Tapered roller bearing, shafting structure and wind driven generator

Abstract

The invention relates to the technical field of transmission parts, and discloses a tapered roller bearing, a shaft system structure and a wind driven generator. The inner diameter surface of the inner ring of the tapered roller bearing is a conical surface, and the diameter of the inner diameter surface of the inner ring is gradually reduced in the direction from the end with the larger outer diameter to the end with the smaller outer diameter. According to the tapered roller bearing, the shaft system structure and the wind driven generator, the matching effect between the bearing and the shaft is improved, and the operation stability of a system is ensured.

Description

Technical Field

[0001] This application relates to low-speed main shaft systems in the field of wind power generation technology, and particularly to a tapered roller bearing, shaft system structure, and wind turbine generator. Background Technology

[0002] With the continuous development of new energy technologies, the proportion of wind power generation is also constantly increasing. Wind power generation utilizes the widely flowing wind in nature to generate electricity. The wind drives the blades of the wind turbine to rotate, converting wind energy into mechanical energy, which in turn drives the rotor to generate electricity. Since no pollutants are produced during the power generation process, it is relatively environmentally friendly and is an important source of electricity among new energy sources.

[0003] The low-speed main shaft system is a key subsystem in wind turbines that plays a crucial role in power transmission. During wind turbine operation, the main shaft transmits power to the rotor, and the main bearing supports the main shaft. The operational stability of the main shaft and its bearings affects the normal operation of the wind turbine; therefore, ensuring the coordination and operational stability between the two is an important issue. Summary of the Invention

[0004] The purpose of this application is to provide a tapered roller bearing, shaft structure, and wind turbine generator that can help ensure the operational stability of a low-speed main shaft system.

[0005] To address the aforementioned technical problems, embodiments of this application provide a tapered roller bearing. The tapered roller bearing includes an inner ring and an outer ring, as well as a set of tapered rollers and a cage located between the inner and outer rings. The intersection of the generatrix of the raceway surface of the inner ring and the generatrix of the raceway surface of the outer ring is located on the central axis of the tapered roller bearing. The inner diameter surface of the inner ring is a conical surface, and the inner diameter of the inner ring gradually decreases from the end with the larger outer diameter to the end with the smaller outer diameter.

[0006] The embodiments of this application provide a shaft system structure. The shaft system structure includes a bearing housing, a shaft, and the aforementioned tapered roller bearing, wherein the shaft is rotatably connected to the bearing housing via the tapered roller bearing.

[0007] The embodiments of this application also provide a wind turbine generator, which includes the shaft system structure described above.

[0008] The tapered roller bearing, shaft system structure, and wind turbine provided in this application have a tapered assembly surface where the bearing inner ring contacts the main shaft. Specifically, the surface of the bearing inner ring in contact with the main shaft has a gradually changing diameter. This tapered shape provides a guiding effect, ensuring the main shaft bearing is properly assembled onto the main shaft. It also increases the minimum wall thickness and wall thickness uniformity of the inner ring, ensuring a tighter fit between the bearing inner ring and the main shaft. This prevents relative slippage between the main shaft and the main shaft bearing from affecting the operational stability of the main shaft.

[0009] In some implementations, the inner diameter taper angle is 3-15°.

[0010] In some implementations, the outer diameter surface of the outer ring is a conical surface, and the outer diameter of the outer ring gradually decreases from the end with the larger inner diameter to the end with the smaller inner diameter.

[0011] In some implementations, the outer diameter taper angle of the outer ring is 3-15°. Attached Figure Description

[0012] One or more embodiments are illustrated by way of example with reference numerals in the accompanying drawings. These illustrations do not constitute a limitation on the embodiments. Elements with the same reference numerals in the drawings are denoted as similar elements. Unless otherwise stated, the figures in the drawings are not to be limited by scale.

