A brake device and a brake method capable of realizing arbitrary angle docking

Abstract

The application discloses a brake device and brake method capable of realizing butt joint at any angle, relates to the field of vane shaft braking, and comprises a shaft sleeve for being connected with a vane shaft and a brake part; a butt joint sliding part is slidably connected to the shaft sleeve through a sliding cavity; a reset part is arranged between the sliding part and the bottom of the sliding cavity; the sliding part is provided with a butt joint head which can be inserted into a butt joint groove arranged on the brake part to realize the connection between the shaft sleeve and the brake part; the brake part is provided with a sliding cylinder which can be close to or away from the shaft sleeve; the sliding cylinder is provided with an annular cavity and a central hole, a rotating shaft is rotatably arranged in the central hole, and the butt joint groove is arranged on the rotating shaft; a friction cylinder is arranged in the annular cavity; and an elastic belt is arranged between the friction cylinder and the rotating shaft. The application can effectively avoid the interference of the joint and ensure effective butt joint regardless of whether the angle of the butt joint head is matched or not, and can effectively reduce the damage of the vane shaft and the vane.

Description

Technical Field

[0001] This invention relates to the field of blade shaft braking, and in particular to a braking device and method capable of achieving arbitrary angle docking. 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 braking device and method that can achieve docking at any angle, addressing the aforementioned problems. Regardless of whether the angles of the docking joints match during docking, it can effectively avoid joint interference and ensure effective docking; it can also effectively reduce damage to the blade shaft and blades.

[0007] The technical solution adopted in this invention is as follows: A braking device capable of docking at any angle includes a bushing for connecting with a blade shaft and a braking part; the bushing has a sliding cavity, and a docking sliding member is slidably connected in the sliding cavity, the docking sliding member being able to slide along the axial direction of the bushing; a reset member is provided between one end of the docking sliding member and the bottom of the sliding cavity; the other end of the docking sliding member is a butt joint, which can be inserted into a docking 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, a rotating shaft being rotatably mounted coaxially in the central hole, and a docking groove being provided on the end face of the rotating shaft; a friction cylinder is provided in the annular cavity, the cylinder wall of the friction cylinder being able to generate sliding friction with the cavity wall of the annular cavity; the annular cavity surrounds the rotating shaft, and several elastic bands are provided between the friction cylinder and the rotating shaft, one end of the elastic band being fixedly connected to the rotating shaft, and the other end of the elastic band being fixedly connected to the friction cylinder.

[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 elastic bands are located within the annular notch.

[0012] Furthermore, the positions where the elastic bands are connected to the rotating shaft are evenly distributed around the circumference of the rotating shaft; the positions where the elastic bands are connected to the friction cylinder are evenly distributed around the circumference of the friction cylinder.

[0013] 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.

[0014] 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.

[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, using the aforementioned braking device capable of achieving arbitrary angle docking, 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, the bushing rotates with the rotating shaft, and the rotating shaft rotates relative to the sliding cylinder on the same axis.

[0022] S4: The rotation of the rotating shaft will cause the elastic band to gradually deform, and the elastic band will begin to have an elastic force F0 and gradually increase; the elastic force F0 of the elastic band acts on the rotating shaft and the friction cylinder in a non-radial direction.

[0023] S5: When the elastic force F0 of the elastic band is insufficient to overcome the static friction between the friction cylinder and the annular cavity, the elastic force F0 of the elastic band inhibits the rotation of the rotating shaft and initially decelerates the blade shaft.

[0024] S6: When the elastic force F0 of the elastic band is sufficient to overcome the static friction between the friction cylinder and the annular cavity, the friction cylinder rotates in the annular cavity under the action of the elastic force F0 of the elastic band, generating dynamic friction between itself and the inner wall of the annular cavity; the dynamic friction between the friction cylinder and the annular cavity consumes the elastic potential energy of the elastic band, and the blade shaft converts kinetic energy into the elastic potential energy of the elastic band through the rotating shaft, continuously consuming the kinetic energy from the blade shaft on the rotating shaft;

[0025] S7: Braking of the blade shaft is completed when the friction cylinder stops rotating and the kinetic energy provided by the blade shaft to the rotating shaft is insufficient to cause the elastic band to continue to deform.

