Sealing assembly for wind generating set

Abstract

The utility model discloses a sealing assembly for a wind generating set. The sealing assembly comprises a main shaft and a sealing ring. The sealing ring comprises a sealing ring seat, a sealing strip and a plurality of compression springs, wherein the sealing ring seat is of an annular structure; wherein the sealing ring seat comprises a sealing groove, and the sealing groove is an annular groove formed in the sealing ring seat and is coaxial with the sealing ring seat; the sealing groove extends from the inner circumferential surface of the sealing ring seat in the radial direction of the sealing ring seat and is not communicated with the outer circumferential surface of the sealing ring seat; the sealing strip is of an annular structure; the compression spring is a spiral spring for bearing the radial pressure of the main shaft; the sealing strip is arranged in the sealing groove, and the compression spring is arranged between the bottom surface of the sealing groove and the outer circumferential surface of the sealing strip; the compression direction of the compression spring coincides with the radial direction of the sealing strip, and radial pressure is provided for the sealing strip so that the sealing strip can be tightly pressed on the surface of the main shaft.

Description

Technical Field

[0001] The utility model relates to a sealing component facing a wind power generator set, belonging to the technical field of wind power generation equipment. Background Art

[0002] Wind turbines are important equipment for utilizing wind energy, and the main shaft bearings and main transmission systems are indispensable core components of wind turbines. These key components are essential to ensure the stable operation and long-term performance of wind turbines. In order to effectively ensure the rotation and power generation of the unit and the safety of equipment operation, the main bearings are usually lubricated with grease or thin oil. Its main functions include: ① reducing bearing friction and wear; ② extending bearing fatigue life; ③ enhancing bearing heat dissipation and cooling; ④ preventing foreign matter from invading the bearing; ⑤ preventing rust and corrosion; ⑥ alleviating impact and reducing vibration.

[0003] The lubrication of rolling bearings is essential for maintaining bearings, improving equipment performance and extending service life. Although bearing sealing technology, especially lip seals made of high-performance materials such as polyurethane rubber, nitrile rubber and hydrogenated nitrile rubber, has been widely used to prevent the leakage of grease or thin oil, in the actual operation of wind turbines, due to the ever-changing load conditions and severe challenges of the external environment, the problem of bearing grease and oil leakage is still difficult to completely avoid. Insufficient lubrication will not only significantly shorten the service life of the bearing, but may also cause the bearing to become stuck due to excessive wear, which in turn causes equipment failure, requiring the use of heavy lifting equipment to replace shaft system components, and causing power generation losses due to downtime.

[0004] Grease or oil leakage may also threaten the personal safety of maintenance personnel, pollute the wind turbine equipment and the surrounding environment, and affect the appearance of the equipment. Therefore, improving the bearing sealing performance and the reliability of the lubrication system and reducing the risk of grease or oil leakage are crucial to protecting the bearings, ensuring the safety of maintenance personnel, preventing environmental pollution, and maintaining the appearance of the equipment. This will help reduce maintenance costs and improve the overall performance and safety of wind turbines. Summary of the invention

[0005] The primary technical problem to be solved by the utility model is to provide a sealing component for a wind turbine generator set.

[0006] In order to achieve the above technical objectives, the utility model adopts the following technical solutions:

[0007] A sealing assembly for a wind turbine generator set comprises a main shaft and a sealing ring, wherein the sealing ring comprises a sealing ring seat, a sealing strip and a plurality of compression springs; wherein:

[0008] The sealing ring seat is an annular structure, and the minimum inner diameter of the inner circumferential surface is a; wherein,

[0009] The sealing ring seat comprises a sealing groove, which is an annular groove formed on the sealing ring seat and is coaxial with the sealing ring seat; the sealing groove extends from the inner circumferential surface of the sealing ring seat along the radial direction of the sealing ring seat and is not connected with the outer circumferential surface of the sealing ring seat; the diameter of the bottom surface of the sealing groove is b; the sealing strip is an annular structure, the outer diameter c is less than or equal to b, the inner diameter d is less than a, and the thickness is f;

[0010] The sealing strip is arranged in the sealing groove; the compression spring is a coil spring that withstands the radial pressure of the main shaft and is arranged between the bottom surface of the sealing groove and the outer circumferential surface of the sealing strip; the compression direction of the compression spring coincides with the radial direction of the sealing strip, providing radial pressure for the sealing strip to press the sealing strip against the surface of the main shaft.

