Blade vibration-suppressing device, blade assembly, wind turbine generator system, and wind farm

Abstract

Provided are a blade vibration-suppressing device, a blade assembly, a wind turbine generator system, and a wind farm. The blade vibration-suppressing device comprises a wind-blocking member and a connecting member, wherein the connecting member is configured to connect the wind-blocking member to a blade of the wind turbine generator system, and the wind-blocking member can be formed as a wind-catching chamber, which can increase the damping of the blade when facing an external airflow, thus suppressing the vibration of the blade. Based on the characteristic that wind resistance is positively correlated with wind speed, the wind-blocking member is arranged on the blade, such that the damping of the blade is increased under the action of the wind-blocking member, thereby solving the problem of blade vibration caused by strong wind.

Description

Blade vibration suppression device, blade assembly, wind turbine generator set and wind farm Technical Field

[0001] The present disclosure relates to the technical field of wind power generation, and in particular to a blade vibration suppression device, a blade assembly, a wind turbine generator set, and a wind farm. Background Art

[0002] Large turbine blades are sometimes stored in large quantities in a storage yard before installation. Under certain wind conditions (such as high wind speeds and wind direction perpendicular to the span direction), first-order vibrations can occur in the blades' shimmy direction. Large vibration amplitudes can cause blades to touch the ground, damaging their shape and structure, or even rendering them useless. Furthermore, prolonged and high-volume vibrations can also cause fatigue damage in this direction. Currently, the main approach is to install a mesh sleeve around the blade tip. This sleeve modifies the blade's aerodynamic performance, creates a turbulent flow on the blade surface, and suppresses vibration.

[0003] However, mesh vibration suppression has the following drawbacks: First, it lacks reliability and efficiency, typically requiring extensive installation of mesh over a wide area of ​​the blade. This is particularly true at high wind speeds, where the vibration suppression effect cannot be guaranteed, and in practice, ground anchoring is often required. Second, it is expensive, difficult to recycle and reuse, and inconvenient to transport. The mesh itself is expensive due to its customization and high material consumption. Furthermore, mesh reuse is difficult because it cannot be shared between different blade models, further exacerbating the cost issue. Furthermore, the mesh itself is bulky and difficult to transport, resulting in high transportation costs. Third, the mesh interferes with pneumatic accessories. Currently, most blades are equipped with vortex generators (VGs) as standard. For example, the VGs are typically installed from the blade root to 80-90% of the blade's span, which is also within the mesh's installation range. Consequently, interference with the mesh can damage the VGs and make mesh removal and installation difficult.

[0004] Summary of the Invention

[0005] The present disclosure aims to at least solve the problems in the above-mentioned prior art or related art that blade vibration can easily cause damage to the blade shape and structure or even cause it to be scrapped, and that the existing solution of suppressing vibration by arranging a mesh on the blade has the disadvantages of insufficient reliability, high cost, non-reusability, interference between the mesh and pneumatic accessories, etc.

[0006] To achieve the above-mentioned purpose, the first aspect embodiment of the present disclosure provides a blade vibration suppression device, which includes a wind blocking member and a connecting member. The connecting member is used to connect the wind blocking member to the blade of the wind turbine. The wind blocking member can be formed into an air circulation cavity. When the air circulation cavity faces the external airflow, the damping of the blade can be increased, thereby suppressing the vibration of the blade.

[0007] A second embodiment of the present disclosure provides a blade assembly, including a blade and the aforementioned blade vibration suppression device, wherein the blade vibration suppression device is installed on the leading edge side and / or the trailing edge side of the blade.

[0008] According to another embodiment of the present disclosure, a wind turbine generator set is provided, which includes a blade assembly. The blade assembly adopts the blade vibration suppression assembly as described above, or the blade assembly is the blade assembly described above.

[0009] According to another embodiment of the present application, a wind farm is provided. The wind farm adopts the blade vibration suppression assembly as described above, or includes the blade assembly as described above, or includes the wind turbine generator set as described above. BRIEF DESCRIPTION OF THE DRAWINGS

[0010] The above and other objects and features of the present application will become more apparent through the following description with reference to the accompanying drawings which exemplarily illustrate an example, in which:

[0011] FIG1 is a schematic diagram of a single blade vibration suppression device installed on the trailing edge side of a blade according to one embodiment of the present application;

[0012] FIG2 is a schematic diagram of a blade vibration suppression device according to an embodiment of the present application after being blown up;

[0013] FIG3 is a schematic diagram of the installation positions of multiple blade vibration suppression devices on the trailing edge side of a blade according to an embodiment of the present application;

[0014] FIG4 is a schematic diagram of a single blade vibration suppression device installed on the leading edge side of a blade according to an embodiment of the present application;

[0015] FIG5 is a schematic diagram of a plurality of blade vibration suppression devices installed on the leading edge side of a blade according to an embodiment of the present application;

[0016] FIG6 is a schematic diagram showing two blade vibration suppression devices respectively installed on the leading edge and trailing edge of a blade according to an embodiment of the present application;

[0017] 7 is a schematic diagram showing a plurality of blade vibration suppression devices respectively installed on the leading edge side and the trailing edge side of a blade according to an embodiment of the present application;

[0018] FIG8 is a schematic diagram of two blade vibration suppression devices installed oppositely on the leading edge and trailing edge sides of a blade according to an embodiment of the present application;

[0019] 9 is a schematic diagram showing that a plurality of blade vibration suppression devices are relatively installed on the leading edge side and the trailing edge side of a blade according to one embodiment of the present application;

[0020] FIG10 is a schematic diagram of a blade vibration suppression device with ventilation holes according to an embodiment of the present application;

[0021] FIG11 shows a structural example of a blade vibration suppression device according to another embodiment of the present application;

[0022] FIG12 is a schematic diagram of the blade vibration suppression device shown in FIG11 in an open state;

[0023] FIG13 is a schematic diagram showing a blade vibration suppression device including a plurality of consecutively arranged air circulation cavities;

[0024] FIG14 is a schematic diagram showing a verification result of the vibration suppression effect of a blade vibration suppression device on a blade according to an embodiment of the present application.

[0025] FIG15 is a single vibration direction stall-induced flutter model according to one embodiment of the present application;

[0026] FIG16 is a stall-induced flutter model in any vibration direction according to an embodiment of the present application;

[0027] FIG17 is a simulation diagram showing the effect of a blade vibration suppression device on a flow field on a blade surface according to an embodiment of the present application;

[0028] FIG18 is another simulation diagram showing the effect of the blade vibration suppression device on the flow field on the blade surface according to one embodiment of the present application;

[0029] 19 and 20 are schematic diagrams showing the results of calculating the damping coefficient using field parameters for a blade without the vibration suppression device of the present disclosure and a blade with the vibration suppression device of the present disclosure installed;

[0030] FIG21 is a wind turbine generator set according to an embodiment of the present application.

