Transmission buffer mechanism for gearbox of wind turbine

Abstract

The invention relates to the technical field of transmission structures, in particular to a wind turbine gearbox transmission buffer mechanism which comprises an oil cylinder, an input shaft and an output shaft, the input shaft and the output shaft are installed at the two ends of the oil cylinder, the end of the input shaft and the end of the output shaft both extend into the oil cylinder, and a transmission cavity and a backflow channel are formed in the oil cylinder. The backflow channel is located on the outer side of the transmission cavity and used for guiding oil in the transmission cavity to flow reversely. Through oil transmission, the power transmitted to the gear box by the impeller can be conveniently subjected to stable and buffer treatment under the condition that external airflow is unstable, so that the gear box can stably operate, the rotating speed or the violent fluctuation of a load is reduced, the instantaneous impact caused by the sudden change of the rotating speed between gears is reduced, the gear box is conveniently and effectively protected, and the service life of the gear box is prolonged. Friction loss of all transmission parts is reduced, the service life is prolonged, and the equipment failure rate is reduced.

Description

Technical Field

[0001] This invention relates to the technical field of transmission structures, and in particular to a wind turbine gearbox transmission buffer mechanism. Background Technology

[0002] Against the backdrop of global efforts to address climate change and achieve "dual carbon" goals, the development and utilization of clean energy has become the core of energy strategies for countries around the world. Among them, wind energy is widely used due to its characteristics of being pollution-free, renewable, and having large reserves.

[0003] In practical engineering, the randomness and uncertainty of wind conditions, such as frequent changes in wind speed and direction, cause the impeller and gearbox in wind turbines to be subjected to alternating loads, leading to fatigue damage. At the same time, the mechanical motion of gear meshing and bearing rotation inside the gearbox can also cause failures such as wear and cracks. Comprehensive statistics and analysis of operating data from multiple wind farms in China show that failures in the impeller-gearbox system account for more than 60% of all wind turbine failures. Summary of the Invention

[0004] This invention provides a wind turbine gearbox transmission buffer mechanism, which can effectively solve the problems in the background art.

[0005] To achieve the above objectives, the technical solution adopted by the present invention is as follows: A wind turbine gearbox transmission buffer mechanism includes a hydraulic cylinder and an input shaft and an output shaft installed at both ends of the hydraulic cylinder. The ends of the input shaft and the output shaft both extend into the hydraulic cylinder. The hydraulic cylinder has a transmission cavity and a return channel inside, and the return channel is located outside the transmission cavity. The return channel is used to guide the oil in the transmission cavity to flow in the reverse direction. Along the axis of the hydraulic cylinder, several fan blades one and several fan blades two are respectively arranged on both sides of the transmission cavity. Several fan blades one are installed on the input shaft, and several fan blades two are installed on the output shaft.

[0006] In some embodiments of the present invention, the fan blade includes a flat blade area coplanar with the axis of the oil cylinder and an inclined blade area inclined relative to the axis of the oil cylinder; The second fan blade includes a section one used in conjunction with the flat blade section and a section two used in conjunction with the oblique blade section.

[0007] In some embodiments of the present invention, the return channel includes a DC channel coaxial with the oil cylinder and a first guide channel and a second guide channel located at both ends of the DC channel. The first guide channel is used in conjunction with the first fan blade and is used to guide and transport oil along the axial direction of the oil cylinder. The second guide channel is used in conjunction with the second fan blade and is used to guide and transport oil along the radial direction of the oil cylinder.

[0008] In some embodiments of the present invention, the hydraulic cylinder includes a cylinder body one, a cylinder body two, and a filling cylinder. The cylinder body one and the cylinder body two are connected to form a closed chamber. The filling cylinder is located in the closed chamber and divides the closed chamber into a transmission chamber located inside the filling cylinder and a return channel located outside the filling cylinder. The filling cylinder is connected to either cylinder one or cylinder two via several connecting seats.

[0009] In some embodiments of the present invention, the shape of the first section along the circumferential direction of the oil cylinder is arc-shaped, and the inner wall of the arc-shaped section is provided with a plurality of guide grooves and a plurality of side edges along the axial direction of the oil cylinder, the side edges being inclined relative to the first section. The second section is arc-shaped along both the axial and radial directions of the cylinder.

[0010] In some embodiments of the present invention, a guide plate is provided inside the transmission cavity, the guide plate is connected to the output shaft, the cross-sectional shape of the guide plate on one side of the cylinder axis is arc-shaped, and the guide plate is used in conjunction with the second drainage channel.

