Wind driven generator bearing cooling mechanism and method

Abstract

The invention relates to a wind driven generator bearing cooling mechanism and method.The cooling mechanism comprises a cooling cavity, a bearing oil inlet pipeline and a bearing oil outlet pipeline; the cooling cavity comprises a bearing oil inlet hole, a bearing oil outlet hole, an oil distribution channel, a branch oil channel and an oil spraying channel, the bearing oil inlet hole, the bearing oil outlet hole and the oil distribution channel are communicated, the branch oil channel is communicated with the oil distribution channel, one end of the oil spraying channel is communicated with the branch oil channel through an auxiliary oil channel, and the other end of the oil spraying channel is communicated with the oil spraying ring groove; the two ends of the bearing oil inlet pipeline are connected and communicated with the bearing oil inlet hole and the output end of the heat exchanger respectively, and the two ends of the bearing oil outlet pipeline are connected and communicated with the bearing oil outlet hole and the gearbox oil outlet pipeline respectively. According to the technical scheme, the production cost can be saved, the heat dissipation efficiency and the heat dissipation effect of the bearing can be improved, it is guaranteed that the temperature of the bearing is kept within the normal operation temperature range of the bearing, and normal operation of a high-power generator is met.

Description

Technical Field

[0001] This invention relates to the field of generators, and more particularly to a wind turbine bearing cooling mechanism and method. Background Technology

[0002] A generator is a mechanical device that converts mechanical energy into electrical energy. In recent years, the technical route of wind turbines has increasingly tended towards semi-direct drive generators and high-speed doubly-fed generators.

[0003] In the existing high-speed doubly fed drive train, the rotor shaft 4 of the generator 2 is fixedly connected to the inner ring 53 of the bearing 5. The outer side of the outer ring 54 of the bearing 5 at the DE end (generator drive end) of the generator 2 is connected to the DE end cover 9 of the generator 2 through the outer end cover 56 of the bearing. The inner side of the outer ring 54 of the bearing 5 is connected to the DE end cover 9 of the generator 2 through the inner end cover 57 of the bearing. The rotor shaft 4 is coaxially connected to the output shaft 35 of the gearbox 3 through the coupling 36. The gearbox 3 is equipped with a lubricating oil cooling system, which includes a gearbox oil inlet pipe 31, a gearbox oil outlet pipe 32, an oil pump 33, and a heat exchanger 34. The oil pump 33 pumps the lubricating oil into the gearbox 3 through the gearbox oil inlet pipe 31 and the heat exchanger 34. The lubricating oil then enters the heat exchanger 34 from the gearbox oil outlet pipe 32. After being cooled by heat exchange in the heat exchanger 34, the lubricating oil is pumped into the gearbox 3 by the oil pump 33.

[0004] The power demand on generators is increasing, especially for high-speed doubly-fed wind turbines. The size of the generator rotor is growing, and the bearings are also becoming larger. This increases bearing friction and wear, and places higher demands on heat dissipation. If the bearings are not cooled effectively and promptly, their temperature will rise continuously. When the bearing temperature exceeds the permissible operating temperature, it will lead to bearing failure and affect the normal operation of the generator.

[0005] Traditionally, the bearing transfers heat to the generator end cover and bearing cover through the space inside the bearing, and then dissipates some of the heat to the outside air of the generator through thermal radiation; some heat can also be carried away by the lubricating grease through convection inside the bearing; and some heat is dissipated by heat exchange between the bearing end cover and the air inside the generator.

[0006] Regarding the aforementioned technologies, the inventors believe that although grease can carry away some heat in traditional bearing heat dissipation methods, grease mainly plays a lubricating role and dissipates heat only through thermal radiation and heat exchange. Moreover, grease has poor fluidity, and heat is carried away very slowly through grease. Therefore, traditional heat dissipation efficiency and heat dissipation effect are low and cannot meet the safe operation requirements of the main shaft bearing of high-power generators. If additional cooling is required for the bearing, an extra cooling system is needed to pump coolant into the bearing, which increases production costs.

[0007] Therefore, there is an urgent need for a cooling mechanism that can save production costs, improve bearing heat dissipation efficiency and effect, and ensure that the bearing temperature is kept within the normal operating temperature range to meet the normal operation requirements of high-power generators. Summary of the Invention

[0008] To address the aforementioned technical problems, this application provides a wind turbine bearing cooling mechanism and method.

[0009] In one aspect, this application provides a wind turbine bearing cooling mechanism.