[0031] Explanation of reference numerals in Figures 1 to 21: 10 wind blocking member, 110 air circulation cavity, 120 ventilation hole, 20 connecting member, 210 cross tying rope, 220 annular tying rope, 30 blade, 310 suction side, 320 pressure side, 330 trailing edge side, 340 leading edge side. DETAILED DESCRIPTION

[0032] The following detailed description is provided to help the reader gain a comprehensive understanding of the methods, devices and / or systems described herein. However, various changes, modifications and equivalents of the methods, devices and / or systems described herein will be clear after understanding the disclosure of this application. For example, the order of operations described herein is merely an example and is not limited to those orders set forth herein, but can be changed as will be clear after understanding the disclosure of this disclosure, except for operations that must occur in a specific order. In addition, for greater clarity and conciseness, descriptions of features known in the art may be omitted.

[0033] The features described herein can be implemented in different forms and should not be construed as limited to the examples described herein. Rather, the examples described herein are provided to illustrate only some of the many possible ways to implement the methods, devices, and / or systems described herein, which will become clear after understanding the disclosure of this disclosure.

[0034] As used herein, the term "and / or" includes any one of the associated listed items and any combination of any two or more.

[0035] Although terms such as "first," "second," and "third" may be used herein to describe various members, components, regions, layers, or portions, these members, components, regions, layers, or portions should not be limited by these terms. Instead, these terms are used solely to distinguish one member, component, region, layer, or portion from another member, component, region, layer, or portion. Thus, what is referred to as a first member, first component, first region, first layer, or first portion in the examples described herein may also be referred to as a second member, second component, second region, second layer, or second portion without departing from the teachings of the examples.

[0036] In the specification, when an element such as a layer, a region, or a substrate is described as being “on,” “connected to,” or “coupled to” another element, the element may be directly “on,” “connected to,” or “coupled to” the other element, or one or more other elements may be present therebetween. Conversely, when an element is described as being “directly on,” “directly connected to,” or “directly coupled to” another element, no other elements may be present therebetween.

[0037] The terms used herein are only used to describe various examples and are not intended to limit the disclosure. Unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. The terms "comprising," "including," and "having" indicate the presence of the described features, quantities, operations, components, elements, and / or combinations thereof, but do not preclude the presence or addition of one or more other features, quantities, operations, components, elements, and / or combinations thereof. The term "plurality" represents any number of two and more than two.

[0038] The definitions of directional terms such as "upper", "lower", "top" and "bottom" in this disclosure are all based on the directional definitions when the product is in normal use and placed upright.

[0039] Unless otherwise defined, all terms used herein, including technical and scientific terms, have the same meaning as commonly understood by one of ordinary skill in the art to which the present disclosure pertains after understanding the present disclosure. Unless expressly defined otherwise herein, terms such as those defined in general dictionaries should be interpreted as having a meaning consistent with their meaning in the context of the relevant art and the present disclosure, and should not be interpreted in an idealized or overly formal manner.

[0040] Furthermore, in describing the examples, when it is deemed that a detailed description of well-known related structures or functions would cause ambiguous interpretation of the present disclosure, such detailed description will be omitted.

[0041] The blade vibration suppression device and blade assembly provided by the embodiments of the present disclosure will be described below with reference to FIG. 1 to FIG. 15 .

[0042] As shown in Figures 1 to 9, the first embodiment of the present disclosure provides a blade vibration suppression device, which includes a wind blocker 10 and a connector 20. The connector 20 is used to connect the wind blocker 10 to the blade 30 of the wind turbine. One side of the wind blocker 10 is concave and can be formed into an air circulation cavity 110, thereby enclosing an air circulation cavity. When the air circulation cavity 110 faces the external flow, the damping of the blade 30 can be increased, thereby suppressing the vibration of the blade 30.

[0043] The blade vibration suppression device provided in the embodiment of this aspect is based on the characteristic that wind resistance is positively correlated with wind speed. A wind-blocking member 10 is provided on the blade 30, so that the damping of the blade 30 is increased under the action of the wind-blocking member 10, thereby solving the problem of yard vibration caused by strong winds. At the same time, the strength of each component is taken into consideration to ensure that each component does not fail under strong wind conditions. The wind-blocking member 10 used in the blade vibration suppression device provided in the embodiment of this aspect is small in size, easy to store and transport, and has the characteristics of low cost and reusability. The application scenarios of this application include but are not limited to the storage of blades 30 in the yard, the blades 30 after hoisting and before being connected to the grid, and the maintenance conditions during the operation of the blades 30.

[0044] In some embodiments, as shown in Figures 1 to 9, the connecting member 20 connects the wind blocking member 10 to the blade 30, so that there is a gap between the wind blocking member 10 and the outer surface of the blade 30 in the working state, thereby increasing the damping of the blade 30 without changing the aerodynamic shape and aerodynamic performance of the blade 30.

[0045] In these embodiments, the air choke 10 is connected to the blade 30 via the connector 20, making the air choke 10 relatively independent of the outer surface of the blade 30. Unlike a net bag, it does not need to match the outer contour of the blade. Therefore, it can be used with blades of different airfoil shapes, providing good versatility. Furthermore, when the blade vibration damping device is not needed, the air choke 10 can be separated from the blade 30 by loosening the connector 20, making it easy to disassemble and reuse.

[0046] In addition, the wind-blocking member 10 is connected to the blade by the connecting member 20, and there is no need to put it on the blade like a net bag. Therefore, interference with the pneumatic accessories on the blade can be avoided, solving the problem of interference with pneumatic accessories such as VG (Vortex Generator), causing damage to the VG and difficulty in installing and disassembling the net.

[0047] In some embodiments, as shown in Figures 1 to 9, the connector 20 can connect the wind blocking member 10 to the blade 30, and make the air circulation chamber 110 at least located on the suction side 310 of the blade 30, so as to reduce the flow rate of the airflow flowing through the suction side 310 of the blade 30.

[0048] Normally, when the air flow passes through the periphery of the blade, the air flow velocity on the suction side 310 of the blade 30 is greater than the air flow velocity on the pressure side 320 of the blade 30. According to the Bernoulli equation, the greater the gas flow velocity, the smaller the pressure. Therefore, the pressure on the pressure side 320 of the blade 30 is greater, and there will be a certain pressure difference between the suction side 310 and the pressure side 320, so that the blade obtains lift.

[0049] Setting the air circulation chamber 110 at least on the suction side 310 of the blade 30 can block the airflow on the suction side 310 of the blade 30, so that the airflow forms a vortex on the suction side 310 of the blade 30, reducing the flow rate of the airflow, thereby increasing the pressure on the suction side 310 of the blade 30, and reducing the pressure difference between the suction side 310 and the pressure side 320 of the blade 30, so that the lift of the blade is reduced, the system damping is increased, and the vibration of the blade 30 is suppressed.

[0050] Furthermore, in some embodiments, as shown in Figures 1 to 9, the air circulation cavity 110 also extends from the suction side 310 of the blade 30 to the pressure side 320 of the blade 30, so that the flow velocity of the airflow flowing through the pressure side 320 of the blade 30 is reduced, and the pressure difference between the pressure side 320 and the suction side 310 is reduced, so that the lift of the blade airfoil is reduced and the system damping is increased.