[0026] In summary, due to the adoption of the above technical solution, the beneficial effects of the present invention are:

[0027] 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.

[0028] 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.

[0029] 3. The present invention uses the buffer of the elastic band to prevent the blade shaft from being abruptly subjected to braking force when it begins to be braked, thus avoiding a sudden drop in the speed of the blade shaft, preventing damage to the blade shaft, and reducing the speed deviation between the blade shaft and the blade, thereby reducing the occurrence of breakage at the connection between the blade and the blade shaft.

[0030] 4. This invention consumes the kinetic energy from the blade shaft through friction between the friction cylinder and the annular cavity, effectively braking the blade shaft. Attached Figure Description

[0031] The present invention will be described by way of example and with reference to the accompanying drawings, wherein:

[0032] Figure 1 This is a schematic diagram of the braking mechanism disclosed in this invention;

[0033] Figure 2 This is a structural diagram of the butt joint inserted into the mating groove disclosed in this invention;

[0034] Figure 3 for Figure 1 Schematic diagram of cross-sectional structure in the middle AA direction

[0035] Figure 4 This is a schematic diagram of the force analysis of the friction cylinder disclosed in this invention;

[0036] 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 shaft; 21-Mating groove; 3-Bearing; 4-Elastic band; 41-Annular notch; 5-Friction cylinder; 6-Sliding cylinder; 61-Sliding body; 7-Mounting cylinder; 71-Slide groove; 8-Linear actuator. Detailed Implementation

[0037] 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.

[0038] 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.

[0039] Example 1

[0040] like Figure 1 - Figure 4 As shown, a braking device capable of docking at any angle includes a bushing 1 for connecting to a blade shaft, and a braking part, wherein the braking part and the bushing 1 are separate components. A sliding cavity 11 is formed on the bushing 1, the depth direction of which is along the axis of the bushing 1. A docking sliding member 12 is slidably connected within the sliding cavity 11, and the docking sliding member 12 can slide along the axis of the bushing 1, allowing it to retract or extend from the sliding cavity 11, further facilitating the movement of the rotating shaft 2 towards the bushing 1 for docking. A reset member 13 is provided between one end of the docking sliding member 12 and the bottom of the sliding cavity 11, causing the sliding member to reset, i.e., extend out of the sliding cavity 11. The other end of the docking sliding member 12 is a connector 14. The bushing 1 can be connected to the braking part by inserting into the docking groove 21 provided on the braking part; the braking part has a sliding cylinder 6, which is slidably mounted on the wind turbine or tower body, and the sliding cylinder 6 can be close to or away from the bushing 1; the sliding cylinder 6 has a coaxial annular cavity and a central hole, and a rotating shaft 2 is rotatably mounted coaxially in the central hole, and the docking groove 21 is provided on the end face of the rotating shaft 2; a friction cylinder 5 is provided in the annular cavity, and the cylinder wall of the friction cylinder 5 can generate sliding friction with the cavity wall of the annular cavity; the annular cavity surrounds the rotating shaft 2, and a number of elastic bands 4 are provided between the friction cylinder 5 and the rotating shaft 2, one end of the elastic band 4 is fixedly connected to the rotating shaft 2, and the other end of the elastic band 4 is fixedly connected to the friction cylinder 5.

[0041] In this embodiment, the reset element 13 can be a compression spring or a magnet. If the reset element 13 is a compression spring, when the docking slider 12 is pushed by the rotating shaft 2, 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 element 13 is a magnet, it works in the same way as the reset element 13 is a compression spring, based on the principle of like poles repulsion, and will not be described in detail here.

[0042] In this embodiment, 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 2 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 2. 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] 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.

