A brake device and a brake method for a vane shaft

Abstract

This invention discloses a braking device and method for a blade shaft, relating to the field of blade shaft braking. The device includes a bushing and a braking part. The bushing has a mating joint that can be inserted into a mating groove. The braking part has a sliding cylinder that can be close to or away from the bushing. The sliding cylinder has an annular cavity and a central hole. A fixed shaft is fixed inside the central hole, and a rotating sleeve is rotatably mounted thereon. The rotating sleeve is fitted between the inner walls of the fixed shaft and the central hole. The mating groove is provided on the rotating sleeve. A friction plate is mounted inside the annular cavity. A guide rod is provided on the rotating sleeve, allowing the friction plate to slide along the length of the guide rod, i.e., in the radial direction of the annular cavity. An elastic band is provided between the friction plate and the fixed shaft, passing through a through hole provided on the rotating sleeve. This invention can prevent the blade shaft from being subjected to sudden braking force, reduce blade shaft damage, reduce speed deviation between the blade shaft and the blade, and reduce the occurrence of breakage at the connection point between the blade and the blade shaft.

Description

Technical Field

[0001] This invention relates to the field of blade shaft braking, and in particular to a braking device and braking method for a blade shaft. Background Technology

[0002] To ensure the long-term normal operation of wind turbines, it is necessary to shut them down for maintenance; or to shut them down before high wind speeds to prevent the blades from rotating at high speeds. High-speed blades, accompanied by large centrifugal forces, can easily damage the blades and the connection between the blades and the shaft. Therefore, in either of these situations, it is necessary to brake the blades or the blade shaft.

[0003] Currently, most small wind turbines do not have braking mechanisms to brake the blades or blade shafts. Large wind turbines, however, do have braking mechanisms, which currently fall into two categories. The first type involves a clutch between the braking mechanism and the blade shaft. When the blade shaft rotates normally, the clutch disengages, and the braking mechanism is not connected to the blade shaft. During braking, the clutch connects the braking mechanism to the blade shaft, and the braking mechanism brakes the blade shaft through friction or other means. The second type maintains a connection between the braking mechanism and the blade shaft. When the blade shaft rotates normally, the braking mechanism does not apply resistance to the blade shaft. During braking, the braking mechanism applies resistance to the blade shaft in the opposite direction to the blade torque, such as by applying reverse current or electrical short-circuit braking, to achieve braking of the blade shaft.

[0004] In the above-mentioned method, at the moment the braking mechanism brakes the blade shaft, the blade shaft is subjected to a large braking force, which will cause a large fluctuation in speed. This will not only cause the blade shaft to vibrate and be damaged, but also cause a speed deviation between the blade and the blade shaft due to the inertia of the blade, which will lead to breakage at the connection between the blade and the blade shaft.

[0005] In summary, when a braking mechanism brakes the blade shaft, there is a need in the art for a braking mechanism that can reduce damage to the blade shaft and blades. Summary of the Invention

[0006] The purpose of this invention is to provide a braking device and method for a blade shaft, which addresses the aforementioned problems by gradually increasing the braking force on the blade shaft. This avoids abrupt braking force on the blade shaft at the start of braking, prevents a sudden drop in the speed of the blade shaft, reduces damage to the blade shaft, reduces the speed deviation between the blade shaft and the blade, and further reduces the occurrence of breakage at the connection between the blade and the blade shaft.

[0007] The technical solution adopted in this invention is as follows: A braking device for a blade shaft includes a bushing for connecting to the blade shaft and a braking part; the bushing is provided with a mating joint, which can be inserted into a mating groove provided on the braking part; the braking part has a sliding cylinder, which is slidably mounted on a wind turbine or tower, and can move closer to or away from the bushing; the sliding cylinder has a coaxial annular cavity and a central hole, the annular cavity surrounding the central hole; a fixed shaft is coaxially fixed inside the central hole and a rotating sleeve is coaxially rotatably mounted thereon, the rotating sleeve being fitted between the fixed shaft and the inner wall of the central hole, and can be positioned relative to the fixed shaft. The fixed shaft and center hole rotate, and the mating groove is set on the end face of the rotating sleeve; several friction plates are fitted in the gap inside the annular cavity, and several guide rods are set on the rotating sleeve. The length direction of the guide rods is along the radial direction of the annular cavity, and the guide rods pass through the friction plates, allowing the friction plates to slide along the length direction of the guide rods; an elastic band is set between the friction plates and the fixed shaft, and several through holes are set on the rotating sleeve. The through holes correspond one-to-one with the friction plates and are distributed along the circumference of the rotating sleeve. One end of the elastic band is fixedly connected to the friction plate, and the elastic band connected to the same friction plate passes through the corresponding through hole and is fixedly connected to the fixed shaft.