[0011] In some embodiments of the present invention, the guide plate is provided with a plurality of flow restrictors, the plurality of flow restrictors are distributed around the axis of the oil cylinder, two adjacent flow restrictors form a flow restricting slit, and the width of the flow restricting slit gradually decreases along the direction away from the axis of the oil cylinder.

[0012] In some embodiments of the present invention, an auxiliary structure is provided between the input shaft and the output shaft in the transmission cavity, the auxiliary structure being used to receive the motion power of the oil between the input shaft and the output shaft.

[0013] In some embodiments of the present invention, the auxiliary structure includes a groove formed at the end of the output shaft and a support column located in the groove. The support column is coaxial with the oil cylinder. The end of the support column is close to or rotatably connected to the end of the input shaft. A spiral blade is provided on the outer wall of the support column. A plurality of oil drain slits communicating with the groove are formed on the outer wall of the output shaft. The oil drain seam is aligned with the arc-shaped inner wall of the first section.

[0014] In some embodiments of the present invention, the hydraulic cylinder is rotatably mounted about its own axis, and the hydraulic cylinder is connected to the output shaft through a transmission structure, which is used to transmit the rotational kinetic energy of the hydraulic cylinder to the output shaft.

[0015] The technical solution of this invention can achieve the following technical effects: By utilizing hydraulic transmission, the power transmitted from the impeller to the gearbox can be smoothly and buffered even when the external airflow is unstable. This allows the gearbox to operate stably, reduces drastic fluctuations in speed or load, and thus reduces instantaneous impacts between gears caused by sudden changes in speed. This facilitates effective protection of the gearbox, reduces frictional losses in various transmission components, extends service life, and lowers the equipment failure rate. Attached Figure Description

[0016] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments recorded in the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0017] Figure 1 This is a schematic diagram of the structure of the present invention; Figure 2 This is a schematic cross-sectional view of the hydraulic cylinder in an embodiment of the present invention; Figure 3 This is a schematic diagram of the exploded structure of the present invention; Figure 4 This is a schematic diagram of the structure of cylinder one in an embodiment of the present invention; Figure 5 This is a schematic diagram of the filling cylinder in an embodiment of the present invention; Figure 6 This is a schematic diagram of the flow guide disk in an embodiment of the present invention; Figure 7 This is a schematic diagram of the structure of fan blade two in an embodiment of the present invention; Figure 8 yes Figure 7 A structural diagram from another perspective; Figure 9 This is a schematic diagram of the spiral blade structure in an embodiment of the present invention; Figure 10 This is a cross-sectional view of the outer sleeve in an embodiment of the present invention.

[0018] Figure label: 100. Hydraulic cylinder; 101. Transmission chamber; 102. Return channel; 103. Direct current channel; 104. Drainage channel one; 105. Drainage channel two; 106. Cylinder body one; 107. Cylinder body two; 108. Filling cylinder; 109. Connecting seat; 110. Push plate; 111. Outer sleeve; 112. Conical cylinder; 113. Transmission cone wheel; 114. Bevel gear one; 115. Bevel gear two; 116. Fixing frame; 117. Rotary wheel; 118. Multi-faceted threaded pipe; 119. Threaded rod; 120. Adjusting motor; 200. Input shaft; 201. Fan blade one; 202. Flat blade area; 203. Slanted blade area; 300. Output shaft; 301. Fan blade 2; 302. Section 1; 303. Section 2; 304. Guide groove; 305. Side edge; 306. Guide plate; 307. Flow limiter; 308. Support column; 309. Spiral blade; 310. Oil drain slit. Detailed Implementation

[0019] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments.

[0020] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. The terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

