Shafting structure of vertical-axis wind turbine with damping device

Abstract

The invention discloses a vertical-axis wind turbine shaft system structure with a damping device, which comprises a middle shaft, a fixed disc, a movable ring and a self-aligning roller thrust bearing sleeved outside the middle shaft, and at least three spring hydraulic dampers, the head and tail ends of the spring hydraulic dampers are respectively hinged with the fixed disc and the movable ring, and the fixed disc and the movable ring are hinged with the fixed disc and the self-aligning roller thrust bearing. When the center shaft deflects around the curvature center of an outer ring raceway of the self-aligning roller thrust bearing, the center shaft drives the movable ring to deflect and rotate, and in the process that the movable ring rotates by the maximum angle or deflects by the maximum distance from the initial centering state, the center shaft rotates by the maximum angle or deflects by the maximum distance from the initial centering state in the overlooking view angle of the fixed disc. The distance between the movable ring and the fixed disc is always larger than or equal to 0 mm, all the spring hydraulic shock absorbers deflect towards the same side in the circumferential direction of the movable ring, and the included angles between all the spring hydraulic shock absorbers and the radial direction of the movable ring are always larger than 0 degree. According to the invention, the fan can still have better stability in a strong wind environment.

Description

Technical Field

[0001] The present invention relates to the technical field of wind turbines, and in particular to a vertical-axis wind turbine shaft system structure with a shock-absorbing device. Background Art

[0002] Vertical-axis wind turbines (VAWTs) have attracted increasing attention in recent years due to their potential advantages, including compact size, insensitivity to wind direction, low noise levels, and suitability for urban and distributed applications. The shafting structure, a core component of VAWTs, is crucial for transmitting the wind energy torque captured by the rotor to the generator and supporting the rotor's rotation.

[0003] Due to its unique aerodynamic working principle, vertical axis wind turbines are prone to generate strong periodic pulsating torque and alternating radial loads on the central axis, which causes resonance and makes the wind turbine less stable in strong wind environments. Summary of the Invention

[0004] The object of the present invention is to provide a vertical axis wind turbine shaft system structure with a shock absorbing device, which can enable the wind turbine to have better stability in a strong wind environment.

[0005] In order to solve the above technical problems, the present invention adopts the following solutions: A vertical axis wind turbine shaft system structure with a shock absorbing device includes a central axis and a fixed plate sleeved outside the central axis. The central axis outer shell is provided with a movable ring separated from the fixed plate, and a spherical roller thrust bearing is arranged below the movable ring. The structure also includes at least three spring hydraulic shock absorbers arranged around the movable ring. The head and tail ends of the spring hydraulic shock absorbers are respectively hinged to the fixed plate and the movable ring. When the central shaft deflects around the curvature center of the outer ring raceway of the spherical roller thrust bearing, the central shaft drives the movable ring to deflect and rotate. Before the movable ring moves from the initial centered state to the maximum deflection distance, all spring hydraulic shock absorbers are in a compressed state; In the process of the movable ring moving from the initial centering state to the maximum offset state, the spring hydraulic shock absorber facing away from the offset direction of the movable ring changes from a compressed state to a tensile state, and the compression degree of the remaining spring hydraulic shock absorbers increases. When the spring hydraulic shock absorber facing away from the deflection direction of the movable ring is in a tensile state, the tension exerted on the spring hydraulic shock absorber causes the movable ring to rotate. The pressure generated by the rotation of the movable ring compresses the remaining spring hydraulic shock absorbers. At the same time, the spring hydraulic shock absorber located in the deflection direction of the central axis is also subjected to the pressure generated by the offset of the central axis. During the process of the movable ring rotating from the initial alignment state to the maximum angle or the maximum offset distance, when viewed from above the fixed plate, the distance between the movable ring and the fixed plate is always greater than or equal to 0 mm, all spring hydraulic shock absorbers are deflected toward the same side in the circumferential direction of the movable ring, and the angle between all spring hydraulic shock absorbers and the radial direction of the movable ring is always greater than 0°. When the center axis is in an offset state, the compression degree of the spring hydraulic shock absorber close to the center axis is greater than that of the spring hydraulic shock absorber far from the center axis. During the center axis deviation process, the movable ring rotates around its own axis, and the rotation direction of the movable ring is opposite to the rotation direction of the spring hydraulic shock absorber around the hinge point of the spring hydraulic shock absorber on the fixed plate. During the centering process, the movable ring rotates in the opposite direction to that during the center axis deflection. The spring-hydraulic shock absorber also rotates in the opposite direction to that during the center axis deflection. The hydraulic damping and spring force of the spring-hydraulic shock absorber are adjustable to suit different vertical axis wind turbine sizes. The movable ring allows the center axis to deflect or rotate the movable ring, converting the center axis deflection and rotation into the stroke of the spring-hydraulic shock absorber. The spring-hydraulic shock absorber also buffers vibrations from the center axis, improving its stability. The spatial arrangement of the spring-hydraulic shock absorber and the movable ring ensures that when the center axis deflects, the center axis pushes the movable ring laterally. The obliquely hinged spring-hydraulic shock absorber resists this displacement, generating a torque that forces the movable ring to rotate around its own axis. The rotation of the movable ring always opposes the swing direction of the spring-hydraulic shock absorber.