[0045] In this embodiment, after the braking unit is connected to the bushing 1, braking of the blade shaft begins. In the initial stage of braking, the elastic band 4 provides buffering, so that the blade shaft is abruptly subjected to braking force when the braking effect begins, avoiding a sharp drop in the speed of the blade shaft, preventing damage to the blade shaft, and reducing the speed deviation between the blade shaft and the blade, thereby reducing the possibility of breakage at the connection between the blade and the blade shaft. The friction between the friction cylinder 5 and the annular cavity consumes the kinetic energy from the blade shaft, effectively achieving braking of the blade shaft.

[0046] Specifically, after the connector 14 is connected to the docking groove 21, the blade shaft rotates the rotating shaft 2 through the bushing 1. The rotation of the rotating shaft 2 causes the other end of the elastic band 4 to move, thereby causing the elastic band 4 to gradually deform and begin to have elastic potential energy. As the rotating shaft 2 rotates, the elastic force of the elastic band 4 gradually increases. At this time, the elastic force of the elastic band 4 will act on the rotating shaft 2 and the friction cylinder 5. The elastic force acting on the rotating shaft 2 will inhibit the rotation of the rotating shaft 2, thereby initially decelerating the blade shaft. The braking force gradually increases from zero, effectively avoiding the blade shaft from being abruptly subjected to braking force when it begins to be braked, thus preventing the blade shaft speed from dropping precipitously.

[0047] It should be noted that since the deformation of the elastic band 4 is caused by the rotation of one end following the rotation of the rotating shaft 2, the elastic force of the elastic band 4 must act on the rotating shaft 2 and the friction cylinder 5 in a non-radial direction. Therefore, the elastic force F0 has two components: one is the radial component F1 of the rotating shaft 2 and the friction cylinder 5, F1 = F0 * cosα, where α is the angle between the tangent of the connection point of the elastic band 4 and the friction cylinder 5 to the tangent direction on the surface of the rotating shaft 2 and the radial direction; the other is the tangential component F2 of the rotating shaft 2 and the friction cylinder 5 in the circumferential direction, F2 = F0 * sinα. The radial component F1 provides pressure between the friction cylinder 5 and the annular cavity to increase the dynamic friction between the friction cylinder 5 and the annular cavity. The tangential component F2 inhibits the rotation of the rotating shaft 2 and provides power for the rotation of the friction cylinder 5 to overcome the dynamic friction between the friction cylinder 5 and the annular cavity.

[0048] It should be noted that, in order to avoid the real-time frictional force f1 between the friction cylinder 5 and the annular cavity always being greater than the tangential component F2, and to ensure that the friction cylinder 5 can be effectively tractioned to rotate as the elastic force F0 increases, it is necessary to ensure that f1 = f0 + μF1 < F2, where f0 is the frictional force between the friction cylinder 5 and the annular cavity when the friction cylinder 5 is not subjected to the elastic force; and μ is the coefficient of kinetic friction. Specifically, this can be achieved by selecting the roughness of the inner wall of the friction cylinder 5, the roughness of the inner wall of the annular cavity (actually selecting the coefficient of kinetic friction μ), the distance between the inner wall of the friction cylinder 5 and the outer wall of the rotating shaft 2 (actually selecting the angle α), and the material of the elastic band 4 (actually selecting the elastic coefficient of the elastic band 4). The specific parameters are determined according to the actual working conditions and will not be elaborated further in this manual. Priority is given to the distance between the inner wall of the friction cylinder 5 and the outer wall of the rotating shaft 2, because this factor is the easiest to adjust during manufacturing and assembly.