[0021] like Figures 1 to 2 As shown, a wind turbine gearbox transmission buffer mechanism of the present invention includes a hydraulic cylinder 100 and an input shaft 200 and an output shaft 300 installed at both ends of the hydraulic cylinder 100. The ends of the input shaft 200 and the output shaft 300 extend into the hydraulic cylinder 100. The hydraulic cylinder 100 has a transmission cavity 101 and a return channel 102 inside, and the return channel 102 is located outside the transmission cavity 101. The return channel 102 is used to guide the oil in the transmission cavity 101 to flow in the opposite direction. Along the axial direction of the cylinder 100, several fan blades 201 and several fan blades 301 are respectively arranged on both sides of the transmission cavity 101. Several fan blades 201 are installed on the input shaft 200, and several fan blades 301 are installed on the output shaft 300. In this invention, the cylinder 100 stores transmission fluid, which can be mineral oil, hydraulic transmission oil, emulsion, etc. Of course, in cases where lubrication requirements are low, water can be used instead of oil, which can significantly reduce costs. The input shaft 200 and output shaft 300 are respectively connected to the impeller and gearbox. Since the flow direction of the fluid is mainly guided by the internal space of the cylinder 100, the relative positional relationship between the input shaft 200 and output shaft 300 can be coaxial, parallel and intersecting, or relatively inclined, all of which are within the scope of this invention. For example, when the axes of the input shaft 200 and output shaft 300 are relatively inclined, the internal space of the cylinder 100 also forms a certain angle. Thus, by utilizing the fluidity of the fluid, the power of the input shaft 200 can be transmitted to the output shaft 300, thereby facilitating the reversal of the power transmission direction. The above methods are not shown in the accompanying drawings. Of course, the input shaft 200 and output shaft 300 can also be coaxial, such as... Figure 2 As shown, this only requires the oil to flow laterally; The transmission chamber 101 and the return channel 102 are mainly used to guide the flow of oil. The transmission chamber 101 is located in the middle of the return channel 102. When the oil flows to the right from the transmission chamber 101, the oil will diffuse from the right side of the transmission chamber 101 to the surrounding areas and enter the return channel 102. The oil flows to the left in the return channel 102 and finally gathers on the left side of the transmission chamber 101. Thus, the oil circulates between the transmission chamber 101 and the return channel 102. The oil in the transmission chamber 101 always maintains a unidirectional flow state, which can provide a constant fluid flow environment for the first fan blade 201 and the second fan blade 301. In operation, wind power drives the impeller to rotate, which in turn drives the input shaft 200 and several fan blades 201 to rotate. These fan blades 201 propel the oil flow within the transmission chamber 101, thus providing power to the oil. The oil flows along the axis of the cylinder 100 within the transmission chamber 101. When the oil reaches the position of the second fan blade 301, it drives the second fan blade 301 to rotate, thereby transmitting the power from the input shaft 200 to the output shaft 300. The output shaft 300 then drives the gearbox to rotate. The oil near the second fan blade 301 is further stimulated by the rotation of the second fan blade 301. The rotational motion causes the oil to centrifugally enter the return channel 102. The oil in the return channel 102 flows in the reverse direction to the vicinity of the fan blade 201, thus enabling the oil to continuously and circulate to transmit power. When the external wind speed and direction change frequently, the rotational speed of the input shaft 200 changes frequently. At this time, the driving force transmitted to the oil by the fan blades 201 is unstable. The oil uses its own fluidity and internal friction to buffer the driving force, so that as the oil flows, it gradually tends to stabilize. Then the oil transmits the stable driving force to the output shaft 300, thereby achieving the transmission buffering effect. By utilizing hydraulic transmission, the power transmitted from the impeller to the gearbox can be smoothly and buffered even when the external airflow is unstable. This allows the gearbox to operate stably, reduces drastic fluctuations in speed or load, and thus reduces instantaneous impacts between gears caused by sudden changes in speed. This facilitates effective protection of the gearbox, reduces frictional losses in various transmission components, extends service life, and lowers the equipment failure rate.

[0022] In the process of fan blade 201 driving the oil flow and the oil driving fan blade 301 to rotate, in order to improve the transmission effect between the oil and fan blades 201 and 301, the following can be adopted: Figure 4 and Figure 7 As shown, the fan blade 201 includes a flat blade area 202 that is coplanar with the axis of the cylinder 100 and an inclined blade area 203 that is relatively inclined to the axis of the cylinder 100. The second fan blade 301 includes a first section 302 used in conjunction with the flat blade section 202 and a second section 303 used in conjunction with the oblique blade section 203; In the above description, the flat blade area 202 and the first plate area 302 are both coplanar with the axis of the cylinder 100, and the inclined blade area 203 and the second plate area 303 are both inclined relative to the axis of the cylinder 100. When the input shaft 200 drives the first fan blade 201 to rotate, the inclined blade area 203 will push the oil to flow. At this time, the oil flows in a spiral motion in the transmission cavity 101, that is, the oil has a motion form in both the axial direction and the circumferential direction of the cylinder 100. The flat blade area 202 will push the oil to flow around the circumference of the cylinder 100, thereby enhancing the flow effect of the oil in the circumferential direction of the cylinder 100. When the oil flows to the position of the second fan blade 301, the circumferential flow of the oil will act on the first plate area 302, and the flow of the oil along the axial direction of the cylinder 100 will act on the second plate area 303. This makes it convenient to make full use of the kinetic energy of the oil flow in each direction, improve the power transmission efficiency, and reduce energy loss. It should be noted that, in order to facilitate the reception of the flow power of the oil in the circumferential direction of the cylinder 100, the tilt direction of the second section 303 is opposite to the tilt direction of the inclined blade section 203. This can increase the angle between the oil flow direction and the second section 303, improve the effectiveness of the oil in driving the second section 303 to rotate, and thus improve the energy transfer effect.

