Wind turbine gearbox

Abstract

The application discloses a wind power gear box, which comprises a first gear shaft provided with an external spline; a second gear shaft sleeve arranged on the first gear shaft and forming a flow channel with the first gear shaft, the second gear shaft being provided with an internal spline, the external spline being engaged with the internal spline; a gear assembly, the gear of which is arranged on the second gear shaft and forms a receiving groove with the second gear shaft, a stopper being arranged in the receiving groove, the second gear shaft being provided with an oil leakage channel extending in a radial direction, a first end of the oil leakage channel being communicated with the flow channel, a second end of the oil leakage channel being communicated with the receiving groove, the receiving groove being further communicated with an oil pool; and a bearing assembly comprising a first bearing connected to the second gear shaft; the flow channel, the external spline, the oil leakage hole and the first bearing are sequentially distributed along an axial direction of the first gear shaft. The efficiency of lubrication and cooling of the external spline and the internal spline is improved, and the phenomenon that the rolling track surface of the first bearing and the rolling surface of the first bearing are damaged by impurities caused by the inflow of lubricating oil into the first bearing is avoided. The structure is simple, the production cost is low, and the assembly and maintenance are facilitated.

Description

Technical Field

[0001] This invention relates to the field of gearbox technology, and more particularly to wind turbine gearboxes. Background Technology

[0002] Wind power, as a renewable energy source, has advantages over thermal power, solar power, and hydropower, including lower construction costs, smaller footprint, and easier maintenance. The splined shaft is a crucial component in wind turbine gearboxes, responsible for transmitting the torque of the sun gear to the high-speed gear pair via splines. Therefore, lubrication and cooling of the splined shaft are extremely important.

[0003] In a current wind turbine gearbox spline lubrication structure, a circular flow channel is formed between the sun gear and the sun gear plate during gearbox assembly. An oil drain channel is located on the right side of the inner and outer spline meshing area of ​​the sun gear and spline shaft, passing through the spline shaft. Lubricating oil flowing from the flow channel between the sun gear and the sun gear plate into the inner and outer spline meshing area flows out through the oil drain channel and ultimately enters the oil sump, thus lubricating and cooling the inner and outer spline meshing area. However, in this wind turbine gearbox spline lubrication structure, a bearing is located on the right side of the oil drain channel outlet. There is a risk that the lubricating oil discharged from the oil drain channel may enter the bearing. If, during lubrication, the lubricating oil mixes with debris from the surfaces of the inner and outer spline meshing areas of the sun gear and spline shaft, or if debris mixes with the lubricating oil while flowing into the oil drain channel, when the lubricating oil enters the bearing, the debris in the lubricating oil can damage the raceway and roller surfaces of the bearing, leading to bearing failure. Summary of the Invention

[0004] The purpose of this invention is to provide a wind turbine gearbox to solve the problem in existing wind turbine gearboxes where, when lubricating oil enters the bearing, debris in the lubricating oil damages the raceway and roller surfaces of the bearing, leading to bearing failure.

[0005] To achieve this objective, the present invention adopts the following technical solution:

[0006] Wind turbine gearbox, comprising:

[0007] A first gear shaft, the first gear shaft being provided with an external spline;

[0008] A second gear shaft is sleeved on the first gear shaft and forms a flow channel with the first gear shaft. The second gear shaft is provided with an internal spline, and the external spline meshes with the internal spline.

[0009] A gear assembly, comprising a stop and a gear, wherein the gear is sleeved on a second gear shaft and forms a receiving groove between the gear and the second gear shaft, the stop is disposed in the receiving groove, the second gear shaft is provided with a radially extending oil drain channel, the first end of the oil drain channel is connected to the flow channel, the second end is connected to the receiving groove, and the receiving groove is also connected to an oil sump;

[0010] The bearing assembly includes a first bearing connected to the second gear shaft;

[0011] The flow channel, the external spline, the oil drain channel, and the first bearing are distributed sequentially along the axial direction of the first gear shaft.