[0049] In this embodiment, during the initial braking of the blade shaft, the tangential force F2 is insufficient to overcome the static friction between the friction cylinder 5 and the annular cavity. The elastic force F0 of the elastic band 4 inhibits the rotation of the rotating shaft 2, thus initially decelerating and braking the blade shaft. As the rotating shaft 2 continues to rotate, the elastic force F0 of the elastic band 4 gradually increases, and its degree of inhibition on the rotating shaft 2 gradually increases. Until f1 = f0 + μF1 < F2, that is, when the tangential force is sufficient to overcome the friction between the friction cylinder 5 and the annular cavity, sliding friction is generated between the friction cylinder 5 and the inner wall of the annular cavity, thereby consuming the elastic potential energy of the elastic band 4. The kinetic energy obtained by the rotating shaft 2 from the blade shaft provides elastic potential energy to the elastic band 4, thereby achieving deceleration and braking of the blade shaft through the sliding friction between the friction cylinder 5 and the inner wall of the annular cavity. Until the kinetic energy provided by the blade shaft to the rotating shaft 2 can no longer cause the elastic band 4 to continue to deform, and the friction cylinder 5 is in a stopped rotating state, the braking of the blade shaft is completed.

[0050] Example 2

[0051] like Figure 1 - Figure 2 As shown, based on Example 1, further feasible implementation methods are proposed.

[0052] In one feasible implementation, the cross-sectional shape of the connector 14 is non-circular, and the geometry of the mating groove 21 is matched with the geometry of the mating groove 21 to ensure stable torque transmission, so that the rotation of the rotating shaft 2 is actually the rotation of the blade shaft.

[0053] Furthermore, the geometry of the mating groove 21 is larger than that of the mating connector 14, so as to facilitate the insertion of the mating connector 14 into the mating groove 21.

[0054] 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.

[0055] In one feasible implementation, 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 shape. 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.

[0056] In one feasible implementation, 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, one above the other. During the transmission process, the two non-adjacent second inclined surfaces 16 are respectively in contact with the groove wall of the mating 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.

[0057] Example 3

[0058] Based on any one of the implementation methods in Examples 1-2, further specific implementation methods that can be implemented are proposed.

[0059] In one feasible implementation, an annular notch 41 is provided between the annular cavity and the central hole, and all elastic bands 4 are located within the annular notch 41. The rotation of the rotating shaft 2 causes the elastic bands 4 to deform and move, and the annular belt causes the friction cylinder 5 to rotate, both of which require the elastic bands 4 to deform and move in the circumferential direction. The design of the annular notch 41 provides space for the deformation and movement of the elastic bands 4.

[0060] In one feasible implementation, the positions where several elastic bands 4 are connected to the rotating shaft 2 are evenly distributed around the circumference of the rotating shaft 2; the positions where the elastic bands 4 are connected to the friction cylinder 5 are evenly distributed around the circumference of the friction cylinder 5, ensuring uniform force distribution and uniform force points.

[0061] In one feasible implementation, a bearing 3 is provided between the rotating shaft 2 and the central hole. The bearing 3 can improve the rotational stability of the rotating shaft 2 on the one hand, and reduce the friction between the outer wall of the rotating shaft 2 and the inner wall of the central hole on the other hand. This can minimize the braking effect of the friction on the blade shaft when the joint 14 and the docking groove 21 are docked, and effectively reduce the sudden drop in speed of the blade shaft at the start of braking.

[0062] In one feasible implementation, the braking part further includes a mounting cylinder 7, which is used to install on a wind turbine or tower. The sliding cylinder 6 is assembled inside the mounting cylinder 7 and is connected to the mounting cylinder 7 in an axial direction. The sliding cylinder 6 is slidably assembled on the wind turbine or tower through the mounting cylinder 7, avoiding the need to re-machine an assembly position for the sliding cylinder 6 to slide on the wind turbine or tower.