[0011] Preferably, the sealing ring seat further comprises a tiny pit; wherein the tiny pit is arranged on two opposite side surfaces of the sealing groove, and the area of ​​the tiny pit and the side surfaces accounts for 7% to 9%.

[0012] Preferably, the sealing strip further comprises an oil storage groove; the oil storage groove is arranged on the third sealing surface of the sealing strip and is a groove structure extending along the circumferential direction of the sealing strip.

[0013] Preferably, the surface roughness of two opposite side surfaces of the sealing groove is Ra0.8-Ra0.2; and the width dimension e of the sealing groove is smaller than the thickness f of the sealing strip.

[0014] Preferably, the sealing assembly further comprises packing; wherein,

[0015] The sealing ring seat comprises a plurality of sealing grooves, the sealing ring comprises a plurality of sealing strips, and the sealing strips correspond to the sealing grooves;

[0016] The packing is arranged between two adjacent sealing grooves and contacts the inner circumferential surface of the sealing ring seat; the position of the packing along the axial direction of the sealing ring is limited by the sealing strips in the adjacent sealing grooves.

[0017] Preferably, the sealing ring seat further comprises a plurality of ring seat pin holes; wherein,

[0018] The axial direction of the ring seat pin hole is parallel to the axial direction of the sealing ring seat, and passes through the two axial end faces of the sealing ring seat and the two axial side faces of the sealing groove; the plurality of ring seat pin holes are evenly distributed in a circular array with the axial direction of the sealing ring seat as the symmetric center;

[0019] The sealing strip further comprises a plurality of sealing strip pin holes; the axial direction of the sealing strip pin holes is parallel to the axial direction of the sealing strip, and penetrates the first sealing surface and the second sealing surface; the positions of the sealing strip pin holes correspond to the ring seat pin holes.

[0020] Preferably, the sealing ring seat further includes a positioning blind hole; wherein,

[0021] The bottom surface of the sealing groove is provided with a plurality of positioning blind holes, and the positioning blind holes extend from the bottom surface of the sealing groove to the outer circumferential surface of the sealing ring seat and are not connected with the outer circumferential surface of the sealing ring seat; the axial direction of the positioning blind holes is parallel to the radial direction of the sealing ring seat and is perpendicular to the axial direction of the sealing ring seat; the diameter of the inscribed circle of the positioning blind holes is larger than the outer diameter of the compression spring, and is used for setting the compression spring.

[0022] Preferably, the sealing strip further comprises a spring blind hole; wherein,

[0023] The position of the spring blind hole corresponds to the positioning blind hole, extending from the outer circumferential surface to the inner circumferential surface of the sealing strip, and not connected to the inner circumferential surface of the sealing strip; the axial direction of the spring blind hole is parallel to the radial direction of the sealing strip and perpendicular to the axial direction of the sealing strip; the diameter of the inscribed circle of the spring blind hole is larger than the outer diameter of the compression spring, and is used to set the compression spring.

[0024] Preferably, the sealing assembly further comprises a guide pin; wherein,

[0025] The guide pin is a rod-shaped structure with a longitudinal direction and a T-shaped longitudinal section; the guide pin is arranged in the spring blind hole, its large diameter end contacts the bottom of the spring blind hole, and its small diameter end extends upward along the spring blind hole; the compression spring is sleeved on the outside of the guide pin, and the two are coaxial.

[0026] Preferably, the sealing strip comprises a plurality of sealing strip petals; the sealing strip petals are independent parts and are designed to overlap each other to form an annular structure; a plurality of sealing strip petals overlap each other to form an annular structure of the sealing strip; the first sealing surface and the second sealing surface of the sealing strip are flat and have no protrusions.

