Asymmetric tapered roller bearing for wind power transmission systems

Abstract

The application discloses an asymmetric conical roller bearing for a wind power transmission system, which comprises an inner ring, a first outer ring and a second outer ring, a first raceway is arranged between the inner ring and the first outer ring in an inclined manner, 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, an annular groove is arranged on the outer circumferential wall of the spacer ring, oil holes are arranged in the annular groove in a spaced manner, hub end rollers are arranged in the first raceway, motor end rollers are matched with the second raceway, retainers are arranged on the motor end rollers and the hub end rollers respectively, the length of the motor end rollers is greater than that of the hub end rollers, the retainers are provided with protrusions extending towards the spacer ring, the protrusions are arranged in a spaced manner, and the protrusions on the two retainers are arranged in a staggered manner. The asymmetric conical roller bearing has the advantages of simple structure, reasonable layout, effectively improved bearing carrying capacity and stiffness support, effectively reduced abnormal sound and good use effect.

Description

TECHNICAL FIELD

[0001] The present application relates to a kind of asymmetric conical roller bearings for wind power transmission system. BACKGROUND

[0002] In 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 conical roller bearing of wind power transmission system is usually installed on the motor side end of the output shaft of 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 blade rotates clockwise, and the force is transmitted through the planetary mechanism speed box gear, and the axial force generated by the gear on the high-speed shaft is directed from the hub end to the motor end. When the system reverses, the axial force direction is instantaneously changed from the motor end to the hub end. This complex and variable stress environment puts high demands on the performance of the bearing.

[0003] Traditional wind power high-speed shafts usually use two sets of single-row conical roller bearings for support. However, this design results in a significant reduction in bearing support stiffness due to the independence of the two bearings. In actual operation, the low support stiffness not only makes it difficult for the bearing to maintain stability when subjected to axial and radial forces, but also causes vibration and noise, exacerbating the wear of internal parts of the bearing, thereby significantly shortening the service life of the bearing. With the development of the wind power industry towards high power and high reliability, the traditional bearing design has been unable to meet the growing performance demands. SUMMARY

[0004] To overcome the shortcomings of the prior art, the present application provides an asymmetric conical roller bearing for wind power transmission system, which has a simple structure, a reasonable layout, effectively improves the bearing load capacity and stiffness support, effectively reduces the noise, and has good use effect.

[0005] To achieve the above-mentioned purpose, the present application provides an asymmetric conical roller bearing for wind power transmission system, comprising 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, an annular groove is provided on the outer peripheral wall of the spacer ring, oil holes are arranged in the annular groove, hub end rollers are arranged in the first raceway, motor end rollers are matched in the second raceway, retaining frames are respectively arranged on the motor end rollers and the hub end rollers, the length of the motor end rollers is greater than that of the hub end rollers, the retaining frames extend to the spacer ring with protrusions, the protrusions are arranged at intervals, and the protrusions on the two retaining frames are arranged staggered.

[0006] The beneficial effect of this arrangement is that, preferably, the bearing is composed of an inner ring, a first outer ring, and a second outer ring forming a basic frame, wherein the inner ring is innovatively designed to have two raceways, one on the hub end and the other on the motor end, and the length of the raceway on the hub side is shorter than that on the motor side. This asymmetric raceway layout is based on the characteristic that when wind turbines are in operation, the axial force is mostly directed from the hub end to the motor end. Through differentiated design, the load-bearing capacity of the raceways on both sides is made more uniform, which greatly improves the stability of the bearing in complex stress environments 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 load-bearing performance of the bearing. The annular groove and oil hole on the outer peripheral wall of the spacer ring form 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 in the annular groove. At the same time, the two retaining frames have protrusions extending toward the spacer ring, arranged in a staggered manner. The staggered arrangement here refers to the staggering of adjacent protrusions on the two retaining frames, forming a certain height difference. This prevents mutual interference between the structures during use, ensures smooth operation of the structure, and forms a unique lubricating oil guide and diversion structure. Once the lubricating oil enters the bearing, the protrusion 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 angles. This design greatly reduces the friction between the rollers and raceways, and between the rollers and retaining frames, not only reducing the abnormal noise caused by dry friction, but also reducing operating energy consumption, extending the service life of the bearings, and ensuring the smooth and efficient operation of the wind power transmission system.

[0007] As a further configuration of the present invention, first guide grooves are respectively provided on the protrusions of the retaining frame, and 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.

[0008] 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, forming 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, delivering 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 fluid to various parts of the roller. This dual guide groove design ensures that the lubricating fluid can evenly and efficiently cover the hub-end roller and the motor-end roller, effectively reducing the frictional resistance during roller movement. It not only significantly reduces the degree of wear of the bearing during operation, but also avoids local overheating problems caused by uneven lubrication, further extending the service life of the bearing and comprehensively improving the operational stability and reliability of the wind power transmission system.