[0051] In these embodiments, the air circulation chamber 110 is arranged on the suction side 310 of the blade 30 and the pressure side 320 of the blade 30, which can block the airflow on the suction side 310 and the pressure side 320 of the blade 30, so that the airflow can form vortices on the suction side 310 and the pressure side 320 of the blade 30, reducing the flow rate of the airflow, thereby balancing the pressure on the suction side 310 and the pressure side 320 of the blade 30, reducing the pressure difference between the suction side 310 and the pressure side 320 of the blade 30, and achieving the purpose of suppressing the vibration of the blade 30.

[0052] According to Bernoulli's equation, the greater the gas flow rate, the lower the pressure. The air on the pressure side 320 of the blade 30 has a slow flow rate and high pressure, while the suction side 310 has low pressure. This generates a pressure from the pressure side toward the suction side, causing the blade 30 to swing in one direction. When wind conditions change, there is a probability that the pressure on both sides will shift. If the wind changes periodically, it will cause the blade 30 to swing frequently, generating vortex-induced vibration. By reducing the airflow velocity flowing through the surface of the blade 30, the pressure difference on both sides of the blade 30 can be reduced, thereby reducing vortex-induced vibration and suppressing the vibration of the blade 30.

[0053] In some embodiments, after the external airflow passes through the blades 30 and enters the air chamber 110, a negative pressure region is formed on the side of the air chamber 110 facing away from the blades 30. The negative pressure region formed on the side of the air chamber 110 facing away from the blades 30 not only helps to support the air blocker 10 made of a flexible material, causing the air blocker 10 to be blown into a hemispherical curved shape, but also creates a pressure differential on both sides of the air blocker 10, allowing the air blocker 10 to apply a pressure differential resistance to the blades 30 that is roughly aligned with the direction of blade vibration, thereby suppressing blade vibration.

[0054] According to some embodiments, a single choke 10 can be provided, with the span-wise length of the choke 10 adjusted based on actual vibration suppression needs. For example, when a single choke 10 is provided, the choke 10 may be relatively long. In this case, multiple sets of connectors 20 can be used to secure the choke 10 to the blade 30 in the span-wise direction of the blade to ensure the strength of the connection between the choke 10 and the blade. In this case, a single choke 10 can form multiple air inlets. Figure 11 illustrates an example of a monolithic choke 10.

[0055] In some embodiments, as shown in Figures 2, 3, 5, 6, 7, 8, and 9, a plurality of wind blocking members 10 may be provided, and may be spaced apart along the span direction of the blade 30. This arrangement can reduce the length of each wind blocking member 10, thereby preventing a single wind blocking member 10 from being too long and increasing installation difficulty, while also ensuring the vibration suppression effect of the blade 30.

[0056] Furthermore, in some embodiments, as shown in FIG10 , the wind blocker 10 may be provided with a plurality of ventilation holes 120 to reduce the wind resistance of a single wind blocker 10. The ventilation holes 120 are easy to manufacture and can be directly perforated in the wind blocker 10. This simple process can reduce the wind resistance of the wind blocker 10, preventing problems such as the connector 20 being broken due to excessive resistance of the wind blocker 10, and preventing excessive pressure from the connector 20 on a localized surface of the blade, which could damage the blade surface.

[0057] In some embodiments, the wind blocker 10 is made of a flexible material. As an example, the flexible material is optionally a combination of one or more of fabric or plastic cloth. The fabric may include relatively strong fabrics such as canvas, polyester, nylon, and Oxford cloth. The flexible material has the advantages of low cost, strength, light weight, easy storage, and low transportation cost, and can be recycled and reused. In addition, if a blade vibration suppression device is not required, the blade vibration suppression device can be detached from the blade 30 by disconnecting the connector 20, making it easy to disassemble. Moreover, due to the light weight of the flexible material, the blade vibration suppression device can fall freely without injuring workers.

[0058] In other embodiments, the wind blocker 10 can be made of a hard material. Compared to wind blocks 10 made of flexible materials, the wind blocker 10 does not need to be lifted by the wind. One side of the wind blocker 10 made of a hard material can directly form a wind chamber 110, thereby increasing the drag coefficient of the blade 30 and suppressing the vibration of the blade 30. This can also be effective in light or gentle winds. For example, the wind blocker 10 can be made of a material such as plastic. One side of the wind blocker 10 is concave. When installed on a blade, the concave side faces the blade.

[0059] In some embodiments, the wind blocking member 10 is a flexible sheet, and the connecting member 20 is a binding rope, which is fixedly connected to the flexible sheet, and can fix the flexible sheet on the blade 30, and make the flexible sheet form a bag with an air inlet opening on the surface of the blade 30. Under the action of external airflow, the flexible sheet can be expanded.

[0060] In these embodiments, a tying rope is selected as the connecting member 20. The tying rope has low cost and can be tied to the surface of the blade 30. It is fixed to the blade 30 by knotting or hooking or other connecting members 20, and the connection between the blade 30 is simple. Furthermore, as shown in FIG1 , the wind blocking member 10 is a flexible sheet that can be formed into a bag with an air inlet opening on the surface of the blade 30. When the flexible sheet is not supported by airflow, that is, when there is no wind or light wind, the flexible sheet naturally droops. The flexible sheet above the blade 30 is attached to the surface of the blade 30, and the flexible sheet below the blade 30 is drooped below the blade 30 due to gravity. As shown in FIG2 , in the case of strong winds, the airflow can support the flexible sheet through the air inlet opening, so that the flexible sheet is blown into a hemispherical curved surface.

[0061] In some embodiments, as shown in FIG1 , the tying ropes include cross tying ropes 210 and hoop tying ropes 220. The flexible sheet is generally square in shape, with its ends respectively covering the pressure side 320 and the suction side 310 of the blade 30. Two corners of the flexible sheet are located on the pressure side 320 of the blade 30, and the other two corners are located on the suction side 310 of the blade 30. The cross tying ropes 210 are used to secure the chordwise position of the flexible sheet and are cross-connected to the four corners of the flexible sheet. On the pressure side 320 of the blade 30, the cross-binding ropes 210 are connected to the two corners of the flexible sheet and cross each other, so that the two corners of the flexible sheet are brought close to each other through the cross-binding ropes 210, and then an air inlet opening is formed between the two corners of the flexible sheet, allowing wind to enter through the air inlet opening to stretch the flexible sheet; similarly, on the suction side 310 of the blade 30, the cross-binding ropes 210 are also connected to the two corners of the flexible sheet and cross each other, so that the two corners of the flexible sheet are brought close to each other through the cross-binding ropes 210, and then an air inlet opening is formed between the two corners of the flexible sheet, allowing wind to enter through the air inlet opening to stretch the flexible sheet; the circumferential binding ropes 220 are connected to the two side edges of the middle part of the flexible sheet, and are wrapped around the circumference of the blade 30 and fixed, for fixing the spanwise position of the flexible sheet to prevent the flexible sheet from moving in the spanwise direction of the blade 30. As an example, since the annular binding rope 220 is connected to both sides of the flexible sheet, approximately the middle of the left and right sides of the flexible sheet can be fixed on the blade, thereby preventing the flexible sheet from moving in the span direction of the blade.

