A kind of floating wind turbine's inertia adjustable tuning inertial mass damper and offshore floating wind turbine system

Abstract

The application discloses a kind of inertia adjustable tuning inertial mass damper of floating fan, including connecting rod;Transmission system, with the connecting rod is connected, for converting horizontal direction movement into vertical direction movement;Elastic reset device;Inertial mass system, including transmission rod, rotating piece driven by the vertical movement of the transmission rod and the radially movable mass piece on the rotating piece;Damping system, for dissipating vibration energy;And shell.The beneficial effects of the application: by the cooperation of bowl-shaped slider concave surface and transmission rod bottom ball, the horizontal vibration of fan is converted into vertical movement, meet the narrow space limit of cabin;When rotating piece rotates, the radial displacement of mass piece continuously changes with rotational speed to change the moment of inertia, realize the wide frequency self-adaptive continuous frequency modulation under multiple working conditions;First, second elastic member and damping system and inertial mass system jointly constitute multiple energy dissipation paths, efficiently absorb vibration energy, significantly inhibit structural fatigue damage, prolong the service life of equipment.

Description

Technical Field

[0001] This invention relates to the field of offshore wind power generation technology, and in particular to an adjustable inertial mass damper for a floating wind turbine and an offshore floating wind turbine system. Background Technology

[0002] With the deepening implementation of the "dual carbon" goals, offshore wind power has become one of the core pillars of the global energy transition. my country's deep-sea areas are rich in wind energy resources, with more than 80% of offshore wind energy concentrated in areas with water depths exceeding 60 meters. Fixed wind turbines, due to soaring costs and high construction difficulties, can no longer meet the needs of deep-sea development. Floating wind turbines, with their advantages of strong adaptability to water depth and minimal environmental impact, have become the mainstream choice for deep-sea wind power development.

[0003] Since the beginning of the 21st century, offshore wind power technology has developed rapidly, but the power generation cost of floating wind turbines is still 2-3 times that of fossil fuel power generation. To reduce costs, floating wind turbines are evolving towards larger sizes; however, the significant increase in the size of components such as turbine blades and towers has led to increasingly prominent vibration problems. Vibration not only causes fluctuations in power generation and reduces power quality, but also exacerbates structural fatigue damage, shortens equipment lifespan, and increases operation and maintenance costs, seriously hindering the high-quality development of the offshore wind power industry. In addition, the operating environment in deep-sea areas is extremely harsh. Floating wind turbines must withstand the combined effects of strong winds, giant waves, and strong currents for extended periods, and frequently encounter extreme sea conditions such as typhoons, further exacerbating the risk of structural vibration and posing a severe challenge to the stability of the turbines.

[0004] To address the vibration issues arising from the increasing size of floating wind turbines, structural vibration control technology used in civil engineering has been applied to the field of floating wind turbines. Among these technologies, tuned mass dampers (TMDs), as classic passive control devices, have received considerable research attention due to their simple structure and lack of external energy input. However, traditional TMDs also suffer from the following technical drawbacks: they require large mass blocks to meet vibration reduction requirements, leading to an upward shift of the floating wind turbine's center of gravity and a decrease in structural stability, while also resulting in high installation difficulty and manufacturing costs; traditional TMDs require a long travel distance for operation, while the available space inside the wind turbine is limited, making it impossible to provide sufficient reciprocating movement margin, which can easily cause collisions between components during operation; and traditional TMDs have a narrow tuning bandwidth, making them unable to adapt to the vibration characteristics of floating wind turbines under different operating conditions, thus limiting their vibration reduction effect. Summary of the Invention

[0005] Therefore, the technical problem to be solved by the present invention is to provide a damper suitable for offshore floating wind turbines, which achieves lightweight device, high space adaptability, and wide-band adaptive frequency modulation capability.

[0006] The above-mentioned technical problems are solved by the following technical solution: The present invention proposes an adjustable inertial-mass tuned inertial-capacitance mass damper for a floating wind turbine, which includes a connecting rod for connecting with the floating wind turbine structure to transmit vibration displacement. A transmission system, connected to the input end of the connecting rod, is used to convert horizontal motion into vertical motion. The elastic reset device is used to provide elastic restoring force and together with the inertial capacitive system, forms a tuning system; An inertial-capacitance system includes a transmission rod, a rotating component driven by the vertical motion of the transmission rod, and a radially movable mass component disposed on the rotating component. The mass component moves radially under the action of centrifugal force when the rotating component rotates, so as to continuously change the moment of inertia of the rotating component. The output end of the transmission system cooperates with the transmission rod. Damping systems are used to dissipate vibrational energy; And a housing for accommodating the transmission system, the elastic reset device, the inertial capacitive system, and the damping system.