[0027] Compared with the prior art, the sealing assembly for wind turbines provided by the embodiment of the utility model is formed by overlapping a plurality of sealing strips into an annular sealing strip, which is compressed by a compression spring and contacts the main shaft surface to form a fluid sealing structure. The characteristics of the wear-resistant, friction-reducing and self-lubricating composite material are utilized to directly contact the main shaft surface and generate sliding friction to prevent fluid leakage. A plurality of compression springs are used to provide uniform and constant pressure to the sealing strip, and an oil pocket is formed by tiny pits to lubricate the side of the sealing strip, reduce the friction loss between the sealing ring seat, and balance the spring force and the friction force of the sealing strip. The space between adjacent sealing strips is filled with packing to increase the length of the main shaft sealing structure. Such reliable axial and radial sealing improves the sealing performance and reliability in long-term use. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] Figure 1 This is a schematic diagram of a partial structure of a sealing ring of a main shaft of a wind turbine generator set in the first embodiment of the utility model;

[0029] Figure 2 for Figure 1 An exploded schematic diagram of the sealing ring in FIG.

[0030] Figure 3 This is a structural schematic diagram of the M section in the first embodiment of the utility model;

[0031] Figure 4 for Figure 3 A schematic diagram of the structure of the sealing ring seat;

[0032] Figure 5 for Figure 3 A schematic diagram of the structure of the sealing strip;

[0033] Figure 6 This is a schematic structural diagram of a cross section of a sealing ring M in the second embodiment of the utility model;

[0034] Figure 7 It is a partial schematic diagram of the side surface N of the sealing groove of the sealing ring seat in the third embodiment of the utility model;

[0035] Figure 8 This is a schematic structural diagram of a cross section of a sealing ring M in a fourth embodiment of the present utility model;

[0036] Fig. 9 This is a structural schematic diagram of a cross section of a sealing ring M in the fifth embodiment of the utility model;

[0037] Fig.10 Schematic diagram of the structure of the sealing component M section in the sixth embodiment of the present utility model. DETAILED DESCRIPTION

[0038] The technical content of the present utility model is described in detail below with reference to the accompanying drawings and specific embodiments.

[0039] The technical concept in the embodiment of the utility model is: a split-structure sealing strip is used to form a circumferential contact seal, an end face contact seal and a packing seal. Wear-resistant and friction-reducing self-lubricating sealing materials, oil storage tanks, tiny oil storage pits and sealing overlaps are used to prevent fluid from leaking outward along the main shaft surface. Specifically, multiple compression springs apply force evenly to press the sealing surface of the sealing strip against the main shaft surface. The sealing strip and the sealing ring seat are interference fit to prevent fluid from leaking out along the contact surface between the sealing strip and the sealing ring seat. A tiny recessed structure is provided on the surface of the sealing seat ring that contacts the sealing strip, and the leaked fluid is retained in the recessed structure to form an oil pocket and an oil film to reduce the friction coefficient and ensure that the sealing strip can reciprocate without getting stuck.

[0040] It should be noted that in the embodiment of the present invention, the Z direction is the axial direction of the main shaft of the wind turbine generator set, the X direction is the horizontal direction perpendicular to the Z direction, and the Y direction is the vertical direction. The M plane is a virtual section that coincides with the Y direction and the Z direction.

[0041] First embodiment

[0042] like Figure 1 to Figure 3 As shown, the sealing ring 100 includes a sealing ring seat 1, a sealing strip 2 and a compression spring 3. Among them, the sealing ring seat 1 is the structural support component of the sealing ring, which supports and positions the sealing strip 2 and the compression spring 3 in space. The sealing strip 2 is made of a wear-resistant, friction-reducing and self-lubricating composite material, which is used to contact the main shaft and prevent fluid leakage, and has the characteristics of oil resistance, high temperature resistance, and self-lubrication. The compression spring 3 is used to apply radial pressure to the sealing strip 2 so that the sealing strip 2 presses the main shaft and blocks the leakage path of the fluid on the main shaft surface. The sealing strip 2 includes a plurality of sealing strip petals 21, which are spliced ​​together to form an annular full-circle structure. In engineering practice, the sealing strip 2 includes one or more sealing strip petals 21. This embodiment takes the sealing ring 2 as an example including six sealing strip petals 21.