[0013] Figure 1 This is a schematic diagram of the structure of a tapered roller bearing provided in some embodiments of this application; Figure 2 These are schematic diagrams of shaft system structures provided in some embodiments of this application; Figure 3 yes Figure 2 Enlarged structural diagram at point A; Figure 4 yes Figure 2 A magnified structural diagram at point B in the middle. Detailed Implementation

[0014] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the various embodiments of this application will be described in detail below with reference to the accompanying drawings. However, those skilled in the art will understand that many technical details have been presented in the various embodiments of this application to enable readers to better understand this application. However, even without these technical details and various changes and modifications based on the following embodiments, the technical solutions claimed in this application can be implemented. The division of the various embodiments below is for the convenience of description and should not constitute any limitation on the specific implementation of this application. The various embodiments can be combined with and referenced by each other without contradiction.

[0015] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains; the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the application; the terms “comprising” and “having”, and any variations thereof, in the specification, claims, and foregoing description of the drawings are intended to cover non-exclusive inclusion.

[0016] In the description of the embodiments of this application, unless otherwise expressly specified and limited, technical terms such as "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this application according to the specific circumstances.

[0017] With the continuous development of wind power generation technology, the capacity of wind turbines is getting higher and higher, and the size of related components is getting larger and larger, which puts forward higher requirements for the tightness of the assembly of various components in wind turbines.

[0018] A wind turbine typically consists of a rotor in the air and a generator inside the nacelle. The rotor rotates with the wind, and its power is transmitted through the main shaft to the gearbox, and then to the generator, driving its rotor to generate electricity. The main shaft is responsible for power transmission. One end of the main shaft is connected to the rotor, and the other end is connected to the gearbox. The main shaft is supported by bearings. In large-capacity wind turbines with larger blades, a larger main shaft is also used to ensure sufficient structural strength to withstand greater loads.

[0019] The spindle is assembled to bearing housings via two spindle bearings, which provide support at different locations. The spindle interior can be hollow to accommodate cables or other components. The spindle bearings are tapered roller bearings, capable of withstanding both radial and axial loads, making them suitable for supporting large spindles.

[0020] The large size of the main shaft also increases the difficulty of assembling the main shaft bearing. When the assembly tightness between the main shaft bearing and the main shaft is insufficient, relative displacement or separation can easily occur, which directly leads to failure of the wind turbine transmission system and seriously affects the normal operation of the wind turbine.

[0021] To ensure the stability of the main shaft during operation, some embodiments of this application provide a tapered roller bearing. The mating area between the tapered roller bearing and the main shaft is tapered, meaning the mating surface between the bearing and the shaft has a varying diameter. When the bearing mates with the shaft, the tapered shape and the wall thickness of the inner ring ensure a tight fit, thereby ensuring the stability of the main shaft's operation and preventing any impact on the normal operation of the wind turbine.

[0022] The following is combined with Figures 1 to 4 This application describes the tapered roller bearing structure provided in some embodiments.

[0023] like Figure 1 As shown, the tapered roller bearing 10 includes an inner ring 101 and an outer ring 102, as well as tapered rollers 103 and a cage 104 located between the inner ring 101 and the outer ring 102. The intersection of the generatrix of the raceway surface of the inner ring 101 and the generatrix of the raceway surface of the outer ring 102 is located on the central axis of the tapered roller bearing 10. The inner diameter surface of the inner ring 101 is a tapered surface, and the inner diameter of the inner ring 101 gradually decreases from the end with the larger inner diameter of the outer ring to the end with the smaller outer diameter.

[0024] The inner diameter surface, i.e., the inner mounting surface of the tapered roller bearing 10, can be tapered by gradually changing the inner diameter of the inner ring 101 along the axial direction of the tapered roller bearing. This increases the interference fit between the tapered roller bearing 10 and the spindle, improving the tightness of the fit. In practice, the diameter of the inner ring's inner diameter surface can be gradually increased or decreased along the axial direction of the tapered roller bearing 10. The trend of change depends on the installation direction of the tapered roller bearing. To ensure a tight fit between the bearing and the spindle, and to increase the interference fit between the bearing inner ring and the spindle, the mating surface where the bearing inner ring contacts the spindle is designed as a tapered shape. This means the contact surfaces of the bearing inner ring and the spindle have a gradually changing diameter. The tapered shape acts as a guide, ensuring the spindle bearing is properly seated on the spindle and that the bearing inner ring forms a tight fit with the spindle. This prevents relative slippage between the spindle and the spindle bearing, which could affect the operational stability of the spindle 12.

