A wind turbine gearbox transmission damping mechanism

Abstract

The present application relates to the technical field of transmission structure, and particularly relates to a wind turbine gear box transmission buffering mechanism, which comprises an oil cylinder, an input shaft and an output shaft installed at 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, the inside of the oil cylinder is provided with a transmission cavity and a backflow channel, the backflow channel is located outside the transmission cavity, and the backflow channel is used for guiding the reverse flow of oil in the transmission cavity; through the oil transmission, the power transmitted to the gear box by the impeller under the condition of unstable external airflow can be smoothly and buffered, the gear box can be stably operated, the dramatic fluctuation of the rotating speed or the load is reduced, the instantaneous impact caused by the sudden change of the rotating speed between the gears is reduced, the gear box can be effectively protected, the friction loss of each transmission part is reduced, the service life is prolonged, and the equipment failure rate is reduced.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of transmission structure, and particularly relates to a wind turbine gearbox transmission buffering mechanism. BACKGROUND

[0002] Under the background of global response to climate change and realization of the "double carbon" target, the development and utilization of clean energy has become the core of the energy strategy of various countries in the world. Wind energy is widely used due to its characteristics of no pollution, renewable, large reserves and the like.

[0003] In engineering practice, due to the randomness and uncertainty of wind conditions, such as frequent changes in wind speed and wind direction, the impeller and gearbox in the wind turbine will bear alternating loads, resulting in fatigue damage. At the same time, the mechanical movements such as gear meshing and bearing rotation in the gearbox will also cause wear, cracks and other failures. The comprehensive statistics and analysis of the operation data of many domestic wind farms show that the failure of the impeller-gearbox system accounts for more than 60% of the total failure of the wind turbine. SUMMARY

[0004] The wind turbine gearbox transmission buffering mechanism provided in the present application can effectively solve the problems in the background art.

[0005] In order to achieve the above-mentioned purpose, the technical scheme adopted by the present application is as follows:

[0006] A wind turbine gearbox transmission buffering mechanism, comprising an oil cylinder and an input shaft and an output shaft installed at both ends of the oil cylinder, the end of the input shaft and the end of the output shaft both extend into the oil cylinder, the oil cylinder has a transmission cavity and a backflow channel inside, and the backflow channel is located outside the transmission cavity, and the backflow channel is used to guide the reverse flow of oil in the transmission cavity.

[0007] Along the oil cylinder axis direction, a plurality of fan blades one and a plurality of fan blades two are arranged on both sides of the transmission cavity, the plurality of fan blades one are installed on the input shaft, and the plurality of fan blades two are installed on the output shaft.

[0008] In some embodiments of the present application, the fan blade one comprises a flat leaf area coplanar with the oil cylinder axis and an inclined leaf area inclined relative to the oil cylinder axis.

[0009] The fan blade two comprises a piece area one used in cooperation with the flat leaf area and a piece area two used in cooperation with the inclined leaf area.

[0010] In some embodiments of the present application, the return flow channel comprises a straight flow channel coaxial with the oil cylinder and two flow guide channels located at both ends of the straight flow channel, the first flow guide channel is used in cooperation with the first vane and is used to guide the oil to flow along the axial direction of the oil cylinder, and the second flow guide channel is used in cooperation with the second vane and is used to guide the oil to flow along the radial direction of the oil cylinder.

[0011] In some embodiments of the present application, the oil cylinder comprises a cylinder body one, a cylinder body two and a filling cylinder, the cylinder body one is connected with the cylinder body two and forms a closed chamber, the filling cylinder is located in the closed chamber, and the filling cylinder divides the closed chamber into a transmission cavity located inside the filling cylinder and a return flow channel located outside the filling cylinder.

[0012] Wherein, the filling cylinder is connected with the cylinder body one or the cylinder body two through a plurality of connecting seats.