[0043] like Figure 4 As shown, the sealing ring seat 1 is an annular structure, the inner circumferential surface is the surface (J surface) in contact with the main shaft of the wind turbine generator set, and the minimum inner diameter size is a. The outer circumferential surface is the K surface. In engineering practice, the sealing ring seat 1 includes a double-piece or multi-piece structure. This embodiment takes the sealing ring seat 1 as an example of a double-piece structure, that is, the sealing ring seat 1 includes an upper and lower half or a left and right half.

[0044] On the J surface of the sealing ring seat 1, a single or multiple sealing grooves 11 and multiple positioning blind holes 12 are opened along the radial direction of the sealing ring seat 1. The sealing groove 11 is an annular groove on the sealing ring seat 1, coaxial with the sealing ring seat 1. The sealing groove 11 extends from the inner circumferential surface J of the sealing ring seat 1 to the radial direction of the sealing ring seat 1, and is not connected with the outer circumferential surface K of the sealing ring seat 1. The diameter size of the bottom surface L of the sealing groove 11 is b. In this embodiment, the sealing ring seat 1 is provided with two sealing grooves 11 as an example, and the two sealing grooves 11 are arranged along the axial direction of the sealing ring seat 1 and are coaxially arranged.

[0045] The positioning blind hole 12 is a hole structure with a longitudinal direction. The bottom surface of the sealing groove 11 is provided with a plurality of positioning blind holes 12, and the axial direction of the positioning blind holes 12 is parallel to the radial direction of the sealing ring seat 1 and perpendicular to the axial direction of the sealing ring seat 1. The positioning blind holes 12 extend from the bottom surface L of the sealing groove 11 to the outer circumferential surface K of the sealing ring seat 1, and are not connected to the outer circumferential surface K of the sealing ring seat 1.

[0046] For easy installation, the sealing ring seat 1 provided in this embodiment adopts a petal structure, including multiple petals of the sealing ring seat 1, and the petals of each sealing ring seat 1 are connected to form an annular full circle structure by bolts, etc. This part is a well-known technology and will not be repeated here.

[0047] like Figure 5 As shown, the sealing strip 2 is a circular ring structure, the outer diameter dimension c is smaller than the diameter dimension b of the bottom surface L of the sealing groove 11, and the inner diameter dimension d is smaller than the inner diameter dimension a of the sealing ring seat 1. The radial cross section of the sealing strip 2 is rectangular, including a first sealing surface R, a second sealing surface S and a third sealing surface T. Among them, the first sealing surface R and the second sealing surface S are the opposite surfaces of the sealing strip 2 along the axial direction, and are annular; the third sealing surface T is the inner circumferential surface of the sealing strip 2, and the surface in contact with the main shaft of the wind turbine generator set. The thickness dimension f of the sealing strip 2 is greater than the width dimension e of the sealing groove 11.

[0048] Preferably, the sealing strip 2 further comprises a plurality of oil storage grooves 24. The oil storage grooves 24 are arranged on the third sealing surface T and are groove structures extending along the circumferential direction of the sealing strip 2. Preferably, the cross-sectional shapes of the oil storage grooves 24 include triangle, semicircle and sector.

[0049] The sealing strip 2 includes a plurality of sealing strip petals 21, each of which is an independent part and overlaps with each other to form an annular full-circle structure. An overlap structure is provided at both ends of the sealing strip petals 21, and the overlapping sealing strip petals 21 form an annular full-circle structure of the sealing strip 2. The first sealing surface R and the second sealing surface S of the sealing strip 2 are flat and have no protrusions.

[0050] The overlapping sealing strip petals 21 can slide freely, and each sealing strip petal 21 can gather (reduce the inner diameter) or expand (enlarge the inner diameter) in the axial direction to adapt to the diameter and radial runout of the main shaft. The overlapping parts of the sealing strip petals 21 are structures to prevent fluid leakage. The overlapping structure of the sealing strip petals 21 is a well-known technology and will not be described in detail here.

[0051] The outer circumferential surface of the sealing strip 2 further includes a plurality of spring blind holes 22, which are hole structures with a longitudinal direction, and whose positions correspond to the positioning blind holes 12. The spring blind holes 22 extend from the outer circumferential surface Q of the sealing strip 2 to the third sealing surface T (inner circumferential surface), and are not connected to the third sealing surface T of the sealing strip 2. The axial direction of the spring blind holes 22 is parallel to the radial direction of the sealing strip 2, and is perpendicular to the axial direction of the sealing strip 2.

