Blade shaft brake device and brake method for preventing interference of joint butt joint

Abstract

The application discloses a kind of blade shaft brake devices and brake methods for preventing butt joint interference, it is related to blade shaft brake field, including shaft sleeve and brake part;Shaft sleeve is slidably connected with butt joint sliding member by sliding cavity;Between butt joint sliding member and sliding cavity bottom, there is reset member;Butt joint sliding member has butt joint that can be inserted into butt joint slot;Brake part has sliding cylinder that can be close to shaft sleeve or away from shaft sleeve;The sliding cylinder has annular cavity, center hole;Center hole is equipped with rotating sleeve, rotating sleeve can rotate relative to fixed shaft, center hole, butt joint slot is arranged on rotating sleeve;Annular cavity has friction plate, guide rod is arranged on rotating sleeve, and friction plate can slide in the radial direction of annular cavity along guide rod;Friction plate and fixed shaft have elastic belt, and elastic belt passes through the through hole arranged on rotating sleeve.The application can effectively avoid interference when shaft sleeve and brake part butt joint, ensure effective butt joint;It can also effectively reduce the damage of blade shaft and blade.

Description

Technical Field

[0001] This invention relates to the field of blade shaft braking, and in particular to a blade shaft braking device and braking method for preventing interference during joint mating. 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 (in a simplified structure, the braking mechanism's connector mates with the blade shaft's connector). 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. 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 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, when the braking mechanism brakes the blade shaft, for the clutch-type method, the blade shaft's mating joint needs to be rotated to a specified position (matching the angle of the mating joint of the braking mechanism) to achieve mating. That is, the angle of the joint needs to match the angle of the mating groove; otherwise, the mating joints will interfere with each other, making mating impossible and potentially causing damage to parts. However, the rotating blade shaft, along with its mating joint, rotates continuously, and the angle of the mating joint changes constantly, making it difficult to achieve mating. In addition, at the moment of solid mating, the blade shaft is subjected to a large braking force, resulting in significant speed fluctuations. This not only causes vibration and damage to the blade shaft but also, due to the inertia of the blade, causes a speed deviation between the blade and the blade shaft, potentially leading to breakage at the connection point between the blade and the blade shaft.

[0005] In summary, when a braking mechanism brakes the blade shaft, there is an urgent need in the field for a braking mechanism that can avoid positional interference at the mating joint and reduce damage to the blade shaft and blades. Summary of the Invention

[0006] The purpose of this invention is to provide a blade shaft braking device and braking method to prevent interference during joint docking, which can effectively avoid joint interference and ensure effective docking regardless of whether the angles of the docking joints match; it can also effectively reduce damage to the blade shaft and blades.

[0007] The technical solution adopted in this invention is as follows: A blade shaft braking device for preventing interference during joint mating includes a bushing for connecting to the blade shaft and a braking part; the bushing has a sliding cavity, and a mating sliding member is slidably connected in the sliding cavity, the mating sliding member being able to slide along the axial direction of the bushing; a reset member is provided between one end of the mating sliding member and the bottom of the sliding cavity; the other end of the mating sliding member is a butt joint, which can be inserted into a mating groove provided on the braking part to realize the connection between the bushing and the braking part; the braking part has a sliding cylinder, the sliding cylinder being slidably mounted on a wind turbine or tower, the sliding cylinder being able to approach or move away from the bushing; the sliding cylinder has a coaxial annular cavity and a central hole, the annular cavity surrounding the central hole; the central hole is coaxially fixed. A fixed shaft and a coaxial rotating assembly are provided. The rotating assembly is fitted between the inner wall of the fixed shaft and the central hole, and can rotate relative to the fixed shaft and the central hole. A mating groove is provided on the end face of the rotating assembly. Several friction plates are fitted with gaps inside the annular cavity. The rotating assembly is provided with guide rods corresponding to the friction plates. 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 provided between the friction plates and the fixed shaft. The rotating assembly is provided with several through holes, each corresponding to a friction plate and distributed circumferentially on the rotating assembly. One end of the elastic band is fixedly connected to a friction plate. Elastic bands connected to the same friction plate pass through the corresponding through hole and are fixedly connected to the fixed shaft.