[0006] Furthermore, at least three preload adjustment devices are provided between the movable ring and the fixed plate, surrounding the movable ring. The preload adjustment devices include a coaxially arranged adjustment rod and an elastic member, each comprising an adjustable fisheye bearing located at both ends of the integral structure of the adjustment rod and the elastic member. The preload adjustment devices function to adjust the position of the central axis so that the initial positions of the central axis and the movable ring are coaxial with the fixed plate. The adjustment rod can be used to adjust the stretched length of the elastic member, thereby controlling the preload on the central axis and ensuring centering of the central axis.

[0007] Furthermore, the adjustment rod comprises an inner rod and an outer rod threaded together, and the elastic member comprises a preload spring and end caps fixedly connected to both ends of the preload spring, one end cap being connected to the adjustment rod, and the other end cap being connected to the adjustable fisheye bearing. The purpose of this design is to precisely control the preload force through the design of the threaded inner and outer rods; the provision of the preload spring provides an elastic foundation, allowing for dynamic fine-tuning of the preload force of the centering axis; and the provision of the end caps encapsulates the preload spring and transmits force, thereby achieving connection between the elastic member, the adjustable fisheye bearing, and the adjustment rod.

[0008] Furthermore, the inner rod is connected to the end cap, and the outer rod is connected to the adjustable fisheye bearing. The adjustable fisheye bearing connected to the outer rod is provided with an embedding section for embedding into the outer rod. The outer wall of the embedding section is provided with a shoulder on the end facing the inner rod and the inner wall of the outer rod is provided with a shoulder on the end facing away from the inner rod. The design of the embedding section and the shoulder serves to axially limit the outer rod and the adjustable fisheye bearing connected thereto, thereby preventing the outer rod and the adjustable fisheye bearing from disengaging.

[0009] Furthermore, the spring hydraulic shock absorber is provided with shock-absorbing fisheye bearings at both ends. A vertical nail arranged parallel to the central axis is fixedly connected to the fixed plate. A vertical rod arranged parallel to the central axis is provided on the inner wall of the movable ring. The shock-absorbing fisheye bearings at both ends of the spring hydraulic shock absorber are respectively mounted on the vertical nail and the vertical rod. A bolt arranged parallel to the central axis is provided on the top surface of the movable ring. The adjustment fisheye bearings at both ends of the preload adjustment device are respectively mounted on the vertical nail and the bolt. The arrangement of the vertical nail, the vertical rod, and the bolt provides an articulated rod parallel to the central axis. The arrangement of the vertical nail and the vertical rod at different positions of the movable ring allows the preload adjustment device and the spring hydraulic shock absorber to be at different heights without interfering with each other.