[0052] The compression spring 3 is a spiral spring that bears axial pressure and is used to bear the radial pressure of the main shaft. The outer diameter of the compression spring 3 is smaller than the diameter of the inscribed circle of the positioning blind hole 12 and the spring blind hole 22.

[0053] The sealing strip 2 is arranged in the sealing groove 11 of the sealing ring seat 1, and the compression spring 3 is arranged in the positioning blind hole 12 and the spring blind hole 22. The compression direction is the radial direction of the sealing strip 2, and the sealing strip petals 21 are provided with pressure pointing to the axis of the sealing strip 2, so as to press the sealing strip 2 against the main shaft surface. The oil storage tank 24 is used to store and block the fluid, and the stored fluid is used to provide lubrication for the sliding friction between the third sealing surface T and the main shaft.

[0054] Because b>c, the sealing strip 2 has displacement space in the radial direction, and can automatically adjust its center with the radial runout of the main shaft under the action of the compression force of the compression spring 3, and always keep the third sealing surface T in contact with the main shaft surface to block the leakage path of the fluid, thereby forming a circumferential contact sealing structure.

[0055] Because f>e, there is an interference fit between the sealing groove 11 and the sealing strip 2. And because the contact surface between the sealing groove 11 and the sealing strip 2 is a plane, the fluid cannot leak out through the installation gap between the sealing strip 2 and the sealing ring seat 1. Thus, an end face contact sealing structure is formed.

[0056] Preferably, the sealing ring seat 1 is provided with an oil drain hole extending downward, connecting the bottom surface L of the sealing groove 11 and the outside atmosphere, so as to balance the pressure difference in the sealing groove 11 caused by the radial movement of the sealing strip 2. At the same time, with the wear of the equipment, the fluid may enter the space between the outer circumferential surface Q of the sealing strip 2 and the bottom surface L of the sealing groove 11, and the oil drain hole can discharge this part of the fluid to the outside.

[0057] It is worth noting that when the fluid enters the space between the outer circumferential surface Q of the sealing strip 2 and the bottom surface L of the sealing groove 11, it indicates that the sealing groove 11 and the sealing strip 2 are no longer an interference fit, but a transition fit or a clearance fit. At this time, the gap between the sealing groove 11 and the sealing strip 2 is equivalent to a labyrinth seal structure.

[0058] Second embodiment

[0059] Different from the above embodiment, Figure 6 As shown, the sealing ring 100 provided in the embodiment of the utility model further includes a limiting pin 4. The limiting pin 4 is a rod structure having a longitudinal direction.

[0060] The sealing ring seat 1 includes a plurality of ring seat pin holes 13. The axial direction of the ring seat pin holes 13 is parallel to the axial direction of the sealing ring seat 1, and penetrates the two axial end faces of the sealing ring seat 1 and the two axial side faces N of each sealing groove 11. The plurality of ring seat pin holes 13 are evenly distributed in a circular array with the axial direction of the sealing ring seat 1 as the symmetric center.

[0061] The sealing strip 2 includes a plurality of sealing strip pin holes 23. The axial direction of the sealing strip pin hole 23 is parallel to the axial direction of the sealing strip 2, and penetrates the first sealing surface R and the second sealing surface S. The position of the sealing strip pin hole 23 corresponds to the ring seat pin hole 13, and the diameter of the sealing strip pin hole 23 is greater than the diameter of the limit pin 4.

[0062] The limit pin 4 passes through the sealing strip pin hole 23 and the corresponding ring seat pin hole 13, limiting the radial movement range of the sealing strip 2 to prevent the sealing strip petal 21 from falling out of the sealing ring seat 1 when the spindle is not installed. At the same time, it will not hinder the rebound and reset action of the sealing strip 2 when the spindle radially runs out.