[0012] Preferably, the receiving groove includes a first groove and a second groove that are connected to each other. The stop member is disposed in the first groove. The second end of the oil drain channel is connected to the second groove. The second groove has an opening facing the first bearing. The opening is connected to the oil sump, and the cross-sectional area of ​​the opening is larger than the cross-sectional area of ​​the oil drain channel.

[0013] Preferably, the second groove includes a first sidewall formed on the gear and a second sidewall formed on the second gear shaft, the first sidewall and the second sidewall forming the opening, and the radial distance between the first sidewall and the second sidewall gradually increases along the axial direction of the gear as the distance to the stop gradually increases.

[0014] Preferably, the first sidewall is inclined from the outer end of the gear to the inner wall of the gear to form a notch in the gear, the second sidewall is the outer circumferential surface of the second gear shaft, and the included angle between the first sidewall and the second sidewall is α, where 45°≤α<90°.

[0015] Preferably, the second gear shaft includes a first shaft segment, a second shaft segment, and a third shaft segment connected in sequence. The diameter of the second shaft segment is larger than the diameter of the first shaft segment and the diameter of the third shaft segment. The receiving groove and the internal spline are both distributed in the second shaft segment, and the first bearing is connected to the third shaft segment.

[0016] The wind turbine gearbox also includes an oil baffle ring that is interference-fitted onto the third shaft section. The two ends of the oil baffle ring along the axial direction abut against the second shaft section and the first bearing, respectively. The oil baffle ring is used to shield the first bearing.

[0017] Preferably, the outer diameter of the end of the oil baffle ring near the opening is greater than or equal to the inner diameter of the outer ring of the first bearing, and less than or equal to the outer diameter of the outer ring of the first bearing.

[0018] Preferably, the outer diameter of the end of the oil baffle ring closest to the first bearing is less than or equal to the outer diameter of the inner ring of the first bearing.

[0019] Preferably, the inner circumferential surface of the second gear shaft is provided with a retaining ring, which is interference-fitted onto the first gear shaft. The outer circumferential surface of the first gear shaft, the inner circumferential surface of the second gear shaft, and the retaining ring form the flow channel. The retaining ring abuts against the external spline along the axial direction.

[0020] Preferably, the wind turbine gearbox further includes a limiting component, wherein the external spline, the retaining ring, and the limiting component are distributed sequentially along the axial direction of the first gear shaft, and the limiting component is used to limit the relative position of the first gear shaft and the second gear shaft along the axial direction.

[0021] Preferably, the limiting component includes a spacer ring and a retaining ring. The spacer ring is sleeved on the first gear shaft, and the retaining ring is partially embedded in the first gear shaft. The two ends of the spacer ring along the axial direction abut against the retaining ring and the retaining ring, respectively.

[0022] The beneficial effects of this invention are:

[0023] The present invention aims to provide a wind turbine gearbox, which includes a first gear shaft, a second gear shaft, a gear assembly, and a bearing assembly. The second gear shaft is sleeved on the first gear shaft and forms a flow channel with the first gear shaft. The second gear shaft is provided with a radially extending oil drain channel. The first end of the oil drain channel communicates with the flow channel, and the second end communicates with a receiving groove. The receiving groove also communicates with an oil sump. An external spline, an oil drain channel, and a first bearing are arranged sequentially along the axial direction of the first gear shaft. It is understood that the external spline and the internal spline are located within the flow channel formed by the first gear shaft and the second gear shaft. When the first gear shaft, the second gear shaft, and the gears rotate synchronously, the lubricating oil flowing in from the flow channel flows through the meshing gap of the external spline and the internal spline and then sequentially flows through the oil drain channel. The lubricating oil flowing out of the receiving tank is mostly radially directed into the second tank under centrifugal force, and then flows into the oil sump. Compared with the prior art, this effectively avoids the phenomenon of debris damaging the raceway and roller surfaces of the first bearing caused by lubricating oil flowing into the first bearing, thus improving the service life of the first bearing and the performance of the wind turbine gearbox. Secondly, the lubricating oil flowing into the flow channel can flow through the meshing gap between the external and internal splines to the oil drain channel, which can lubricate and cool the external and internal splines. The oil drain channel extends radially, which can effectively improve the flow efficiency of the lubricating oil when it flows out of the oil drain channel, thereby improving the cooling efficiency of the external and internal splines.