[0010] Furthermore, the movable ring includes an upper ring and a lower ring, with a portion of the vertical rod located on the upper ring and the other portion of the vertical rod located on the lower ring. Bolts are threadedly connected to both the upper and lower rings. The arrangement of the upper and lower rings facilitates the attachment of the shock-absorbing fisheye bearing to the vertical rod. The bolts provide both a hinged rod and a connection between the upper and lower rings.

[0011] Furthermore, a self-aligning bearing is provided between the inner wall of the movable ring and the outer wall of the central shaft, which allows the movable ring to swing adaptively when the central shaft rotates or deflects, thereby avoiding rigid interference.

[0012] Furthermore, the system also includes a bearing plate arranged parallel to the fixed plate. A constant velocity joint coupling connected to the central shaft is mounted on the bottom surface of the bearing plate. A spherical roller thrust bearing is mounted on the top surface of the bearing plate, and a bearing cap is mounted on top of the spherical roller thrust bearing. The constant velocity joint coupling utilizes a ball cage coupling or a tripod coupling. Its function is to compensate for angular deviations of the central shaft and maintain transmission efficiency through the constant velocity joint coupling; to withstand axial wind pressure loads and allow for slight misalignment of the shaft system through the spherical roller thrust bearing; and to support the thrust bearing and mount the constant velocity joint coupling through the bearing plate.

[0013] Furthermore, the constant velocity joint coupling utilizes a ball cage coupling, with the center of the spherical ball of the constant velocity joint coupling coinciding with the center of curvature of the outer raceway of the spherical roller thrust bearing. This ensures that the constant velocity joint coupling maintains normal operation during the rotation of the center shaft, through the spatial and dimensional design of the constant velocity joint coupling and the spherical roller thrust bearing.

[0014] Furthermore, the system includes a motor plate positioned parallel to the fixed plate, with a generator connected to the bottom end of the motor plate, which is in turn connected to a constant velocity universal joint coupling. A bearing plate is positioned between the fixed plate and the motor plate, with the fixed plate and the bearing plate, as well as the bearing plate and the motor plate, connected and supported by studs.

[0015] The present invention has the beneficial effects: 1. The movable ring allows the center shaft to drive the movable ring to deflect or rotate, converting the center shaft's deflection and rotation into the travel of the spring hydraulic shock absorber. The spring hydraulic shock absorber can buffer and absorb vibrations to the center shaft, improving its stability. The spatial arrangement of the spring hydraulic shock absorber and the movable ring ensures that all spring hydraulic shock absorbers are compressed in coordination when the center shaft deflects or rotates. 2. The position of the central axis can be adjusted by setting the preload adjustment device, so that the initial position of the central axis and the movable ring is coaxial with the fixed plate; the stretching length of the elastic member can be adjusted by setting the adjustment rod, thereby controlling the preload of the central axis and centering the central axis; 3. The setting of the constant velocity universal joint coupling can compensate for the angular deviation of the center shaft and maintain the transmission efficiency; the setting of the spherical roller thrust bearing can withstand the axial wind pressure load and allow slight misalignment of the shaft system; the setting of the bearing plate can support the thrust bearing and install the constant velocity universal joint coupling. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 Schematic diagram of the three-dimensional structure of Example 1; Figure 2 Schematic diagram of the top view of the structure of Example 1; Figure 3 This is a schematic cross-sectional view of the preload force adjustment device in Example 1.