[0025] In some embodiments, the inner diameter taper angle of the inner ring 101 is 3-15°.

[0026] This allows control over the taper range of the inner diameter surface of the inner ring 101, preventing excessive taper that could cause the bearing to slip easily, and also controlling the wall thickness variation of the inner ring 101 to avoid affecting the tightness of the assembly due to large deformation differences in various parts of the inner ring 101. In practice, the tapered mating surface on the inner side of the inner ring 101 can be formed by increasing the minimum wall thickness of the inner ring 101.

[0027] like Figure 1 As shown, the outer diameter surface of the outer ring 102 is a conical surface, and the outer diameter of the outer ring 102 gradually decreases from the end with the larger outer inner diameter to the end with the smaller outer inner diameter.

[0028] The outer diameter surface, i.e., the portion of the outer ring 102 of the tapered roller bearing 10 that mates with the bearing housing, can also be tapered. When the spindle bearing mates with the bearing housing, a tapered surface can also be used to guide the assembly and ensure tightness, preventing slippage between the spindle bearing and the bearing housing. In this way, a relatively tight fit can be achieved between the inner and outer rings of the spindle bearing, resulting in more uniform stress distribution and ensuring the stability of the spindle bearing during long-term use.

[0029] In some embodiments, the outer diameter taper angle of the outer ring 102 is 3-15°.

[0030] This allows control over the taper range of the outer diameter surface of the outer ring 102, preventing excessive taper that could cause the bearing to slip easily, and also controlling the wall thickness variation of the outer ring 102 to avoid affecting the tightness of the assembly due to large differences in deformation at various points. In practice, the tapered mating surface on the outer side of the outer ring 102 can be formed by increasing the minimum wall thickness of the outer ring 102.

[0031] This application also provides a shaft system structure, which includes a bearing housing, a shaft, and the tapered roller bearing described above. The shaft is rotatably connected to the bearing housing via the tapered roller bearing.

[0032] Furthermore, the diameter changes of the mating surface between the shaft and the inner ring are consistent with the inner diameter surface of the inner ring, and the diameter changes of the mating surface between the bearing housing and the outer ring are consistent with the outer diameter surface of the outer ring. This ensures a tight fit between the bearing, the shaft, and the bearing housing.

[0033] In practice, considering the need to set different interference fits along the axial direction, the taper deviation between the mating surface of the shaft and the inner ring and the inner diameter surface of the inner ring can be kept to no more than 0.2°, and the taper deviation between the mating surface of the bearing housing and the outer ring and the outer diameter surface of the outer ring can be kept to no more than 0.2°.

[0034] like Figures 2 to 4As shown, some embodiments of this application provide a shaft system structure including a bearing housing 11, a main shaft 12, a first tapered roller bearing 13, and a second tapered roller bearing 14. The bearing housing 11 is provided with a mounting hole 111, and a first mounting surface 112 and a second mounting surface 113 located on the wall of the mounting hole 111. The main shaft 12 is provided with a first mating surface 121 and a second mating surface 122. The first tapered roller bearing 13 includes a first inner ring 131 and a first outer ring 132. The first inner ring 131 is fitted onto the first mating surface 121, and the first outer ring 132 abuts against the first mounting surface 112. The second tapered roller bearing 14 includes a second inner ring 141 and a second outer ring 142. The second inner ring 141 is fitted onto the second mating surface 122, and the second outer ring 142 abuts against the second mounting surface 113. Along the axial direction of the main shaft 12, the diameter of the surface of the first inner ring 131 that contacts the first mating surface 121 gradually changes, and the diameter of the surface of the second inner ring 141 that contacts the second mating surface 122 gradually changes.