[0024] Therefore, this wind turbine gearbox can lubricate and cool both the external and internal splines. After cooling the external and internal splines, the lubricating oil can flow sequentially through the oil drain channel and the receiving groove into the oil sump. This effectively avoids the phenomenon of debris damaging the raceway and roller surfaces of the first bearing caused by lubricating oil flowing into the first bearing. It also improves the cooling efficiency of cooling the external and internal splines, effectively improving the performance of the wind turbine gearbox. Furthermore, it has a simple structure, low production cost, and is easy to assemble and maintain. Attached Figure Description

[0025] Figure 1 This is a structural schematic diagram of a wind turbine gearbox provided in a specific embodiment of the present invention;

[0026] Figure 2 This is a partial structural schematic diagram of a wind turbine gearbox provided in a specific embodiment of the present invention;

[0027] Figure 3 yes Figure 1 A partial view at point A.

[0028] In the picture:

[0029] 1. First gear shaft; 11. External spline; 12. Flow channel;

[0030] 2. Second gear shaft; 21. First shaft section; 22. Second shaft section; 221. Internal spline; 222. Oil drain channel; 23. Third shaft section; 231. Retaining ring;

[0031] 3. Gear assembly; 31. Stop; 32. Gear;

[0032] 4. Receiving slot; 41. First slot; 42. Second slot; 421. First side wall; 422. Second side wall; 423. Opening;

[0033] 51. First bearing; 52. Second bearing;

[0034] 6. Oil baffle ring;

[0035] 7. Limiting component; 71. Distance ring; 72. Snap ring. Detailed Implementation

[0036] To make the technical problems solved by the present invention, the technical solutions adopted, and the technical effects achieved clearer, the technical solutions of the embodiments of the present invention will be further described in detail below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0037] In the description of this invention, unless otherwise explicitly specified and limited, the terms "connected," "linked," and "fixed" 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 this invention based on the specific circumstances.

[0038] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0039] This invention provides a wind turbine gearbox, such as Figure 1 and Figure 2 As shown, the wind turbine gearbox includes a first gear shaft 1, a second gear shaft 2, a gear assembly 3, and a bearing assembly. The first gear shaft 1 is provided with an external spline 11. The second gear shaft 2 is sleeved on the first gear shaft 1 and forms a flow channel 12 with the first gear shaft 1. The second gear shaft 2 is provided with an internal spline 221, and the external spline 11 meshes with the internal spline 221. The gear assembly 3 includes a stop member 31 and a gear 32. The gear 32 is sleeved on the second gear shaft 2 and forms a receiving groove 4 between the gear 32 and the second gear shaft 2. The stop member 31 is disposed in the receiving groove 4. The second gear shaft 2 is provided with a radially extending oil drain channel 222. The first end of the oil drain channel 222 communicates with the flow channel 12, and the second end communicates with the receiving groove 4. The receiving groove 4 also communicates with an oil sump. The bearing assembly includes a first bearing 51 connected to the second gear shaft 2. The flow channel 12, the external spline 11, the oil drain channel 222, and the first bearing 51 are distributed sequentially along the axial direction of the first gear shaft 1.