[0017] Figure markings: 1. central axis; 2. fixed plate; 3. movable ring; 4. spring hydraulic shock absorber; 5. adjusting rod; 6. elastic member; 7. adjusting fisheye bearing; 8. inner rod; 9. outer rod; 10. end cover; 11. preload spring; 12. embedded section; 13. shoulder; 14. shock-absorbing fisheye bearing; 15. vertical nail; 16. vertical rod; 17. bolt; 18. upper ring; 19. lower ring; 20. self-aligning bearing; 21. bearing plate; 22. constant velocity universal joint coupling; 23. self-aligning roller thrust bearing; 24. bearing cover; 25. motor plate; 26. generator. DETAILED DESCRIPTION

[0018] The present invention will be further described in detail below with reference to the embodiments and the accompanying drawings, but the embodiments of the present invention are not limited thereto.

[0019] In the description of the present invention, it should be noted that the terms "center", "up", "down", "left", "right", "vertical", "longitudinal", "lateral", "horizontal", "inside", "outside", "front", "back", "top", "bottom", etc., indicating the orientation or position relationship, are based on the orientation or position relationship shown in the accompanying drawings, or are the orientation or position relationship in which the inventive product is usually placed when used. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation to the present invention.

[0020] In the description of the present invention, it should also be noted that, unless otherwise expressly specified or limited, the terms "disposed," "having," "installed," "connected," and "connected" should be understood in a broad sense. For example, they may refer to fixed connections, detachable connections, or integral connections; mechanical connections or electrical connections; direct connections or indirect connections through an intermediate medium; and internal connections between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention in specific contexts.

[0021] Example 1 A vertical axis wind turbine shafting structure with a vibration damping device, such as Figure 1 As shown, it includes a central axis 1, a fixed plate 2 sleeved outside the central axis 1, a movable ring 3 separated from the fixed plate 2 and a spherical roller thrust bearing 23 arranged below the movable ring 3, and at least three spring hydraulic shock absorbers 4 arranged around the movable ring 3. The head and tail ends of the spring hydraulic shock absorber 4 are respectively hinged to the fixed plate 2 and the movable ring 3. When the central shaft 1 deflects around the center of curvature of the outer raceway of the spherical roller thrust bearing 23, the central shaft 1 drives the movable ring 3 to deflect and rotate. Before the movable ring 3 moves from the initial centering state to the maximum displacement distance, all the spring hydraulic shock absorbers 4 are in a compressed state; In the process of the movable ring 3 moving from the initial centering state to the state of maximum offset, the spring hydraulic shock absorber 4 facing away from the offset direction of the movable ring 3 changes from a compressed state to a tensile state, and the compression degree of the remaining spring hydraulic shock absorbers 4 increases. When the spring hydraulic shock absorber 4 facing away from the deflection direction of the movable ring 3 is in a tensile state, the tension exerted on the spring hydraulic shock absorber 4 causes the movable ring 3 to rotate. The pressure generated by the rotation of the movable ring 3 compresses the remaining spring hydraulic shock absorbers 4. At the same time, the spring hydraulic shock absorber 4 located in the deflection direction of the central axis 1 is also subjected to the pressure caused by the offset of the central axis 1. During the process of the movable ring 3 rotating from the initial centering state to the maximum angle or the maximum offset distance, when viewed from above the fixed plate 2, the distance between the movable ring 3 and the fixed plate 2 is always greater than or equal to 0 mm, all the spring hydraulic shock absorbers 4 are deflected toward the same side in the circumferential direction of the movable ring 3, and the angle between all the spring hydraulic shock absorbers 4 and the radial direction of the movable ring 3 is always greater than 0°. When the center axis 1 is in an offset state, the compression degree of the spring hydraulic shock absorber 4 close to the center axis 1 is greater than the compression degree of the spring hydraulic shock absorber 4 far from the center axis 1. During the deviation of the central axis 1, the movable ring 3 rotates around its own axis, and the rotation direction of the movable ring 3 is opposite to the rotation direction of the spring hydraulic shock absorber 4 around the hinge point of the spring hydraulic shock absorber 4 on the fixed plate 2. During the centering process of the central axis 1, the rotation direction of the movable ring 3 is opposite to that of the movable ring 3 during the deflection process of the central axis 1. The rotation direction of the spring hydraulic shock absorber 4 is opposite to that of the spring hydraulic shock absorber 4 during the deflection process of the central axis 1. Its function is that, through the setting of the movable ring 3, the central axis 1 can drive the movable ring 3 to deflect or rotate. Before the movable ring 3 moves from the initial centering state to the maximum displacement distance, all spring hydraulic shock absorbers 4 are in a compressed state; When the movable ring 3 is in the state of maximum displacement, the spring hydraulic shock absorber 4 facing away from the displacement direction of the movable ring 3 is in a natural state; The offset and rotation of the central axis 1 are converted into the stroke of the spring hydraulic shock absorber 4; through the setting of the spring hydraulic shock absorber 4, the vibration exerted on the central axis 1 can be buffered and consumed, thereby improving the stability of the central axis 1; through the design of the spatial arrangement relationship between the spring hydraulic shock absorber 4 and the movable ring 3, when the central axis 1 is offset, the central axis 1 can push the movable ring 3 to move laterally, and the obliquely hinged spring hydraulic shock absorber 4 generates a torque when resisting the displacement, forcing the movable ring 3 to rotate around its own axis, and the rotation direction of the movable ring 3 is always opposite to the swing direction of the spring hydraulic shock absorber 4.