[0007] In a preferred embodiment of the adjustable inertial-mass tuned inertial-capacitance mass damper for a floating wind turbine according to the present invention: the transmission system includes a guide rail and a bowl-shaped slider disposed on the guide rail; the bowl-shaped slider can slide on the guide rail and contact the bottom of the transmission rod of the inertial-capacitance system through its concave surface to change the longitudinal height of the contact point, thereby converting the horizontal displacement of the connecting rod into the vertical displacement of the transmission rod and the inertial-capacitance system.

[0008] In a preferred embodiment of the adjustable inertial-mass mass damper for a floating wind turbine according to the present invention: the rotating component is an adaptive flywheel, and the transmission rod includes a rod body and ball bearings rotatably disposed at the bottom of the rod body. The outer circumferential surface of the rod body is provided with an external thread, and the central hole of the rotating component is provided with an internal thread that mates with the external thread, so that the vertical movement of the transmission rod drives the rotating component to rotate; the rotating component is provided with a radially extending limiting groove, and the mass component is slidably assembled in the limiting groove.

[0009] In a preferred embodiment of the adjustable inertial-mass tuned inertial-capacitance mass damper for a floating wind turbine according to the present invention: the mass component is connected to the rotating component via an elastic component, the extension direction of the elastic component is consistent with the extension direction of the limiting slide groove; when the rotating component rotates, the mass component overcomes the elastic force of the elastic component under the action of centrifugal force and moves radially outward along the limiting slide groove, and the radial displacement of the mass component changes continuously with the rotational speed of the rotating component.

[0010] In a preferred embodiment of the adjustable inertial-mass tuned inertial-capacitance mass damper for a floating wind turbine according to the present invention: the damping system is disposed in the lower cavity of the rotating member, and the damping system includes a damping cavity, a spring plate disposed in the damping cavity, and a damping fluid filled in the damping cavity; when the rotating member rotates, it drives the damping fluid to move to dissipate vibration energy.

[0011] In a preferred embodiment of the adjustable inertial-mass tuned inertial-capacitance mass damper for a floating wind turbine according to the present invention: the elastic reset device includes a first elastic element disposed between the connecting rod and the outer shell, and a second elastic element disposed between the guide rail of the transmission system and the outer shell; the first elastic element and the second elastic element deform with vertical movement to convert kinetic energy into elastic potential energy dissipation, thereby forming multiple energy dissipation paths together with the rotational kinetic energy conversion of the damping system and the inertial-capacitance system.

[0012] In a preferred embodiment of the adjustable inertial-mass mass damper for a floating wind turbine according to the present invention: a ball bearing is provided on the outside of the rotating component, and the ball bearing is axially limited by a retainer so that the rotating component can rotate at high speed relative to the outer shell.

[0013] In a preferred embodiment of the adjustable inertial-mass mass damper for a floating wind turbine according to the present invention: the bowl-shaped slider has a concave-facing curved surface shape. When the bowl-shaped slider slides horizontally along the guide rail, the contact point between the concave surface of the bowl-shaped slider and the ball at the bottom of the transmission rod moves along the curved surface, thereby nonlinearly converting the horizontal displacement of the bowl-shaped slider into the vertical displacement of the ball and the transmission rod.

[0014] In a preferred embodiment of the adjustable inertial-mass mass damper for a floating wind turbine according to the present invention: the transmission system further includes a bracket, rollers disposed on the guide rail, and a connecting ring connected to the cup-shaped slider; the guide rail is connected to the outer shell through an elastic element, and the rollers enable the guide rail to move vertically along the outer shell.

[0015] The present invention also provides an offshore floating wind turbine system, including a floating platform, a tower, a nacelle, and wind turbine blades, characterized in that an adjustable inertial mass damper for the floating wind turbine according to any one of claims 1 to 9 is installed in the nacelle or the tower.