[0035] The bearing housing 11 serves as the foundation for mounting and supporting the main shaft 12. The bearing housing 11 can be installed inside the nacelle of a wind turbine, with one side of the bearing housing 11 corresponding to the wind turbine and the other side corresponding to the gearbox. The bearing housing 11 has through-holes 111 at both ends. Different mounting surfaces are located at different positions on the wall of the mounting holes 111: the first mounting surface 112 corresponds to the mounting position of the front main shaft bearing, and the second mounting surface 113 corresponds to the mounting position of the rear main shaft bearing. The first mounting surface 112 is located near the end face of the bearing housing 11 facing the wind turbine, and the second mounting surface 113 is located near the end face of the bearing housing 11 facing the gearbox. Space can also be reserved inside the bearing housing 11 to accommodate lubricating oil or grease for lubricating the main shaft bearings, and the space is sealed by an end cap structure.

[0036] The main shaft 12 is the shaft of the wind turbine. The gearbox and generator of the wind turbine are installed in the nacelle, and the wind turbine is connected to the gearbox via the main shaft 12. The main shaft 12 not only transmits the torque of the wind turbine's rotation but also resists the oscillation of the wind turbine. The front end of the main shaft 12 has a connecting flange 123 for connecting the hub. The interior of the main shaft 12 can be provided with through holes as channels for the arrangement of control cables, oil lines, or mechanical rods. The front end of the main shaft 12 is driven by blades, and the rear end of the main shaft 12 is connected to the gearbox for power transmission, driving the generator rotor to rotate and generate electricity.

[0037] The main shaft 12 is assembled to the bearing housing 11 via tapered roller bearings. The first tapered roller bearing 13 serves as the front support bearing, providing support at the location of the first mounting surface 112 of the bearing housing 11. The second tapered roller bearing 14 serves as the rear support bearing, providing support at the location of the second mounting surface 113 of the bearing housing 11. Both the inner and outer rings of the tapered roller bearings have tapered raceways. The tapered rollers enable relative rotation between the inner and outer rings, allowing them to withstand loads in multiple directions. Figure 3 As shown, the first tapered roller bearing 13 has a first tapered roller 133 between its first inner ring 131 and first outer ring 132, and the surfaces of the raceway formed by the first inner ring 131 and the first outer ring 132 have a taper corresponding to the first tapered roller 133. Figure 4 As shown, the second tapered roller bearing 14 has a second tapered roller 143 between the second inner ring 141 and the second outer ring 142, and the surfaces of the raceway formed by the second inner ring 141 and the second outer ring 142 have a taper corresponding to the second tapered roller 143.

[0038] The first tapered roller bearing 13 and the second tapered roller bearing 14 are both located between the mounting hole 111 of the main shaft 12 and the bearing housing 11. The first inner ring 131 of the first tapered roller bearing 13 is fitted onto the first mating surface 121 of the main shaft 12, and the first outer ring 132 abuts against the first mounting surface 112 of the bearing housing 11. The second inner ring 141 of the second tapered roller bearing 14 is fitted onto the second mating surface 122 of the main shaft 12, and the second outer ring 142 abuts against the second mounting surface 113 of the bearing housing 11. A limiting structure can also be provided on the mounting hole 111 of the main shaft 12 and the bearing housing 11 to axially position the main shaft bearings, ensuring that the bearings are installed in place and their position remains fixed. A connecting locking element 15 can also be used to limit the main shaft bearings and facilitate easy disassembly.

[0039] The surface where the first inner ring 131 contacts the first mating surface 121 is the inner mounting surface of the first tapered roller bearing 13. By gradually changing the diameter of the surface where the first inner ring 131 contacts the first mating surface 121 along the axial direction of the spindle 12, the inner mounting surface of the first tapered roller bearing 13 can be made tapered. Simultaneously, the first mating surface 121 of the spindle 12 is also tapered, which increases the interference fit between the first tapered roller bearing 13 and the spindle, improving the tightness of the fit. In practice, the diameter of the surface where the first inner ring 131 contacts the first mating surface 121 can be gradually increased or decreased along the axial direction of the spindle 12. The trend of change can be determined according to the installation direction of the first tapered roller bearing 13. For example, Figure 2If the first tapered roller bearing 13 shown is assembled along the axial direction from right to left, then the diameter of the surface of the first inner ring 131 that contacts the first mating surface 121 can be set to gradually increase along the axial direction from right to left.