[0010] The wind turbine bearing cooling mechanism provided in this application adopts the following technical solution: A wind turbine bearing cooling mechanism includes a cooling chamber, a bearing oil inlet pipe, and a bearing oil outlet pipe; The inner circumferential surface of the inner ring of the bearing is fixedly connected to the outer circumferential surface of the rotor shaft, and the outer circumferential surface of the outer ring of the bearing is in contact with the inner circumferential surface of the DE end cover of the generator; the two ends of the bearing axially are respectively provided with an outer end cover and an inner end cover, the end face of the outer end cover near the inner end cover is in contact with the end face of the DE end cover away from the inner end cover, and the end face of the outer ring of the bearing away from the inner end cover; the end face of the inner end cover near the outer end cover is in contact with the end face of the DE end cover away from the outer end cover, and the end face of the outer ring of the bearing away from the outer end cover; the outer end cover of the bearing is fixedly connected to the DE end cover, and the inner end cover of the bearing is fixedly connected to the DE end cover. An oil slinger ring plate is provided on the inner side of the outer end cover of the bearing along its axial direction. The inner circumferential surface of the oil slinger ring plate is fixedly connected to the outer circumferential surface of the rotor shaft. An oil slinger ring groove is provided between the outer circumferential surface of the oil slinger ring plate and the inner circumferential surface of the outer end cover of the bearing. The oil slinger ring groove is connected to the annular raceway of the bearing. The end face of the oil slinger ring plate near the inner end cover of the bearing is in contact with the end face of the inner ring of the bearing away from the inner end cover. The outer end cover of the bearing is provided with a sealing end cover at the end away from the inner end cover of the bearing. The sealing end cover is fixedly connected to the outer end cover of the bearing and rotatably connected to the oil slinger ring plate. There is a first labyrinth sealing structure between the sealing end cover and the oil slinger ring plate for sealing the end of the oil slinger ring groove away from the inner end cover of the bearing. A sealing ring plate is provided on the inner side of the bearing inner end cover along its axial direction. The inner circumferential surface of the sealing ring plate is fixedly connected to the outer circumferential surface of the rotor shaft. An oil injection ring groove is provided between the inner circumferential surface of the sealing ring plate and the inner circumferential surface of the bearing inner end cover. The oil injection ring groove communicates with the annular raceway of the bearing. The end face of the sealing ring plate near the bearing outer end cover is in contact with the end face of the bearing inner ring away from the bearing outer end cover. The sealing ring plate is rotatably connected to the bearing inner end cover. A second labyrinth seal structure is provided between the sealing ring plate and the bearing inner end cover for sealing the end of the oil injection ring groove away from the bearing outer end cover. The cooling chamber includes a bearing oil inlet, a bearing oil outlet, a distribution oil channel, a branch oil channel, and an injection oil channel. The bearing oil inlet is located on the peripheral side wall of the DE end cover, and the bearing oil outlet is located on the end face of the sealing end cover. The bearing oil outlet is connected to the oil slinger groove. The distribution oil channel is located on the inner peripheral surface of the DE end cover, and the bearing oil inlet, bearing oil outlet, and distribution oil channel are connected. The branch oil passage is located on the side where the DE end cover connects to the inner end cover of the bearing, and the branch oil passage is connected to the distribution oil passage. The oil injection passage is located on the inner end cover of the bearing near the outer end cover of the bearing. One end of the oil injection passage is connected to the branch oil passage through an auxiliary oil passage, and the other end of the oil injection passage is connected to the oil injection ring groove. One end of the bearing oil inlet pipe is fixedly connected to the bearing oil inlet hole, and the other end of the bearing oil inlet pipe is connected and communicated with the output end of the heat exchanger. One end of the bearing oil outlet pipe is fixedly connected to the bearing oil outlet hole, and the other end of the bearing oil outlet pipe is connected and communicated with the gearbox oil outlet pipe. The heat exchanger is located above the bearing oil inlet hole, and the gearbox oil outlet pipe is located below the bearing oil outlet hole.

[0011] By adopting the above technical solution, the generator bearings are cooled by utilizing the lubricating oil, heat exchanger, and oil pump of the gearbox cooling system. This eliminates the need for an additional cooling system that pumps coolant; the gearbox's lubricating oil cooling system can efficiently dissipate heat from the bearings, saving production costs. Furthermore, the fluidity of lubricating oil is greater than that of grease, improving both lubrication and heat dissipation efficiency. This allows for the rapid and timely removal of heat from the bearings, and, combined with the heat exchanger's cooling function, ensures that the bearing temperature remains within the normal operating range, meeting the requirements for the normal operation of high-power generators.

[0012] Preferably, multiple branch oil passages are equidistantly arranged along the circumference of the DE end cover, and all branch oil passages are connected to the distribution oil passages.

[0013] By adopting the above technical solution, the uniformity of bearing cooling and the cooling effect of bearing are improved by the branch oil passages evenly distributed along the circumference of the DE end cover.

[0014] Preferably, multiple oil injection channels are equidistantly arranged along the circumference of the inner end cover of the bearing. Each oil injection channel corresponds to a branch oil channel. One end of each oil injection channel is connected to the corresponding branch oil channel through an auxiliary oil channel, and the other end of all oil injection channels is connected to the oil injection ring groove.

[0015] By adopting the above technical solution, the uniformity of bearing cooling and the cooling effect are further improved by using oil spray channels that are evenly distributed circumferentially along the inner end cover of the bearing.

[0016] Preferably, the bearing includes a first bearing body and a second bearing body that are fitted together. The outer diameter of the first bearing body is larger than the outer diameter of the second bearing body. The first bearing body is fitted with the outer end cap of the bearing, and the second bearing body is fitted with the inner end cap of the bearing. The annular raceway of the first bearing body is connected to the annular raceway of the second bearing body. The oil slinger groove is connected to the annular raceway of the first bearing body, and the oil spraying groove is connected to the annular raceway of the second bearing body.

[0017] By adopting the above technical solution, the bearing is set as a first bearing body and a second bearing body that fit together, and the two have different outer diameters to distribute the load of the rotor shaft. The first bearing body fits with the outer end cover of the bearing, and the second bearing body fits with the inner end cover of the bearing, which can meet the structural requirements of the DE end cover installation space. Meanwhile, the annular raceway of the first bearing housing is connected to the annular raceway of the second bearing housing, and the oil slinger groove is connected to the annular raceway of the first bearing housing, and the oil spraying groove is connected to the annular raceway of the second bearing housing, so that the lubricating oil can flow smoothly in the annular raceways of the two bearing housings. Together with the oil distribution channel, it can dissipate heat and cool the entire bearing, thereby improving the heat dissipation effect of the entire bearing.

[0018] Preferably, the first labyrinth seal structure includes a first sealing protrusion and a first sealing groove. The first sealing protrusion is coaxially connected to the end face of the oil slinger plate away from the inner end cover of the bearing. The first sealing groove is coaxially formed on the end face of the sealing end cover near the inner end cover of the bearing. The first sealing protrusion passes into the first sealing groove. There is a first sealing gap between the first sealing protrusion and the first sealing groove, which allows the oil slinger plate and the sealing end cover to rotate relative to each other. The first sealing gap is labyrinth-shaped and communicates with the oil slinger groove.

[0019] By adopting the above technical solution, the cooperation between the first sealing protrusion and the first sealing groove forms a first sealing gap in a labyrinth shape, which provides dynamic sealing and pressure resistance without affecting the relative rotation between the oil slinger plate and the sealing end cover, constructs an efficient sealing structure, maximizes the sealing effect, effectively blocks the leakage of lubricating oil from the oil slinger groove, improves the sealing performance of the oil circuit and the recycling rate of lubricating oil, ensures the efficiency and continuity of the cooling cycle, improves the heat dissipation effect of the bearing, and the first labyrinth sealing structure also avoids the pollution of the working environment by oil and oil-gas mixture.