[0016] The beneficial effects of this invention are as follows: by cooperating with the concave surface of the bowl-shaped slider and the ball bearing at the bottom of the transmission rod, the horizontal vibration of the fan is converted into vertical motion, which meets the space constraints of the narrow nacelle; when the rotating part rotates, the radial displacement of the mass part changes continuously with the rotational speed to change the moment of inertia, realizing wide-frequency adaptive continuous frequency modulation under multiple working conditions; the first and second elastic parts, together with the damping system and the inertial capacitance system, constitute multiple energy dissipation paths, which efficiently absorb vibration energy, significantly suppress structural fatigue damage, and extend the service life of the equipment. Attached Figure Description

[0018] To more clearly illustrate the technical solutions of the embodiments of the present invention, the accompanying drawings of the embodiments of the present invention will be briefly described below. Obviously, the drawings described below only relate to some embodiments of the present invention and are not intended to limit the present invention. Wherein: Figure 1 A cross-sectional view of the adjustable inertial-mass mass damper for a floating wind turbine is shown. Figure 2 A partially enlarged view of the transmission system is shown; Figure 3 A partially enlarged sectional view of the rotating component is shown; Figure 4 A cross-sectional view of the rotating component is shown; Figure 5 A partially enlarged cross-sectional view of the bowl-shaped slider is shown; Figure 6 A structural diagram of the transmission rod is shown; Figure 7 The graph shows the relationship between the radial displacement of the mass block and the rotational speed. Figure 8 The following are the platform roll time history diagrams with and without dampers installed under the corresponding free decay conditions; Figure 9 The following are the platform roll spectrum diagrams with and without dampers installed under the corresponding free decay conditions; Figure 10 The following diagrams show the time history response of the frame displacement before and after installation under the corresponding free decay conditions: Figure 11 The table shows the displacement spectrum of the tower before and after installation with and without dampers under the corresponding free decay conditions. Detailed Implementation

[0019] To enable those skilled in the art to better understand the present invention, the present invention will be further described in detail below with reference to specific embodiments and accompanying drawings.

[0020] The terminology used in this invention is that which is currently widely used in the art in consideration of the function of the invention; however, these terms may vary according to the intent of those skilled in the art, precedent, or new technology in the art. Furthermore, specific terms may be chosen by the applicant, and in such cases, their detailed meanings will be described in the detailed description of the invention. Therefore, the terms used in this specification should not be construed as simple names, but rather based on their meanings and the overall description of the invention.

[0021] Reference Figure 1 , Figure 4 During the operation of a wind turbine, the wind turbine tower or nacelle structure will generate multi-directional vibrations. This embodiment provides an adjustable inertial-mass tuned inertial-capacitance mass damper for a floating wind turbine, including a connecting rod 1, which is used to connect with the floating wind turbine structure to transmit vibration displacement and serves as the power input end of the entire damper, directly capturing and transmitting the vibration displacement and load of the wind turbine structure. Due to the cramped interior space of the floating wind turbine nacelle and the extremely small horizontal movement margin, a transmission system 2 is installed, which is connected to the input end of the connecting rod 1. Its core function is to convert the horizontal motion transmitted from the connecting rod 1 into vertical motion, thereby converting the horizontal vibration into vertical displacement output. This effectively avoids the damper occupying too much space in the horizontal direction and prevents collisions between components. The elastic reset device 3 is used to provide elastic restoring force and together with the inertial capacitive system 4, it forms a tuning system. During vibration, it stores and releases energy through elastic deformation. In conjunction with the rotational kinetic energy conversion of the inertial capacitive system 4, it achieves the synergistic effect of tuning and vibration reduction. When the vibration weakens, the elastic reset device 3 pushes each moving part to reset, preparing for the next vibration response. The inertial-capacitance system 4 includes a transmission rod 41, a rotating component 42, and a mass component 422. The transmission rod 41 is connected to the output end of the transmission system 2 and receives the vertical motion transmitted by the transmission system 2. When the transmission rod 41 moves vertically, it drives the rotating component 42 to rotate, thereby converting translational energy into rotational energy. The output end of the transmission system 2 cooperates with the transmission rod 41 to achieve mass efficiency enhancement, which greatly improves the equivalent mass of the damper. A radially movable mass component 422 is provided on the rotating component 42. When the rotating component 42 rotates at high speed, the mass component 422 overcomes its own constraints and moves radially outward under the action of centrifugal force. Its radial displacement changes continuously with the rotational speed of the rotating component 42. This mechanism allows the rotational inertia of the rotating component 42 to change continuously, thereby realizing the continuous adjustability of the system inertial mass. This enables the damper to adaptively match the vibration frequency of the fan under different operating conditions and broadens the tuning bandwidth. The damping system 5 is used to dissipate vibration energy. During the operation of the inertial-capacitive system 4 driven by the vibration of the wind turbine, the damping system 5 converts the transmitted mechanical energy into heat energy or other forms of dissipated energy through a specific damping medium or structural friction, thereby further suppressing structural vibration. And a housing 6 for accommodating the transmission system 2, the elastic reset device 3, the inertial capacitance system 4, and the damping system 5, which facilitates overall hoisting and maintenance inside the floating wind turbine, while protecting the internal precision structure from corrosion by the harsh external marine environment.