[0008] Furthermore, an annular notch is provided between the annular cavity and the central hole, and all guide rods and elastic bands are located within the annular notch.

[0009] Furthermore, each friction plate is connected to an even number of elastic bands, and the elastic bands connected to the same friction plate are evenly distributed on both sides of the guide rod along the generatrix direction of the annular cavity.

[0010] Furthermore, the connection points between the elastic bands connected to the different friction plates and the fixed shaft are evenly distributed along the circumference of the fixed shaft.

[0011] Furthermore, the braking unit also includes a mounting cylinder for mounting on a wind turbine or tower, wherein the sliding cylinder is assembled inside the mounting cylinder and the sliding cylinder and the mounting cylinder are connected in an axial sliding manner.

[0012] Furthermore, a sliding groove is provided inside the mounting cylinder, and a sliding body is provided on the outer wall of the sliding cylinder. The sliding body is slidably connected to the sliding groove, and the length direction of the sliding groove is parallel to the axial direction of the mounting cylinder.

[0013] Furthermore, a linear actuator is provided inside the mounting cylinder, and the linear actuator is connected to the end of the sliding cylinder.

[0014] Furthermore, the cross-sectional shape of the connector is non-circular, and the geometry of the mating groove matches the geometry of the mating groove.

[0015] Furthermore, the cross-section of the connector is star-shaped.

[0016] A braking method for a blade shaft, using the aforementioned braking device for the blade shaft, includes the following steps:

[0017] S1: The linear actuator pushes the sliding cylinder toward the bushing;

[0018] S2: Insert the connector into the mating groove to complete the mating of the bushing and the brake unit;

[0019] S3: The blade shaft rotates with the bushing, and the bushing rotates with the rotating sleeve. The rotating sleeve rotates relative to the center hole and the fixed shaft. The rotating sleeve carries the friction plate in a circumferential motion within the annular cavity through the guide rod.

[0020] S4: As the rotating sleeve rotates, the elastic band gradually wraps around the fixed shaft. The elastic band gradually deforms and generates an elastic force F0, which gradually increases. The friction plate is subjected to the elastic force F0 of the elastic band. The elastic band pulls the friction plate and compresses the inner wall of the annular cavity. The pressure between the friction plate and the annular cavity gradually increases, and the friction between the friction plate and the annular cavity gradually increases.

[0021] S5: The friction between the friction plate and the annular cavity inhibits the rotation of the rotating sleeve, thereby inhibiting the rotation of the blade shaft and completing the braking of the blade shaft.

[0022] In summary, due to the adoption of the above technical solution, the beneficial effects of the present invention are:

[0023] 1. This invention consumes the kinetic energy of the blade shaft through friction between the friction plate and the inner wall of the annular cavity, effectively achieving braking of the blade shaft;

[0024] 2. The pressure between the friction plate and the annular cavity in this invention is provided by the elastic force F0 generated by the elastic band. The elastic force F0 generated by the deformation of the elastic band comes from the action of the rotating sleeve. The rotating sleeve rotates synchronously with the blade shaft. Therefore, the elastic force F0 of the elastic band increases gradually from nothing to something, and the pressure between the friction plate and the annular cavity increases accordingly from nothing to something. That is, the braking force on the blade shaft also increases gradually from nothing to something. This effectively avoids the blade shaft from being subjected to a sudden braking force when braking begins, and avoids a sudden drop in the speed of the blade shaft. This reduces damage to the blade shaft and reduces the speed deviation between the blade shaft and the blade, further reducing the occurrence of breakage at the connection between the blade and the blade shaft. Attached Figure Description