[0063] Specifically, the mounting cylinder 7 is provided with a sliding groove 71, and the outer wall of the sliding cylinder 6 is provided with a sliding body. The sliding body is slidably connected to the sliding groove 71, and the length direction of the sliding groove 71 is parallel to the axial direction of the mounting cylinder 7. The sliding body slides in the sliding groove 71, so that the sliding cylinder 6 slides in the mounting cylinder 7, thereby allowing the sliding cylinder 6 to move closer to or away from the bushing 1. On the other hand, the sliding groove 71 constrains the sliding body to make circumferential movements, effectively constraining the sliding cylinder 6 to make circumferential movements, providing a basis for the friction cylinder 5 and the annular cavity to make relative circumferential sliding.

[0064] In one feasible implementation, a linear actuator 8 is provided inside the mounting cylinder 7. The linear actuator 8 is connected to the end of the sliding cylinder 6. The linear actuator 8 pushes the sliding cylinder 6 to slide relative to the mounting cylinder 7, so that the sliding cylinder 6 moves closer to or away from the bushing 1.

[0065] Furthermore, the linear actuator 8 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.

[0066] Example 4

[0067] A braking method, such as Figures 1-4 As shown, a braking device capable of docking at any angle, as described in any of the embodiments 1-3, is used to brake the blade shaft, and includes the following steps:

[0068] S1: Linear driver 8 pushes sliding cylinder 6 toward bushing 1.

[0069] S2: Insert the connector 14 into the mating groove 21 to complete the mating of the bushing 1 and the brake unit.

[0070] 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.

[0071] 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 2 will contact the front end face of the mating joint 14 under the action of the linear actuator 8, and push the mating sliding member 12 to slide into the sliding cavity 11, providing clearance for the movement of the rotating shaft 2; 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.

[0072] S3: The blade shaft rotates with the bushing 1, and the bushing 1 rotates with the rotating shaft 2. The rotating shaft 2 rotates relative to the sliding cylinder 6 on the same axis.

[0073] S4: As the rotating shaft 2 rotates, the elastic band 4 gradually deforms, and the elastic band 4 begins to have an elastic force F0, which gradually increases. The elastic force F0 of the elastic band 4 acts on the rotating shaft 2 and the friction cylinder 5 in a non-radial direction. Specifically, the elastic force F0 of the elastic band 4 has two directional components: one is the radial component F1 in the radial direction of the rotating shaft 2 and the friction cylinder 5, F1 = F0 * cosα; the other is the tangential component F2 in the circumferential direction of the rotating shaft 2 and the friction cylinder 5, F2 = F0 * sinα. The radial component F1 provides pressure between the friction cylinder 5 and the annular cavity to increase the dynamic friction between the friction cylinder 5 and the annular cavity. The tangential component F2 inhibits the rotation of the rotating shaft 2 and provides power for the rotation of the friction cylinder 5, overcoming the dynamic friction between the friction cylinder 5 and the annular cavity.

[0074] S5: When the elastic force F0 of the elastic band 4 is insufficient to overcome the static friction between the friction cylinder 5 and the annular cavity, that is, in the initial stage of braking the blade shaft, the tangential component force F2 is insufficient to overcome the friction between the friction cylinder 5 and the annular cavity, and f1=f0+μF1>F2; the elastic force F0 of the elastic band 4 inhibits the rotation of the rotating shaft 2 and initially decelerates the blade shaft.

[0075] S6: As the blade shaft is braked, the blade shaft continues to rotate with the rotating shaft 2. The rotation of the rotating shaft 2 causes the elastic force of the elastic band 4 to continuously increase. When the elastic force F0 of the elastic band 4 is sufficient to overcome the static friction between the friction cylinder 5 and the annular cavity, that is, when the tangential component F2 is sufficient to overcome the frictional force between the friction cylinder 5 and the annular cavity, and f1=f0+μF1<F2, under the action of the tangential component F2 of the friction cylinder 5, the friction cylinder 5 rotates in the annular cavity and generates dynamic friction with the inner wall of the annular cavity. The dynamic friction between the friction cylinder 5 and the annular cavity consumes the elastic potential energy of the elastic band 4, and the elastic band 4 recovers part of its deformation. The blade shaft converts kinetic energy into the elastic potential energy of the elastic band 4 through the rotating shaft 2, and the elastic band 4 increases its deformation. Thus, the blade shaft is indirectly braked by the dynamic friction between the friction cylinder 5 and the annular cavity. In this process, there are three situations as described in steps S61-S63; the specific steps are as follows: steps S61-S64.