[0062] As an example, optionally, the tying rope may be a strap, a strap with a tightener, a rope, etc. The cross tying rope 210 may be provided as one, and the annular tying rope 220 may be provided as two.

[0063] Although in the foregoing embodiment, the choke 10 and the connector 20 are constructed as separate structures, and the choke 10 is mounted on the blade 30 using a binding rope as the connector 20 , the construction of the choke 10 and the connector 20 is not limited thereto.

[0064] As shown in Figures 11, 12 and 13, according to another aspect of the present application, the wind blocker 10 is formed in a sheet shape, which can form at least one air circulation cavity 110, and the connecting member 20 is formed in a strip shape, including a plurality of connecting belts 210. The wind blocker 10 and the connecting member 20 can be connected to each other as an annular integral structure, so that they can be sleeved on the blade 30. Under the action of external wind, the air circulation cavity 110 can open, thereby increasing the damping of the blade. According to an embodiment of the present application, the blade vibration suppression device is sleeved within the tip range of the blade 30. When the wind blows from the area where the connecting member 20 is located to the area where the wind blocker 10 is located, the wind blocker 10 is blown open, and the air circulation cavity 110 changes from state 110b to state 110a, thereby destroying the free flow of airflow in the tip range. On the one hand, the damping of the blade 30 is increased and the lift is reduced, which is beneficial to suppressing the stall flutter of the blade 30. On the other hand, a pressure difference is formed on both sides of the wind blocking member 10, so that the wind blocking member 10 can apply a backward pulling force to the blade 30 that is roughly consistent with the vibration direction of the blade, thereby suppressing the vibration of the blade 30.

[0065] The blade vibration suppression device and blade assembly provided in the embodiments of the present application are based on the fact that wind resistance is positively correlated with wind speed. The relationship between wind resistance and wind speed is quadratic, so the greater the wind speed, the greater the added damping. By providing the wind blocking member 10, wind resistance can be efficiently utilized to increase the damping of the blade 30, preventing stall-induced flutter of the blade 30. This can address the problem of yard vibration caused by high winds, thereby preventing blade 30 vibration from causing damage to the blade 30 or even structural failure.

[0066] In addition, the blade vibration suppression device can be made of flexible materials and can be stacked when not in use, without taking up additional space. It has the characteristics of being small in size, easy to store and transport, and reusable. The flexible wind blocker 10 and the connecting member 20 can be made of common materials such as canvas, resin, PVC, etc., which are not easy to be damaged and have low cost. In addition, the wind blocker 10 and the connecting member 20 are sleeved on the blade 30. The contact area between the connecting member 20 and the blade 30 is very small compared to the wind blocker 10, and its effect on the aerodynamic shape of the blade 30 can be ignored. The air chamber 110 surrounded by the wind blocker 10 can be blown away from the blade 30 in the working state, which can increase the damping of the blade 30 without changing the aerodynamic shape and aerodynamic performance of the blade 30, and can reduce the probability of interference with pneumatic accessories, thereby avoiding the problem in the related art that it is easy to interfere with pneumatic accessories such as VG (vortex generator), causing damage to the VG and difficulty in installing and disassembling the mesh. In addition, flexible materials have low requirements for conformability and good adaptability. They can be reused on different blade models and have good versatility.

[0067] In addition, it should be noted that the air blocking member 10 can enclose a wind chamber 110 on the side where the blade 30 is located. The shape of the wind chamber 110 is not strictly limited here, as long as the air blocking member 10 can be inflated to increase the damping of the blade 30. According to the embodiments of the present application, the air blocking member 10 can enclose the wind chamber 110 on the side where the blade 30 is located in a natural state (for example, in the absence of wind or in very low wind), or it can be blown and inflated by wind.

[0068] According to embodiments of the present application, the wind blocker 10 and the connector 20 can be formed separately and then connected together, or they can be formed into an integrally connected structure. Regarding the integral connection of the wind blocker 10 and the connector 20, in some embodiments, the wind blocker 10 and the connector 20 can be made from a single piece of flexible material. This reduces the risk of the blade vibration damping device being blown apart by strong winds, particularly reducing the risk of tearing at the stitched joints. Furthermore, by cutting the structure from a single piece of flexible material, the number of stitching steps is reduced, making processing easier and reducing costs.

[0069] As shown in FIG. 13 , in some embodiments, the blade vibration suppression device can form a plurality of air circulation cavities 110 , and the plurality of air circulation cavities 110 can be arranged sequentially along the span direction of the blade 30 .

[0070] In these embodiments, multiple ventilation chambers 110 are arranged in the span direction of the blade 30, which increases the ventilation range and can better increase the damping of the blade 30, thereby improving the vibration suppression effect. At the same time, the length of each ventilation chamber 110 can also be reduced to avoid the length of a single ventilation chamber 110 being too long and increasing the difficulty of installation. While providing the same damping, the solution of using a single ventilation chamber 110 has higher requirements on the strength of the components, especially the strength requirements of the connecting member 20. However, this embodiment uses multiple ventilation chambers 110 connected to the blade 30 through multiple connecting belts 210, which can disperse the force and improve the reliability of the components.

[0071] In this case, the multiple air cavities 110 can be formed separately and then connected together, or the multiple air cavities 110 can be made of the same piece of flexible material, and the multiple air cavities 110 can be arranged continuously along the span direction of the blade 30. In addition, similar to the previously described embodiment, the multiple air cavities 110 can also be arranged at intervals along the span direction of the blade, which will not be described in detail here.

[0072] In some embodiments, the number of connecting straps 210 can be increased or decreased depending on the desired vibration damping effect. When one ventilation chamber 110 is provided, at least two connecting straps 210 are required. When multiple ventilation chambers 110 are provided consecutively, adjacent ventilation chambers can share a connecting strap 210.

[0073] As an example, a wind chamber 110 includes two connecting belts 210, which are located on both sides of the wind chamber 110 in the span direction of the blade 30. On the one hand, it is convenient for the outside wind to blow into the wind chamber 110 from between the two connecting belts 210, so that the wind chamber 110 opens and bulges under the action of the outside wind; on the other hand, the connecting belt 210 can limit the wind chamber 110 and can pull the two ends of the wind chamber 110 blown by the wind, so as to facilitate the enclosed formation of the shape of the wind chamber 110 and maintain the shape of the wind chamber 110, as well as limit the movement of the blade vibration suppression device in the span direction of the blade.

[0074] As an example, when the blade vibration suppression device includes multiple air cavities 110 and corresponding connecting belts 210 and the multiple air cavities 110 are continuously arranged along the span direction of the blade 30, the multiple air cavities 110 located at both ends can be connected to each connecting belt 210, and the same connecting belt 210 can be used to connect two adjacent air cavities 110, thereby reducing material usage and saving costs.