[0020] Preferably, the second labyrinth sealing structure includes a second sealing protrusion and a second sealing groove. The second sealing protrusion is coaxially connected to the end face of the sealing ring plate away from the outer end cover of the bearing, the second sealing groove is coaxially formed on the end face of the inner end cover of the bearing close to the outer end cover of the bearing, the second sealing protrusion penetrates into the second sealing groove, and there is a second sealing gap for the relative rotation between the sealing ring plate and the inner end cover of the bearing between the second sealing protrusion and the second sealing groove. The second sealing gap is in a labyrinth shape and is connected to the oil injection ring groove.

[0021] By adopting the above technical solution, the cooperation between the second sealing protrusion and the second sealing groove forms a second sealing gap in a labyrinth shape, which provides dynamic sealing and pressure resistance without affecting the relative rotation between the sealing ring plate and the inner end cover of the bearing, constructs an efficient sealing structure, maximizes the sealing effect, effectively blocks the leakage of lubricating oil from the oil injection ring groove, improves the sealing performance of the oil circuit and the recycling rate of lubricating oil, ensures the efficiency and continuity of the cooling cycle, improves the heat dissipation effect of the bearing, and the second labyrinth sealing structure also avoids the entry of oil and oil-gas mixture into the generator with negative pressure to protect the generator.

[0022] Preferably, the second sealing protrusion is in a "卜" shape, and the surface of the second sealing protrusion close to the outer end cover of the bearing protrudes out of the second sealing groove.

[0023] By adopting the above technical solution, the design of the protruding part extends the anti-overflow and anti-leakage path of the lubricating oil, further improves the dynamic sealing effect, and can more effectively block the leakage of lubricating oil from the oil injection ring groove.

[0024] Preferably, the oil slinger groove is arranged in a gradually expanding manner from the direction close to the rotor shaft to the direction away from the rotor shaft.

[0025] By adopting the above technical solution, it avoids the accumulation of lubricating oil in the oil slinger groove causing overflow and ensures the smooth oil outlet path of the lubricating oil.

[0026] Preferably, the outer end cover of the bearing has a first inclined surface on the side near the rotor shaft, and the oil slinger ring plate has a second inclined surface on the side away from the rotor shaft. There is an anti-overflow gap between the first inclined surface and the second inclined surface. The anti-overflow gap is inclined from the direction near the rotor shaft to the direction away from the rotor shaft towards the direction away from the inner end cover of the bearing. The anti-overflow gap is connected to the oil slinger ring groove and the annular raceway of the bearing. The outer end cover of the bearing is also provided with an anti-overflow convex ring on the side near the rotor shaft. There is an oil discharge gap between the anti-overflow convex ring and the oil slinger plate. The oil discharge gap is located at the end of the anti-overflow gap near the rotor shaft and is connected to the anti-overflow gap.

[0027] By adopting the above technical solution, the coordination between the oil discharge gap and the anti-overflow gap guides the lubricating oil in the annular raceway of the first bearing body to smoothly enter the oil slinger groove, while preventing the lubricating oil in the oil slinger groove from splashing back into the annular raceway of the first bearing body, ensuring the normal operation of the cooling cycle and preventing hot lubricating oil from affecting the heat dissipation and cooling of the first bearing body.

[0028] Secondly, this application provides a method for cooling wind turbine bearings.

[0029] This application provides a method for cooling wind turbine bearings, which includes the following steps: S1. Tighten the threaded connection between one end of the bearing oil inlet pipe and the connecting pipe head at the bearing oil inlet hole, and tighten the threaded connection between the other end of the bearing oil inlet pipe and the connecting pipe head at the heat exchanger output end. S2. Tighten the threaded connection between one end of the bearing oil outlet pipe and the connecting pipe head at the bearing oil outlet hole, and tighten the threaded connection between the other end of the bearing oil outlet pipe and the connecting pipe head at the gearbox oil outlet pipe. S3. Driven by the oil pump, lubricating oil enters the distribution oil channel from the heat exchanger through the bearing oil inlet pipe and bearing oil inlet hole. The lubricating oil in the distribution oil channel can perform initial heat dissipation and cooling on the first bearing body. The lubricating oil continues to enter the annular raceway of the second bearing body through the branch oil channel, auxiliary oil channel, oil injection channel, and oil injection ring groove, where it performs heat dissipation and cooling on the second bearing body. The lubricating oil in the annular raceway of the second bearing body then enters the annular raceway of the first bearing body for secondary cooling. The lubricating oil in the annular raceway of the first bearing body enters the oil slinger ring groove through the oil discharge gap and anti-overflow gap. The lubricating oil in the oil slinger ring groove then enters the bearing oil outlet pipe from the bearing oil outlet hole. The oil pump draws the hot lubricating oil in the bearing oil outlet pipe to the heat exchanger. After being cooled by heat exchange in the heat exchanger, the lubricating oil enters the bearing body through the bearing oil inlet pipe, and the cycle continues.

[0030] By adopting the above technical methods, the installation steps of the oil pipeline between the generator and the gearbox are simple and convenient, and the connection is firm and has good sealing performance. By utilizing the gearbox's lubricating oil cooling system, the lubricating oil is cooled by heat exchanger before entering the bearing, providing efficient heat dissipation and cooling to the bearing, thus significantly improving the heat dissipation efficiency and effectiveness of the bearing. The lubricating oil in the gearbox is recycled, and the cooled lubricating oil continues to circulate and act on the bearings. This not only saves production costs, but also enables continuous heat dissipation and cooling of the bearings, ensuring that the bearing temperature remains stable within the normal operating range and meeting the long-term operating requirements of high-power generators.