[0040] The surface where the second inner ring 141 contacts the second mating surface 122 is the inner mounting surface of the second tapered roller bearing 14. By gradually changing the diameter of the surface where the second inner ring 141 contacts the second mating surface 122 along the axial direction of the main shaft 12, the inner mounting surface of the second tapered roller bearing 14 can be made tapered. Simultaneously, the second mating surface 122 of the main shaft 12 is also tapered, which increases the interference fit between the second tapered roller bearing 14 and the main shaft, improving the tightness of the fit. In practice, the diameter of the surface where the second inner ring 141 contacts the second mating surface 122 can be gradually increased or decreased along the axial direction of the main shaft 12. The trend of change can be determined according to the installation direction of the second tapered roller bearing 14. For example, Figure 2 If the second tapered roller bearing 14 shown is assembled along the axial direction from right to left, then the diameter of the surface of the second inner ring 141 that contacts the second mating surface 122 can be set to gradually increase along the axial direction from right to left.

[0041] To ensure a tight fit between the bearing and the spindle 12, and to increase the interference fit between the bearing inner ring and the spindle 12, the mating surface where the bearing inner ring contacts the spindle is tapered. This means the contact surfaces of the bearing inner ring and the spindle 12 have a gradually changing diameter. The tapered shape acts as a guide, ensuring the spindle bearing is properly seated on the spindle 12 and that the bearing inner ring forms a tight fit with the spindle 12. This prevents relative slippage between the spindle 12 and the spindle bearing, which could affect the operational stability of the spindle 12.

[0042] When the inner ring of the spindle bearing is tapered, the minimum size of the inner ring can be controlled, thereby controlling the minimum wall thickness. During assembly of the spindle bearing with the spindle 12, the deformation at the smaller parts of the inner ring can be controlled, preventing excessive deformation during assembly due to the thinner wall thickness, and thus ensuring a tight fit between the inner ring and the spindle mating surfaces.

[0043] In some embodiments, the minimum distance between the first inner ring 131 and the first outer ring 132 is greater than the minimum distance between the second inner ring 141 and the second outer ring 142, and the maximum distance between the first inner ring 131 and the first outer ring 132 is greater than the maximum distance between the second inner ring 141 and the second outer ring 142.

[0044] In other words, the inner and outer rings of the spindle bearings at different positions have different distances. The space between the inner and outer rings is used to accommodate the tapered rollers. By controlling the distance between the inner and outer rings, the size of the tapered rollers inside the bearing can be controlled, thereby controlling the load-bearing capacity of the spindle bearings at different positions.

[0045] In practice, the minimum diameter of the first tapered roller 133 is larger than the minimum diameter of the second tapered roller 143, and the maximum diameter of the first tapered roller 133 is larger than the maximum diameter of the second tapered roller 143. By using different sizes of the tapered rollers in different bearings, differentiated support capabilities can be achieved. For the first tapered roller bearing 13, which is close to the wind turbine, the load it experiences is relatively large when the wind turbine rotates. Therefore, a main shaft bearing with larger tapered rollers can be used to distribute the load.

[0046] In some embodiments, the minimum inner diameter of the first inner ring 131 may be greater than the maximum inner diameter of the second inner ring 141.

[0047] The inner diameter of the bearing inner ring defines the diameter of the mating surface on the main shaft where the bearing can be assembled. By controlling the inner diameter of the bearing inner ring at different locations, proper assembly of bearings at different positions can be ensured, avoiding interference. Simultaneously, a larger first tapered roller bearing 13 can be used to distribute the load on the main shaft 12 near the impeller.