[0075] Furthermore, at least the connecting straps 210 located at both ends of the blade 30 in the spanwise direction are connected to the blade 30 to limit the spanwise movement of the blade vibration damping device, thereby improving the connection stability of the blade vibration damping device. When the wind choke 10 expands under the action of wind, it forms a bulge, blocking the airflow. At this time, the wind force acting on the wind choke 10 can be transmitted to the blade 30 via the connecting strap 210 located in the middle, reducing the vibration amplitude of the blade 30. In other words, the connecting straps 210 located at both ends can primarily limit the spanwise movement of the wind choke 10 in the blade 30, while the connecting strap 210 located in the middle can primarily transmit the pressure difference on both sides of the wind choke 10 to the blade 30.

[0076] Regarding the connection method between the blade vibration suppression device and the blade 30, further, in some embodiments, the ring formed by the connecting member 20 and the wind blocking member 10 has a certain tensioning force, can be tightly mounted on the blade 30, and make the air chamber 110 in a relaxed state in a natural state.

[0077] Furthermore, similar to the previously described embodiment, the opening of the air intake chamber 110 faces the leading edge side 340 or the trailing edge side 330 of the blade 30. When multiple air intake chambers 110 are arranged in the spanwise direction of the blade 30, the openings of the multiple air intake chambers 110 may all face the leading edge side 340 of the blade 30, or all face the trailing edge side 330 of the blade 30, or some face the leading edge side 340 of the blade 30 and some face the trailing edge side 330 of the blade 30. This allows the vibration suppression function to be achieved regardless of the direction of the external wind.

[0078] In some embodiments, the blade vibration suppression device further includes a bracket (not shown in the figure), which is located inside the air chamber 110 of the wind blocker 10 and is used to hold open the wind blocker 10 made of a flexible material. As an example, the bracket can optionally be a plastic stick that can be elastically deformed, etc., to support the wind blocker 10. Since the wind blocker 10 itself also has a certain weight, it may not be able to be opened when the wind force is small, and therefore it is difficult to play a vibration suppression role. According to some embodiments of the present application, by providing a bracket, the wind blocker 10 is kept in an open state, so that the blade vibration can be suppressed even when the wind force is small.

[0079] As an example, optionally, the bracket can be arc-shaped, so that the wind blocker 10 can be expanded into a hemispherical shape; further, the bracket can be a foldable bracket, and when the blade vibration suppression device is not needed, the bracket is folded and the wind blocker 10 is not supported, so that space can be saved and transportation is convenient; when the blade vibration suppression device is needed, the bracket is supported so that the bracket supports the wind blocker 10 into a hemispherical shape, thereby achieving the effect of suppressing blade vibration.

[0080] A second embodiment of the present disclosure provides a blade assembly, including a blade 30 and a blade vibration suppression device as described in any one of the above embodiments, wherein the blade vibration suppression device is installed on the leading edge side 340 and / or the trailing edge side 330 of the blade 30 .

[0081] The blade assembly provided in this embodiment has the blade vibration suppression device of any of the above embodiments, and thus has the beneficial effects of any of the above embodiments, which will not be described in detail here.

[0082] It is worth noting that, as shown in Figures 1, 2, and 3, the wind blocker 10 of the blade vibration suppression device can be positioned on the trailing edge 330 of the blade 30. In this configuration, the air intake opening of the air intake chamber 110 faces the leading edge 340. As shown in Figures 4 and 5, the wind blocker 10 of the blade vibration suppression device can also be positioned on the leading edge 340 of the blade 30. In this configuration, the air intake opening of the air intake chamber 110 faces the trailing edge 330 of the blade. Of course, as shown in Figures 6, 7, 8, and 9, the blade vibration suppression device can also be positioned on both the leading edge 340 and the trailing edge 330 of the blade 30. This allows the device to achieve vibration suppression regardless of the direction of the external wind.

[0083] Furthermore, the blade vibration suppression devices can be grouped according to their orientation. As an example, at least one blade vibration suppression device arranged on the leading edge side 340 of the blade 30 is referred to as a first blade vibration suppression device, and at least one blade vibration suppression device arranged on the trailing edge side 330 of the blade 30 is referred to as a second blade vibration suppression device. The number of first blade vibration suppression devices and second blade vibration suppression devices can be approximately the same, and they are alternately arranged in the span direction of the blade 30; alternatively, the number of first blade vibration suppression devices is less than the number of second blade vibration suppression devices. In this case, they may not be arranged in an alternating manner.

[0084] Furthermore, the air inlet openings of at least some of the air intake cavities 110 of the plurality of first blade vibration suppression devices and the air inlet openings of at least some of the air intake cavities 110 of the plurality of second blade vibration suppression devices may face each other. Specifically, the first blade vibration suppression devices and the second blade vibration suppression devices may be arranged overlappingly in the spanwise direction of the blade 30, with the air inlet openings of the first blade vibration suppression devices and the air inlet openings of the second blade vibration suppression devices facing each other. The first blade vibration suppression devices and the second blade vibration suppression devices may also be arranged partially overlappingly in the spanwise direction of the blade 30, that is, a portion of the air inlet openings of the first blade vibration suppression devices and a portion of the air inlet openings of the second blade vibration suppression devices face each other.

[0085] It is worth noting that, because wind resistance and wind speed have a quadratic positive correlation, the greater the wind speed, the greater the wind force acting on the wind blocker 10, the greater the resistance generated, and the greater the added damping of the blade system. Therefore, by providing the wind blocker 10, wind resistance can be efficiently utilized to increase the damping of the blade 30, thereby preventing stall-induced flutter of the blade 30.

[0086] In some embodiments, the blade vibration suppression device is installed within a range of 85% to 95% of the span of the blade 30. That is, the blade vibration suppression device is installed within a range of 85% to 95% of the span from the blade root to the blade 30. On the one hand, based on the positive correlation between wind resistance and wind speed, installing the blade vibration suppression device near the blade tip can utilize the high drag coefficient near the blade tip to address the problem of high wind-induced vibration in the leading-edge-to-trailing-edge and trailing-edge-to-leading-edge wind directions. Furthermore, installing the blade vibration suppression device within a range of 85% to 95% of the span from the blade root to the blade 30 can also avoid interference with aerodynamic accessories installed on the blade 30, such as vortex generators.

[0087] In some embodiments, the blade vibration suppression device is installed in an area near the tip of the blade 30, with the distance between the wind blocking element 10 and the blade tip being greater than or equal to 2 meters and less than or equal to 10 meters. Within this range, the area within 2 meters of the blade tip 30 can be avoided. Generally, the inner chord length of the blade 30 2 meters from the tip is too small to facilitate installation of the blade vibration suppression device. Therefore, the blade vibration suppression device is installed on the blade 30 beyond 2 meters from the tip, and then installed inward. Furthermore, based on the positive correlation between wind resistance and wind speed, installing the blade vibration suppression device within 10 meters of the blade tip can utilize the high drag coefficient in the area near the tip to address the problem of high wind-induced vibration in the stacking yard in the leading-edge-to-trailing-edge and trailing-edge-to-leading-edge wind directions. While also taking into account the strength of various components, it ensures that none of them will fail in high wind conditions. Furthermore, installing the device within 2 meters to approximately 10 meters from the blade tip avoids interference with aerodynamic accessories installed on the blade 30, such as vortex generators.