[0022] Reference Figure 1 , Figure 2 As an optional embodiment, the transmission system 2 includes a guide rail 21 and a bowl-shaped slider 22 disposed on the guide rail 21. The bowl-shaped slider 22 can slide on the guide rail 21, which provides basic support and horizontal movement guidance for the bowl-shaped slider 22. The bowl-shaped slider 22 is movably mounted on the guide rail 21 and can slide smoothly horizontally on the guide rail 21. Its concave surface contacts the bottom of the transmission rod 41 of the inertial-capacitance system 4 to change the longitudinal height of the contact point, thereby converting the horizontal displacement of the connecting rod 1 into the vertical displacement of the transmission rod 41 and the inertial-capacitance system 4. The bowl-shaped slider 22 has a curved surface with the concave surface facing upward. This concave surface directly contacts the bottom of the transmission rod 41 of the inertial-capacitance system 4, forming a dynamic fit structure. During vibration, the connecting rod 1 directly transmits the horizontal vibration displacement and load to the transmission system 2, driving the bowl-shaped slider 22 to slide horizontally relative to the guide rail 21. During the horizontal sliding of the bowl-shaped slider 22 along the guide rail 21, since the upper surface of the bowl-shaped slider 22 is curved (concave), the contact point between the bottom of the transmission rod 41 and the concave surface will change position as the slider moves horizontally. The contact point moves from one height to another on the curved surface, thereby directly changing the longitudinal height (i.e., the vertical position) of the contact point. This structure solves the drawback of traditional dampers requiring a long horizontal movement stroke. It utilizes the curved surface characteristics to complete the change of motion direction in the compact cabin space, laying the foundation for the rotational work of the subsequent inertial capacitive system.

[0023] Reference Figure 1 , Figure 3 , Figure 7 As an optional embodiment, the inertial capacity system 4 is the core component for achieving mass efficiency and continuous frequency modulation. It mainly includes a transmission rod 41, an adaptive flywheel that serves as a rotating component 42 in this embodiment, and a mass component 422. The transmission rod 41 includes a rod body 411 and a ball bearing 412 rotatably disposed at the bottom of the rod body 411. During operation, the ball bearing 412 can effectively reduce the friction at the bottom, so that the transmission rod 41 can smoothly undergo vertical displacement when subjected to vertical force. The outer circumferential surface of the rod body 411 is provided with an external thread, and the central hole of the rotating component 42 is provided with an internal thread that mates with the external thread, so that the vertical movement of the transmission rod 41 drives the rotating component 42 to rotate. The rotating component 42 is provided with a radially extending limiting groove 421, and the mass component 422 is slidably assembled in the limiting groove 421. Through the helical transmission of the internal and external threads, when the transmission rod 41 reciprocates in the vertical direction, it can convert linear motion into rotational motion, thereby directly driving the rotating component 42 to rotate. This threaded transmission structure converts translational energy into rotational energy, and achieves mass efficiency through the high-speed rotation of the rotating component 42, significantly increasing the equivalent physical mass of the system (i.e., exhibiting inertial mass effect) with a small physical mass. The rotating component 42 is provided with a radially extending limiting groove 421, and the mass component 422 is slidably assembled in the limiting groove 421. When the rotating component 42 rotates at high speed under the drive of the transmission rod 41, the mass component 422 rotates along with it. When the mass component 422 rotates, it is subjected to centrifugal force. The magnitude of the centrifugal force is proportional to the square of the rotational speed. Under the action of centrifugal force, the mass component 422 can slide radially along the limiting groove 421. The limiting groove 421 provides precise radial guidance support for the mass component 422 and reduces sliding friction.