[0025] The present invention will be described by way of example and with reference to the accompanying drawings, wherein:

[0026] Figure 1 This is a schematic diagram of the structure of the present invention;

[0027] Figure 2 for Figure 1 Schematic diagram of the cross section at point AA;

[0028] Figure 3 for Figure 1 Schematic diagram of the cross section at point BB;

[0029] Figure 4 This is a schematic diagram showing the force analysis of the rotating sleeve and the friction plate;

[0030] Figure 5 This is a schematic diagram of the geometric structure of the butt joint;

[0031] The markings in the diagram are: 1-shaft sleeve; 11-joint; 2-rotating sleeve; 21-connecting groove; 22-through hole; 3-sliding cylinder; 31-sliding body; 32-annular notch; 4-friction plate; 5-bearing; 6-elastic band; 7-guide rod; 8-fixed shaft; 9-linear actuator; 10-mounting cylinder; 101-slide groove. Detailed Implementation

[0032] All features disclosed in this specification, or all steps in all disclosed methods or processes, may be combined in any way, except for mutually exclusive features and / or steps.

[0033] Any feature disclosed in this specification, unless otherwise stated, may be replaced by other equivalent or similar features. That is, unless otherwise stated, each feature is merely one example of a series of equivalent or similar features.

[0034] Example 1

[0035] like Figure 1 - Figure 5 As shown, a braking mechanism for a blade shaft includes a bushing 1 for connecting to the blade shaft and a braking part, wherein the bushing 1 and the braking part are separate. A connector 11 is provided at the end face of the bushing 1, and the braking part has a mating groove 21. The connector 11 can be inserted into the mating groove 21 to connect the bushing 1 and the braking part, thereby achieving docking between the blade shaft and the braking part. The braking part has a sliding cylinder 3, which is slidably mounted on a wind turbine or tower. The sliding cylinder 3 can be close to or away from the bushing 1. When the sliding cylinder 3 is away from the bushing 1, the braking part is disconnected from the blade shaft. When the sliding cylinder 3 is close to the bushing 1 and the connector 11 is inserted into the mating groove 21, the blade shaft is docked with the braking part, thereby braking the blade shaft.

[0036] In this embodiment, the sliding cylinder 3 has a coaxial annular cavity and a central hole, with the annular cavity surrounding the central hole. A fixed shaft 8 is coaxially fixed inside the central hole, and a rotating sleeve 2 is rotatably mounted on the same axis. The rotating sleeve 2 is mounted between the fixed shaft 8 and the inner wall of the central hole, and can rotate relative to the fixed shaft 8 and the central hole. A mating groove 21 is provided on the end face of the rotating sleeve 2. Specifically, the rotating sleeve 2 has a coaxial countersunk hole, the fixed shaft 8 is fixed to the end face of the sliding cylinder 3, and the fixed shaft 8 is mounted in the countersunk hole, so that the rotating sleeve 2 can rotate relative to the fixed shaft 8. After the mating joint 11 and the mating groove 21 are mated, the rotating shaft obtains the rotation of the blade shaft, so that the rotating shaft and the blade shaft move synchronously. Therefore, only the rotating shaft needs to be braked to achieve the braking of the blade shaft.

[0037] Furthermore, in this embodiment, several friction plates 4 are fitted inside the annular cavity with gaps. The shape of the friction plates 4 matches the shape and size of the annular cavity, and the friction plates 4 are fitted inside the annular cavity with gaps. That is, when the friction plates 4 are not subjected to the elastic force F0 of the elastic band 6, the pressure between them and the annular cavity is low, and the friction is almost negligible. This allows the blade shaft to not be subjected to too much friction as a braking force in the initial stage of braking. Several guide rods 7 are provided on the rotating sleeve 2. The length direction of the guide rods 7 is along the radial direction of the annular cavity, and the guide rods 7 pass through the friction plates 4, allowing the friction plates 4 to slide along the length direction of the guide rods 7. The presence of the guide rods 7, on the one hand, allows the friction plates 4 to be converted into pressure along the radial direction of the annular cavity after being subjected to the elastic force F0 of the elastic band 6, thereby achieving the purpose of restricting the friction plates 4; on the other hand, the guide rods 7 allow the friction plates 4 to rotate synchronously with the rotating sleeve 2, thereby forming relative friction with the inner wall of the annular cavity.