[0013] In some embodiments of the present application, the shape of the first area along the circumferential direction of the oil cylinder is arc-shaped, a plurality of flow guide grooves and a plurality of side edges are arranged on the arc-shaped inner wall of the first area along the axial direction of the oil cylinder, and the side edges are inclined relative to the first area.

[0014] The shape of the second area along the axial direction and the radial direction of the oil cylinder is arc-shaped.

[0015] In some embodiments of the present application, a flow guide disc is arranged inside the transmission cavity, the flow guide disc is connected with the output shaft, the cross-sectional shape of the flow guide disc on one side of the oil cylinder axis is arc-shaped, and the flow guide disc is used in cooperation with the second flow guide channel.

[0016] In some embodiments of the present application, a plurality of flow limiting bodies are arranged on the flow guide disc, the plurality of flow limiting bodies are distributed around the oil cylinder axis, two adjacent flow limiting bodies form a flow limiting gap, and the width of the flow limiting gap gradually decreases away from the oil cylinder axis.

[0017] In some embodiments of the present application, an auxiliary structure is arranged between the input shaft and the output shaft in the transmission cavity, and the auxiliary structure is used to receive the movement power of the oil between the input shaft and the output shaft.

[0018] In some embodiments of the present application, the auxiliary structure comprises a groove opened 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 rotationally connected with the end of the input shaft, a helical fin is arranged on the outer wall of the support column, and a plurality of oil discharge grooves are opened on the outer wall of the output shaft and are in communication with the groove.

[0019] The oil discharge gap is aligned with the arc-shaped inner wall of the first section.

[0020] In some embodiments of the present application, the oil cylinder is rotatably arranged around its own axis, and the oil cylinder and the output shaft are connected through a transmission structure, which is used to transmit the rotational kinetic energy of the oil cylinder to the output shaft.

[0021] The technical scheme of the present application can achieve the following technical effects:

[0022] By using oil transmission, the power transmitted from the impeller to the gear box can be smoothly and buffered under unstable external airflow, so that the gear box can operate stably, the drastic fluctuation of the rotation speed or load is reduced, the instantaneous impact caused by sudden change of the rotation speed between gears is reduced, the gear box is effectively protected, the friction loss of each transmission component is reduced, the service life is prolonged, and the equipment failure rate is reduced. BRIEF DESCRIPTION OF DRAWINGS

[0023] In order to more clearly illustrate the technical scheme in the embodiments of the present application or the prior art, the drawings needed in the following embodiment or prior art description will be briefly introduced. Obviously, the drawings in the following description are only some embodiments of the present application, and those skilled in the art can obtain other drawings according to these drawings without creative labor.

[0024] Figure 1 is a structural schematic diagram of the present application;

[0025] Figure 2 is a sectional view of the oil cylinder in the embodiment of the present application;

[0026] Figure 3 is an exploded structural schematic diagram of the present application;

[0027] Figure 4 is a structural schematic diagram of the first cylinder body in the embodiment of the present application;

[0028] Figure 5 is a structural schematic diagram of the filling cylinder in the embodiment of the present application;

[0029] Figure 6 is a structural schematic diagram of the flow guide disc in the embodiment of the present application;

[0030] Figure 7 is a structural schematic diagram of the second fan blade in the embodiment of the present application;

[0031] Figure 8 is Figure 7 is a structural schematic diagram from another perspective;

[0032] Figure 9is a structural schematic diagram of a helical blade in the embodiment of the present application;

[0033] Figure 10 is a sectional structural schematic diagram of an outer sleeve in the embodiment of the present application.

[0034] Reference signs:

[0035] 100, oil cylinder; 101, transmission cavity; 102, backflow channel; 103, straight-flow channel; 104, flow guide channel one; 105, flow guide channel two; 106, cylinder one; 107, cylinder two; 108, filling cylinder; 109, connecting seat; 110, push plate; 111, outer sleeve; 112, tapered cylinder; 113, transmission cone wheel; 114, bevel gear one; 115, bevel gear two; 116, fixed frame; 117, rotating wheel; 118, multi-ribbed threaded pipe; 119, threaded rod; 120, adjusting motor;

[0036] 200, input shaft; 201, fan blade one; 202, flat blade area; 203, inclined blade area;

[0037] 300, output shaft; 301, fan blade two; 302, blade area one; 303, blade area two; 304, flow guide groove; 305, side edge; 306, flow guide disc; 307, flow limiting body; 308, support column; 309, helical blade; 310, oil discharge gap. DETAILED DESCRIPTION

[0038] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all the embodiments of the present application.