[0076] S61: If the increased deformation of the elastic band 4 is greater than the restored deformation of the elastic band 4, that is, the linear velocity of the rotating shaft 2 is greater than the linear velocity of the friction cylinder 5, the deformation of the elastic band 4 will continue to increase, and the elastic force F0 of the elastic band 4 will increase. Since the direction of the elastic force F0 is not the tangential direction of the friction cylinder 5, the radial component force F1 between the friction cylinder 5 and the annular cavity will increase, that is, the radial pressure between the friction cylinder 5 and the annular cavity will increase, the friction force between the friction cylinder 5 and the annular cavity will increase, and the tangential component force F2 on the friction cylinder 5 will increase, the rotation speed of the friction cylinder 5 will increase, and more elastic potential energy of the elastic band 4 will be consumed to overcome friction and do work, thereby improving the braking efficiency of the blade shaft.

[0077] Furthermore, the elastic band 4 will stop deforming until the increased deformation equals the restored deformation, or until the deformation reaches its maximum value. The friction between the friction cylinder 5 and the annular cavity will then reach its maximum value, allowing the friction cylinder 5 to dissipate the kinetic energy from the blade shaft with maximum energy consumption. After the deformation reaches its maximum value, the elastic band 4 will transmit tension, meaning the friction cylinder 5 will experience both elastic force F0 and tension from the elastic band 4, causing its speed to increase rapidly. This achieves synchronous rotation between the friction cylinder 5 and the rotating shaft 2 through the traction of the elastic band 4. This state ends when the increased deformation of the elastic band 4 is less than its restored deformation.

[0078] S62: If the increased deformation of the elastic band 4 is equal to the restored deformation of the elastic band 4, that is, the linear velocity of the rotating shaft 2 is the same as the linear velocity of the friction cylinder 5, the elastic potential energy converted from the kinetic energy of the elastic band 4 from the blade shaft is just consumed by the friction between the friction cylinder 5 and the annular cavity; this state ends when the increased deformation of the elastic band 4 is less than the restored deformation of the elastic band 4.

[0079] S63: Since the deformation recovery of the elastic band 4 is delayed, which is a common characteristic of all elastic elements, and the speed change of the friction cylinder 5 is also delayed, during the entire process of braking the blade shaft, the linear velocity of the friction cylinder 5 is greater than the linear velocity of the rotating shaft 2, that is, the increase in deformation of the elastic band 4 is less than the recovery of deformation of the elastic band 4. If this state occurs, the deformation of the elastic band 4 gradually recovers, and the elastic force F0 of the elastic band 4 gradually decreases until the elastic force F0 of the elastic band 4 is insufficient to overcome the static friction between the friction cylinder 5 and the annular cavity, at which point the speed of the friction cylinder 5 decreases; until step S62 or step S63 occurs or the friction cylinder 5 stops rotating.

[0080] S64: If the blade shaft is still rotating, repeat steps S61-S63 to consume the rotational kinetic energy of the blade shaft.

[0081] S7: Braking of the blade shaft is completed when the friction cylinder 5 stops rotating and the kinetic energy provided by the blade shaft to the rotating shaft 2 is insufficient to cause the elastic band 4 to continue to deform.