[0088] In some embodiments, as shown in Figures 1 to 10, the wind blocker 10 can cover at least a portion of the chord-wise width of the blade 30, that is, it can overlap at least a portion of the blade, for example, covering 50% to 80% of the chord length of the blade 30. Within this range, the wind blocker 10 can address the problem of yard vibration caused by strong winds in the leading edge to trailing edge or trailing edge to leading edge wind direction, effectively suppressing vibration, while also preventing the wind blocker 10 from covering too much of the blade 30 in the chord-wise direction, making it difficult for the blade 30 to be blown away.

[0089] In some embodiments, as shown in Figures 2, 3, 5, 7, and 9, multiple blade vibration suppression devices are provided, spaced apart along the span of blade 30, with the distance between adjacent blade vibration suppression devices ranging from 20 cm to 50 cm. This arrangement prevents interference between adjacent blade vibration suppression devices while also preventing them from being too far apart to affect the vibration suppression effect.

[0090] FIG1 is a schematic diagram showing a single blade vibration suppression device installed on a blade 30. Optionally, in actual application, 3 to 6 blade vibration suppression devices may be used, which are installed sequentially from 2 m away from the blade tip toward the blade root, as shown in FIG3 , FIG5 , FIG7 and FIG9 .

[0091] In some embodiments, the width of each wind blocker 10 in the span direction of the blade 30 is 1-4 meters. Within this range, the wind blocker 10 has a sufficient length to effectively suppress vibrations, but does not cause excessive resistance due to the excessive width of a single wind blocker 10 in the span direction of the blade 30, which may easily cause the connector 20 to break.

[0092] In some embodiments, the blade vibration suppression device is installed with a width of 8 to 10 meters in the span direction of the blade 30. Within this range, the blade vibration suppression device has a sufficient length to effectively suppress vibrations, but does not interfere with other components on the blade 30 due to the excessive width of the blade vibration suppression device in the span direction of the blade 30.

[0093] The dynamic working process of the blade vibration suppression device of the embodiment of the present application is described below with reference to the accompanying drawings. As shown in Figure 1, in the case of no wind or light wind, the wind blocking member 10 of the flexible material naturally droops, and the upper section is attached to the upper surface of the blade 30. Due to the fixation of the cross-binding rope 210, an inward closing is formed on the wind blocking member 10, and the lower section of the wind blocking member 10 is used as a whole by gravity and hangs below the lower surface of the blade 30.

[0094] Taking the example of the wind blocker 10 with its air inlet opening facing the leading edge 340 of the blade 30, when a certain wind speed is reached, such as 8 m / s or above, and the wind direction is from the leading edge to the trailing edge or at a certain angle, such as less than 45°, the wind blocker 10 will be blown into a hemispherical curved surface due to pressure difference resistance. At the same time, the wind passing through the blade 30 will form turbulent vortices due to separation, causing the upper and lower sides of the blade 30 to vibrate. When the wind direction forms a certain angle with the chord direction of the blade 30, the wind resistance exerts a lateral force on the wind blocker 10, that is, a spanwise force component. At this time, the connecting member 20 will provide a constraint to prevent the blade vibration suppression device from moving in the spanwise direction. A schematic diagram of the wind blocker 10 after being blown is shown in Figure 2.

[0095] When the wind direction is from the trailing edge to the leading edge, or at a certain angle, such as less than 45°, and the wind direction is along the span direction of the blade 30, the effect on the shape of the canvas is small at low wind speeds. When the wind speed is large, such as greater than 10m / s, the canvas is affected by the wind and sticks to the surface of the blade 30.

[0096] It is understandable that the embodiment in which the air inlet opening of the air choke 10 faces the trailing edge 330 of the blade 30 has a similar result to the embodiment in which the air inlet opening of the air choke 10 faces the leading edge 340 of the blade 30 , and will not be described in detail here.

[0097] As shown in Figure 14, in a specific embodiment of the present application, a 95m blade equipped with the blade vibration suppression device of the present application was placed in a storage yard as a test object and tested for over 300 hours. The verification period included winds exceeding 18m / s, with wind directions including a certain angle from the leading edge to the trailing edge and a certain angle from the trailing edge to the leading edge. As shown in Figure 13, Figure (a) in Figure 13 shows the original data collected by the acceleration sensor, and Figure (b) below shows the vibration results after the original data is zeroed. As can be clearly seen from the figure, the maximum acceleration during the verification period was approximately 0.1g (g is the acceleration due to gravity), which is less than the threshold value (0.15-0.2g). No significant vibration occurred during the verification period of the unit of this embodiment.

[0098] In order to better understand the present application, the principle of stall-induced flutter and the mechanism by which the vibration suppression device of the present application can suppress vibration are briefly analyzed below.

[0099] Figure 15 shows a stall-induced flutter model with a single vibration direction. In this simplified model, the airfoil vibrates in a single degree of freedom in a direction perpendicular to the incoming flow.

[0100] According to the simplified single-degree-of-freedom model, vibration causes periodic changes in the angle of attack, which in turn causes periodic changes in the aerodynamic force. When the direction of the increase in aerodynamic force is the same as the direction of vibration, or in other words, there is a phase difference between the aerodynamic force and the vibration displacement within a vibration cycle, the aerodynamic force does positive work within a vibration cycle, resulting in the accumulation of total energy of the system. The mechanical energy of the incoming flow is converted into the elastic potential energy of the bending deformation of the blade, resulting in an increasing trend in blade deformation, which ultimately manifests as self-excited vibration with a continuous increase in blade deflection. For example, at a large angle of attack, the blade vibrates upward, and the angle of attack α0 reduces the lift coefficient C. L Increase, C L If the vibration direction component increases and its direction is the same as the vibration direction, the vibration will tend to increase.

[0101] According to the technical solution of the present application, by providing a vibration suppression device, the pressure difference between the pressure side and the suction side of the blade can be reduced, thereby reducing the lift and further reducing the energy that excites the blade flutter.