[0038] In this embodiment, an elastic band 6 is provided between the friction plate 4 and the fixed shaft 8. The rotating sleeve 2 is provided with a plurality of through holes 22, which correspond one-to-one with the friction plate 4 and are distributed along the circumference of the rotating sleeve 2. One end of the elastic band 6 is fixedly connected to the friction plate 4. The elastic band 6 connected to the same friction plate 4 passes through the corresponding through hole 22 and is fixedly connected to the fixed shaft 8. When the rotating sleeve 2 rotates, the constraint of the hole wall of the through hole 22 on the elastic band 6 causes the elastic band 6 to wrap around the fixed shaft 8, thereby stretching the elastic band 6 to have an elastic force F0. This elastic force F0 further acts on the friction plate 4. Due to the support of the inner wall of the annular cavity, the friction plate 4 is converted into friction between the friction plate 4 and the inner wall of the annular cavity.

[0039] In this embodiment, to avoid scratching the elastic band 6 at the edge of the hole wall of the through hole 22, pulleys can be set at both ends of the through hole 22, and the elastic band 6 passes around the corresponding pulleys; the pulleys support the elastic band 6.

[0040] In order to ensure the stable rotation of the rotating sleeve 2 between the fixed shaft 8 and the inner wall of the central hole, and to reduce the friction between the rotating sleeve 2 and the fixed shaft 8 and the inner wall of the central hole, thereby reducing the impact of the friction at this position on the rotation of the blade shaft and reducing the large braking force on the blade shaft at the moment when the joint 11 and the docking groove 21 are docked; in this embodiment, the bearing 5 is provided between the rotating sleeve 2 and the fixed shaft 8, and between the rotating sleeve 2 and the inner wall of the central hole.

[0041] Furthermore, two bearings 5 ​​are provided between the rotating sleeve 2 and the fixed shaft 8. The bearings 5 ​​are installed at both ends of the fixed shaft 8 (rotating sleeve 2). The gap between the bearings 5 ​​provides space and constraint for the winding of the elastic band 6, ensuring that the elastic band 6 is wound circumferentially. Two bearings 5 ​​are provided between the rotating sleeve 2 and the inner wall of the central hole. The bearings 5 ​​are installed at both ends of the rotating sleeve 2 (central hole). The gap between the bearings 5 ​​provides space for the guide rod 7, the through hole 22 and the elastic band 6.

[0042] In this embodiment, the blade shaft needs to be braked, and the process is as follows:

[0043] The sliding cylinder 3 is pushed towards the bushing 1, and the sliding cylinder 3, along with the rotating sleeve 2, moves towards the bushing 1. The mating joint 11 on the bushing 1 is inserted into the mating groove 21 on the rotating sleeve 2, completing the mating of the bushing 1 and the braking part. The blade shaft rotates synchronously with the rotating sleeve 2 through the bushing 1. The rotating sleeve 2 rotates relative to the center hole and the fixed shaft 8. The rotating sleeve 2, through the guide rod 7, carries the friction plate 4 to move circumferentially within the annular cavity. As the rotating sleeve 2 rotates, the elastic band 6 gradually wraps around the fixed shaft 8. The elastic band 6 gradually deforms and generates an elastic force F0, which gradually increases. The friction plate 4 is subjected to the elastic force F0 of the elastic band 6. The elastic band 6 pulls the friction plate 4 and compresses the inner wall of the annular cavity, gradually increasing the pressure between the friction plate 4 and the annular cavity, and gradually increasing the friction between the friction plate 4 and the annular cavity. The friction between the friction plate 4 and the annular cavity inhibits the rotation of the rotating sleeve 2, thereby inhibiting the rotation of the blade shaft and completing the braking of the blade shaft.