[0022] At least three preload adjustment devices are provided between the movable ring 3 and the fixed plate 2, surrounding the movable ring 3. These preload adjustment devices comprise a coaxially arranged adjustment rod 5 and an elastic member 6. The preload adjustment devices include adjustable fisheye bearings 7 located at both ends of the integral structure of the adjustment rod 5 and the elastic member 6. These preload adjustment devices function to adjust the position of the central axis 1, ensuring that the initial positions of the central axis 1 and the movable ring 3 are coaxial with the fixed plate 2. The adjustment rod 5 can be used to adjust the stretched length of the elastic member 6, thereby controlling the preload on the central axis 1 and ensuring proper centering of the central axis 1.

[0023] Specifically, such as Figure 3 As shown, the adjustment rod 5 includes an inner rod 8 and an outer rod 9 that are threadedly connected to each other, and the elastic member 6 includes a preload spring 11 and end caps 10 fixedly connected to both ends of the preload spring 11. One end cap 10 is connected to the adjustment rod 5, and the other end cap 10 is connected to the adjustment fisheye bearing 7. Its functions are as follows: through the design of the inner rod 8 and outer rod 9 that are threadedly connected to each other, the preload force can be precisely controlled; through the provision of the preload spring 11, an elastic foundation can be provided, allowing dynamic fine-tuning of the preload force of the centering shaft 1; through the provision of the end cap 10, the preload spring 11 can be encapsulated and force can be transmitted, thereby achieving the connection between the elastic member 6, the adjustment fisheye bearing 7 and the adjustment rod 5.

[0024] Specifically, such as Figure 3 As shown, the inner rod 8 is connected to the end cover 10, and the outer rod 9 is connected to the adjustable fisheye bearing 7. The adjustable fisheye bearing 7 connected to the outer rod 9 is provided with an embedding section 12 for embedding into the outer rod 9. The outer wall of the embedding section 12 is provided with a shoulder 13 at one end facing the inner rod 8 and the inner wall of the outer rod 9 is provided with a shoulder 13 at one end away from the inner rod 8. Its function is to axially limit the outer rod 9 and the adjustable fisheye bearing 7 connected thereto through the design of the embedding section 12 and the shoulder 13, so as to prevent the outer rod 9 from being separated from the adjustable fisheye bearing 7.