[0031] In summary, this application includes at least one of the following beneficial technical effects: 1. By utilizing the lubricating oil, heat exchanger, and oil pump of the gearbox cooling system, the generator bearings are cooled, eliminating the need for an additional cooling system that pumps coolant. The gearbox's lubricating oil cooling system can efficiently dissipate heat from the bearings, saving production costs. 2. Lubricating oil has a higher fluidity than lubricating grease, which improves lubrication and heat dissipation efficiency, allowing the heat of the bearing to be dissipated quickly and promptly. Combined with the heat exchanger's cooling function, it ensures that the bearing temperature is kept within the normal operating temperature range, meeting the requirements for the normal operation of high-power generators. 3. The first labyrinth seal structure seals the oil slinger groove, and the second labyrinth seal structure seals the oil spraying ring groove. This not only prevents lubricating oil leakage that could lead to waste and pollution, but also maintains stable pressure within the oil circuit, ensuring efficient cooling circulation. Attached Figure Description

[0032] Figure 1 This is a schematic diagram of the overall structure of the generator and gearbox sharing a single lubricating oil cooling system, as shown in the embodiments of this application.

[0033] Figure 2 This is a structural schematic diagram from another perspective used in the embodiments of this application to illustrate that the generator and gearbox share a common lubricating oil cooling system.

[0034] Figure 3 This is an overall cross-sectional view of the wind turbine bearing cooling mechanism shown in the embodiments of this application.

[0035] Figure 4 This is used to illustrate the embodiments of this application. Figure 3 A magnified structural diagram of point A in the middle.

[0036] Figure 5 This is used to illustrate the embodiments of this application. Figure 4 A magnified structural diagram of point A1 in the middle.

[0037] Figure 6 This is used to illustrate the embodiments of this application. Figure 4 A magnified structural diagram at point A2 in the middle.

[0038] Figure 7 This is a schematic diagram of the planar structure of the end face of the DE end cover near the outer end cover of the bearing in an embodiment of this application.

[0039] Figure 8 This is used to illustrate the embodiments of this application. Figure 7 Sectional view along the BB direction.

[0040] Figure 9 This is a schematic diagram of the planar structure of the end face of the DE end cover near the inner end cover of the bearing in an embodiment of this application.

[0041] Figure 10 This is used to illustrate the embodiments of this application. Figure 9 A cross-sectional view along the CC direction.

[0042] Figure 11 This is a schematic diagram of the planar structure of the end face of the inner end cover of the bearing near the outer end cover of the bearing, as shown in the embodiments of this application.

[0043] Figure 12 This is used to illustrate the embodiments of this application. Figure 11 A sectional view along the DD direction.

[0044] Figure 13 This is used to illustrate the embodiments of this application. Figure 11 A cross-sectional view along the EE direction.

[0045] Explanation of reference numerals in the attached diagram: 1. Cooling chamber; 11. Bearing oil inlet; 12. Bearing oil outlet; 13. Branch oil passage; 14. Branch oil passage; 15. Injection oil passage; 16. Auxiliary oil passage; 2. Generator; 21. Bearing oil inlet pipe; 22. Bearing oil outlet pipe; 3. Gearbox; 31. Gearbox oil inlet pipe; 32. Gearbox oil outlet pipe; 33. Oil pump; 34. Heat exchanger; 35. Output shaft; 36. Coupling; 4. Rotor shaft; 5. Bearing; 51. First bearing housing; 52. Second bearing housing; 53. Inner ring; 54. Outer ring; 5 5. Annular raceway; 56. Outer end cap of bearing; 561. Anti-overflow protrusion ring; 562. Oil discharge gap; 57. Inner end cap of bearing; 6. Oil slinger ring plate; 61. Oil slinger ring groove; 62. First labyrinth seal structure; 621. First sealing protrusion; 622. First sealing groove; 623. First sealing gap; 624. Anti-overflow gap; 7. Sealing end cap; 8. Sealing ring plate; 81. Oil spray ring groove; 82. Second labyrinth seal structure; 821. Second sealing protrusion; 822. Second sealing groove; 823. Second sealing gap; 9. DE end cap. Detailed Implementation

[0046] The following is in conjunction with the appendix Figure 1-13 This application will be described in further detail.

[0047] This application discloses a wind turbine bearing cooling mechanism and method.

[0048] In a first aspect, embodiments of this application disclose a wind turbine bearing cooling mechanism.

[0049] Reference Figure 1-13 The wind turbine bearing cooling mechanism includes a cooling chamber 1, a bearing oil inlet pipe 21, and a bearing oil outlet pipe 22.

[0050] The inner circumferential surface of the inner ring 53 of bearing 5 is fixedly connected to the outer circumferential surface of rotor shaft 4 by heat fitting or interference fit. The outer circumferential surface of the outer ring 54 of bearing 5 is fixedly connected to the inner circumferential surface of DE end cover 9 of generator 2 by heat fitting or interference fit. Bearing 5 has an outer end cover 56 and an inner end cover 57 coaxially mounted at both ends of its axial direction. The end face of the outer end cover 56 near the inner end cover 57 is fitted with the end face of DE end cover 9 away from the inner end cover 57, and the end face of the outer ring 54 of bearing 5 away from the inner end cover 57. The end face of the inner end cover 57 near the outer end cover 56 is fitted with the end face of DE end cover 9 away from the outer end cover 56, and the end face of the outer ring 54 of bearing 5 away from the outer end cover 56. The outer end cover 56 and DE end cover 9 are fixedly connected by screws, and the inner end cover 57 and DE end cover 9 are fixedly connected by screws.

[0051] An oil slinger ring plate 6 is provided on the inner side of the bearing outer end cover 56 along its axial direction. The inner circumferential surface of the oil slinger ring plate 6 is fixedly connected to the outer circumferential surface of the rotor shaft 4 by heat fitting or interference fit. An oil slinger ring groove 61 is provided between the outer circumferential surface of the oil slinger ring plate 6 and the inner circumferential surface of the bearing outer end cover 56. The oil slinger ring groove 61 communicates with the annular raceway 55 of the bearing 5. The end face of the oil slinger ring plate 6 near the bearing inner end cover 57 is in contact with the end face of the inner ring 53 of the bearing 5 away from the bearing inner end cover 57.