[0023] When the oil enters or flows out of the return channel 102, in order to improve the transmission effect of the oil with the first fan blade 201 and the second fan blade 301, such as Figure 2As shown, the return channel 102 includes a DC channel 103 coaxial with the cylinder 100 and a first diversion channel 104 and a second diversion channel 105 located at both ends of the DC channel 103. The first diversion channel 104 is used in conjunction with the first fan blade 201 and is used to guide and transport oil along the axial direction of the cylinder 100. The second diversion channel 105 is used in conjunction with the second fan blade 301 and is used to guide and transport oil along the radial direction of the cylinder 100. Based on the above description, when the oil is centrifugally diffused by the rotation of the second fan blade 301, the arc angle of the second drainage channel 105 is 90°. In this way, the centrifugally diffused oil will directly enter the second drainage channel 105. Alternatively, the arc angle of the second drainage channel 105 can be adjusted according to the direction of oil flow guided by the second fan blade 301. When the oil flows into the transmission chamber 101 through the drainage channel 104, since the fan blades 201 cannot easily utilize the oil flowing in the radial direction of the cylinder 100, it is necessary to guide the oil discharged from the drainage channel 104 along the axial direction of the cylinder 100, that is, to use the drainage channel 104 to guide the oil, thereby facilitating the direct use of the oil with the fan blades 201; the arc angle of the drainage channel 104 can be 180°. By using the above-mentioned arrangement of the first flow channel 104 and the second flow channel 105, the flow direction of the oil can be guided, thereby improving the smoothness of the oil flow and the transmission effect between the oil and the first fan blade 201 and the second fan blade 301.

[0024] Optimized from the above implementation, such as Figure 3 As shown, the hydraulic cylinder 100 includes a cylinder body 106, a cylinder body 107, and a filling cylinder 108. The cylinder body 106 and the cylinder body 107 are connected to form a closed chamber. The filling cylinder 108 is located in the closed chamber and divides the closed chamber into a transmission chamber 101 located inside the filling cylinder 108 and a return channel 102 located outside the filling cylinder 108. The filling cylinder 108 is connected to cylinder one 106 or cylinder two 107 via several connecting seats 109. In this invention, cylinder body 106 and cylinder body 107 are joined to form a closed chamber. The specific connection method can be snap-fit, bolted, welding, etc. Along the axis of the hydraulic cylinder 100, both end faces of the closed chamber are shaped to correspond to the first drainage channel 104 and the second drainage channel 105. A filling cylinder 108 is located within the closed chamber, and its two ends respectively form the shapes of the first drainage channel 104 and the second drainage channel 105 with the end faces of the closed chamber. The interior of the filling cylinder 108 is a transmission chamber 101, and the exterior is a direct current channel 103. The filling cylinder 108 can be connected to cylinder body 106 or cylinder body 107 via several connecting seats 109. Figure 3 For example, the connecting seat 109 contacts the inside of the cylinder body 107, and the connecting seat 109 is fixed to the cylinder body 107 by bolts, thereby fixing the filling cylinder 108. Using the above method, the equipment can be easily assembled and maintained, and its structure is simple. When filling oil, oil holes or connectors can be set on the cylinder body 106 or the cylinder body 107.