[0040] The wind turbine gearbox, such as Figure 1 and Figure 2As shown, the second gear shaft 2 is sleeved on the first gear shaft 1 and forms a flow channel 12 with the first gear shaft 1. The second gear shaft 2 is provided with a radially extending oil drain channel 222. The first end of the oil drain channel 222 is connected to the flow channel 12, and the second end is connected to the receiving groove 4. The receiving groove 4 is also connected to the oil sump. The external spline 11, the oil drain channel 222, and the first bearing 51 are distributed sequentially along the axial direction of the first gear shaft 1. It can be understood that the external spline 11 and the internal spline 221 are located in the flow channel 12 formed by the first gear shaft 1 and the second gear shaft 2. When the first gear shaft 1, the second gear shaft 2, and the gear 32 rotate synchronously, the lubricating oil flowing in from the flow channel 12 flows through the meshing gap of the external spline 11 and the internal spline 221 and then flows sequentially through the oil drain channel 222 and the receiving groove 4. The lubricating oil flowing out from the receiving groove 4 is separated from the oil sump. Under the action of the centrifugal force, the lubricating oil flows radially into the second groove 42 and then into the oil sump. Compared with the prior art, this can effectively avoid the phenomenon of debris damage to the raceway surface and roller surface of the first bearing 51 caused by the lubricating oil flowing into the first bearing 51, thereby improving the service life of the first bearing 51 and the performance of the wind turbine gearbox. Secondly, the lubricating oil flowing into the flow channel 12 can flow through the meshing gap between the external spline 11 and the internal spline 221 to the oil drain channel 222, which can lubricate and cool the external spline 11 and the internal spline 221. The oil drain channel 222 extends radially, which can effectively improve the flow efficiency of the lubricating oil when it flows out of the oil drain channel 222, thereby improving the cooling efficiency of the external spline 11 and the internal spline 221. Therefore, this wind turbine gearbox can lubricate and cool the external spline 11 and the internal spline 221. The lubricating oil that has cooled the external spline 11 and the internal spline 221 can flow sequentially through the oil drain channel 222 and the receiving groove 4 into the oil sump. This can effectively prevent the phenomenon of debris damage to the raceway surface and roller surface of the first bearing 51 caused by the lubricating oil flowing into the first bearing 51. It can also improve the cooling efficiency of cooling the external spline 11 and the internal spline 221, effectively improve the performance of the wind turbine gearbox, and has a simple structure, low production cost, and is easy to assemble and maintain.

[0041] in, Figure 1 The direction ab in the diagram is the axial direction of the first gear shaft 1. The axial directions of the first gear shaft 1, the second gear shaft 2, the gear 32, and the oil baffle ring 6 are all parallel.

[0042] Among them, such as Figure 1 and Figure 2As shown, the receiving groove 4 includes a first groove 41 and a second groove 42 that are connected. A stop member 31 is disposed within the first groove 41. The second end of the oil drain channel 222 is connected to the second groove 42. The second groove 42 has an opening 423 facing the first bearing 51 and connected to the oil sump. The cross-sectional area of ​​the opening 423 is larger than the cross-sectional area of ​​the oil drain channel 222. It can be understood that the second groove 42 is located between the first groove 41 and the first bearing 51, and the opening 423 of the second groove 42 is located on the gear 32 on the side closest to the first bearing 51. When the first gear shaft 1, the second gear shaft 2, and the gear 32 rotate synchronously, the lubricating oil flowing in from the flow channel 12 passes through the meshing gap between the external spline 11 and the internal spline 221 and then flows sequentially through the oil drain channel 222 and the second groove 42. The lubricating oil flowing out from the second groove 42, under the action of centrifugal force, basically flows into the oil sump along the radial direction of the gear 32. This effectively avoids the phenomenon of debris damaging the raceway surface and roller surface of the first bearing 51 caused by the lubricating oil flowing into the first bearing 51, thus effectively improving the performance of the wind turbine gearbox. Secondly, the cross-sectional area of ​​the opening 423 of the second groove 42 is set to be larger than the cross-sectional area of ​​the oil drain channel 222, so that after the lubricating oil cools the internal spline 221 and the external spline 11, it can quickly flow into the oil sump through the oil drain channel 222 and the second groove 42, thereby effectively improving the flow efficiency of the lubricating oil after cooling the internal spline 221 and the external spline 11, and further improving the cooling efficiency of the external spline 11 and the internal spline 221.