[0044] It should be noted that, as Figure 4As shown, since the deformation of the elastic band 6 is caused by its winding around the fixed shaft 8 as it rotates with the rotating shaft, the elastic force F0 of the elastic band 6 must act between the fixed shaft 8 and the rotating sleeve 2 in a non-radial direction. Therefore, the elastic force F0 has two components: one is the radial component F1 of the fixed shaft 8 and the rotating sleeve 2, F1 = F0 * cosα, where α is the angle between the tangent direction of the tangent line passing through the hole 22 on the surface of the fixed shaft 8 and the radial direction; the other is the tangential component F2 of the fixed shaft 8 and the rotating sleeve 2 in the circumferential direction, F2 = F0 * sinα. Since there is no relative gap between the fixed shaft 8 and the rotating sleeve 2 in the radial direction, the radial component F1 will be canceled out. The tangential component F2 inhibits the rotation of the rotating sleeve 2 and the friction plate 4, further gradually improving the braking effect on the blade shaft.

[0045] On the other hand, after the blade shaft completes braking, to prevent the tangential component F2 from acting on the rotating sleeve 2 and friction plate 4, causing the rotating sleeve 2 and friction plate 4 to rotate with the blade shaft, i.e., to achieve self-locking, the rotating sleeve 2 and friction plate 4 can be considered as a whole for force analysis. The friction between the friction plate 4 and the annular cavity is actually the friction between the rotating sleeve 2 and friction plate 4 as a whole relative to the annular cavity (sliding cylinder 3). That is, the real-time frictional force between the friction plate 4 and the annular cavity needs to be f = μF0 > F2 = F0 * sinα, i.e., μ is greater than si. nα, where μ is the coefficient of dynamic friction between the friction plate 4 and the annular cavity; the specific method can be achieved by selecting the surface roughness of the friction plate 4, the roughness of the inner wall of the annular cavity (actually selecting the coefficient of dynamic friction μ), and / or selecting the distance between the through hole 22 on the rotating sleeve 2 and the outer wall of the fixed shaft 8 (actually selecting the angle α). The specific parameters are determined according to the actual working conditions and will not be explained in detail in this specification; priority should be given to the design of the distance between the through hole 22 and the outer wall of the fixed shaft 8, because this factor is the easiest to adjust in manufacturing and assembly.

[0046] Example 2

[0047] like Figure 1 - Figure 3 As shown, based on Example 1, further feasible implementation methods are proposed.

[0048] In one feasible implementation, an annular notch 32 is provided between the annular cavity and the central hole. All guide rods 7 and elastic bands 6 are located within the annular notch 32. The rotating sleeve 2 rotates with the friction plate 4 through the guide rods 7. Part of the elastic band 6 between the friction plate 4 and the rotating sleeve 2 also moves accordingly. That is, both the guide rods 7 and the elastic band 6 will make circumferential movements. The design of the annular notch 32 provides them with space for movement.

[0049] In one feasible implementation, each friction plate 4 is connected to an even number of elastic bands 6. The elastic bands 6 connected to the same friction plate 4 are evenly distributed on both sides of the guide rod 7 along the generatrix of the annular cavity, so that the elastic force from the elastic bands 6 on the same friction plate 4 is evenly distributed on both sides of the guide rod 7, providing a uniform positive pressure between the friction plate 4 and the inner wall of the annular cavity.

[0050] In one feasible implementation, the connection points of the elastic bands 6 connected to the different friction plates 4 and the fixed shaft 8 are evenly distributed along the circumference of the fixed shaft 8. It should be noted that, in order to achieve this technical feature, the through holes 22 are also evenly distributed along the circumference of the rotating sleeve 2. This ensures that when the rotating sleeve 2 rotates at any angle, the deformation of all elastic bands 6 is equal, thereby making the frictional force between all friction plates 4 and the inner wall of the annular cavity equal.

[0051] Furthermore, several friction plates 4 completely fill the annular cavity, meaning that the friction plates 4 are evenly distributed, and the frictional force between the friction plates 4 and the inner wall of the annular cavity is evenly distributed.

[0052] In one feasible implementation, the braking part further includes a mounting cylinder 10, which is used to install on a wind turbine or tower. The sliding cylinder 3 is assembled inside the mounting cylinder 10 and is connected to the mounting cylinder 10 in an axial direction. The sliding cylinder 3 is slidably assembled on the wind turbine or tower through the mounting cylinder 10, avoiding the need to process the mounting position for the sliding cylinder 3 to slide on the wind turbine or tower again.