[0009] As a further configuration of the present invention, an oil seepage hole is provided in the first guide groove.

[0010] The beneficial effect of such an arrangement is that, in this way, the traditional bearing lubrication often fails to fully consider the hidden areas such as the back of the protruding structure, and the presence of the oil seepage hole enables the oil to break through the conventional path and enter the back of the protruding structure. When the lubricating oil flows along the guide groove, part of the oil can penetrate to the back of the protruding structure through the oil seepage hole, filling the lubrication blind area and achieving all-round lubrication of the rollers and the retainer. This design effectively reduces the wear caused by insufficient local lubrication, reduces the abnormal friction during bearing operation, further enhances the stability of the bearing under complex working conditions, and prolongs the service life of the bearing.

[0011] As a further arrangement of the present application, the inner ring outer peripheral wall is provided with a boss between the first raceway and the second raceway, and a circumferential oil distribution groove is arranged on the end face of the boss, and a plurality of branch grooves are arranged on both sides of the oil distribution groove.

[0012] The beneficial effect of such an arrangement is that, in this way, the traditional bearing often lacks effective flow guide structure when distributing lubricating oil, 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 circumferential oil distribution groove begins to play a role, which can quickly and evenly disperse the concentrated lubricating oil in the circumferential direction. The plurality of 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 enables the lubricating oil to quickly and evenly infiltrate the contact area between the rollers and the raceways, effectively avoiding local dry friction 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.

[0013] As a further arrangement of the present application, the hub end roller cone angle is greater than the motor end roller cone angle.

[0014] The beneficial effect of such an arrangement is that, in this way, the raceway cone angles on both sides of the outer ring are not the same. In order to make the bearing have good stiffness and carrying capacity during operation, the hub end roller cone angle is greater than the motor end roller cone angle, so that the rollers near the motor end side have higher carrying capacity, ensuring the stability of the structure in use and having good use effect.

[0015] As a further arrangement of the present application, the inner ring rim is provided with a retaining edge corresponding to the positions of the first raceway and the second raceway.

[0016] The beneficial effect of such an arrangement is that, in this way, the axial displacement of the rollers can be effectively limited to prevent them from being separated from the raceway during high-speed operation or sudden force change. This design enhances the stability of the bearing structure, reduces the abnormal friction between the rollers and the edges 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 DRAWINGS

[0017] Figure 1Schematic diagram of the overall structure cross-section of an embodiment of the present invention;

[0018] Figure 2 Schematic diagram of the cross-sectional structure of the spacer ring in an embodiment of the present invention;

[0019] Figure 3 Schematic diagram of the structure of the retaining frame in an embodiment of the present invention. DETAILED DESCRIPTION

[0020] The present invention provides an embodiment of an asymmetric tapered roller bearing for a wind power transmission system, such 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 provided 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 protrusions 41 are arranged at intervals, and the protrusions 41 on the two retainers 4 are staggered. The beneficial effects of this arrangement are as follows: Preferably, the bearing comprises an inner ring 1, a first outer ring 21, and a second outer ring 22 forming the basic framework. The inner ring 1 is innovatively designed with two raceways, one on the hub side and the other on the motor side, with the hub-side raceway being shorter than the motor-side raceway. This asymmetric raceway layout is based on the characteristic that axial forces in wind turbines are primarily directed from the hub side to the motor side during operation. This differentiated design ensures a more uniform load-bearing capacity on both sides of the raceway, significantly improving the bearing's stability under complex load conditions and effectively preventing premature wear and failure caused by localized overload. Furthermore, the two rows of raceways utilize different shaping methods to further optimize the contact between the rollers and the raceways, reduce stress concentration, and significantly enhance the bearing's overall load-bearing performance. The annular groove 51 and oil hole 52 on the outer circumferential wall of the spacer ring 5 form an efficient lubrication channel. With an oil filler installed at the corresponding location on the equipment, lubricating oil can be precisely injected into the bearing through the oil hole 52 in 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 refers to the staggering of adjacent protrusions 41 on the two retaining frames 4, and forming a certain height difference to avoid mutual interference between the structures during use, ensure the smooth operation of the structure, and form a unique lubricating oil guiding and diversion 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 angles. This design greatly reduces the friction between the roller and the raceway, and between the roller and the retaining frame 4, not only reducing the abnormal noise caused by dry friction, but also reducing operating energy consumption, extending the service life of the bearing, and ensuring the smooth and efficient operation of the wind power transmission system.