[0043] Specifically, such as Figure 1 and Figure 2 As shown, the second groove 42 includes a first sidewall 421 formed on the gear 32 and a second sidewall 422 formed on the second gear shaft 2. The first sidewall 421 and the second sidewall 422 form an opening 423. Along the axial direction of the gear 32, as the distance to the stop 31 gradually increases, the radial distance between the first sidewall 421 and the second sidewall 422 gradually increases. It can be understood that, along the axial direction of the gear 32, the cross-sectional area of ​​the opening 423 formed at the end of the second groove 42 away from the stop 31 is larger than the cross-sectional area of ​​the end of the second groove 42 near the stop 31. It can be understood that the second groove 42 is funnel-shaped, thereby allowing the lubricating oil flowing into the second groove 42 to flow into the oil sump quickly and efficiently.

[0044] More specifically, such as Figure 1 and Figure 2 As shown, the first sidewall 421 is inclined from the outer end face of the gear 32 to the inner wall of the gear 32 to form a notch in the gear 32. The second sidewall 422 is the outer circumferential surface of the second gear shaft 2. The included angle between the first sidewall 421 and the second sidewall 422 is α, where 45° ≤ α < 90°. Figure 1 and Figure 2It can be seen that the second end of the oil drain channel 222 is located on the second side wall 422 and is connected to the second groove 42. In this embodiment, the oil drain channel 222 is a circular channel, so 45°≤α<90° is set so that the span of the opening 423 along the radial direction of the gear 32 is always greater than the diameter of the oil drain channel 222. This makes the area of ​​the opening 423 of the second groove 42 greater than the cross-sectional area of ​​the oil drain channel 222, thereby effectively improving the flow efficiency of lubricating oil after cooling the inner spline 221 and the outer spline 11, improving the cooling efficiency of cooling the outer spline 11 and the inner spline 221, and effectively avoiding the phenomenon of debris damage to the raceway surface and roller surface of the first bearing 51 caused by the lubricating oil flowing into the first bearing 51 after passing through the meshing gap of the outer spline 11 and the inner spline 221. It is understood that the second groove 42 can also be configured in other shapes, as long as the area of ​​the opening 423 of the second groove 42 is larger than the cross-sectional area of ​​the oil drain channel 222 and it is easy to guide the lubricating oil away from the first bearing 51. Preferably, in this embodiment, the included angle between the first sidewall 421 and the second sidewall 422 is 45°.

[0045] Among them, such as Figure 1 and Figure 2 As shown, the second gear shaft 2 includes a first shaft segment 21, a second shaft segment 22, and a third shaft segment 23 connected in sequence. The diameter of the second shaft segment 22 is larger than the diameters of the first shaft segment 21 and the third shaft segment 23. The receiving groove 4 and the internal spline 221 are both distributed on the second shaft segment 22. The first bearing 51 is connected to the third shaft segment 23. The wind turbine gearbox also includes an oil retainer ring 6 that is interference-fitted onto the third shaft segment 23. The two ends of the oil retainer ring 6 along the axial direction are respectively pressed against the second shaft segment 22 and the first bearing 51. The oil retainer ring 6 is used to shield the first bearing 51. Specifically, the inner ring of the first bearing 51 is interference-fitted onto the third shaft segment 23. By setting an oil baffle ring 6 between the second shaft section 22 and the first bearing 51, the oil baffle ring 6 can prevent the lubricating oil discharged from the second groove 42 to the oil sump from splashing onto the first bearing 51, thereby further avoiding the phenomenon of debris damage to the raceway surface and roller surface of the first bearing 51 caused by lubricating oil entering the first bearing 51, thus further improving the performance of the wind turbine gearbox.

[0046] Specifically, such as Figure 1 and Figure 2 As shown, the outer diameter of the end of the oil baffle ring 6 near the opening 423 is greater than or equal to the inner diameter of the outer ring of the first bearing 51, and less than or equal to the outer diameter of the outer ring of the first bearing 51. This arrangement effectively prevents lubricating oil discharged from the second groove 42 into the oil sump from splashing into the first bearing 51.