[0102] By generalizing the previous single-degree-of-freedom simplified model, the stall-induced flutter model of the airfoil in any vibration direction x can be obtained. Figure 16 shows the stall-induced flutter model of the airfoil in any vibration direction. Since the aerodynamic forces in other directions do not work on the vibration, only the aerodynamic resultant force of the blade airfoil in the vibration direction is discussed below. The aerodynamic resultant forces Fx and F0 in the vibration direction x can be expressed by the following equations (2) and (3), respectively:

[0103] in,

[0104] Based on equations (2) and (3), the aerodynamic force F under dynamic conditions is x The aerodynamic resultant force F0 in the steady state is linearized at the equilibrium point x = 0, that is, a first-order Taylor expansion is performed according to the following formula (4) to obtain the equivalent damping coefficient η of the model, which can be expressed by the following formula (5). x ≈F0-ηx Formula (4)

[0105] Among them, in the above formula (2), formula (3), formula (4), and formula (5), the meanings of each parameter are as follows:

[0106] η-equivalent damping coefficient;

[0107] F x -Aerodynamic resultant force in unsteady state;

[0108] F0-aerodynamic resultant force in steady state;

[0109] x- vibration direction;

[0110] ρ - air density;

[0111] c-chord length;

[0112] W-the combined speed of the unsteady downflow wind speed and the vibration wind speed;

[0113] W0-incoming flow velocity in steady state;

[0114] C L - lift coefficient;

[0115] C D - drag coefficient;

[0116] α-angle of attack in unsteady state;

[0117] α0-angle of attack in steady state;

[0118] φ - inflow angle under unsteady state;

[0119] φ0-inflow angle in steady state;

[0120] θ-angle between vibration direction and reference line;

[0121] C′ L - the gradient of the lift coefficient with respect to the angle of attack;

[0122] C′ D - Gradient of the drag coefficient with respect to the angle of attack.

[0123] According to formula (5), in addition to the vibration direction, other parameters that affect the vibration include the angle of attack, the incoming flow velocity, the lift and drag coefficient and its gradient. When η is negative, the aerodynamic resultant at the cross section of the blade 30 does positive work, resulting in instability. From the expression (5) of η, it can be seen that the way to increase damping and improve stability can be to increase the drag coefficient, reduce the lift coefficient, and reduce the gradient of the lift and drag coefficients. In this application, by adding a vibration suppression device to the blade 30, it is possible to simultaneously increase the drag coefficient, reduce the lift coefficient, reduce the lift and reduce the gradient of the drag coefficient, thereby achieving the purpose of increasing damping and improving blade stability.

[0124] In formula (5), C D The coefficient range of the term is larger than that of the other two terms. Obviously, it is better to improve C D The most efficient way to increase the damping coefficient is D When η is large and changes little with the angle of attack, it can ensure that η is always greater than zero at any large wind speed.

[0125] The expression of formula (5) can also be used to analyze the stall-induced flutter model with a single vibration direction shown in Figure 13. In this model, since the vibration direction of the blade section is perpendicular to the incoming flow direction, θ-φ0=π / 2. Substituting into formula (5), the part in the brackets of formula (5) can be simplified to 2(C D +C′ L ), it can be seen that when C′ L Negative and with an absolute value greater than C D When , the system is unstable. In this case, C D The coefficient of the term ranges from [2,4], which is larger than the coefficients of the other two terms, indicating that the C D The most efficient way to increase the damping coefficient is D It is larger than the coefficients of the other two terms, so it can ensure that η is always greater than zero, thereby ensuring the stability of the system.

[0126] According to the embodiment of the present disclosure, a vibration suppression device is provided so that a negative pressure is formed on the leeward side of the vibration suppression device. Due to the pressure difference on both sides, the blade is subjected to an opposite pressure difference resistance in the vibration direction, thereby achieving the purpose of improving C DThe purpose is to more effectively increase the equivalent damping coefficient η and enhance the vibration suppression effect of the blade.

[0127] Figures 17 and 18 are the velocity field results of the two-dimensional CFD (Computational Fluid Dynamics) simulation of the present application. As shown, the presence of the vibration suppression device exacerbates the surface flow separation between the pressure side and the suction side of the blade 30, making the surface velocities on both sides tend to be consistent, thereby causing the pressure difference to decrease and the lift to decrease. According to formula (5), it can be determined that the damping coefficient can be increased, thereby enhancing the vibration suppression effect. At the same time, due to the obstruction of the blade vibration suppression device, the airflow velocity on the side of the blade vibration suppression device close to the blade 30 decreases and approaches 0, thereby forming a negative pressure on the other side, generating a large pressure difference resistance. Since the flow velocity on the side of the device close to the blade 30 is close to 0 and relatively stable at different attack angles, it shows a small resistance gradient. According to formula (5), it can be determined that the damping coefficient can be increased and the vibration suppression effect can be enhanced. The present application has the most significant effect on increasing the drag coefficient by adopting the vibration suppression device. At large angles of attack, the drag coefficient can be increased from 0.3-0.5 to 1.5-2.0.

[0128] It is worth noting that in an actual three-dimensional scenario, the equivalent stiffness distribution of the blade 30 is inversely proportional to the cube of the length from the blade root. Therefore, the most efficient way is to set the blade vibration suppression device at the blade tip; the blade tip resistance part makes the direction of increase of the aerodynamic resultant force opposite to the direction of velocity, and the aerodynamic force does negative work, avoiding the increase and accumulation of total energy in the system, thereby achieving the effect of a damper.

[0129] Figures 19 and 20 are based on the field parameters (wind speed, air density, etc.) of the embodiment disclosed by this institute, and the corresponding aerodynamic data (C L ,C D ,C′ L ,C′ D ), the calculation results obtained by applying the above model. Among them, Figure 19 shows the calculation results when the vibration suppression device of the present invention is not installed, and the calculation uses basic aerodynamic data; Figure 20 shows the results after the vibration suppression device of the present invention is installed, and the calculation uses modified aerodynamic data (relative to the basic aerodynamic data, the main difference is that the lift coefficient is reduced and the drag coefficient is increased). In the application scenario of this example, the blade vibration direction occurs near the chord direction, corresponding to the dotted box area in the figure. Observing the dotted box areas in the two figures, it can be seen that the damping coefficient is significantly improved after the vibration suppression device is installed, and is greater than 0 at all angles of attack.

[0130] According to the vibration suppression device of the present application, by increasing the damping by changing the flow on the blade surface and by increasing the drag coefficient, it is still possible to achieve added resistance and vibration suppression even at high wind speeds (for example, wind speeds greater than 20m / s), thereby ensuring the vibration suppression effect and the structural strength of the device and solving the stability problems in blade yards and blade shutdown maintenance conditions.

[0131] According to another aspect of the present application, a wind turbine generator system having the aforementioned vibration suppression device or blade assembly is also provided. As shown in Figure 21 , the wind turbine generator system according to an embodiment of the present application includes a tower 200, a nacelle 300 mounted on the upper end of the tower 200, a generator 100 mounted within or in front of the nacelle 300, a hub 410 connected to the generator main shaft, and an impeller 400 connected to the hub. The impeller 400 includes a plurality of blades 420. The blades 420 are subjected to vibration suppression using the blade vibration suppression device described above.

[0132] According to another aspect of the present application, a wind farm is also provided, in which a plurality of blades are stacked, and the blades are provided with the blade vibration suppression device described above for vibration suppression, or the wind farm includes the wind turbine generator set described above, and the wind turbine generator set includes the blade assembly described above or uses the blade vibration suppression device described above for vibration suppression.