[0024] The centrifugal force and radial displacement of the mass component 422 satisfy a specific mechanical equilibrium relationship, which makes the radial displacement of the mass component 422 continuously change with the rotational speed of the rotating component 42. As the radial position of the mass component 422 changes, the overall radius of rotation of the rotating component 42 changes, thereby allowing its moment of inertia to be continuously adjusted. This rotational speed-based adaptive moment of inertia adjustment mechanism enables the inertial mass parameters of the damper system to be continuously adjustable, thereby realizing adaptive frequency modulation of the system under multiple operating conditions and effectively broadening the tuning bandwidth.

[0025] Combined with appendix Figure 7 Set the original length of the spring to be After elongation, it becomes quality block quality Spring stiffness When in equilibrium, the centrifugal force equals the tension generated by the spring's extension, therefore: After sorting, we can obtain: The correlation diagram is based on the assumption that the original length of the spring is 0.1m and the maximum displacement is 0.3m.

[0026] Reference Figure 1 , Figure 3 , Figure 7As an optional embodiment, the mass component 422 is connected to the rotating component 42 via an elastic component 423. To ensure the accuracy of force transmission and the smoothness of movement, the extension direction of the elastic component 423 is consistent with the extension direction of the limiting slide groove 421, so that the mass component 422 can smoothly slide in a straight line along the trajectory of the limiting slide groove 421 when subjected to force, avoiding deviation or jamming. When the rotating component 42 rotates, the mass component 422 rotates together and generates centrifugal force. Under the action of this centrifugal force, the mass component 422 overcomes the elastic tension of the elastic component 423 and moves radially outward along the limiting slide groove 421 away from the rotation center. The radial displacement of the mass component 422 changes continuously with the rotation speed of the rotating component 42.

[0027] Regarding the mechanical mechanism and kinematic characteristics of the continuous change of radial displacement of a mass component with rotational speed, combined with the appendix... Figure 7 Set the original length of the spring to be After elongation, it becomes quality block quality Spring stiffness At equilibrium, the centrifugal force equals the tension generated by the extension of the spring. Therefore, based on the principle that the centrifugal force equals the tension generated by the extension of the elastic element at equilibrium, we can derive the mechanical equilibrium formula. .

[0028] The data and charts together show that the radial displacement of mass component 422 It will rotate at a speed of 42 degrees. The rotational inertia of the system changes continuously and smoothly. When the speed of the flywheel increases, the centrifugal force increases accordingly. The mass component 422 overcomes the tension of the elastic component and moves radially outward along the limiting groove 421, thereby increasing the rotational radius. When the speed decreases, the elastic component contracts and pulls the mass component 422 back, thereby decreasing the rotational radius. This stepless radial displacement change allows the rotational inertia of the system to be continuously and adaptively adjusted according to the speed.

[0029] Reference Figure 4As an optional embodiment, the damping system 5 is disposed in the lower cavity of the rotating member 42. The damping system 5 includes a damping cavity 51, a spring plate 52 disposed in the damping cavity 51, and a damping fluid filled in the damping cavity 51. When the rotating member 42 rotates, it drives the damping fluid to move to dissipate vibration energy. In the actual operation of the damper, when the rotating member 42 rotates at high speed, it will directly drive the damping fluid in the damping cavity 51 in its lower cavity to rotate at high speed. During this process, the damping fluid generates relative movement and friction between the gaps inside the damping cavity 51. Through the viscous friction inside the fluid and the friction between the fluid and the cavity wall and the spring plate 52, the mechanical kinetic energy is converted into heat energy and dissipated. At the same time, the spring plate 52 set in the damping cavity 51 undergoes elastic deformation and micro-vibration under the impact and disturbance of the high-speed flow of the damping fluid. This not only breaks the streamline of the damping fluid and increases the turbulence and internal shear friction of the fluid movement, but its own elastic hysteresis effect also further consumes the vibration energy. Through the synergistic effect of the energy consumption of fluid friction of the damping fluid and the energy consumption of structural disturbance of the spring plate, the efficient absorption and dissipation of the vibration energy of the fan is achieved.