[0047] Specifically, such as Figure 1 and Figure 2As shown, the outer diameter of the end of the oil baffle ring 6 closest to the first bearing 51 is less than or equal to the outer diameter of the inner ring of the first bearing 51. This arrangement prevents the oil baffle ring 6 from interfering with the first bearing 51.

[0048] Preferably, the first shaft segment 21, the second shaft segment 22, and the third shaft segment 23 of the second gear shaft 2 are integrally formed. This arrangement reduces the number of parts while ensuring the structural strength of the second gear shaft 2.

[0049] Among them, such as Figure 1-3 As shown, a retaining ring 231 is provided on the inner circumferential surface of the second gear shaft 2. The retaining ring 231 is interference-fitted onto the first gear shaft 1. The outer circumferential surface of the first gear shaft 1, the inner circumferential surface of the second gear shaft 2, and the retaining ring 231 form a flow channel 12. The retaining ring 231 abuts against the external spline 11 axially. Specifically, the retaining ring 231 is disposed on the inner circumferential surface of the third shaft section 23. It can be understood that the lubricating oil flowing in from the flow channel 12 is blocked at the retaining ring 231, causing the lubricating oil to flow into the oil sump through the oil drain channel 222 and the second groove 42.

[0050] Specifically, the internal spline 221 is integrally formed on the first gear shaft 1. The retaining ring 231 is also integrally formed on the first gear shaft 1. This further reduces the number of parts while ensuring the structural strength of the first gear shaft 1. It is understood that the first gear shaft 1 in this embodiment is a splined shaft.

[0051] Specifically, the external spline 11 is integrally formed on the second gear shaft 2. This further reduces the number of parts while ensuring the structural strength of the second gear shaft 2. It is understood that the second gear shaft 2 in this embodiment is also a spline shaft.

[0052] Among them, such as Figure 1 and Figure 3 As shown, the wind turbine gearbox also includes a limiting component 7. The external spline 11, the retaining ring 231, and the limiting component 7 are sequentially distributed along the axial direction of the first gear shaft 1. The limiting component 7 is used to limit the relative position of the first gear shaft 1 and the second gear shaft 2 along the axial direction. The limiting component 7 can prevent relative movement of the first gear shaft 1 and the second gear shaft 2 along the axial direction.

[0053] Specifically, such as Figure 1 and Figure 3 As shown, the sealing assembly 7 includes a spacer ring 71 and a retaining ring 72. The spacer ring 71 is sleeved on the first gear shaft 1, and the retaining ring 72 is partially embedded in the first gear shaft 1. The two ends of the spacer ring 71 along the axial direction abut against the retaining ring 231 and the retaining ring 72, respectively. This arrangement can effectively prevent relative movement between the first gear shaft 1 and the second gear shaft 2 along the axial direction.

[0054] In this embodiment, such as Figure 1As shown, the first shaft segment 21 is also connected to a second bearing 52. In this embodiment, the first bearing 51 is a self-aligning roller bearing; the second bearing 52 is a thrust ball bearing.

[0055] Obviously, the above embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the implementation of the present invention. Those skilled in the art can make other variations or modifications based on the above description. It is neither necessary nor possible to exhaustively describe all embodiments here. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the scope of protection of the claims of the present invention.

