged in a staggered manner. The staggered arrangement here means that the adjacent protrusions 41 on the two retaining frames 4 are staggered, and a certain height difference is formed to avoid mutual interference between the structures during use, ensure the smooth operation of the structure, and form a unique lubricating oil guiding and diverting structure. When the lubricating oil enters the bearing, the protrusion 41 structure can effectively guide the oil to evenly cover the hub end roller 31 and the motor end roller 32, achieving full lubrication in all directions and without dead ends. This design greatly reduces the friction between the roller and the raceway, and between the roller and the retaining frame 4, which not only reduces the abnormal noise caused by dry friction, but also reduces the operating energy consumption, extends the service life of the bearing, and ensures the smooth and efficient operation of the wind power transmission system.

[0018] As a further setting of this embodiment, first guide grooves 42 are respectively provided on the protrusions 41 of the cage 4, and second guide grooves 43 are respectively provided on the outer wall of the cage 4. The first guide grooves 42 and the second guide grooves 43 are communicated. The beneficial effect of such a setting is as follows: With such a setting, the first guide grooves 42 on the protrusions 41 and the second guide grooves 43 on the outer walls of the two cages 4 are communicated with each other, constructing a more precise lubricating oil guiding network. When the lubricating oil is injected into the bearing through the oil holes 52 of the spacer ring 5, the first guide grooves 42 can accurately guide the oil to flow along the structure of the protrusions 41, and transport the lubricating oil to the key areas where the rollers contact the raceways; while the second guide grooves 43 cooperate with the first guide grooves 42 to further disperse the lubricating liquid to all parts of the rollers. This double guide groove design ensures that the lubricating liquid can evenly and efficiently cover the hub-end rollers 31 and the motor-end rollers 32, effectively reducing the frictional resistance during the movement of the rollers. It not only significantly reduces the wear degree during the operation of the bearing, but also avoids the local overheating problem caused by uneven lubrication, further prolongs the service life of the bearing, and comprehensively improves the operation stability and reliability of the wind power transmission system.

[0019] As a further setting of this embodiment, oil seepage holes 44 are provided in the first guide grooves 42. The beneficial effect of such a setting is as follows: With such a setting, it is often difficult for traditional bearing lubrication to fully cover hidden areas such as the back of the protrusion 41 structure. The existence of the oil seepage holes 44 enables the oil to break through the conventional path and enter the back position of the protrusion 41 structure. When the lubricating oil flows along the guide grooves, part of the oil can penetrate through the oil seepage holes 44 to the back of the protrusion 41 structure, filling the lubrication blind area and achieving full lubrication of the rollers and the cage 4. This design effectively reduces the wear caused by insufficient local lubrication, reduces the abnormal friction during the operation of the bearing, further enhances the stability of the bearing under complex working conditions, and prolongs the service life of the bearing.

[0020] As a further setting of this embodiment, a boss 11 is provided on the outer peripheral wall of the inner ring 1 between the first raceway and the second raceway. An oil distribution groove 12 is provided along the circumferential direction on the end face of the boss 11, and a plurality of branch grooves are provided on both sides of the oil distribution groove 12. The beneficial effect of such a setting is as follows: With such a setting, when traditional bearings distribute lubricating oil, due to the lack of an effective diversion structure, it is often difficult for the oil to evenly cover the raceways, resulting in uneven lubrication. When the lubricating oil drips from the spacer ring 5 onto the end face of the boss 11, the circumferentially arranged oil distribution groove 12 begins to play a role. It can quickly disperse the concentrated lubricating oil evenly along the circumferential direction. The plurality of branch grooves on both sides of the oil distribution groove 12 accurately transport the lubricating oil to the first raceway and the second raceway. This design enables the lubricating oil to quickly and evenly infiltrate the contact areas between the rollers and the raceways, effectively avoiding local dry friction phenomena and reducing the wear of the rollers and the raceways. At the same time, through reasonable oil distribution path planning, the consumption of lubricating oil is reduced, and the lubrication efficiency of the bearing is improved.

[0021] As a further setting of this embodiment, the cone angle of the hub-end roller 31 is set to be larger than that of the motor-end roller 32. The beneficial effect of this setting is as follows: With this setting, the raceway cone angles on both sides of the outer ring are also different. In order to ensure that the bearing has good stiffness and load-carrying capacity during operation, the cone angle of the hub-end roller 31 is larger than that of the motor-end roller 32, so that the rollers closer to the motor-end side have higher load-carrying capacity, ensuring the stability of the structure during use and having good usage effects.

[0022] As a further setting of this embodiment, the inner ring 1 is provided with ribs 13 at positions corresponding to the first raceway and the second raceway. The beneficial effect of this setting is as follows: With this setting, the axial displacement of the rollers can be effectively restricted, preventing them from disengaging from the raceway during high-speed operation or sudden force changes. This design enhances the stability of the bearing structure, reduces abnormal friction between the rollers and the raceway edges, and reduces the wear risk caused by roller offset, ensuring that the bearing maintains good performance during long-term operation.

[0023] The above examples are only one of the preferred specific examples of the present invention, and the common changes and substitutions made by those skilled in the art within the scope of the technical solution of the present invention are included in the protection scope of the present invention.

Claims

1. An asymmetric tapered roller bearing for a wind power transmission system, comprising an inner ring, a first outer ring and a second outer ring, a first raceway being obliquely arranged between the inner ring and the first outer ring, and a second raceway being arranged between the inner ring and the second outer ring, characterized in that: A spacer ring is arranged between the first outer ring and the second outer ring, an annular groove is arranged on the upper edge of the outer peripheral wall of the spacer ring, oil holes are arranged at intervals in the annular groove, a hub end roller is arranged in the first raceway, a motor end roller is matched in the second raceway, retaining frames are respectively arranged on the motor end roller and the hub end bearing, the length of the motor end roller is greater than that of the hub end roller, the retaining frame has protrusions extending toward the spacer ring, the protrusions are arranged at intervals, and the protrusions on the two retaining frames are staggered.

2. The asymmetric tapered roller bearing for a wind power transmission system according to claim 1, characterized in that: The retaining frame protrusions are respectively provided with first guide grooves, and the outer walls of the retaining frame are respectively provided with second guide grooves, and the first guide grooves and the second guide grooves are connected to each other.

3. The asymmetric tapered roller bearing for a wind power transmission system according to claim 2, characterized in that: An oil seepage hole is arranged in the first guide groove.

4. The asymmetric tapered roller bearing for a wind power transmission system according to claim 2, characterized in that: The outer peripheral wall of the inner ring is provided with a boss between the first raceway and the second raceway, an oil separation groove is provided on the end surface of the boss along the circumferential direction, and a plurality of branch grooves are provided on both sides of the oil separation groove.

5. The asymmetric tapered roller bearing for a wind power transmission system according to claim 1, characterized in that: The cone angle of the roller at the hub end is set larger than the cone angle of the roller at the motor end.

6. The asymmetric tapered roller bearing for a wind power transmission system according to claim 1, characterized in that: The inner ring edge is provided with ribs corresponding to the first raceway and the second raceway.

Images