[0025] Specifically, such as Figure 1 As shown, the spring hydraulic shock absorber 4 is provided with shock-absorbing fisheye bearings 14 at both ends, a vertical nail 15 arranged parallel to the central axis 1 is fixedly connected to the fixed plate 2, and a vertical rod 16 arranged parallel to the central axis 1 is provided on the outer wall of the movable ring 3. The shock-absorbing fisheye bearings 14 at both ends of the spring hydraulic shock absorber 4 are respectively mounted on the vertical nail 15 and the vertical rod 16, and a bolt 17 is provided on the top surface of the movable ring 3 and is arranged parallel to the central axis 1. The adjustment fisheye bearings 7 at both ends of the preload adjustment device are respectively mounted on the vertical nail 15 and the bolt 17. The function of the preload adjustment device is to provide a hinged rod parallel to the central axis 1 by providing the vertical nail 15, the vertical rod 16 and the bolt 17; and by arranging the vertical nail 15 and the vertical rod 16 at different positions of the movable ring 3, the preload adjustment device and the spring hydraulic shock absorber 4 are at different heights and do not interfere with each other.

[0026] Specifically, such as Figure 1 As shown, the movable ring 3 includes an upper ring 18 and a lower ring 19. A portion of the vertical rod 16 is located on the upper ring 18, and the other portion of the vertical rod 16 is located on the lower ring 19. Bolts 17 are threadedly connected to both the upper ring 18 and the lower ring 19. The arrangement of the upper ring 18 and the lower ring 19 facilitates the attachment of the shock-absorbing fisheye bearing 14 to the vertical rod 16. The arrangement of the bolts 17 not only provides a hinged rod but also connects the upper ring 18 and the lower ring 19.

[0027] Specifically, such as Figure 1 As shown, a self-aligning bearing 20 is provided between the inner wall of the movable ring 3 and the outer wall of the central axis 1. Its function is to allow the movable ring 3 to swing adaptively when the central axis 1 rotates or deflects through the setting of the self-aligning bearing 20, thereby avoiding rigid interference.

[0028] Specifically, such as Figure 1 As shown, the system also includes a bearing plate 21, arranged parallel to the fixed plate 2. A constant velocity joint coupling 22 connected to the central shaft 1 is mounted on the bottom surface of the bearing plate 21. A spherical roller thrust bearing 23 is mounted on the top surface of the bearing plate 21, and a bearing cap 24 is mounted on top of the spherical roller thrust bearing 23. The constant velocity joint coupling 22 utilizes a ball cage coupling or a tripod coupling. Its functions are: the constant velocity joint coupling 22 can compensate for angular deviations of the central shaft 1 and maintain transmission efficiency; the spherical roller thrust bearing 23 can withstand axial wind pressure loads and allow for slight misalignment of the shaft system; and the bearing plate 21 can support the thrust bearing and mount the constant velocity joint coupling 22.

[0029] Specifically, such as Figure 1 As shown, the constant velocity joint 22 is a ball cage coupling, and the center of the ball of the constant velocity joint 22 coincides with the center of curvature of the outer raceway of the spherical roller thrust bearing 23. This ensures that the constant velocity joint 22 maintains normal operation during the rotation of the center shaft 1, through the design of the spatial and dimensional relationship between the constant velocity joint 22 and the spherical roller thrust bearing 23.

[0030] Specifically, such as Figure 1 As shown, the motor plate 25 is also provided parallel to the fixed plate 2. A generator 26 is connected to the bottom end of the motor plate 25. The generator 26 is connected to the constant velocity universal joint coupling 22. A bearing plate 21 is located between the fixed plate 2 and the motor plate 25. The fixed plate 2 and the bearing plate 21, as well as the bearing plate 21 and the motor plate 25, are connected and supported by studs.