[0039] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used in the description of the application herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the application. As used in this description, the term "and / or" includes any and all combinations of one or more of the associated listed items.

[0040] As Figures 1 to 2 shown, the wind turbine gearbox transmission buffer mechanism of the present application comprises an oil cylinder 100 and an input shaft 200 and an output shaft 300 installed at both ends of the oil cylinder 100, the end of the input shaft 200 and the end of the output shaft 300 both extend into the oil cylinder 100, the oil cylinder 100 has a transmission cavity 101 and a backflow channel 102 inside, and the backflow channel 102 is located outside the transmission cavity 101, the backflow channel 102 is used for guiding the reverse flow of oil in the transmission cavity 101;

[0041] A plurality of fan blades one 201 and a plurality of fan blades two 301 are arranged on both sides of the transmission cavity 101 along the axis direction of the oil cylinder 100, the plurality of fan blades one 201 are installed on the input shaft 200, and the plurality of fan blades two 301 are installed on the output shaft 300;

[0042] In the present application, the oil cylinder 100 stores oil for transmission, which can be mineral oil, hydraulic transmission oil, emulsion, etc. Of course, in some cases where the lubricity requirement is low, water can also be used to replace oil, which can greatly reduce the cost. The input shaft 200 and the output shaft 300 are connected with the impeller and the gear box respectively. Since the flow direction of the oil is mainly guided by the internal space of the oil cylinder 100, the relative position relationship of the input shaft 200 and the output shaft 300 can adopt coaxial, axis parallel and interlaced, axis relative inclination and other ways, which are all within the protection scope of the present application. For example, when the axis of the input shaft 200 and the output shaft 300 is relatively inclined, the internal space of the oil cylinder 100 is also at a certain angle. Thus, by the flowability of the oil, the power of the input shaft 200 can be transmitted to the output shaft 300, thereby facilitating the reversing adjustment of the power transmission direction. The above-mentioned way is not shown in the drawings. Of course, the input shaft 200 and the output shaft 300 can also adopt the coaxial way, as shown in the figure. Thus, only the lateral flow of the oil is needed. Figure 2

[0043] The transmission cavity 101 and the return channel 102 are mainly used to guide the flow of the oil. The transmission cavity 101 is located in the middle of the return channel 102. When the oil flows from the transmission cavity 101 to the right, the oil will spread from the right side of the transmission cavity 101 to the surrounding 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 cavity 101, thereby making the oil circulate between the transmission cavity 101 and the return channel 102. The oil in the transmission cavity 101 always maintains a one-way flow state, which can provide a constant liquid flow environment for the fan blades one 201 and the fan blades two 301.

[0044] ​In use, the wind drives the impeller to rotate, the impeller drives the input shaft 200 and a plurality of fan blades one 201 to rotate, the plurality of fan blades one 201 can drive the oil in the transmission cavity 101 to flow, thereby providing power for the oil, the oil flows in the transmission cavity 101 along the oil cylinder 100 axis direction, when the oil flows to the fan blade two 301 position, the oil drives a plurality of fan blades two 301 to rotate, thereby using the oil to transmit the power of the input shaft 200 to the output shaft 300, the output shaft 300 drives the gear box to rotate; The oil near the fan blade two 301 will use the rotating motion of the fan blade two 301 to make the oil centrifugal into the backflow channel 102, the oil in the backflow channel 102 flows in the reverse direction to the fan blade one 201, thereby making the oil continuously and cyclically transmit power; When the external wind speed and wind direction change frequently, the rotation speed of the input shaft 200 changes frequently, at this time the pushing force transmitted by the plurality of fan blades one 201 to the oil is unstable, the oil uses its flowability and internal friction to buffer the pushing force, thereby gradually stabilizing with the flow of the oil, and then the oil transmits the stable pushing force to the output shaft 300, thereby realizing the transmission buffering effect;