[0030] Reference Figure 1 As an optional embodiment, the elastic reset device 3 includes a first elastic element 31 disposed between the connecting rod 1 and the housing 6, and a second elastic element 32 disposed between the guide rail 21 of the transmission system 2 and the housing 6. The first elastic element 31 and the second elastic element 32 deform with vertical movement to convert kinetic energy into elastic potential energy for dissipation, thereby forming multiple energy dissipation paths together with the rotational kinetic energy conversion of the damping system 5 and the inertial-capacitive system 4. The connecting rod 1 captures and transmits the vibration displacement of the structure. During the process of the transmission system 2 converting horizontal vibration into vertical movement, the first elastic element 31 deforms with the vertical movement of the connecting rod 1 and related components. During the elastic deformation, the second elastic element 32 undergoes elastic deformation along the vertical movement of the guide rail 21 of the transmission system 2 along the outer shell. During this deformation process, the first elastic element 31 and the second elastic element 32 convert the mechanical kinetic energy transmitted from the fan into elastic potential energy for temporary storage, and dissipate it through internal damping and system coupling during the reset process. This elastic potential energy dissipation mechanism based on dual elastic elements, together with the fluid friction energy dissipation of the damping system 5 and the energy conversion mechanism of the inertial capacitive system 4 that converts translational motion into high-speed rotational kinetic energy, constitute multiple energy dissipation paths, ensuring efficient energy dissipation channels in different vibration stages and frequency bands.

[0031] The efficient vibration reduction effect of the aforementioned multiple energy dissipation paths was verified by simulation data. The verification charts, using platform roll and tower forward / backward displacement as examples, provide simulation data for the free attenuation conditions at this location with and without dampers. It is worth noting that this set of amplitude-frequency results only conducted vibration reduction analysis at a single fixed frequency, and the adaptive frequency tuning characteristics of the damper have not yet been utilized. Figure 8 and Figure 10 It can be seen that after installing the damper proposed in this paper, both the platform's yaw displacement and the tower's forward and backward displacement can be rapidly attenuated in a short period of time, with the root mean square values ​​of displacement decreasing by 12.5% ​​and 18.3%, respectively; combined with Figure 9 and Figure 11 The frequency domain results show that the damper, after single-frequency tuning, can efficiently dissipate the vibration energy within the natural frequency bands of platform roll (0.04Hz band) and tower forward / backward displacement (0.4Hz band). The peak amplitudes corresponding to the two main frequencies are reduced by 38.6% and 36.1%, respectively. Moreover, the increased width of the main peak in the platform roll spectrum after installing the damper of this patent reflects a certain broadband characteristic, which fully verifies the damper's ability to dissipate vibration energy at the structure's natural frequency. This indicates that after applying the damper of this invention, which includes the above-mentioned multiple energy dissipation paths, the vibration time history amplitudes of platform roll and tower forward / backward displacement are rapidly and significantly attenuated, and the resonance peaks in the frequency domain are greatly weakened. This directly proves the effective control capability of the multiple energy dissipation path design for the complex vibrations of floating wind turbines.

[0032] Reference Figure 4 As an optional embodiment, the rotating member 42 is provided with a ball bearing 43 on its exterior, and the ball bearing 43 is axially limited by a retainer 44 so that the rotating member 42 can rotate at high speed relative to the housing 6.

[0033] In the operation of the damper of the present invention, in order to effectively convert the translational energy of the fan vibration into rotational energy to achieve significant mass enhancement (i.e., inertial mass effect), the vertical movement of the transmission rod 41 drives the rotating component 42 to generate extremely high-speed rotational motion through the threaded transmission pair. Under this high-speed rotational condition, the setting of the ball bearing 43 greatly reduces the frictional resistance between the rotating component 42 and the outer shell 6, reducing unnecessary energy loss in the support link; at the same time, the axial limiting function of the retainer 44 ensures the uniform distribution of the rolling elements inside the ball bearing 43, prevents axial movement and structural loosening under high-speed operation, and ensures the operational stability and safety of the rotating component 42 under extreme speeds.