[0008] Furthermore, the cross-sectional shape of the connector is non-circular, the geometry of the mating groove matches the geometry of the mating groove, and the geometry of the mating groove is larger than the geometry of the connector.

[0009] Furthermore, both the upper and lower surfaces of the connector have a first inclined surface.

[0010] Furthermore, both sides of the connector are provided with a second inclined surface, which fits against the groove wall of the mating groove during transmission.

[0011] 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.

[0012] 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 of the annular cavity; the connection points of the elastic bands connected to different friction plates and the fixed shaft are evenly distributed along the circumference of the fixed shaft.

[0013] Furthermore, bearings are provided between the rotating sleeve and the fixed shaft, and between the rotating sleeve and the inner wall of the central hole.

[0014] Furthermore, the braking unit also includes a mounting cylinder for mounting on a wind turbine or tower. The mounting cylinder has a sliding groove inside, 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.

[0015] Furthermore, a linear actuator is provided inside the mounting cylinder, and the linear actuator is connected to the end of the sliding cylinder.

[0016] A braking method for braking a blade shaft, employing the aforementioned blade shaft braking device for preventing joint mating interference, 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] S21: In step S2, if the angle of the connector matches the angle of the mating groove, the connector is directly inserted into the mating groove;

[0020] S22: In step S2, if the angle of the mating joint does not match the angle of the mating groove, the end face of the rotating shaft will contact the front face of the mating joint under the action of the linear actuator, and push the mating sliding member to slide into the sliding cavity, providing clearance for the movement of the rotating shaft; at the same time, the blade shaft keeps rotating with the mating sliding member, and the angle of the mating joint matches the angle of the mating groove during the 360° rotation of the blade shaft. The reset member works on the mating sliding member, the mating sliding member extends out of the sliding cavity, and the mating joint is inserted into the mating groove.

[0021] 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.

[0022] 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.

[0023] 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.

[0024] In summary, due to the adoption of the above technical solution, the beneficial effects of the present invention are:

[0025] 1. The present invention provides a docking sliding member that can extend or retract into the sliding cavity, thereby allowing the rotating shaft sleeve to move closer to the docking point and effectively avoiding interference between the joint and the rotating shaft.

[0026] 2. By setting a reset component, when the docking sliding component rotates with the blade shaft through the bushing, there is a moment when the angle between the docking joint and the docking groove matches. Thus, the docking sliding component extends out of the sliding cavity under the action of the reset component, allowing the docking joint to be inserted into the docking groove, thereby further realizing the docking of the bushing and the braking part.

[0027] 3. 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;

[0028] 4. 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

[0029] The present invention will be described by way of example and with reference to the accompanying drawings, wherein:

[0030] Figure 1 This is a schematic diagram of the structure of the present invention;

[0031] Figure 2 This is a structural diagram of the butt joint inserted into the mating groove disclosed in this invention;

[0032] Figure 3 for Figure 1 Schematic diagram of the cross section at point AA;

[0033] Figure 4 for Figure 1 Schematic diagram of the cross section at point BB;

[0034] Figure 5 This is a schematic diagram showing the force analysis of the rotating sleeve and the friction plate;

[0035] The markings in the diagram are: 1-Sleeve; 11-Sliding cavity; 12-Mating sliding component; 13-Reset component; 14-Mating joint; 15-First inclined surface; 16-Second inclined surface; 2-Rotating sleeve; 21-Mating 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

[0036] 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.

[0037] 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.