[0063] Third embodiment

[0064] Different from the above embodiment, Figure 7 As shown, the two opposite side surfaces N of the sealing groove 11 provided by the embodiment of the utility model, where the first sealing surface R and the second sealing surface S of the sealing strip 2 meet, have a contact surface roughness of Ra0.8 to Ra0.2, and are provided with micro-pits 14. The diameter of the circumscribed circle of the micro-pits 14 is 0.5 to 1.5 μm, the depth is 0.5 to 1.5 μm, and the density is 7% to 9% of the area. The micro-pits 14 are provided on the surface of the sealing groove 11 to store fluid during operation, forming micro-oil pockets, and having a certain fluid tension to reduce the friction coefficient between the sealing groove 11 and the sealing strip 2, while preventing fluid leakage.

[0065] The processing methods of the micro pits 14 include laser processing, etching and other processes.

[0066] In engineering practice, the outer circumferential surface of the sealing strip 2 has multiple (about two hundred) compression springs 3 to apply radial pressure to the sealing strip 2. Because the number of compression springs 3 is large and evenly distributed, with one spring distributed every 2 degrees on average, the pressure provided by a single compression spring 3 required by the sealing strip 2 is small, which is beneficial to improving the wear life and sealing performance of the seal.

[0067] Therefore, the force exerted by each compression spring 3 on the sealing strip 2 is small, making it possible to select a small-sized spring. This type of small-sized spring uses the Japanese imported piano steel material SWP-B, with uniform wire diameter and good consistency. The processed spring is treated with a tempering process, and the elastic stiffness and fatigue resistance are better through the material and process, which is more than 20 times that of ordinary springs. This small-sized spring ensures that the elastic force of each spring remains the same after long-term use, thereby ensuring the uniformity and reliability of the seal after long-term use. At the same time, the compression spring 3 is arranged between the sealing ring seat 1 and the sealing strip 2, and adopts a pre-compression design. The spring travel is ±1mm, the compression change is small, and the spring life is high, which extends the service life of the sealing ring.

[0068] Since the compression spring 3 is a small-sized spring, the force of each spring is also small, so the friction resistance between the first sealing surface R, the second sealing surface S and the side N of the sealing groove 11 is a very important factor affecting the compression spring 3. In order to ensure the "degree of freedom" of the compression spring 3 when it is extended and retracted, the friction resistance generated by the aforementioned friction surface must be small enough. However, in order to ensure the sealing performance, the embodiment of the utility model has an interference fit between the sealing groove 11 and the sealing strip 2, resulting in a large friction force.

[0069] Therefore, in this embodiment, a plurality of evenly distributed tiny pits 14 are provided on the side surface N of the sealing groove 11 to reduce the friction area, thereby reducing the friction force. Thus, a balance is achieved between the technical requirement of smaller friction force (resulting in small friction force) and the technical requirement of good sealing performance (resulting in large friction force).

[0070] The tiny dimples 14 not only reduce frictional resistance, but also play the role of oil storage. Preferably, when the area S14 of the tiny dimples 14 accounts for 7% to 9% of the area SN of the side surface N (S14 / SN), the effect of reducing frictional resistance is the best, the wear rate is the lowest, and the oil storage capacity is large. In this way, a balance between friction and oil storage capacity can be achieved.

[0071] Fourth embodiment

[0072] Different from the above embodiment, Figure 8As shown, the sealing ring 100 provided in the embodiment of the utility model further includes a packing 5. The packing 5 is arranged between two adjacent sealing grooves 11 and contacts the inner circumferential surface J of the sealing ring seat 1. The axial position of the packing 5 along the sealing ring 100 is limited by the sealing strip 2 in the adjacent sealing grooves 11. Packing seal is also called stuffing seal, which is a well-known technology and will not be described in detail here.

[0073] The packing 5 and the sealing strip 2 contact the main shaft together, blocking the leakage path of the fluid on the main shaft surface.

[0074] Fifth embodiment

[0075] Different from the above embodiment, Fig. 9 As shown, the sealing ring 100 provided by the embodiment of the utility model further includes a guide pin 6, and does not include a positioning blind hole 12. The guide pin 6 is a rod-shaped structure with a longitudinal direction, and the longitudinal section is T-shaped, that is, the diameters of the two ends of the guide pin 6 are significantly different.