[0053] Specifically, a sliding groove 101 is provided inside the mounting cylinder 10, and a sliding body 31 is provided on the outer wall of the sliding cylinder 3. The sliding body 31 is slidably connected to the sliding groove 101, and the length direction of the sliding groove 101 is parallel to the axial direction of the mounting cylinder 10. The sliding body 31 slides in the sliding groove 101, so that the sliding cylinder 3 slides in the mounting cylinder 10, thereby allowing the sliding cylinder 3 to move closer to or away from the bushing 1. On the other hand, the sliding groove 101 constrains the sliding body 31 to make circumferential movements, effectively constraining the sliding cylinder 3 to make circumferential movements, providing a basis for the friction plate 4 and the annular cavity to make relative circumferential sliding.

[0054] In one feasible implementation, a linear actuator 9 is provided inside the mounting cylinder 10. The linear actuator 9 is connected to the end of the sliding cylinder 3. The linear actuator 9 pushes the sliding cylinder 3 to slide relative to the mounting cylinder 10, so that the sliding cylinder 3 moves closer to or away from the bushing 1.

[0055] Furthermore, the linear actuator 9 is a hydraulic cylinder or a linear motor, the specific structure of which is known to those skilled in the art and will not be described in detail in this specification.

[0056] Example 3

[0057] Based on any one of the implementation methods in Examples 1-2, further feasible specific implementation methods are proposed.

[0058] In one feasible implementation, the cross-sectional shape of the connector 11 is non-circular, and the geometry of the mating groove 21 is matched with the geometry of the mating groove 21 to ensure that the torque of the blade shaft can be transmitted to the rotating shaft.

[0059] One feasible implementation method is, for example Figure 5 As shown, the cross-section of the connector 11 is star-shaped, which increases the probability of the connector 11 being inserted into the docking groove 21, thereby achieving the purpose of rapid docking.

[0060] Example 4

[0061] A braking method for a blade shaft, using the braking device for the blade shaft described in any one of Examples 1-3, includes the following steps:

[0062] S1: Linear actuator 9 pushes sliding cylinder 3 toward bushing 1;

[0063] S2: Insert the connector 11 into the mating groove 21 to complete the mating of the bushing 1 and the brake part;

[0064] S3: The blade shaft rotates with the bushing 1, and the bushing 1 rotates with the rotating sleeve 2. The rotating sleeve 2 rotates relative to the center hole and the fixed shaft 8. The rotating sleeve 2 carries the friction plate 4 in a circumferential motion within the annular cavity through the guide rod 7.

[0065] S4: The rotating sleeve 2 rotates and the elastic band 6 gradually wraps around the fixed shaft 8. The elastic band 6 gradually deforms and has an elastic force F0, and the elastic force F0 gradually increases. The friction plate 4 is subjected to the elastic force F0 of the elastic band 6. The elastic band 6 pulls the friction plate 4 and squeezes the inner wall of the annular cavity. The pressure between the friction plate 4 and the annular cavity gradually increases, and the friction between the friction plate 4 and the annular cavity gradually increases.

[0066] S5: The friction between the friction plate 4 and the annular cavity inhibits the rotation of the rotating sleeve 2, thereby inhibiting the rotation of the blade shaft and completing the braking of the blade shaft.

[0067] This invention is not limited to the specific embodiments described above. The invention extends to any new feature or combination disclosed in this specification, as well as any new method or process step or combination disclosed herein.