[0038] Example 1

[0039] like Figure 1 - Figure 5 As shown, a blade shaft braking device for preventing interference during joint mating includes a bushing 1 for connecting to the blade shaft and a braking part, wherein the braking part and the bushing 1 are separate units. A sliding cavity 11 is provided on the bushing 1, and a mating sliding member 12 is slidably connected within the sliding cavity 11. The mating sliding member 12 can slide along the axial direction of the bushing 1, allowing it to retract or extend from the sliding cavity 11, further allowing the rotating shaft 1 to move closer to the mating point. A reset member 13 is provided between one end of the mating sliding member 12 and the bottom of the sliding cavity 11, causing the mating sliding member 12 to reset, i.e., extend. The sliding cavity 11; the other end of the docking sliding member 12 is a docking joint 14, which can be inserted into the docking groove 21 provided on the braking part to realize the connection between the bushing 1 and the braking part, and further realize the docking between the blade shaft and the braking part; the braking part has a sliding cylinder 3, which is slidably mounted on the wind turbine or tower body, and the sliding cylinder 3 can be close to the bushing 1 or away from the bushing 1; specifically, the sliding cylinder 3 is away from the bushing 1 to realize the disconnection between the braking part and the blade shaft; the sliding cylinder 3 is close to the bushing 1, and the docking joint 14 is inserted into the docking groove 21 to realize the docking between the blade shaft and the braking part, and then the braking part brakes the blade shaft.

[0040] In this embodiment, the reset member 13 can be a compression spring or a magnet. If the reset member 13 is a compression spring, when the docking slider 12 is pushed by the rotating shaft, the docking slider 12 slides into the sliding cavity 11. The compression spring is compressed and has elastic potential energy, which is used to reset the docking slider 12, that is, to push the docking connector 14 into the docking groove 21. If the reset member 13 is a magnet, it works in the same way as the reset member 13 is a compression spring, based on the principle of like poles repulsion, and will not be described in detail here.

[0041] In this embodiment, the specific docking method between the connector 14 and the docking groove 21 is as follows:

[0042] Since the mating joint 14 is the front end of the mating sliding member 12, and the mating sliding member 12 is connected to the blade shaft through the bushing 1, the mating joint 14 rotates with the blade shaft. Therefore, the angle of the mating groove 21 relative to the mating joint 14 is arbitrary. When the braking part mates with the bushing 1, when the angle between the mating groove 21 and the mating joint 14 is 0° (the length direction of the mating groove 21 is parallel to the length direction of the mating joint 14, and the width direction of the mating groove 21 is parallel to the width direction of the mating joint 14), the mating joint 14 can be directly inserted into the mating groove 21 to achieve the mating of the braking part and the bushing 1.

[0043] In this embodiment, when the angle between the mating groove 21 and the mating head 14 is not 0°, the mating head 14 cannot be inserted into the mating groove 21 due to positional interference. At this time, the rotating shaft continues to move closer to the bushing 1, squeezing the mating sliding member 12 so that it moves into the sliding cavity 11, avoiding interference with the movement of the rotating shaft. The mating head 14 rotates under the drive of the blade shaft until the angle between the mating head 14 and the mating groove 21 is 0°. Under the action of the reset member 13, the mating sliding member 12 extends out of the sliding cavity 11, realizing the insertion of the mating head 14 into the mating groove 21, and realizing the mating of the braking part and the bushing 1.

[0044] 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 connector 14 is mated with the mating groove 21, 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.

[0045] It should be noted that in order to ensure that the mating sliding member 12 rotates together with the bushing 1 to stably transmit torque, it is necessary to avoid relative circumferential movement between the mating sliding member 12 and the bushing 1; therefore, the cross-sectional shape of the mating sliding member 12 matches the cross-sectional shape of the sliding cavity 11 and is non-circular.

[0046] 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 with gaps inside the annular cavity. 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 ensures that the blade shaft will not be subjected to too much friction as a braking force in the initial stage of braking. The rotating sleeve 2 is provided with a guide rod 7 corresponding to the friction plates 4. The length direction of the guide rod 7 is along the radial direction of the annular cavity, and the guide rod 7 passes through the friction plates 4, allowing the friction plates 4 to slide along the length direction of the guide rod 7. On the one hand, this 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 limiting the friction plates 4. On the other hand, the guide rod 7 allows the friction plates 4 to rotate synchronously with the rotating sleeve 2, thereby forming relative friction with the inner wall of the annular cavity.