[0045] By using oil transmission, the power transmitted by the impeller to the gear box can be smoothly and buffered under the condition of unstable external airflow, so that the gear box can operate stably, the dramatic fluctuations of the rotation speed or load are reduced, the instantaneous impact caused by the sudden change of the rotation speed between gears is reduced, the gear box is effectively protected, the friction loss of each transmission component is reduced, the service life is prolonged, and the equipment failure rate is reduced.

[0046] In the process of the fan blade one 201 driving the oil to flow and the oil driving the fan blade two 301 to rotate, in order to improve the transmission effect between the oil and the fan blade one 201 and the fan blade two 301, the mode shown in Figure 4 and Figure 7 The fan blade one 201 includes a flat blade area 202 coplanar with the oil cylinder 100 axis and a inclined blade area 203 inclined opposite to the oil cylinder 100 axis;

[0047] The fan blade two 301 includes a piece area one 302 used in cooperation with the flat blade area 202 and a piece area two 303 used in cooperation with the inclined blade area 203;

[0048] In the above description, the flat blade area 202 and the first blade area 302 are coplanar with the oil cylinder 100 axis, and the inclined blade area 203 and the second blade area 303 are inclined relative to the oil cylinder 100 axis; when the input shaft 200 drives the fan blade one 201 to rotate, the inclined blade area 203 pushes the oil to flow, at this time, the oil performs spiral flow in the transmission cavity 101, that is, the oil has movement forms in the oil cylinder 100 axis direction and the circumferential direction, the flat blade area 202 pushes the oil to flow around the oil cylinder 100 circumferential direction, thereby strengthening the flow effect of the oil in the oil cylinder 100 circumferential direction, when the oil flows to the fan blade two 301 position, the circumferential flow of the oil acts on the first blade area 302, and the flow of the oil in the oil cylinder 100 axis direction acts on the second blade area 303, thereby facilitating full use of the flow kinetic energy of the oil in each direction, improving the power transmission efficiency, and reducing energy loss.

[0049] It should be pointed out that, in order to facilitate receiving the flow power of the oil in the oil cylinder 100 circumferential direction, the inclination direction of the second blade area 303 is opposite to the inclination direction of the inclined blade area 203, so as to increase the included angle between the oil flow direction and the second blade area 303, improve the effectiveness of the oil pushing the second blade area 303 to rotate, and thereby improve the energy transmission effect.

[0050] When the oil enters or flows out of the backflow channel 102, in order to improve the cooperation transmission effect of the oil and the fan blade one 201 and the fan blade two 301, as shown in Figure 2 The backflow channel 102 includes a straight channel 103 coaxial with the oil cylinder 100 and a flow guide channel one 104 and a flow guide channel two 105 located at both ends of the straight channel 103, the flow guide channel one 104 is used in cooperation with the fan blade one 201, and is used for guiding and conveying the oil in the oil cylinder 100 axis direction, the flow guide channel two 105 is used in cooperation with the fan blade two 301, and is used for guiding and conveying the oil in the oil cylinder 100 radial direction;

[0051] Based on the above description, when the oil is centrifugally diffused by the rotation of the fan blade two 301, the arc angle of the flow guide channel two 105 is 90°, so that the centrifugally diffused oil directly enters the flow guide channel two 105, or on this basis, the arc angle of the flow guide channel two 105 can be adjusted according to the oil flow direction guided by the fan blade two 301;

[0052] When the oil flows into the transmission cavity 101 through the flow guide channel one 104, since the fan blade one 201 is not easy to utilize the oil flowing in the oil cylinder 100 radial direction, it is necessary to make the oil discharged from the flow guide channel one 104 flow in the oil cylinder 100 axis direction, that is, to guide the oil by the flow guide channel one 104, thereby facilitating the oil to be directly used in cooperation with the fan blade one 201; the arc angle of the flow guide channel one 104 can be 180°;

[0053] 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.