[0034] The aforementioned characteristics of high-speed rotation and the necessity of this support design are discussed in the appendix. Figure 7 This indirectly confirms that the rotating component 42 operates at a high speed during system operation. In this state, the continuous operation at high speed places stringent requirements on the friction performance and limiting ability of the support structure. It is precisely because of the cooperative design of the ball bearing 43 and the retainer 44 that the rotating part 42 can operate stably at high speed, thereby ensuring the smooth realization of the continuous frequency modulation mechanism based on centrifugal force and the overall vibration reduction effect.

[0035] Reference Figure 2 , Figure 5As an optional embodiment, the bowl-shaped slider 22 has a concave-facing curved surface. When the bowl-shaped slider 22 slides horizontally along the guide rail 21, the contact point between the concave surface of the bowl-shaped slider 22 and the ball 412 at the bottom of the transmission rod 41 moves along the curved surface, thereby nonlinearly converting the horizontal displacement of the bowl-shaped slider 22 into the vertical displacement of the ball 412 and the transmission rod 41. During this sliding process, the concave surface of the bowl-shaped slider 22 and the ball 412 at the bottom of the transmission rod 41 always remain in contact. Since the concave surface is a curved structure, when the bowl-shaped slider 22 moves horizontally, the contact point of the ball 412 on the concave surface will change position accordingly and move along the curved surface. According to the geometric characteristics of the curved surface, as the contact point moves horizontally, its longitudinal height also changes continuously. Through this curved surface contact mechanism, the horizontal displacement of the bowl-shaped slider 22 is nonlinearly converted into the vertical displacement of the ball 412 and the transmission rod 41. This design resolves the drawback of traditional dampers requiring a long horizontal motion stroke. It utilizes the curved surface characteristics to complete the conversion of motion direction within the compact cabin space, avoiding the damper occupying too much space in the horizontal direction and the risk of collision with the internal structure. At the same time, it provides a stable basic power input for the subsequent inertial capacitive system to convert vertical translational motion into rotational motion.

[0036] Reference Figure 2 As an optional embodiment, the transmission system 2 further includes a bracket 24, rollers 25 mounted on the guide rail 21, and a connecting ring 26 connected to the bowl-shaped slider 22. In terms of structural connection and fit, the guide rail 21 is connected to the outer shell 6 via a second elastic element 32. The rollers 25 are mounted on the guide rail 21, allowing the guide rail 21 to move smoothly up and down along the outer shell 6 in the vertical direction, thus providing low-friction motion guidance for the vertical displacement of the guide rail 21. The bracket 24 provides a stable support foundation for the transmission system 2, and the connecting ring 26 ensures stable connection and power transmission of the bowl-shaped slider 22 during movement. The guide rail 21 is connected to the outer shell 6 via the second elastic element 32, and the rollers... 25 enables the guide rail 21 to move vertically along the outer shell 6. When the floating fan vibrates, the connecting rod 1 transmits the horizontal vibration displacement and load to the transmission system, driving the bowl-shaped slider 22 to slide horizontally on the guide rail 21. During this sliding process, due to the contact and cooperation between the concave curved surface of the bowl-shaped slider 22 and the bottom ball 412 of the transmission rod 41, the horizontal movement of the bowl-shaped slider 22 will drive the guide rail 21 to overcome the constraint of the above-mentioned elastic element and generate vertical displacement along the outer shell 6 by relying on the roller 25. This structural linkage mechanism successfully changes the longitudinal height of the bottom of the ball 412, thereby smoothly converting the horizontal motion transmitted by the fan into vertical motion, laying the foundation for the subsequent rotation work of the inertial capacitive system.

[0037] As an alternative embodiment, an offshore floating wind turbine system includes a floating platform, a tower, a nacelle, and wind turbine blades, wherein an adjustable inertial mass damper for the floating wind turbine is installed in the nacelle or tower.

[0038] Finally, it should be noted that the methods and devices described in detail above are merely embodiments, and those skilled in the art can modify these embodiments in different ways as long as they do not depart from the scope of the present invention.