[0047] 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.

[0048] 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.

[0049] In this embodiment, the blade shaft needs to be braked, and the process is as follows:

[0050] 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 14 on the bushing 1 is inserted into the mating groove 21 on the rotating sleeve 2 through the above-mentioned mating method, 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 along 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 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. 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.

[0051] It should be noted that, as Figure 5 As 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.

[0052] 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.

[0053] Example 2

[0054] Based on Example 1, further feasible implementation methods are proposed.

[0055] In one feasible implementation, the cross-sectional shape of the connector 14 is non-circular, and the geometry of the mating groove 21 matches that of the mating groove 21 to ensure stable torque transmission, so that the rotation of the rotating shaft is actually the rotation of the blade shaft; the geometric dimensions of the mating groove 21 are larger than those of the connector 14 to facilitate the insertion of the connector 14 into the mating groove 21.

[0056] It should be noted that, in this embodiment, the cross-sectional shape of the mating groove 21 and the cross-sectional shape of the mating joint 14 are preferably waist-shaped or rectangular, and their length is greater than their width, so as to ensure stable torque transmission and prevent the mating joint 14 from rotating in the mating groove 21.

[0057] One feasible implementation method is, for example Figure 1 As shown, both the upper and lower surfaces of the connector 14 have a first inclined surface 15, making the shape of the connector 14 close to a wedge. The first inclined surface 15 makes way for the connector 14 to be inserted into the mating groove 21, avoiding interference and improving the stability of the connector 14 when inserted into the mating groove 21.

[0058] One feasible implementation method is, for example Figure 2As shown, the two sides of the connector 14 are provided with a second inclined surface 16, and each side has two second inclined surfaces 16. The two second inclined surfaces 16 are respectively provided at two locations on the same side. During the transmission process, the two non-adjacent second inclined surfaces 16 are respectively in contact with the groove wall of the docking groove 21 to achieve surface contact to transmit torque, reduce contact pressure, increase the limit of torque that can be transmitted, and effectively avoid damage to parts during high torque transmission.

[0059] Example 3

[0060] Based on any one of the implementation methods in Examples 1-2, further feasible implementation methods are proposed.

[0061] 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.

[0062] 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. 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. 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, so that the deformation of all elastic bands 66 is equal when the rotating sleeve 2 rotates at any angle, thereby making the frictional force between all friction plates 4 and the inner wall of the annular cavity equal.

[0063] 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.

[0064] In one feasible implementation, in order to ensure that the rotating sleeve 2 rotates stably 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 14 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.

[0065] 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.

[0066] Example 4

[0067] Based on any one of the implementation methods in Examples 1-3, further feasible implementation methods are proposed.

[0068] 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.

[0069] 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.

[0070] 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.

[0071] 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.

[0072] Example 5

[0073] like Figures 1-5 As shown, a braking method for braking a blade shaft, using the blade shaft braking device for preventing joint interference as described in any of the embodiments 1-4, includes the following steps:

[0074] S1: Linear actuator 9 pushes sliding cylinder 3 toward bushing 1;

[0075] S2: Insert the connector 14 into the mating groove 21 to complete the mating of the bushing 1 and the brake part;

[0076] S21: In step S2, if the angle of the connector 14 matches the angle of the mating groove 21, the connector 14 is directly inserted into the mating groove 21.

[0077] S22: In step S2, if the angle of the mating joint 14 does not match the angle of the mating groove 21, the end face of the rotating shaft will contact the front end face of the mating joint 14 under the action of the linear actuator 9, and push the mating sliding member 12 to slide into the sliding cavity 11, providing clearance for the movement of the rotating shaft; at the same time, the blade shaft carries the mating sliding member 12 to keep rotating, and the angle of the mating joint 14 matches the angle of the mating groove 21 during the 360° rotation of the blade shaft. The reset member 13 works on the mating sliding member 12, the mating sliding member 12 extends out of the sliding cavity 11, and the mating joint 14 is inserted into the mating groove 21;

[0078] 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.