[0048] like Figure 2 and Figure 3 As shown, the inner diameter of the first inner ring 131 of the first tapered roller bearing 13 is relatively large, allowing it to smoothly pass over the second mating surface 122 of the main shaft 12 and reach the first mating surface 121, forming a tight fit with the first mating surface 121. In contrast, the inner diameter of the second inner ring 141 of the second tapered roller bearing 14 is relatively small, and it can be confined to the position of the second mating surface 122 of the main shaft 12.

[0049] In some embodiments, the taper of the surface of the first inner ring 131 that contacts the first mating surface 121 is smaller than the taper of the surface of the first inner ring 131 that is close to the first outer ring 132, and the taper of the surface of the second inner ring 141 that contacts the second mating surface 122 is smaller than the taper of the surface of the second inner ring 141 that is close to the second outer ring 142.

[0050] In other words, the two sides of the first inner ring 131 have different tapers, and the surface of the first inner ring 131 that contacts the first mating surface 121 of the main shaft 12 has a smaller taper, resulting in a smaller change in diameter. This allows for control over the wall thickness differences at various points on the first inner ring 131 while ensuring a smoother change in the inner diameter of the first inner ring 131. This prevents the first inner ring 131 from becoming too loose when mating with the main shaft, thus avoiding easy slippage of the first tapered roller bearing 13 and ensuring the normal operation of the main shaft 12.

[0051] The two sides of the second inner ring 141 have different tapers. The surface of the second inner ring 141 that contacts the second mating surface 122 of the main shaft 12 has a smaller taper, and the effect of the diameter variation on the wall thickness is negligible. A tapered fit is formed, and variable interference can be achieved through taper angle deviation, improving the tightness of the fit.

[0052] In some embodiments, the dimension of the first inner ring 131 along the radial direction of the main shaft 12 corresponds to the wall thickness of the first inner ring 131, and the dimension of the first outer ring 132 along the radial direction of the main shaft 12 corresponds to the wall thickness of the first outer ring 132. By making the minimum wall thickness of the first inner ring 131 greater than the minimum wall thickness of the first outer ring 132, the structural strength of the rotating portion of the inner ring can be ensured, that is, the structural strength of the portion of the first tapered roller bearing 13 that mates with the main shaft can be ensured, so that the first inner ring 131 can form an interference fit with the main shaft 12 with a large interference amount, while controlling its own deformation.

[0053] In some embodiments, the dimension of the second inner ring 141 along the radial direction of the main shaft 12 corresponds to the wall thickness of the second inner ring 141, and the dimension of the second outer ring 142 along the radial direction of the main shaft 12 corresponds to the wall thickness of the second outer ring 142. By making the minimum wall thickness of the second inner ring 141 greater than the minimum wall thickness of the second outer ring 142, the structural strength of the rotating portion of the inner ring can be ensured, that is, the structural strength of the portion of the second tapered roller bearing 14 that mates with the main shaft can be ensured, so that the second inner ring 141 can form an interference fit with the main shaft 12 with a large interference amount, while controlling its own deformation.

[0054] In some embodiments, along the axial direction of the main shaft 12, the length of the first inner ring 131 is greater than the length of the first outer ring 132, and the length of the second inner ring 141 is greater than the length of the second outer ring 142.

[0055] By making the length of the inner ring of the spindle bearing greater than the length of the outer ring, the inner ring can form a wider range of fit with the spindle 12, ensuring a tight fit between the inner ring and the spindle 12. At the same time, it reduces the material used for the outer ring and enables convenient assembly of the outer ring and the bearing housing 11.

[0056] In some embodiments, along the axial direction of the main shaft 12, the diameter of the surface of the first outer ring 132 that contacts the first mounting surface 112 gradually changes, and the diameter of the surface of the second outer ring 142 that contacts the second mounting surface 113 gradually changes.