[0133] According to the wind turbine generator set and wind farm of the embodiments of the present application, a blade vibration suppression device is used to suppress vibration. The blade vibration suppression device of the embodiments of the present application can be used to suppress vibration during the blade stacking process, the blade transportation process, or the shutdown process of the wind turbine generator set to prevent the blades from vibrating under the action of external wind and avoid damage to the blades due to large vibration of the blades.

[0134] Although the embodiments of the present application have been described in detail above, those skilled in the art may make various modifications and variations to the embodiments of the present disclosure without departing from the spirit and scope of the present disclosure. It should be understood that, in the opinion of those skilled in the art, such modifications and variations will still fall within the spirit and scope of the embodiments of the present disclosure as defined by the claims.

Claims

1. A blade vibration suppression device, characterized in that: The blade vibration suppression device comprises a wind blocking member (10) and a connecting member (20). The connecting member (20) is used to connect the wind blocking member (10) to a blade (30) of a wind power generation group. The wind blocking member (10) can be formed into a wind chamber (110). When the wind chamber (110) faces the external airflow, the damping of the blade (30) can be increased, thereby suppressing the vibration of the blade (30).

2. The blade vibration suppression device according to claim 1, characterized in that: The connecting member (20) connects the wind blocking member (10) to the blade (30), so that a gap exists between the wind blocking member (10) and the outer surface of the blade (30) in a working state, thereby increasing the damping of the blade (30) without changing the aerodynamic shape of the blade (30).

3. The blade vibration suppression device according to claim 1, characterized in that: The connecting member (20) is capable of connecting the wind blocking member (10) to the blade (30), and positioning the wind chamber (110) on the suction side (310) of the blade (30), so as to reduce the velocity of the airflow flowing through the suction side (310) of the blade (30).

4. The blade vibration suppression device according to claim 3, characterized in that: The air circulation cavity (110) also extends from the suction side (310) of the blade (30) to the pressure side (320) of the blade (30), so that the flow velocity of the airflow flowing through the pressure side (320) of the blade (30) is reduced, and the pressure difference between the pressure side (320) and the suction side (310) is reduced.

5. The blade vibration suppression device according to claim 1, characterized in that: After passing through the blades (30), the external airflow enters the air circulation chamber (110), so that a negative pressure area is formed on the side of the air circulation chamber (110) facing away from the blades.

6. The blade vibration suppression device according to claim 1, characterized in that: The wind blocking members (10) are multiple and can be arranged continuously or at intervals along the span direction of the blade (30).

7. The blade vibration suppression device according to claim 1, characterized in that: The wind blocking member (10) is provided with a plurality of ventilation holes (120) for adjusting the wind resistance of the wind blocking member (10).

8. The blade vibration suppression device according to any one of claims 1 to 7, characterized in that: The wind blocking member (10) is made of a flexible material or a hard material.

9. The blade vibration suppression device according to any one of claims 1 to 7, characterized in that: The wind blocking member (10) is a flexible sheet, and the connecting member (20) is fixedly connected to the flexible sheet, capable of fixing the flexible sheet on the blade (30) and allowing the flexible sheet to be formed into a bag-like shape with an air inlet opening on the surface of the blade (30); under the action of external wind, the flexible sheet can be opened to form the air chamber (110).

10. The blade vibration suppression device according to claim 9, characterized in that: The connecting member (20) is a binding rope, and the binding rope includes a cross binding rope (210) and an annular binding rope (220). The flexible sheet is roughly square, and its two ends are respectively wrapped around the pressure side (320) and the suction side (310) of the blade (30), and two of the corners of the flexible sheet are located on the pressure side (320) of the blade (30), and the other two corners are located on the suction side (310) of the blade (30). On each side of the pressure side (320) and the suction side (310), the cross binding rope (210) brings the two corners of the flexible sheet closer to each other, thereby forming an air inlet opening between the two corners of the flexible sheet. The annular binding rope (220) is connected to the two side edges of the middle part of the flexible sheet, and is wrapped around the circumference of the blade (30) to prevent the flexible sheet from moving in the extension direction of the blade (30).

11. The blade vibration suppression device according to any one of claims 1 to 7, characterized in that: The wind blocking member (10) is a flexible sheet, and the connecting member (20) is in the shape of a belt, integrally connected to the wind blocking member (10) to form a ring so as to be sleeved on the blade (30).

12. The blade vibration suppression device according to claim 11, characterized in that: The wind blocking member (10) comprises a plurality of wind chambers (110), wherein the plurality of wind chambers (110) are made of the same piece of flexible material, or the plurality of wind chambers (110) are made separately and then sewn together.

13. The blade vibration suppression device according to claim 8, characterized in that: The blade vibration suppression device also includes a bracket, which is located inside the wind-blocking cavity (110) of the wind-blocking member (10) and is used to open the wind-blocking member (10) made of a flexible material.

14. A blade assembly, comprising a blade (30), characterized in that: The blade assembly further comprises a blade vibration suppression device as claimed in any one of claims 1 to 13, wherein the blade vibration suppression device is installed on the leading edge side (340) and / or the trailing edge side (330) of the blade (30).

15. The blade assembly according to claim 14, characterized in that There are a plurality of blade vibration suppression devices, the plurality of blade vibration suppression devices comprising at least one first blade vibration suppression device and at least one second blade vibration suppression device, the air circulation cavity (110) of the first blade vibration suppression device being located at a leading edge side (340) of the blade (30), and the air circulation cavity (110) of the second blade vibration suppression device being located at a trailing edge side (330) of the blade (30), The first blade vibration suppression device and the second blade vibration suppression device are arranged facing each other or staggered.

16. The blade assembly according to claim 14, wherein: The blade vibration suppression device is installed within a range of 85% to 95% in the span direction of the blade (30).

17. The blade assembly according to claim 14, wherein: The blade vibration suppression device is installed at one end close to the blade tip of the blade (30), and the distance between the wind blocking member (10) and the blade tip is greater than or equal to 2 m and less than or equal to 10 m.

18. The blade assembly according to claim 14, characterized in that The wind blocking member (10) overlaps the blade portion and can cover 50% to 80% of the chord-wise width of the blade (30).

19. The blade assembly according to claim 14, characterized in that There are a plurality of blade vibration suppression devices, which are arranged at intervals along the span direction of the blade (30), and the distance between two adjacent blade vibration suppression devices is 20 cm-50 cm; and / or The width of each wind blocking member in the span direction of the blade (30) is 1m-4m; and / or The laying width of the blade vibration suppression device in the span direction of the blade (30) is 8m to 10m.

20. A wind turbine generator set, characterized in that: The wind turbine generator set comprises a blade assembly, and the blade assembly adopts the blade vibration suppression assembly as described in any one of claims 1-14, or the blade assembly is the blade assembly as described in any one of claims 15-19.

21. A wind farm, characterized in that: The wind farm adopts the blade vibration suppression assembly according to any one of claims 1 to 14, or includes the blade assembly according to any one of claims 15 to 19, or includes the wind turbine generator set according to claim 20.

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