[0079] 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.

[0080] 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.

[0081] 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 blade shaft braking device for preventing interference during joint mating, comprising a bushing (1) for connection with the blade shaft, and a braking part; characterized in that: The bushing (1) has a sliding cavity (11), and a docking sliding member (12) is slidably connected in the sliding cavity (11). The docking sliding member (12) can slide along the axis of the bushing (1). A reset member (13) is provided between one end of the docking sliding member (12) and the bottom of the sliding cavity (11). The other end of the docking sliding member (12) is a connector (14), which can be inserted into the docking groove (21) provided on the brake part to realize the connection between the bushing (1) and the brake part. The brake 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. The annular cavity surrounds the central hole. A fixed shaft (8) is coaxially fixed in the central hole and a rotating sleeve (2) is coaxially rotatably mounted in the central hole. The rotating sleeve (2) is mounted on the fixed shaft (8) and the rotating sleeve (2) is mounted on the fixed shaft (8) and the rotating sleeve (2) is rotatably mounted in the central hole. Between the inner walls of the central hole, it is possible to rotate relative to the fixed shaft (8) and the central hole. The mating groove (21) is set on the end face of the rotating sleeve (2). Several friction plates (4) are fitted in the gap of the annular cavity. The rotating sleeve (2) is provided with a guide rod (7) corresponding to the friction plate (4). The length direction of the guide rod (7) is along the radial direction of the annular cavity, and the guide rod (7) passes through the friction plate (4). The friction plate (4) can slide along the length direction of the guide rod (7). An elastic band (6) is provided between the friction plate (4) and the fixed shaft (8). Several 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 blade shaft braking device according to claim 1, characterized in that: The cross-sectional shape of the connector (14) is non-circular, the geometry of the mating groove (21) matches the geometry of the mating groove (21), and the geometry of the mating groove (21) is larger than the geometry of the connector (14).

3. The blade shaft braking device according to claim 1, characterized in that: The upper and lower surfaces of the connector (14) both have a first inclined surface (15).

4. The blade shaft braking device according to claim 3, characterized in that: The two sides of the connector (14) are provided with a second inclined surface (16), which fits against the groove wall of the docking groove (21) during transmission.

5. The blade shaft braking device according to claim 1, characterized in that: 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).

6. The blade shaft braking device according to claim 1, characterized in that: 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. 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).

7. The blade shaft braking device according to claim 1, characterized in that: Bearings (5) are 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.

8. The blade shaft braking device according to any one of claims 1-7, characterized in that: The braking part also includes a mounting cylinder (10), which is used to install on a wind turbine or tower. 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).

9. The blade shaft braking device according to claim 8, characterized in that: 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).

10. A braking method for braking a blade shaft, employing the blade shaft braking device for preventing joint mating interference as described in 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 (14) into the mating groove (21) to complete the mating of the bushing (1) with the brake part; S21: In step S2, if the angle of the connector (14) matches the angle of the mating groove (21), the connector (14) is directly inserted into the mating groove (21); S22: In step S2, if the angle of the mating joint (14) does not match the angle of the mating groove (21), the end face of the rotating shaft will contact the front end face of the mating joint (14) under the action of the linear actuator (9), and push the mating sliding member (12) to slide into the sliding cavity (11) to make way for the movement of the rotating shaft; at the same time, the blade shaft carries the mating sliding member (12) to keep rotating. During the 360° rotation of the blade shaft, the angle of the mating joint (14) matches the angle of the mating groove (21). The reset member (13) works on the mating sliding member (12), the mating sliding member (12) extends out of the sliding cavity (11), and the mating joint (14) is inserted into the mating groove (21); 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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