Claims

1. A wind turbine gearbox, characterized in that, include: The first gear shaft (1) is provided with an external spline (11); The second gear shaft (2) is sleeved on the first gear shaft (1) and forms a flow channel (12) with the first gear shaft (1). The second gear shaft (2) is provided with an internal spline (221), and the external spline (11) meshes with the internal spline (221). Gear assembly (3), the gear assembly (3) includes a stop (31) and a gear (32), the gear (32) is sleeved on the second gear shaft (2) and forms a receiving groove (4) between the gear (32) and the second gear shaft (2), the stop (31) is disposed in the receiving groove (4), the second gear shaft (2) is provided with an oil drain channel (222) extending radially, the first end of the oil drain channel (222) is connected to the flow channel (12), the second end is connected to the receiving groove (4), and the receiving groove (4) is also connected to an oil sump; A bearing assembly, the bearing assembly including a first bearing (51) connected to the second gear shaft (2); The flow channel (12), the external spline (11), the oil drain channel (222) and the first bearing (51) are distributed sequentially along the axial direction of the first gear shaft (1); The receiving groove (4) includes a first groove (41) and a second groove (42) that are connected. The stop (31) is disposed in the first groove (41). The second end of the oil drain channel (222) is connected to the second groove (42). The second groove (42) is provided with an opening (423). The opening (423) faces the first bearing (51). The opening (423) is connected to the oil pool. The cross-sectional area of ​​the opening (423) is larger than the cross-sectional area of ​​the oil drain channel (222).

2. The wind turbine gearbox according to claim 1, characterized in that, The second groove (42) includes a first sidewall (421) formed on the gear (32) and a second sidewall (422) formed on the second gear shaft (2). The first sidewall (421) and the second sidewall (422) form the opening (423). Along the axial direction of the gear (32), as the distance to the stop (31) gradually increases, the radial distance between the first sidewall (421) and the second sidewall (422) gradually increases.

3. The wind turbine gearbox according to claim 2, characterized in that, The first sidewall (421) is inclined from the outer end of the gear (32) to the inner wall of the gear (32) so that the gear (32) forms a notch. The second sidewall (422) is the outer peripheral surface of the second gear shaft (2). The included angle between the first sidewall (421) and the second sidewall (422) is α, where 45°≤α<90°.

4. The wind turbine gearbox according to claim 2, characterized in that, The second gear shaft (2) includes a first shaft segment (21), a second shaft segment (22) and a third shaft segment (23) connected in sequence. The diameter of the second shaft segment (22) is larger than the diameter of the first shaft segment (21) and the diameter of the third shaft segment (23). The receiving groove (4) and the internal spline (221) are both distributed on the second shaft segment (22). The first bearing (51) is connected to the third shaft segment (23). The wind turbine gearbox also includes an oil baffle ring (6) that is interference-fitted onto the third shaft section (23). The two ends of the oil baffle ring (6) along the axial direction abut against the second shaft section (22) and the first bearing (51) respectively. The oil baffle ring (6) is used to shield the first bearing (51).

5. The wind turbine gearbox according to claim 4, characterized in that, The outer diameter of the oil baffle ring (6) near the opening (423) is greater than or equal to the inner diameter of the outer ring of the first bearing (51) and less than or equal to the outer diameter of the outer ring of the first bearing (51).

6. The wind turbine gearbox according to claim 4, characterized in that, The outer diameter of the oil baffle ring (6) at the end near the first bearing (51) is less than or equal to the outer diameter of the inner ring of the first bearing (51).

7. The wind turbine gearbox according to any one of claims 1-6, characterized in that, The inner circumferential surface of the second gear shaft (2) is provided with a retaining ring (231), which is interference-fitted onto the first gear shaft (1). The outer circumferential surface of the first gear shaft (1), the inner circumferential surface of the second gear shaft (2), and the retaining ring (231) form the flow channel (12). The retaining ring (231) abuts against the external spline (11) axially.

8. The wind turbine gearbox according to claim 7, characterized in that, The wind turbine gearbox also includes a limiting component (7). The external spline (11), the retaining ring (231) and the limiting component (7) are distributed sequentially along the axial direction of the first gear shaft (1). The limiting component (7) is used to limit the relative position of the first gear shaft (1) and the second gear shaft (2) along the axial direction.

9. The wind turbine gearbox according to claim 8, characterized in that, The limiting component (7) includes a spacer ring (71) and a retaining ring (72). The spacer ring (71) is sleeved on the first gear shaft (1), and the retaining ring (72) is partially embedded in the first gear shaft (1). The two ends of the spacer ring (71) along the axial direction abut against the retaining ring (231) and the retaining ring (72) respectively.

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