[0052] The oil slinger groove 61 is gradually widened from the direction close to the rotor shaft 4 to the direction far away from the rotor shaft 4, so as to avoid the accumulation of lubricating oil in the oil slinger groove 61 and cause overflow, and ensure that the oil outlet path of the lubricating oil is smooth.

[0053] A sealing end cover 7 is provided at the end of the bearing outer end cover 56 away from the bearing inner end cover 57. The sealing end cover 7 is fixedly connected to the bearing outer end cover 56 by screws, and the sealing end cover 7 is rotatably connected to the oil slinger ring plate 6.

[0054] A sealing ring plate 8 is provided on the inner side of the bearing inner end cover 57 along its axial direction. The inner circumferential surface of the sealing ring plate 8 is fixedly connected to the outer circumferential surface of the rotor shaft 4 by heat fitting or interference fit. An oil injection groove 81 is provided between the inner circumferential surface of the sealing ring plate 8 and the inner circumferential surface of the bearing inner end cover 57, and the oil injection groove 81 communicates with the annular raceway 55 of the bearing 5. The end face of the sealing ring plate 8 near the bearing outer end cover 56 is in contact with the end face of the inner ring 53 of the bearing 5 away from the bearing outer end cover 56. The sealing ring plate 8 is rotatably connected to the bearing inner end cover 57.

[0055] The cooling chamber 1 includes a bearing oil inlet 11, a bearing oil outlet 12, an oil distribution channel 13, a branch oil channel 14, and an oil injection channel 15. The bearing oil inlet 11 is a straight hole and is located on the peripheral side wall of the DE end cover 9. The bearing oil outlet 12 is a straight hole and is located on the end face of the sealing end cover 7. The bearing oil outlet 12 is connected to the oil slinger groove 61. The oil distribution channel 13 is annular and is located on the inner peripheral surface of the DE end cover 9. The bearing oil inlet 11, the bearing oil outlet 12, and the oil distribution channel 13 are connected.

[0056] Branch oil passage 14 is a straight hole and is opened on the side where DE end cover 9 connects to the bearing inner end cover 57. Branch oil passage 14 is connected to the distribution oil passage 13.

[0057] Multiple branch oil passages 14 are equidistantly arranged along the circumference of the DE end cover 9, and all branch oil passages 14 are connected to the distribution oil passages 13. By uniformly distributing branch oil passages 14 along the circumference of the DE end cover 9, the uniformity of cooling of the bearing 5 is improved, and the cooling effect of the bearing 5 is enhanced.

[0058] The oil injection passage 15 is a straight hole located on the inner end cover 57 of the bearing near the outer end cover 56 of the bearing. One end of the oil injection passage 15 is connected to the branch oil passage 14 via the auxiliary oil passage 16, and the other end of the oil injection passage 15 is connected to the oil injection ring groove 81. The auxiliary oil passage 16 is shaped like a "7". One end of the auxiliary oil passage 16 is connected to the branch oil passage 14, and the other end of the auxiliary oil passage 16 is connected to the oil injection passage 15.

[0059] Multiple oil injection channels 15 are equidistantly arranged along the circumference of the inner end cover 57 of the bearing. Each oil injection channel 15 corresponds to a branch oil channel 14. One end of each oil injection channel 15 is connected to the corresponding branch oil channel 14 through an auxiliary oil channel 16, and the other end of all oil injection channels 15 is connected to the oil injection ring groove 81. The uniform distribution of oil injection channels 15 along the circumference of the inner end cover 57 of the bearing further improves the uniformity of cooling of the bearing 5 and further enhances the cooling effect of the bearing 5.

[0060] One end of the bearing oil inlet pipe 21 is fixedly connected to the bearing oil inlet hole 11, and the other end of the bearing oil inlet pipe 21 is connected and communicated with the output end of the heat exchanger 34. One end of the bearing oil outlet pipe 22 is fixedly connected to the bearing oil outlet hole 12, and the other end of the bearing oil outlet pipe 22 is connected and communicated with the gearbox oil outlet pipe 32. The heat exchanger 34 is located above the bearing oil inlet hole 11, and the gearbox oil outlet pipe 32 is located below the bearing oil outlet hole 12, achieving a height difference. The oil pump 33 works in conjunction with the height difference to ensure that the lubricating oil smoothly enters and flows out of the bearing 5.

[0061] By utilizing the lubricating oil, heat exchanger, and oil pump of the gearbox cooling system to dissipate heat and cool the generator bearings, there is no need to set up an additional cooling system that pumps coolant. The gearbox's lubricating oil cooling system can efficiently dissipate heat from the bearings, saving production costs.

[0062] The bearing 5 includes a first bearing body 51 and a second bearing body 52 that are fitted together. The outer diameter of the first bearing body 51 is larger than the outer diameter of the second bearing body 52. ​​The first bearing body 51 is fitted with the outer end cover 56 of the bearing, and the second bearing body 52 is fitted with the inner end cover 57 of the bearing. The annular raceway 55 of the first bearing body 51 is connected to the annular raceway 55 of the second bearing body 52. ​​The oil slinger groove 61 is connected to the annular raceway 55 of the first bearing body 51, and the oil spraying groove 81 is connected to the annular raceway 55 of the second bearing body 52.

[0063] The bearing 5 is configured as a first bearing body 51 and a second bearing body 52 that fit together, with different outer diameters to distribute the load on the rotor shaft 4. The first bearing body 51 fits with the outer end cover 56, and the second bearing body 52 fits with the inner end cover 57, which can meet the structural requirements of the installation space of the DE end cover 9. At the same time, the annular raceway 55 of the first bearing body 51 is connected to the annular raceway 55 of the second bearing body 52, and the oil slinger groove 61 is connected to the annular raceway 55 of the first bearing body 51, and the oil spraying groove 81 is connected to the annular raceway 55 of the second bearing body 52. ​​This allows the lubricating oil to flow smoothly in the annular raceways 55 of the two bearing bodies 5, and together with the oil distribution channel 13, it can achieve heat dissipation and cooling of the entire bearing 5, thereby improving the heat dissipation effect of the entire bearing 5.