[0057] In other words, the portion of the outer ring of the first tapered roller bearing 13 that mates with the bearing housing 11, and the portion of the outer ring of the second tapered roller bearing 14 that mates with the bearing housing 11, also adopt a tapered shape. When the spindle bearing mates with the bearing housing 11, a tapered surface can also be used to guide the assembly, ensuring tightness and preventing slippage between the spindle bearing and the bearing housing 11. In this way, a relatively tight fit can be achieved between the inner and outer rings of the spindle bearing, resulting in more uniform stress on both rings and ensuring the stability of the spindle bearing during long-term use.

[0058] The mating surface of the spindle and the inner ring of the tapered roller bearing are tapered, with the diameter gradually increasing along the installation direction of the spindle bearing.

[0059] It is also possible to have a slight difference between the outer diameter at the spindle mating surface and the taper angle of the assembly surface on the inner side of the spindle bearing, so as to achieve variable interference fit along the axial direction.

[0060] In addition, the mounting surface on the wall of the mounting hole 111 of the bearing housing 11 and the assembly surface of the outer ring of the tapered roller bearing can be tapered, with the diameter gradually decreasing from large to small along the installation direction of the main shaft bearing.

[0061] When the inner ring assembly surface, outer ring assembly surface, spindle mating surface, and bearing housing mounting surface of the spindle bearing are all cylindrical surfaces, measures such as thickening or widening the bearing ring wall and increasing the rigidity of the surrounding structure are used to reduce the risk of slippage. However, adopting overall thickening and widening designs will result in larger bearing and system dimensions and higher costs.

[0062] Furthermore, the mating surface pressure between the inner ring and the spindle is related to the bearing ring wall thickness, and slippage is prone to occur in localized areas where the wall thickness is smaller. The mating surface pressure is also related to the interference fit, which is limited by the heating and installation temperature and alignment safety margin; therefore, simply increasing the wall thickness will not increase the interference fit. Moreover, with the same interference fit at the mating surfaces, even if the circumferential stress of the raceway at thicker wall locations has not yet reached its upper limit, the mating surface pressure cannot be increased.

[0063] The tapered hole design in the middle of the inner ring can make the inner ring wall thickness of the spindle bearing more uniform, increase the minimum cross-sectional thickness of the inner ring, and reduce the difficulty of installation and alignment, so as to form a larger interference fit when assembled with the spindle 12.

[0064] The cone angle of the inner mounting surface of a tapered roller bearing can be less than or equal to the angle of the outer raceway, while meeting the minimum angle requirements for interference fit. This allows for a smaller difference in the wall thickness of the bearing rings, making it suitable for spindle bearings where the inner ring is mounted from the larger end face. In practice, the raceway angle is generally within 23°, and the cone angle of the inner mounting surface of the tapered roller bearing can range from 3° to 15°.

[0065] The cone angle of the inner mounting surface of a tapered roller bearing can also be set to a very small cone angle, such as 0.1° to 0.2°. In this case, the effect of the cone angle on the wall thickness is negligible, and it is mainly used to achieve variable interference fit and meet the requirements of convenient tapered installation. It is suitable for spindle bearings in which the inner ring is installed from the small end face.

[0066] When the inner ring of the spindle bearing is fitted with a tapered bore to the spindle 12, the minimum wall thickness of the inner ring can be increased while maintaining the maximum bearing capacity and the maximum wall thickness of the inner ring. This is beneficial for application, material selection, and production machinability.

[0067] Similarly, the tapered design of the outer mounting surface of the outer ring can make the outer ring wall thickness of the spindle bearing more uniform, increase the minimum cross-sectional thickness of the outer ring, and reduce the difficulty of installation and alignment, so as to form a tighter fit when assembled with the bearing housing 11.

[0068] When the outer ring of the spindle bearing is fitted with a tapered mounting surface to the bearing housing 11, the fitting pressure between the outer ring and the bearing housing 11 is higher under the same system constraints; while under the same fitting pressure, the size and weight of the spindle bearing are smaller. The tapered mounting surface also makes installation easier.