[0025] like Figures 7 to 8 As shown, the shape of the section 302 along the circumference of the cylinder 100 is arc-shaped. The inner wall of the arc-shaped section 302 is provided with a number of guide grooves 304 and a number of side edges 305 along the axis of the cylinder 100. The side edges 305 are inclined relative to the section 302. The shape of section 2 303 along both the axial and radial directions of the hydraulic cylinder 100 is arc-shaped; By utilizing the arc-shaped design of section 302, the oil can be easily gathered, thereby improving the driving effect of the oil on section 302, reducing the kinetic energy loss caused by the oil flowing radially along the cylinder 100, and improving the kinetic energy transfer effect; several guide grooves 304 on section 302 can be used to guide the oil to flow along the axial direction of the cylinder 100; several side edges 305 on section 302 can further improve the gathering effect of section 302 on the oil. Of course, the side edges 305 can also assist in intercepting the oil flowing along the arc-shaped inner wall of section 302, thereby using the oil's flow pattern to provide auxiliary thrust to section 302 in the reverse direction. By making the shape of the second section 303 arc-shaped in both the axial and radial directions of the cylinder 100, the second section 303 can comprehensively receive and utilize the kinetic energy of the oil flow in the axial, radial and circumferential directions of the cylinder 100. Furthermore, the shape of the second section 303 can facilitate the guidance and diffusion of the oil towards the second drainage channel 105.

[0026] To improve the smoothness of oil flow between fan blade 2 301 and drainage channel 2 105, such as Figure 6 As shown, a guide plate 306 is provided inside the transmission cavity 101. The guide plate 306 is connected to the output shaft 300. The cross-sectional shape of the guide plate 306 on one side of the axis of the cylinder 100 is arc-shaped. The guide plate 306 is used in conjunction with the second flow channel 105. By utilizing the shape characteristics of the guide plate 306, it can be used in conjunction with the second flow channel 105, thereby facilitating the diffusion and pushing of the oil between two adjacent fan blades 301 toward the second flow channel 105, avoiding the direct impact of this part of the oil on the inner wall of the cylinder block 107 end face and causing energy loss.

[0027] like Figure 6As shown, in the optimized implementation described above, the guide plate 306 is provided with a plurality of fluid limiting 307s, the plurality of fluid limiting 307s are distributed around the axis of the oil cylinder 100, two adjacent fluid limiting 307s form a flow limiting slit, and the width of the flow limiting slit gradually decreases along the direction away from the axis of the oil cylinder 100. Several limiting fluids 307 are located at the inlet of the second flow channel 105. The oil guided by the guide plate 306 and the second fan blade 301 can flow into the limiting slit between two adjacent limiting fluids 307. Since the width of the limiting slit gradually decreases along the direction away from the axis of the oil cylinder 100, the flow velocity of the oil will increase. When the oil is discharged from the opening of the limiting slit, it can have a high speed. Therefore, the oil will provide a reverse thrust to the limiting fluids 307. Using this reverse thrust, the output shaft 300 can be rotated.

[0028] Since the oil between the input shaft 200 and the output shaft 300 in the middle of the transmission cavity 101 also has lateral and rotational flow, an auxiliary structure can be set between the input shaft 200 and the output shaft 300 to utilize the kinetic energy of this part of the oil. The auxiliary structure is used to receive the motion power of the oil between the input shaft 200 and the output shaft 300. The auxiliary structure can be a set of blades or other structures, as long as it can make the oil between the input shaft 200 and the output shaft 300 push the structure to move and transmit the power to the output shaft 300.

[0029] Based on the above implementation, such as Figure 6 and Figure 9 As shown, the auxiliary structure includes a groove at the end of the output shaft 300 and a support column 308 located in the groove. The support column 308 is coaxial with the oil cylinder 100. The end of the support column 308 is close to or rotatably connected to the end of the input shaft 200. A spiral blade 309 is provided on the outer wall of the support column 308. Several oil drain slits 310 communicating with the groove are provided on the outer wall of the output shaft 300. Among them, the oil drain joint 310 is aligned with the arc-shaped inner wall of section 302; Several oil drain slits 310 on the groove are used in conjunction with each fan blade 301. That is, after the oil in the groove is discharged through the oil drain slits 310, it will flow towards the inner wall of the plate area 302. The oil between the input shaft 200 and the output shaft 300 is in contact with the spiral blade 309. The flow of this part of the oil will act on the surface of the spiral blade 309, thereby causing the spiral blade 309 to rotate. The spiral blade 309 is connected to the output shaft 300, thereby providing auxiliary thrust to the output shaft 300. When the spiral blade 309 rotates, the oil between the input shaft 200 and the output shaft 300 will enter the groove in the axial direction of the oil cylinder 100. By using the groove and the oil drain slits 310 to guide the oil, the oil will flow away from the axial direction of the oil cylinder 100. In some embodiments, if the internal space of the cylinder 100 is large enough, or if the limitation on the amount of oil stored is low, a column can be used to occupy the position between the input shaft 200 and the output shaft 300.