[0076] The guide pin 6 is arranged in the spring blind hole 22, with its large diameter end in contact with the bottom of the spring blind hole 22, and its small diameter end extending upward along the spring blind hole 22. The compression spring 3 is sleeved on the outside of the guide pin 6, and the two are coaxial. The pressing force of the compression spring 3 makes the guide pin 6 abut against the bottom of the spring blind hole 22, and the guide pin 6 provides support force for the compression spring 3, avoiding axial torsion of the compression spring 3 and failure of the support force.

[0077] Sixth embodiment

[0078] like Fig.10 As shown, the sealing assembly 200 provided in the embodiment of the utility model includes a plurality of sealing rings 100. The plurality of sealing rings 100 are coaxially arranged to form a multi-channel fluid sealing structure on the outer surface of the main shaft. In this embodiment, the sealing assembly 200 includes two sealing rings 100 as an example.

[0079] The sealing assembly 200 further includes an assembly seat 201, which is an annular support structure of the sealing assembly 200. The assembly seat 201 includes a plurality of assembly grooves 202. The assembly groove 202 is an annular groove on the assembly seat 201, which is coaxial with the assembly seat 201 and extends radially from the inner circumferential surface of the assembly seat 201 to the outer circumferential surface. The size of the assembly groove 202 corresponds to the sealing ring 100. The sealing ring 100 is disposed in the assembly groove 202, so that the plurality of sealing rings 100 are coaxial and arranged along the axial direction of the sealing assembly 200 to form a multi-channel fluid sealing structure.

[0080] In summary, the sealing assembly for wind turbines provided by the embodiment of the utility model is formed by overlapping a plurality of sealing strips into an annular sealing strip, which is compressed by a compression spring and contacts the main shaft surface to form a fluid sealing structure. The characteristics of the wear-resistant, friction-reducing and self-lubricating composite material are utilized to directly contact the main shaft surface and generate sliding friction to prevent fluid leakage. A plurality of compression springs are used to provide uniform and constant pressure to the sealing strip, and an oil bag is formed by tiny pits to lubricate the side of the sealing strip, thereby reducing the friction loss between the sealing ring seat and balancing the spring force and the friction force of the sealing strip. The space between adjacent sealing strips is filled with packing to increase the length of the main shaft sealing structure. Such reliable axial and radial sealing improves the sealing performance and reliability of long-term use (for example, 10 years).

[0081] It should be noted that the above-mentioned multiple embodiments are only examples, and the technical solutions of the various embodiments can be combined. For example, the combination of the first embodiment, the fourth embodiment and the fifth embodiment are all within the protection scope of the present utility model.

[0082] It should be noted that the process referred to in the present invention refers to one of a variety of processes that can be used, and is not limited to the processes listed in the embodiments. The order of steps in the present invention can be changed according to actual needs, the order between steps can be changed, and serial processing can also be changed to parallel processing, which is not limited to the order of steps listed in the embodiments.

[0083] The orientation or position relationship indicated by terms such as "thickness", "depth", "up", "down", "horizontal", "vertical", "top", and "bottom" are based on the orientation or position relationship shown in the accompanying drawings and are only for the convenience of describing the present invention and simplifying the description. They do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0084] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present utility model, the meaning of "plurality" is two or more, unless otherwise clearly and specifically defined.

[0085] The sealing assembly for wind turbine generator provided by the utility model is described in detail above. For those skilled in the art, any obvious changes made to the utility model without departing from the essence of the utility model will constitute an infringement of the patent right of the utility model and will bear corresponding legal responsibilities.

Claims

1. A sealing assembly for a wind turbine generator set, characterized in that It includes a main shaft and a sealing ring, wherein the sealing ring includes a sealing ring seat, a sealing strip and a plurality of compression springs; wherein, The sealing ring seat is an annular structure, and the minimum inner diameter of the inner circumferential surface is a; wherein, The sealing ring seat comprises a sealing groove, which is an annular groove formed on the sealing ring seat and is coaxial with the sealing ring seat; the sealing groove extends from the inner circumferential surface of the sealing ring seat along the radial direction of the sealing ring seat and is not connected with the outer circumferential surface of the sealing ring seat; the diameter of the bottom surface of the sealing groove is b; the sealing strip is an annular structure, the outer diameter c is less than or equal to b, the inner diameter d is less than a, and the thickness is f; The sealing strip is arranged in the sealing groove; the compression spring is a coil spring that withstands the radial pressure of the main shaft and is arranged between the bottom surface of the sealing groove and the outer circumferential surface of the sealing strip; the compression direction of the compression spring coincides with the radial direction of the sealing strip, providing radial pressure for the sealing strip to press the sealing strip against the surface of the main shaft.