[0064] Lubricating oil has a higher fluidity than lubricating grease. While improving lubrication, it also improves heat dissipation efficiency, dissipating the heat from the bearing quickly and efficiently. Combined with the heat exchanger's cooling function, it ensures that the bearing temperature remains within the normal operating temperature range, meeting the requirements for the normal operation of high-power generators.

[0065] A first labyrinth seal structure 62 is provided between the sealing end cap 7 and the oil slinger ring plate 6 to seal the end of the oil slinger ring groove 61 away from the bearing inner end cap 57. The first labyrinth seal structure 62 includes a first sealing protrusion 621 and a first sealing groove 622. The first sealing protrusion 621 is coaxially connected to the end face of the oil slinger ring plate 6 away from the bearing inner end cap 57. The first sealing groove 622 is coaxially opened on the end face of the sealing end cap 7 near the bearing inner end cap 57. The first sealing protrusion 621 passes into the first sealing groove 622. A first sealing gap 623 is provided between the first sealing protrusion 621 and the first sealing groove 622, allowing the oil slinger ring plate 6 and the sealing end cap 7 to rotate relative to each other. The first sealing gap 623 is labyrinth-shaped and communicates with the oil slinger ring groove 61.

[0066] The first sealing protrusion 621 and the first sealing groove 622 cooperate to form a labyrinth-shaped first sealing gap 623. Without affecting the relative rotation of the oil slinger ring 6 and the sealing end cover 7, it provides dynamic sealing and pressure resistance, and constructs a high-efficiency sealing structure to maximize the sealing effect, effectively prevent lubricating oil from leaking from the oil slinger ring groove 61, improve the sealing of the oil circuit and the circulation rate of lubricating oil, ensure the efficiency and continuity of the cooling cycle, improve the heat dissipation effect of the bearing 5, and the first labyrinth sealing structure 62 also avoids oil and oil gas from polluting the working environment.

[0067] The outer end cover 56 of the bearing has a first inclined surface on the side near the rotor shaft 4, and the oil slinger ring plate 6 has a second inclined surface on the side away from the rotor shaft 4. An anti-overflow gap 624 is located between the first and second inclined surfaces. The anti-overflow gap 624 is inclined from the direction near the rotor shaft 4 to the direction away from the rotor shaft 4 towards the direction away from the inner end cover 57 of the bearing. The anti-overflow gap 624 is connected to the oil slinger ring groove 61 and the annular raceway 55 of the bearing 5. The outer end cover 56 of the bearing also has an anti-overflow protruding ring 561 on the side near the rotor shaft 4. An oil discharge gap 562 is located between the anti-overflow protruding ring 561 and the oil slinger ring plate 6. The oil discharge gap 562 is located at the end of the anti-overflow gap 624 near the rotor shaft 4 and is connected to the anti-overflow gap 624.

[0068] The cooperation between the oil discharge gap 562 and the anti-overflow gap 624 guides the lubricating oil in the annular raceway 55 of the first bearing body 51 to smoothly enter the oil slinger groove 61, while preventing the lubricating oil in the oil slinger groove 61 from splashing back into the annular raceway 55 of the first bearing body 51, ensuring the normal operation of the cooling cycle and preventing hot lubricating oil from affecting the heat dissipation and cooling of the first bearing body 51.

[0069] There is a second labyrinth seal structure 82 between the sealing ring plate 8 and the inner end cover 57 of the bearing for sealing one end of the oil injection ring groove 81 away from the outer end cover 56 of the bearing. The second labyrinth seal structure 82 includes a second sealing projection 821 and a second sealing groove 822. The second sealing projection 821 is coaxially connected to the end face of the sealing ring plate 8 away from the outer end cover 56 of the bearing. The second sealing groove 822 is coaxially formed on the end face of the inner end cover 57 of the bearing close to the outer end cover 56 of the bearing. The second sealing projection 821 penetrates into the second sealing groove 822. There is a second sealing gap 823 for the relative rotation of the sealing ring plate 8 and the inner end cover 57 of the bearing between the second sealing projection 821 and the second sealing groove 822. The second sealing gap 823 is in a labyrinth shape and is connected to the oil injection ring groove 81.

[0070] The cooperation of the second sealing projection 821 and the second sealing groove 822 forms a labyrinth-shaped second sealing gap 823, which provides dynamic sealing and pressure resistance, constructs an efficient sealing structure, maximizes the sealing effect, effectively blocks the leakage of lubricating oil from the oil injection ring groove 81, improves the sealing performance of the oil circuit and the recycling rate of lubricating oil, ensures the efficiency and continuity of the cooling cycle, improves the heat dissipation effect of the bearing 5, and the second labyrinth seal structure 82 also prevents oil and oil-gas from entering the generator 2 with negative pressure, protecting the generator 2.

[0071] The second sealing projection 821 is in a "卜" shape, and the side of the second sealing projection 821 close to the outer end cover 56 of the bearing protrudes out of the second sealing groove 822. The design of the protruding part extends the anti-overflow and anti-leakage path of the lubricating oil, further improves the dynamic sealing effect, and can more effectively block the leakage of lubricating oil from the oil injection ring groove 81.

[0072] The first labyrinth seal structure seals the oil slinging ring groove, and the second labyrinth seal structure seals the oil injection ring groove, which not only avoids waste and pollution caused by lubricating oil leakage, but also maintains the pressure stability in the oil circuit, ensuring the efficient progress of the cooling cycle.

[0073] In a second aspect, the embodiment of the present application also discloses a method for cooling a wind turbine bearing.