[0054] 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.

[0055] The filling cylinder 108 is connected to cylinder one 106 or cylinder two 107 via several connecting seats 109.

[0056] 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.

[0057] 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.

[0058] The shape of section 2 303 along both the axial and radial directions of the hydraulic cylinder 100 is arc-shaped;

[0059] 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.

[0060] 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.

[0061] 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.

[0062] 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.

[0063] like Figure 6 As 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.

[0064] 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.

[0065] 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.

[0066] 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.

[0067] Among them, the oil drain joint 310 is aligned with the arc-shaped inner wall of section 302;

[0068] 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.

[0069] 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.

[0070] 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.

[0071] 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.

[0072] 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.

[0073] like Figure 10As shown, the transmission structure comprises an outer sleeve 111 fixed to the outer wall of the second cylinder body 107, the end of the outer sleeve 111 is provided with a tapered cylinder 112, the tapered cylinder 112 is provided with a transmission bevel gear 113, the tapered cylinder 112 and the transmission bevel gear 113 are driven through the inclined rotating wheel 117; the output shaft 300 is provided with a bevel gear one 114, the bevel gear one 114 is engaged with a bevel gear two 115, the bevel gear two 115 and the transmission bevel gear 113 are provided with a fixed frame 116, and the bevel gear two 115 and the transmission bevel gear 113 are both rotatably installed on the fixed frame 116, the bevel gear two 115 and the transmission bevel gear 113 are in transmission connection, the fixed frame 116 is provided with an adjusting motor 120, the output end of the adjusting motor 120 is provided with a threaded rod 119, the threaded rod 119 is coaxially sleeved with a multi-ribbed threaded pipe 118, and the multi-ribbed threaded pipe 118 is in threaded connection with the threaded rod 119, the multi-ribbed threaded pipe 118 is slidably arranged on the fixed frame 116, and the rotating wheel 117 is in transmission connection with the multi-ribbed threaded pipe 118; when the second cylinder body 107 rotates, it will drive the outer sleeve 111 and the tapered cylinder 112 to rotate, the tapered cylinder 112 drives the transmission bevel gear 113 to rotate through the rotating wheel 117, and the transmission bevel gear 113 drives the output shaft 300 to rotate through the bevel gear two 115 and the bevel gear one 114, so as to transmit the power of the oil cylinder 100 to the output shaft 300; the adjusting motor 120 can drive the multi-ribbed threaded pipe 118 to move on the fixed frame 116 by rotating the threaded rod 119, so as to adjust the position of the rotating wheel 117 between the tapered cylinder 112 and the transmission bevel gear 113, and facilitate the adjustment of the transmission ratio between the tapered cylinder 112 and the transmission bevel gear 113, so that the rotation speed of the oil cylinder 100 matches the rotation speed of the output shaft 300.

[0074] The basic principles, main features and advantages of the present application are shown and described above. It should be understood by those skilled in the art that the present application is not limited by the above examples, and the above examples and descriptions in the specification are only to illustrate the principles of the present application. Without departing from the spirit and scope of the present application, various changes and improvements can be made to the present application, and these changes and improvements all fall within the scope of the claimed present application. The scope of protection of the present application 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. 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; An auxiliary structure is provided between the input shaft and the output shaft in the transmission cavity. The auxiliary structure is used to receive the kinetic power of the oil between the input shaft and the output shaft. 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.

2. 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.

3. 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.

4. The wind turbine gearbox transmission buffer mechanism according to claim 1, 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.

5. A wind turbine gearbox transmission buffer mechanism according to claim 2, 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.

6. The wind turbine gearbox transmission buffer mechanism according to claim 5, 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.

7. The 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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