2. The sealing assembly according to claim 1, characterized in that The sealing ring seat further comprises a tiny pit, wherein the tiny pit is arranged on two opposite side surfaces of the sealing groove, and the area of ​​the tiny pit and the side surfaces accounts for 7% to 9%.

3. The sealing assembly according to claim 1, characterized in that The sealing strip also includes an oil storage tank; The oil storage groove is arranged on the third sealing surface of the sealing strip and is a groove structure extending along the circumferential direction of the sealing strip.

4. The sealing assembly according to claim 1, characterized in that: The surface roughness of two opposite side surfaces of the sealing groove is Ra0.8-Ra0.2; the width dimension e of the sealing groove is smaller than the thickness f of the sealing strip.

5. The sealing assembly according to claim 4, characterized in that Also includes packing; wherein, The sealing ring seat comprises a plurality of sealing grooves, the sealing ring comprises a plurality of sealing strips, and the sealing strips correspond to the sealing grooves; The packing is arranged between two adjacent sealing grooves and contacts the inner circumferential surface of the sealing ring seat; the position of the packing along the axial direction of the sealing ring is limited by the sealing strips in the adjacent sealing grooves.

6. The sealing assembly according to claim 4, characterized in that The sealing ring seat also includes a plurality of ring seat pin holes; wherein, The axial direction of the ring seat pin hole is parallel to the axial direction of the sealing ring seat, and passes through the two axial end faces of the sealing ring seat and the two axial side faces of the sealing groove; the plurality of ring seat pin holes are evenly distributed in a circular array with the axial direction of the sealing ring seat as the symmetric center; The sealing strip further comprises a plurality of sealing strip pin holes; the axial direction of the sealing strip pin holes is parallel to the axial direction of the sealing strip, and penetrates the first sealing surface and the second sealing surface of the sealing strip; the positions of the sealing strip pin holes correspond to the ring seat pin holes.

7. The sealing assembly according to claim 4, characterized in that The sealing ring seat also includes a positioning blind hole; wherein, The bottom surface of the sealing groove is provided with a plurality of positioning blind holes, and the positioning blind holes extend from the bottom surface of the sealing groove to the outer circumferential surface of the sealing ring seat and are not connected with the outer circumferential surface of the sealing ring seat; the axial direction of the positioning blind holes is parallel to the radial direction of the sealing ring seat and is perpendicular to the axial direction of the sealing ring seat; the diameter of the inscribed circle of the positioning blind holes is larger than the outer diameter of the compression spring, and is used for setting the compression spring.

8. The sealing assembly according to claim 7, characterized in that The sealing strip also includes a spring blind hole; wherein, The position of the spring blind hole corresponds to the positioning blind hole, extending from the outer circumferential surface to the inner circumferential surface of the sealing strip, and not connected to the inner circumferential surface of the sealing strip; the axial direction of the spring blind hole is parallel to the radial direction of the sealing strip and perpendicular to the axial direction of the sealing strip; the diameter of the inscribed circle of the spring blind hole is larger than the outer diameter of the compression spring, and is used to set the compression spring.

9. The sealing assembly according to claim 8, characterized in that Also includes guide pins; wherein, The guide pin is a rod-shaped structure with a longitudinal direction and a T-shaped longitudinal section; the guide pin is arranged in the spring blind hole, its large diameter end contacts the bottom of the spring blind hole, and its small diameter end extends upward along the spring blind hole; the compression spring is sleeved on the outside of the guide pin, and the two are coaxial.

10. The sealing assembly according to claim 1, wherein: The sealing strip comprises a plurality of sealing strip petals; the sealing strip petals are independent parts and are designed to overlap each other to form an annular structure; a plurality of sealing strip petals overlap each other to form an annular structure of the sealing strip; the first sealing surface and the second sealing surface of the sealing strip are flat and have no protrusions.

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