[0074] A method for cooling a wind turbine bearing provided by the present application includes the following steps: S1. Threadedly connect and tighten one end of the bearing oil inlet pipe 21 with the connecting pipe head at the bearing oil inlet hole 11, and threadedly connect and tighten the other end of the bearing oil inlet pipe 21 with the connecting pipe head at the output end of the heat exchanger 34; S2. Threadedly connect and tighten one end of the bearing oil outlet pipe 22 with the connecting pipe head at the bearing oil outlet hole 12, and threadedly connect and tighten the other end of the bearing oil outlet pipe 22 with the connecting pipe head at the oil outlet pipe 32 of the gearbox; The conventional method of connecting the pipelines by threaded connection makes the installation of the oil pipeline between generator 2 and gearbox 3 simple and convenient, and the connection is firm and has good sealing performance.

[0075] S3. Driven by the oil pump 33, lubricating oil enters the distribution oil passage 13 from the heat exchanger 34 through the bearing oil inlet pipe 21 and the bearing oil inlet hole 11. The lubricating oil in the distribution oil passage 13 can provide initial heat dissipation and cooling for the first bearing body 51. The lubricating oil continues to enter the annular raceway 55 of the second bearing body 52 from the distribution oil passage 13 through the branch oil passage 14, the auxiliary oil passage 16, the oil injection passage 15, and the oil injection ring groove 81, where it provides heat dissipation and cooling for the second bearing body 52. ​​The lubricating oil in the annular raceway 55 of the second bearing body 52 then enters... The first bearing body 51 is subjected to secondary cooling in the annular raceway 55. The lubricating oil in the annular raceway 55 of the first bearing body 51 enters the oil slinger groove 61 through the oil discharge gap 562 and the anti-overflow gap 624. The lubricating oil in the oil slinger groove 61 then enters the bearing oil outlet pipe 22 from the bearing oil outlet hole 12. The oil pump 33 draws the hot lubricating oil in the bearing oil outlet pipe 22 to the heat exchanger 34. After being cooled by heat exchanger 34, the lubricating oil enters the bearing 5 from the bearing oil inlet pipe 21, and so on.

[0076] By utilizing the lubricating oil cooling system of gearbox 3, the lubricating oil is cooled by heat exchanger 34 and then enters the bearing 5 to efficiently dissipate heat and cool the bearing 5, greatly improving the heat dissipation efficiency and effect of the bearing 5.

[0077] The lubricating oil in gearbox 3 is recycled, and the cooled lubricating oil continues to circulate and act on bearing 5. This not only saves production costs, but also enables continuous heat dissipation and cooling of bearing 5, ensuring that the temperature of bearing 5 remains stable within the normal operating range and meeting the long-term operating requirements of high-power generator 2.

[0078] The above are all preferred embodiments of this application, and are not intended to limit the scope of protection of this application. Therefore, all equivalent changes made in accordance with the structure, shape and principle of this application should be covered within the scope of protection of this application.

Claims

1. A wind turbine bearing cooling mechanism, characterized by: The bearing includes a cooling chamber, a bearing oil inlet pipeline, and a bearing oil outlet pipeline. An inner circumferential surface of an inner ring of the bearing is fixedly connected with an outer circumferential surface of the rotor shaft, and an outer circumferential surface of an outer ring of the bearing is attached to an inner circumferential surface of a DE end cover of the generator; the bearing is coaxially provided with a bearing outer end cover and a bearing inner end cover at two axial ends thereof, respectively; an end surface of the bearing outer end cover close to the bearing inner end cover is attached to an end surface of the DE end cover away from the bearing inner end cover and to an end surface of the outer ring of the bearing away from the bearing inner end cover; an end surface of the bearing inner end cover close to the bearing outer end cover is attached to an end surface of the DE end cover away from the bearing outer end cover and to an end surface of the outer ring of the bearing away from the bearing outer end cover; the bearing outer end cover is fixedly connected with the DE end cover, and the bearing inner end cover is fixedly connected with the DE end cover; An oil flinger plate is axially provided on an inner side of the bearing outer end cover; an inner circumferential surface of the oil flinger plate is fixedly connected with the outer circumferential surface of the rotor shaft, and an outer circumferential surface of the oil flinger plate is provided with an oil flinger groove between the inner circumferential surface of the bearing outer end cover; the oil flinger groove is communicated with the annular raceway of the bearing; an end surface of the oil flinger plate close to the bearing inner end cover is attached to an end surface of the inner ring of the bearing away from the bearing inner end cover; An end of the bearing outer end cover away from the bearing inner end cover is provided with a sealing end cover; the sealing end cover is fixedly connected with the bearing outer end cover and rotatably connected with the oil flinger plate; the sealing end cover and the oil flinger plate are provided with a first labyrinth seal structure for sealing an end of the oil flinger groove away from the bearing inner end cover; An inner side of the bearing inner end cover is axially provided with a sealing ring plate; an inner circumferential surface of the sealing ring plate is fixedly connected with the outer circumferential surface of the rotor shaft, and an inner circumferential surface of the sealing ring plate is provided with an oil jet ring groove between the inner circumferential surface of the bearing inner end cover; the oil jet ring groove is communicated with the annular raceway of the bearing; an end surface of the sealing ring plate close to the bearing outer end cover is attached to an end surface of the inner ring of the bearing away from the bearing outer end cover; the sealing ring plate is rotatably connected with the bearing inner end cover; the sealing ring plate and the bearing inner end cover are provided with a second labyrinth seal structure for sealing an end of the oil jet ring groove away from the bearing outer end cover; The cooling chamber includes a bearing oil inlet hole, a bearing oil outlet hole, a distribution oil channel, a branch oil channel, and an oil jet channel; the bearing oil inlet hole is formed on a circumferential wall of the DE end cover; the bearing oil outlet hole is formed on an end surface of the sealing end cover; the bearing oil outlet hole is communicated with the oil flinger groove; the distribution oil channel is formed on an inner circumferential surface of the DE end cover; the bearing oil inlet hole, the bearing oil outlet hole, and the distribution oil channel are communicated; The branch oil channel is formed on a side where the DE end cover is connected with the bearing inner end cover; the branch oil channel is communicated with the distribution oil channel; The oil jet channel is formed on a side of the bearing inner end cover close to the bearing outer end cover; one end of the oil jet channel is communicated with the branch oil channel through an auxiliary oil channel, and the other end of the oil jet channel is communicated with the oil jet ring groove; One end of the bearing oil inlet pipe is fixedly connected to the bearing oil inlet hole, and the other end of the bearing oil inlet pipe is connected and communicated with the output end of the heat exchanger. One end of the bearing oil outlet pipe is fixedly connected to the bearing oil outlet hole, and the other end of the bearing oil outlet pipe is connected and communicated with the gearbox oil outlet pipe. The heat exchanger is located above the bearing oil inlet hole, and the gearbox oil outlet pipe is located below the bearing oil outlet hole.