[0031] The working principle of this embodiment is described as follows: Figure 2As shown, the obliquely hinged spring hydraulic shock absorber 4 converts the offset of the central axis 1 into a clockwise rotational motion of the movable ring 3, driving all the spring hydraulic shock absorbers 4 to swing counterclockwise, the spring buffers low-frequency vibrations and the hydraulic damping dissipates high-frequency impacts; the initial verticality of the central axis 1 is corrected by adjusting the difference of the preload adjustment device; the curvature center of the outer ring raceway of the spherical roller thrust bearing 23 is strictly coincident with the ball center of the ball cage coupling to ensure that the thrust bearing self-aligns to maintain the horizontality of the bearing seat when the central axis 1 rotates, and at the same time the ball cage coupling maintains a constant speed output without displacement deviation, and finally the system's impact resistance is improved by the synergistic effect of oblique shock absorption, providing core technical support for anti-turbulence and anti-resonance for vertical axis fans.

[0032] The above description is merely a preferred embodiment of the present invention and does not constitute any form of limitation to the present invention. Based on the technical essence of the present invention and within the spirit and principles of the present invention, any simple modification, equivalent replacement and improvement of the above embodiment shall still fall within the scope of protection of the technical solution of the present invention.

Claims

1. A vertical axis wind turbine shafting structure with a vibration damping device, comprising a central axis (1), characterized in that: The central shaft (1) further comprises a fixed plate (2) sleeved on the outside of the central shaft (1), a movable ring (3) separated from the fixed plate (2) and a spherical roller thrust bearing (23) arranged below the movable ring (3) are provided on the outer sleeve of the central shaft (1), and at least three spring hydraulic shock absorbers (4) arranged around the movable ring (3), the front and rear ends of the spring hydraulic shock absorbers (4) being hinged to the fixed plate (2) and the movable ring (3) respectively. When the central shaft (1) deflects around the center of curvature of the outer ring raceway of the spherical roller thrust bearing (23), the central shaft (1) drives the movable ring (3) to deflect and rotate. Before the movable ring (3) moves from the initial centering state to the maximum displacement distance, all the spring hydraulic shock absorbers (4) are in a compressed state; In the process of the movable ring (3) changing from the initial centering state to the maximum offset state, the spring hydraulic shock absorber (4) facing away from the offset direction of the movable ring (3) changes from a compressed state to a tensile state, and the compression degree of the remaining spring hydraulic shock absorbers (4) increases. When the spring hydraulic shock absorber (4) facing away from the deflection direction of the movable ring (3) is in a tensile state, the tension exerted on the spring hydraulic shock absorber (4) causes the movable ring (3) to rotate, and the pressure generated by the rotation of the movable ring (3) compresses the remaining spring hydraulic shock absorbers (4). At the same time, the shock absorber located in the deflection direction of the central axis (1) is also subjected to the pressure generated by the offset of the central axis (1); In the process of the movable ring (3) rotating from the initial centering state to the maximum angle or the maximum offset distance, in the top view of the fixed disk (2), the distance between the movable ring (3) and the fixed disk (2) is always greater than or equal to 0 mm, all the spring hydraulic shock absorbers (4) are deflected toward the same side in the circumferential direction of the movable ring (3) and the angle between all the spring hydraulic shock absorbers (4) and the radial direction of the movable ring (3) is always greater than 0°, When the center axis (1) is in an offset state, the compression degree of the spring hydraulic shock absorber (4) close to the center axis (1) is greater than the compression degree of the spring hydraulic shock absorber (4) away from the center axis (1). During the displacement of the central axis (1), the movable ring (3) rotates around its own axis, and the rotation direction of the movable ring (3) is opposite to the rotation direction of the spring hydraulic shock absorber (4) around the hinge point of the spring hydraulic shock absorber (4) on the fixed plate (2). During the process of the center axis (1) returning to the center, the rotation direction of the movable ring (3) is opposite to the rotation direction of the movable ring (3) during the process of the center axis (1) deflecting, and the rotation direction of the spring hydraulic shock absorber (4) is opposite to the rotation direction of the spring hydraulic shock absorber (4) during the process of the center axis (1) deflecting.