[0030] Because the oil in the transmission cavity 101 experiences friction with the inner wall of the transmission cavity 101 as it flows along the circumference of the cylinder 100, the fluidity of the oil decreases, resulting in a loss of kinetic energy input from the input shaft 200. To reduce this loss, such as... Figure 5 and Figure 10 As shown, the hydraulic cylinder 100 is rotatably mounted around its own axis, and the hydraulic cylinder 100 is connected to the output shaft 300 through a transmission structure, which is used to transmit the rotational kinetic energy of the hydraulic cylinder 100 to the output shaft 300. In this invention, the hydraulic cylinder 100 can be driven by, for example... Figure 1 The cylinder 100 is supported by a support frame, bearings, and other structures, allowing it to rotate freely. The rotational flow of oil in the transmission chamber 101 drives the filling cylinder 108 to rotate through friction, thereby rotating the cylinder 100. To enhance this transmission effect, several push plates 110 can be installed on the inner wall of the filling cylinder 108, with the push plates 110 located between the input shaft 200 and the output shaft 300. Thus, the oil flowing along the circumference of the cylinder 100 in the filling cylinder 108 will pass through the push plates 110. 0 drives the hydraulic cylinder 100 to rotate; further understood, the input shaft 200 will drive the oil in the hydraulic cylinder 100 to rotate and flow in the circumferential direction of the hydraulic cylinder 100 through several fan blades 201. The viscosity of the oil will cause the hydraulic cylinder 100 to rotate and flow, so that the hydraulic cylinder 100 carries all the oil in it to flow in the circumferential direction of the hydraulic cylinder 100. The oil then drives the fan blades 301 and the output shaft 300 to rotate. Thus, based on the circumferential flow power of the oil, the power is transmitted to the output shaft 300. The rotation of the hydraulic cylinder 100 is transmitted to the output shaft 300 through the transmission structure, which facilitates the utilization of the rotational kinetic energy of the hydraulic cylinder 100 and avoids the hydraulic cylinder 100 from spinning idly and causing kinetic energy loss. like Figure 10As shown, the transmission structure includes an outer sleeve 111 fixed to the outer wall of cylinder 2 107. A cone 112 is provided at the end of the outer sleeve 111, and a transmission cone wheel 113 is provided inside the cone 112. The cone 112 and the transmission cone wheel 113 are connected by an inclined rotating wheel 117. A bevel gear 114 is provided on the output shaft 300, and a bevel gear 115 meshes with the bevel gear 114. A fixed frame 116 is provided between the bevel gear 115 and the transmission cone wheel 113, and both the bevel gear 115 and the transmission cone wheel 113 are rotatably mounted on the fixed frame 116. The bevel gear 115 and the transmission cone wheel 113 are connected by a transmission mechanism. An adjusting motor 120 is provided on the fixed frame 116, and a threaded rod 119 is provided at the output end of the adjusting motor 120. A multi-faceted threaded tube 118 is coaxially sleeved on the threaded rod 119, and the multi-faceted threaded tube 118 and the threaded rod 119 are connected by a threaded rod 119. 9. Threaded connection: The multi-ribbed threaded tube 118 is slidably mounted on the fixed frame 116, and the rotating wheel 117 is rotatably connected to the multi-ribbed threaded tube 118. When the cylinder body 107 rotates, it drives the outer sleeve 111 and the cone cylinder 112 to rotate. The cone cylinder 112 drives the transmission cone wheel 113 to rotate through the rotating wheel 117. The transmission cone wheel 113 drives the output shaft 300 to rotate through the second bevel gear 115 and the first bevel gear 114, thereby transmitting the power of the hydraulic cylinder 100 to the output shaft 300. The adjusting motor 120 can rotate the threaded rod 119 to push the multi-ribbed threaded tube 118 to move on the fixed frame 116, thereby adjusting the position of the rotating wheel 117 between the cone cylinder 112 and the transmission cone wheel 113, facilitating the adjustment of the transmission ratio between the cone cylinder 112 and the transmission cone wheel 113, thus matching the rotational speed of the hydraulic cylinder 100 with the rotational speed of the output shaft 300.