[0069] In one example: The surface of the spindle bearing that contacts the spindle 12 is a 6° tapered surface. The minimum wall thickness of the inner ring is increased by 25mm, and the interference fit between the inner ring and the spindle 12 can be increased by 0.12mm to 0.15mm. Under the maximum interference fit, the local maximum circumferential stress in the raceway inside the spindle bearing remains unchanged, ensuring reliable application. Under the minimum interference fit, the average mating surface pressure between the bearing inner ring and the spindle 12 increases by 2.6MPa, and the local minimum mating surface pressure increases by 3.8MPa, which improves the tightness of the fit between the spindle bearing and the spindle 12.

[0070] The surface of the spindle bearing that contacts the spindle 12 has a 0.1° tapered surface, allowing for variable interference fit. The inner ring wall thickness remains constant at its minimum and increases by 0.1 mm at its maximum. Under maximum interference fit, the local maximum circumferential stress in the internal raceway of the spindle bearing remains unchanged, ensuring reliable application. Under minimum interference fit, the average mating surface pressure between the bearing inner ring and the spindle 12 increases by 0.4 MPa, improving the tightness of the fit between the spindle bearing and the spindle 12.

[0071] Some embodiments of this application also provide a wind turbine generator, which includes the shaft system structure described above.

[0072] Wind turbines generate electricity by rotating blades, which drive the main shaft. Power is then transmitted through a gearbox, which in turn drives the generator's rotor. The main shaft is a crucial component for power transmission. It is mounted on bearing housings via main shaft bearings, which are lubricated during operation to ensure smooth rotation of the main shaft.

[0073] The spindle bearing engages with the spindle using a tapered mounting surface, forming a contact surface whose diameter varies along the spindle's axial direction. This tapered mounting surface ensures a tight fit between the spindle bearing and the spindle, thereby guaranteeing stable support and ensuring the spindle's operational stability.

[0074] In practice, wind turbines can be installed on land or sea, with the base forming the installation foundation. Tower-type, lattice-type, or hybrid towers can be fixed to the base to form an installation platform for arranging the wind turbines, allowing them to harvest wind energy at a suitable altitude.

[0075] Those skilled in the art will understand that the above embodiments are specific implementations of this application, and in practical applications, various changes can be made in form and detail without departing from the spirit and scope of this application.

Claims

1. A tapered roller bearing, characterized in that, include: A tapered roller bearing includes an inner ring and an outer ring, as well as tapered rollers and a cage located between the inner ring and the outer ring. The intersection of the generatrix of the raceway surface of the inner ring and the generatrix of the raceway surface of the outer ring is located on the central axis of the tapered roller bearing. The inner diameter surface of the inner ring is a tapered surface, and the inner diameter of the inner ring gradually decreases from the end with the larger outer diameter to the end with the smaller outer diameter.

2. The tapered roller bearing according to claim 1, characterized in that, The inner diameter taper angle of the inner ring is 3-15°.

3. The tapered roller bearing according to claim 1, characterized in that, The outer diameter surface of the outer ring is a conical surface, and the outer diameter of the outer ring gradually decreases from the end with the larger inner diameter to the end with the smaller inner diameter.

4. The novel tapered roller bearing according to claim 3, characterized in that, The outer diameter taper angle of the outer ring is 3-15°.

5. A shaft system structure, characterized in that, The invention includes a bearing housing, a shaft, and a tapered roller bearing as described in any one of claims 1 to 4, wherein the shaft is rotatably connected to the bearing housing via the tapered roller bearing.

6. The shaft system structure according to claim 5, characterized in that, The diameter changes of the mating surface between the shaft and the inner ring are consistent with the diameter changes of the inner diameter surface of the inner ring, and the diameter changes of the mating surface between the bearing housing and the outer ring are consistent with the diameter changes of the outer diameter surface of the outer ring.

7. The shaft system structure according to claim 5, characterized in that, The taper deviation between the mating surface of the shaft and the inner ring and the inner diameter surface of the inner ring shall not exceed 0.2°, and the taper deviation between the mating surface of the bearing housing and the outer ring and the outer diameter surface of the outer ring shall not exceed 0.2°.

8. A wind turbine generator, characterized in that, Includes the shaft system structure as described in any one of claims 5 to 7.

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