[0082] 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 brake device capable of realizing arbitrary angle docking, comprising a shaft sleeve (1) for connecting with a vane shaft, and a brake part; characterized in that: The bushing (1) has a sliding cavity (11), and a docking sliding member (12) is slidably connected inside 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 braking part to realize the connection between the bushing (1) and the braking part. The braking part has a sliding cylinder (6), which is slidably mounted on the wind turbine or tower. The sliding cylinder (6) can... The sliding cylinder (6) is close to or far from the bushing (1); the sliding cylinder (6) has a coaxial annular cavity and a central hole, and a rotating shaft (2) is coaxially mounted in the central hole. A mating groove (21) is provided on the end face of the rotating shaft (2); a friction cylinder (5) is provided in the annular cavity, and the cylinder wall of the friction cylinder (5) can generate sliding friction with the cavity wall of the annular cavity; the annular cavity surrounds the rotating shaft (2), and several elastic bands (4) are provided between the friction cylinder (5) and the rotating shaft (2). One end of the elastic band (4) is fixedly connected to the rotating shaft (2), and the other end of the elastic band (4) is fixedly connected to the friction cylinder (5).

2. The 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 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 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 braking device according to claim 1, characterized in that: An annular notch (41) is provided between the annular cavity and the central hole, and all elastic bands (4) are located within the annular notch (41).

6. The braking device according to claim 1, characterized in that: The positions where the elastic bands (4) are connected to the rotating shaft (2) are evenly distributed around the circumference of the rotating shaft (2); the positions where the elastic bands (4) are connected to the friction cylinder (5) are evenly distributed around the circumference of the friction cylinder (5).

7. The braking device according to claim 1, characterized in that: The braking part also includes a mounting cylinder (7), which is used to install on a wind turbine or tower. The sliding cylinder (6) is assembled inside the mounting cylinder (7) and is connected to the mounting cylinder (7) in an axial sliding manner.

8. The braking device according to claim 7, characterized in that: The mounting cylinder (7) is provided with a sliding groove (71), and the outer wall of the sliding cylinder (6) is provided with a sliding body. The sliding body is slidably connected to the sliding groove (71), and the length direction of the sliding groove (71) is parallel to the axial direction of the mounting cylinder (7).

9. The braking device according to claim 7 or 8, characterized in that: A linear actuator (8) is provided inside the mounting cylinder (7), and the linear actuator (8) is connected to the end of the sliding cylinder (6).

10. A braking method for braking a blade shaft, employing the braking device according to any one of claims 1-9 capable of docking at any angle, characterized in that: Includes the following steps: S1: The linear actuator (8) pushes the sliding cylinder (6) 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 (2) will contact the front end face of the mating joint (14) under the action of the linear actuator (8), and push the mating slider (12) to slide into the sliding cavity (11) to make way for the movement of the rotating shaft (2); at the same time, the blade shaft carries the mating slider (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 slider (12), the mating slider (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 shaft (2), and the rotating shaft (2) rotates relative to the sliding cylinder (6) on the same axis; S4: The rotation of the rotating shaft (2) will cause the elastic band (4) to gradually deform. The elastic band (4) will start to have an elastic force F0 and gradually increase. The elastic force F0 of the elastic band (4) acts on the rotating shaft (2) and the friction cylinder (5) in a non-radial direction. S5: When the elastic force F0 of the elastic band (4) is insufficient to overcome the static friction between the friction cylinder (5) and the annular cavity, the elastic force F0 of the elastic band (4) inhibits the rotation of the rotating shaft (2) and initially decelerates the blade shaft. S6: When the elastic force F0 of the elastic band (4) is sufficient to overcome the static friction between the friction cylinder (5) and the annular cavity, the friction cylinder (5) rotates in the annular cavity under the action of the elastic force F0 of the elastic band (4), and dynamic friction is generated between it and the inner wall of the annular cavity; the dynamic friction between the friction cylinder (5) and the annular cavity consumes the elastic potential energy of the elastic band (4), and the blade shaft converts the kinetic energy into the elastic potential energy of the elastic band (4) through the rotating shaft (2), continuously consuming the kinetic energy from the blade shaft on the rotating shaft (2); S7: Braking of the blade shaft is completed when the friction cylinder (5) is stopped rotating and the kinetic energy provided by the blade shaft to the rotating shaft (2) is insufficient to cause the elastic band (4) to continue to deform.

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