[0031] The foregoing has shown and described the basic principles, main features, and advantages of the present invention. Those skilled in the art should understand that the present invention is not limited to the above embodiments. The embodiments and descriptions in the specification are merely illustrative of the principles of the invention. Various changes and modifications can be made to the invention without departing from its spirit and scope, and all such changes and modifications fall within the scope of the present invention as claimed. The scope of protection of the present invention is defined by the appended claims and their equivalents.

Claims

1. A wind turbine gearbox transmission buffer mechanism, characterized in that, The device includes a hydraulic cylinder and an input shaft and an output shaft mounted at both ends of the hydraulic cylinder. The ends of the input shaft and the output shaft both extend into the hydraulic cylinder. The hydraulic cylinder has a transmission cavity and a return channel inside, and the return channel is located outside the transmission cavity. The return channel is used to guide the oil in the transmission cavity to flow in the reverse direction. Along the axis of the hydraulic cylinder, several fan blades one and several fan blades two are respectively arranged on both sides of the transmission cavity. Several fan blades one are installed on the input shaft, and several fan blades two are installed on the output shaft.

2. The wind turbine gearbox transmission buffer mechanism according to claim 1, characterized in that, The fan blade includes a flat blade area that is coplanar with the axis of the oil cylinder and an oblique blade area that is inclined relative to the axis of the oil cylinder. The second fan blade includes a section one used in conjunction with the flat blade section and a section two used in conjunction with the oblique blade section.

3. The wind turbine gearbox transmission buffer mechanism according to claim 1, characterized in that, The return channel includes a DC channel coaxial with the oil cylinder and a first guide channel and a second guide channel located at both ends of the DC channel. The first guide channel is used in conjunction with the first fan blade and is used to guide and transport oil along the axial direction of the oil cylinder. The second guide channel is used in conjunction with the second fan blade and is used to guide and transport oil along the radial direction of the oil cylinder.

4. The wind turbine gearbox transmission buffer mechanism according to claim 1, characterized in that, The hydraulic cylinder includes a cylinder body one, a cylinder body two, and a filling cylinder. The cylinder body one and the cylinder body two are connected to form a closed chamber. The filling cylinder is located in the closed chamber and divides the closed chamber into a transmission chamber located inside the filling cylinder and a return channel located outside the filling cylinder. The filling cylinder is connected to either cylinder one or cylinder two via several connecting seats.

5. A wind turbine gearbox transmission buffer mechanism according to claim 2, characterized in that, The shape of the first section along the circumference of the oil cylinder is arc-shaped. The inner wall of the arc-shaped section is provided with a plurality of guide grooves and a plurality of side edges along the axis of the oil cylinder. The side edges are inclined relative to the first section. The second section is arc-shaped along both the axial and radial directions of the cylinder.

6. The wind turbine gearbox transmission buffer mechanism according to claim 3, characterized in that, A guide plate is provided inside the transmission cavity. The guide plate is connected to the output shaft. The cross-sectional shape of the guide plate on one side of the cylinder axis is arc-shaped. The guide plate is used in conjunction with the second flow channel.

7. A wind turbine gearbox transmission buffer mechanism according to claim 6, characterized in that, The guide plate is provided with several flow restrictors, which are distributed around the axis of the oil cylinder. Adjacent flow restrictors form a flow restricting slit, and the width of the flow restricting slit gradually decreases in the direction away from the axis of the oil cylinder.

8. A wind turbine gearbox transmission buffer mechanism according to claim 2, characterized in that, An auxiliary structure is provided between the input shaft and the output shaft within the transmission cavity. The auxiliary structure is used to receive the kinetic power of the oil between the input shaft and the output shaft.

9. A wind turbine gearbox transmission buffer mechanism according to claim 8, characterized in that, The auxiliary structure includes a groove formed at the end of the output shaft and a support column located in the groove. The support column is coaxial with the oil cylinder. The end of the support column is close to or rotatably connected to the end of the input shaft. A spiral blade is provided on the outer wall of the support column. Several oil drain slits communicating with the groove are formed on the outer wall of the output shaft. The oil drain seam is aligned with the arc-shaped inner wall of the first section.

10. A wind turbine gearbox transmission buffer mechanism according to claim 1, characterized in that, The hydraulic cylinder is rotatably mounted around its own axis, and is connected to the output shaft via a transmission structure, which transmits the rotational kinetic energy of the hydraulic cylinder to the output shaft.

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