2. The vertical axis wind turbine shafting structure with a vibration damping device according to claim 1, characterized in that: At least three preload adjustment devices are provided between the movable ring (3) and the fixed disk (2), and are arranged around the movable ring (3). The preload adjustment device includes a coaxially arranged adjustment rod (5) and an elastic member (6). The preload adjustment device includes an adjustment fisheye bearing (7) provided at both ends of the integral body formed by the adjustment rod (5) and the elastic member (6).

3. The vertical axis wind turbine shafting structure with a shock absorbing device according to claim 2, characterized in that: The adjusting rod (5) comprises an inner rod (8) and an outer rod (9) which are threadedly connected to each other, and the elastic member (6) comprises a preload spring (11) and end covers (10) fixedly connected to both ends of the preload spring (11), wherein one end cover (10) is connected to the adjusting rod (5), and the other end cover (10) is connected to the adjusting fisheye bearing (7).

4. The vertical axis wind turbine shafting structure with a vibration damping device according to claim 3, characterized in that: The inner rod (8) is connected to the end cover (10), and the outer rod (9) is connected to the adjusting fisheye bearing (7). The adjusting fisheye bearing (7) connected to the outer rod (9) is provided with an embedding section (12) for embedding into the outer rod (9), and the outer wall of the embedding section (12) is provided with an end facing the inner rod (8) and an inner wall of the outer rod (9) is provided with a shaft shoulder (13).

5. The vertical axis wind turbine shafting structure with a vibration damping device according to claim 3, characterized in that: The spring hydraulic shock absorber (4) is provided with a shock-absorbing fisheye bearing (14) at both ends, a vertical nail (15) arranged parallel to the central axis (1) is fixedly connected to the fixed plate (2), a vertical rod (16) arranged parallel to the central axis (1) is provided inside the outer wall of the movable ring (3), the shock-absorbing fisheye bearing (14) at both ends of the spring hydraulic shock absorber (4) is respectively sleeved on the vertical nail (15) and the vertical rod (16), a bolt (17) arranged parallel to the central axis (1) is provided on the top surface of the movable ring (3), and the adjustment fisheye bearing (7) at both ends of the preload adjustment device is respectively sleeved on the vertical nail (15) and the bolt (17).

6. The vertical axis wind turbine shafting structure with a vibration damping device according to claim 5, characterized in that: The movable ring (3) comprises an upper ring (18) and a lower ring (19), a portion of the vertical rod (16) is located on the upper ring (18) and another portion of the vertical rod (16) is located on the lower ring (19), and the bolt (17) is threadedly connected to both the upper ring (18) and the lower ring (19).

7. The vertical axis wind turbine shafting structure with a vibration damping device according to claim 1, characterized in that: A self-aligning bearing (20) is provided between the inner wall of the movable ring (3) and the outer wall of the central shaft (1).

8. The vertical axis wind turbine shafting structure with a vibration damping device according to claim 1, characterized in that: It also includes a bearing plate (21) arranged parallel to the fixed plate (2), a constant velocity universal joint coupling (22) connected to the central shaft (1) is provided on the bottom surface of the bearing plate (21), a spherical roller thrust bearing (23) is provided on the top surface of the bearing plate (21), and a bearing cover (24) is provided on the top of the spherical roller thrust bearing (23).

9. The vertical axis wind turbine shafting structure with a vibration damping device according to claim 8, characterized in that: The constant velocity universal joint coupling (22) adopts a ball cage coupling, and the ball center of the constant velocity universal joint coupling (22) coincides with the curvature center of the outer ring raceway of the spherical roller thrust bearing (23).

10. The vertical axis wind turbine shafting structure with a shock absorbing device according to claim 8, characterized in that: It also includes a motor plate (25) arranged parallel to the fixed plate (2), the bottom end of the motor plate (25) is connected to a generator (26), and the generator (26) is connected to the constant velocity universal joint coupling (22).

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