Claims

1. A braking device for a blade shaft, comprising a bushing (1) for connection with the blade shaft, and a braking part; the bushing (1) is provided with a mating joint (11), the mating joint (11) being insertable into a mating groove (21) provided on the braking part; characterized in that: The braking part has a sliding cylinder (3), which is slidably mounted on the wind turbine or tower. The sliding cylinder (3) can be close to or away from the bushing (1). The sliding cylinder (3) has a coaxial annular cavity and a central hole, with the annular cavity surrounding the central hole. A fixed shaft (8) is coaxially fixed inside the central hole, and a rotating sleeve (2) is coaxially rotatably mounted inside the central hole. The rotating sleeve (2) is mounted between the fixed shaft (8) and the inner wall of the central hole, and can rotate relative to the fixed shaft (8) and the central hole. A mating groove (21) is provided on the end face of the rotating sleeve (2). Several friction plates (4) are fitted in the gap inside the annular cavity. The rotating sleeve (2) has... A number of guide rods (7) are provided. The length direction of the guide rods (7) is along the radial direction of the annular cavity, and the guide rods (7) pass through the friction plate (4). The friction plate (4) can slide along the length direction of the guide rods (7). An elastic band (6) is provided between the friction plate (4) and the fixed shaft (8). A number of through holes (22) are provided on the rotating sleeve (2). The through holes (22) correspond one-to-one with the friction plate (4) and are distributed along the circumference of the rotating sleeve (2). One end of the elastic band (6) is fixedly connected to the friction plate (4). The elastic band (6) connected to the same friction plate (4) passes through the corresponding through hole (22) and is fixedly connected to the fixed shaft (8).

2. The brake device according to claim 1, characterized by: An annular notch (32) is provided between the annular cavity and the central hole, and all guide rods (7) and elastic bands (6) are located within the annular notch (32).

3. The brake device according to claim 1, characterized by: Each friction plate (4) is connected to an even number of elastic bands (6), and the elastic bands (6) connected to the same friction plate (4) are evenly distributed on both sides of the guide rod (7) along the generatrix of the annular cavity.

4. The brake device according to claim 3, characterized in that: The connection points of the elastic bands (6) connected to different friction plates (4) and the fixed shaft (8) are evenly distributed along the circumference of the fixed shaft (8).

5. The brake device of claim 1, wherein: The braking part also includes a mounting cylinder (10), which is used to install on a wind turbine or tower. The sliding cylinder (3) is assembled inside the mounting cylinder (10) and is connected to the mounting cylinder (10) in an axial sliding manner.

6. The brake device according to claim 5, characterized in that: The mounting cylinder (10) is provided with a sliding groove (101), and a sliding body (31) is provided on the outer wall of the sliding cylinder (3). The sliding body (31) is slidably connected to the sliding groove (101), and the length direction of the sliding groove (101) is parallel to the axis direction of the mounting cylinder (10).

7. The brake device of claim 5, wherein: A linear actuator (9) is provided inside the mounting cylinder (10), and the linear actuator (9) is connected to the end of the sliding cylinder (3).

8. A brake device according to any one of claims 1 to 7, wherein: The cross-sectional shape of the connector (11) is non-circular, and the geometry of the mating groove (21) matches the geometry of the mating groove (21).

9. The brake device of claim 8, wherein: The cross-section of the connector (11) is star-shaped.

10. A braking method for a blade shaft, using the braking device for the blade shaft according to any one of claims 1-9, characterized in that: Includes the following steps: S1: The linear actuator (9) pushes the sliding cylinder (3) toward the bushing (1); S2: Insert the connector (11) into the mating groove (21) to complete the mating of the bushing (1) and the brake part; S3: The blade shaft rotates with the bushing (1), the bushing (1) rotates with the rotating sleeve (2), and the rotating sleeve (2) rotates relative to the center hole and the fixed shaft (8); the rotating sleeve (2) moves circumferentially along the annular cavity with the friction plate (4) through the guide rod (7); S4: The rotating sleeve (2) rotates and the elastic band (6) gradually wraps around the fixed shaft (8). The elastic band (6) gradually deforms and has an elastic force F0, and the elastic force F0 gradually increases. The friction plate (4) is subjected to the elastic force F0 of the elastic band (6). The elastic band (6) pulls the friction plate (4) and squeezes the inner wall of the annular cavity. The pressure between the friction plate (4) and the annular cavity gradually increases, and the friction between the friction plate (4) and the annular cavity gradually increases. S5: The friction between the friction plate (4) and the annular cavity inhibits the rotation of the rotating sleeve (2), thereby inhibiting the rotation of the blade shaft and completing the braking of the blade shaft.

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