2. The wind generator bearing cooling mechanism according to claim 1, wherein: A plurality of branch oil channels are equidistantly arranged along the circumferential direction of the DE end cover, and all the branch oil channels are communicated with the distributing oil channel.

3. The wind turbine bearing cooling mechanism of claim 1, wherein: A plurality of oil injection channels are equidistantly arranged along the circumferential direction of the inner bearing end cover. The oil injection channels correspond to the branch oil channels one by one. One end of each oil injection channel is communicated with the corresponding branch oil channel through an auxiliary oil channel, and the other ends of all the oil injection channels are communicated with the oil injection ring groove.

4. The wind turbine bearing cooling mechanism of claim 1, wherein: The bearing includes a first bearing body and a second bearing body that are fitted together. The outer diameter of the first bearing body is larger than that of the second bearing body. The first bearing body is fitted with the outer bearing end cover, and the second bearing body is fitted with the inner bearing end cover. The annular raceway of the first bearing body is communicated with the annular raceway of the second bearing body. The oil throwing ring groove is communicated with the annular raceway of the first bearing body, and the oil injection ring groove is communicated with the annular raceway of the second bearing body.

5. The wind turbine bearing cooling mechanism of claim 1, wherein: The first labyrinth seal structure includes a first sealing protrusion and a first sealing groove. The first sealing protrusion is coaxially connected to the end face of the oil throwing ring plate away from the inner bearing end cover, and the first sealing groove is coaxially opened on the end face of the sealing end cover close to the inner bearing end cover. The first sealing protrusion penetrates into the first sealing groove, and there is a first sealing gap for the relative rotation of the oil throwing ring plate and the sealing end cover between the first sealing protrusion and the first sealing groove. The first sealing gap is in a labyrinth shape and is communicated with the oil throwing ring groove.

6. The wind turbine bearing cooling mechanism of claim 1, wherein: The second labyrinth seal structure includes a second sealing protrusion and a second sealing groove. The second sealing protrusion is coaxially connected to the end face of the sealing ring plate away from the outer bearing end cover, and the second sealing groove is coaxially opened on the end face of the inner bearing end cover close to the outer bearing end cover. The second sealing protrusion penetrates into the second sealing groove, and there is a second sealing gap for the relative rotation of the sealing ring plate and the inner bearing end cover between the second sealing protrusion and the second sealing groove. The second sealing gap is in a labyrinth shape and is communicated with the oil injection ring groove.

7. A wind turbine bearing cooling mechanism according to claim 6, wherein: The second sealing protrusion is in a "卜” shape, and the side of the second sealing protrusion close to the outer bearing end cover protrudes out of the second sealing groove.

8. The wind turbine bearing cooling mechanism of claim 1, wherein: The oil throwing ring groove is arranged to gradually expand from the direction close to the rotor shaft to the direction away from the rotor shaft.

9. The wind turbine bearing cooling mechanism of claim 1, wherein: On one side of the outer bearing end cover close to the rotor shaft, there is a first inclined surface. On one side of the oil throwing ring plate away from the rotor shaft, there is a second inclined surface. There is an anti-overflow gap between the first inclined surface and the second inclined surface. The anti-overflow gap is inclined in the direction away from the inner bearing end cover from the direction close to the rotor shaft to the direction away from the rotor shaft. The anti-overflow gap is communicated with both the oil throwing ring groove and the annular raceway of the bearing; The bearing outer end cover is also provided with an anti-overflow convex ring near the side of the rotor shaft, and the anti-overflow convex ring and the oil throwing ring plate have an oil discharge gap, which is located at one end of the anti-overflow gap near the rotor shaft and is communicated with the anti-overflow gap.

10. A method for cooling a bearing of a wind power generator using the cooling mechanism according to any one of claims 1 to 9, characterized in that, The method comprises the following steps: S1, one end of the bearing oil inlet pipeline is screwed and tightened with the connecting pipe head at the bearing oil inlet hole, and the other end of the bearing oil inlet pipeline is screwed and tightened with the connecting pipe head at the output end of the heat exchanger; S2, one end of the bearing oil outlet pipeline is screwed and tightened with the connecting pipe head at the bearing oil outlet hole, and the other end of the bearing oil outlet pipeline is screwed and tightened with the connecting pipe head at the gear box oil outlet pipeline; S3, under the drive of the oil pump, the lubricating oil enters the oil distribution oil passage from the heat exchanger through the bearing oil inlet pipeline and the bearing oil inlet hole, the lubricating oil in the oil distribution oil passage can perform primary heat dissipation and cooling on the first bearing body, the lubricating oil continues to enter the annular raceway of the second bearing body from the oil distribution oil passage through the branch oil passage, the auxiliary oil passage, the oil injection oil passage and the oil injection ring groove, and performs heat dissipation and cooling on the second bearing body, the lubricating oil in the annular raceway of the second bearing body enters the annular raceway of the first bearing body again, and performs secondary cooling on the first bearing body, the lubricating oil in the annular raceway of the first bearing body enters the oil throwing ring groove through the oil discharge gap and the anti-overflow gap, the lubricating oil in the oil throwing ring groove enters the bearing oil outlet pipeline from the bearing oil outlet hole again, the oil pump pumps the hot lubricating oil in the bearing oil outlet pipeline to the heat exchanger, the lubricating oil cooled by the heat exchanger enters the bearing from the bearing oil inlet pipeline again, and the circulation is repeated.

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