[0021] As a further feature of this embodiment, the protrusions 41 of the retainer 4 are each provided with a first guide groove 42, and the outer wall of the retainer 4 is each provided with a second guide groove 43. The first guide groove 42 and the second guide groove 43 are interconnected. This configuration has the beneficial effect of interconnecting the first guide groove 42 on the protrusion 41 and the second guide groove 43 on the outer walls of the two retainers 4, creating a more precise lubricating oil guiding network. When lubricating oil is injected into the bearing through the oil hole 52 of the spacer ring 5, the first guide groove 42 precisely guides the oil along the protrusion 41 structure, delivering the lubricating oil to the key area where the rollers contact the raceway. The second guide groove 43, in conjunction with the first guide groove 42, further disperses the lubricating oil to various parts of the rollers. This dual guide groove design ensures that the lubricating oil evenly and efficiently covers the hub-end roller 31 and the motor-end roller 32, effectively reducing frictional resistance during roller movement. It not only significantly reduces the degree of bearing wear during operation, but also avoids local overheating problems caused by uneven lubrication, further extends the service life of the bearings, and comprehensively improves the operating stability and reliability of the wind power transmission system.

[0022] As a further feature of this embodiment, an oil seepage hole 44 is provided in the first guide groove 42. This advantageous feature is that, while conventional bearing lubrication often struggles to fully address hidden areas such as the back of the protrusion 41, the presence of oil seepage hole 44 allows the oil to bypass conventional pathways and reach the back of the protrusion 41. As the lubricating oil flows along the guide groove, some of the oil can penetrate through the oil seepage hole 44 to the back of the protrusion 41, filling the lubrication blind spot and achieving all-round lubrication of the rollers and retainer 4. This design effectively reduces wear caused by localized insufficient lubrication, reduces abnormal friction during bearing operation, further enhances the bearing's stability under complex operating conditions, and extends its service life.

[0023] As a further feature of this embodiment, a boss 11 is provided on the outer circumferential wall of the inner ring 1 between the first and second raceways. An oil distribution groove 12 is circumferentially arranged on the end face of the boss 11, with several branch grooves flanking the oil distribution groove 12. This advantageous arrangement reduces the lubrication unevenness caused by the lack of effective flow-guiding structures in conventional bearings, which often prevents even coverage of the raceways with lubricant. When lubricant drips from the spacer ring 5 onto the end face of the boss 11, the circumferentially arranged oil distribution grooves 12 come into play, quickly dispersing the concentrated lubricant evenly along the circumference. The branch grooves flanking the oil distribution groove 12 precisely deliver the lubricant to the first and second raceways. This design allows the lubricant to quickly and evenly penetrate the contact area between the rollers and raceways, effectively avoiding localized dry friction and reducing wear on the rollers and raceways. Furthermore, through rational oil distribution path planning, lubricant consumption is reduced, improving the bearing's lubrication efficiency.

[0024] As a further feature of this embodiment, the cone angle of the hub-end roller 31 is greater than that of the motor-end roller 32. This configuration has the beneficial effect of varying the cone angles of the raceways on either side of the outer ring. To ensure good rigidity and load-bearing capacity during operation, the cone angle of the hub-end roller 31 is greater than that of the motor-end roller 32, ensuring a higher load-bearing capacity for the rollers closer to the motor end, ensuring structural stability, and delivering excellent performance.

[0025] As a further feature of this embodiment, ribs 13 are installed along the edges of the inner ring 1, corresponding to the first and second raceways. This arrangement effectively limits the axial displacement of the rollers, preventing them from dislodging from the raceways 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 mitigates the risk of wear caused by roller misalignment, ensuring that the bearing maintains good performance over extended periods of operation.

[0026] The above example is only one preferred specific example of the present invention. Common changes and substitutions made by those skilled in the art within the scope of the technical solution of the present invention are all 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, wherein a first raceway is obliquely disposed between the inner ring and the first outer ring, and a second raceway is disposed between the inner ring and the second outer ring, characterized in that: A spacer ring is provided between the first outer ring and the second outer ring, an annular groove is provided on the outer peripheral wall of the spacer ring, oil holes are provided at intervals in the annular groove, a hub end roller is provided in the first raceway, a motor end roller is matched in the second raceway, a retaining frame is respectively provided 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, a protrusion is extended toward the spacer ring by the retaining frame, the protrusions are arranged at intervals, and the protrusions on the two retaining frames are staggered, a first guide groove is respectively provided on the retaining frame protrusions, a second guide groove is respectively provided on the outer wall of the retaining frame, and the first guide groove and the second guide groove are connected.

2. The asymmetric tapered roller bearing for a wind power transmission system according to claim 1, characterized in that: An oil seepage hole is provided in the first guide groove.

3. The asymmetric tapered roller bearing for a wind power transmission system according to claim 1, 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.

4. 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 greater than the cone angle of the roller at the motor end.

5. 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