Claims

1. A tuned inertial-capacitive mass damper for a floating wind turbine, characterized in that: include, Connecting rod (1) is used to connect with the floating wind turbine structure to transmit vibration displacement; The transmission system (2) is connected to the input end of the connecting rod (1) and is used to convert horizontal motion into vertical motion; The elastic reset device (3) is used to provide elastic restoring force and together with the inertial capacitive system (4) forms a tuning system; The inertial system (4) includes a transmission rod (41), a rotating component (42) driven by the vertical motion of the transmission rod (41), and a radially movable mass component (422) disposed on the rotating component (42). The mass component (422) moves radially under the action of centrifugal force when the rotating component (42) rotates, so as to continuously change the moment of inertia of the rotating component (42). The output end of the transmission system (2) is engaged with the transmission rod (41). Damping system (5) is used to dissipate vibrational energy; And a housing (6) for accommodating the transmission system (2), the elastic reset device (3), the inertial capacitive system (4) and the damping system (5).

2. The adjustable inertial-mass mass damper for a floating wind turbine according to claim 1, characterized in that: The transmission system (2) includes a guide rail (21) and a bowl-shaped slider (22) disposed on the guide rail (21); the bowl-shaped slider (22) can slide on the guide rail (21) and contact the bottom of the transmission rod (41) of the inertial-capacitance system (4) through its concave surface to change the longitudinal height of the contact point, thereby converting the horizontal displacement of the connecting rod (1) into the vertical displacement of the transmission rod (41) and the inertial-capacitance system (4).

3. The adjustable inertial-mass mass damper for a floating wind turbine according to claim 1, characterized in that: The rotating component (42) is an adaptive flywheel, wherein the transmission rod (41) includes a rod body (411) and a ball bearing (412) rotatably disposed at the bottom of the rod body (411). The outer circumferential surface of the rod body (411) is provided with an external thread, and the central hole of the rotating part (42) is provided with an internal thread that matches the external thread, so that the vertical movement of the transmission rod (41) drives the rotating part (42) to rotate; a radially extending limiting groove (421) is provided on the rotating part (42), and the mass part (422) is slidably assembled in the limiting groove (421).

4. The adjustable inertial-mass mass damper for a floating wind turbine according to claim 3, characterized in that: The mass component (422) is connected to the rotating component (42) through an elastic component (423). The extension and retraction direction of the elastic component (423) is consistent with the extension direction of the limiting slide (421). When the rotating component (42) rotates, the mass component (422) overcomes the elastic force of the elastic component (423) under the action of centrifugal force and moves radially outward along the limiting slide (421). The radial displacement of the mass component (422) changes continuously with the rotation speed of the rotating component (42).

5. The adjustable inertial-mass mass damper for a floating wind turbine according to claim 1, characterized in that: The damping system (5) is disposed in the lower cavity of the rotating member (42). The damping system (5) includes a damping cavity (51), a spring plate (52) disposed in the damping cavity (51), and a damping fluid filled in the damping cavity (51). When the rotating component (42) rotates, it drives the damping fluid to move in order to dissipate vibration energy.

6. The adjustable inertial-mass mass damper for a floating wind turbine according to claim 1, characterized in that: The elastic reset device (3) includes a first elastic element (31) disposed between the connecting rod (1) and the outer shell (6), and a second elastic element (32) disposed between the guide rail (21) of the transmission system (2) and the outer shell (6); the first elastic element (31) and the second elastic element (32) deform with vertical movement to convert kinetic energy into elastic potential energy dissipation, thereby forming multiple energy dissipation paths together with the rotational kinetic energy conversion of the damping system (5) and the inertial capacitive system (4).

7. The adjustable inertial-mass mass damper for a floating wind turbine according to claim 3, characterized in that: The rotating component (42) is provided with a ball bearing (43) on its exterior. The ball bearing (43) is axially limited by a retainer (44) so ​​that the rotating component (42) can rotate at high speed relative to the housing (6).

8. The adjustable inertial-mass mass damper for a floating wind turbine according to claim 2, characterized in that: The bowl-shaped slider (22) has a concave surface. When the bowl-shaped slider (22) slides horizontally along the guide rail (21), the contact point between the concave surface of the bowl-shaped slider (22) and the ball (412) at the bottom of the transmission rod (41) moves along the curved surface, thereby nonlinearly converting the horizontal displacement of the bowl-shaped slider (22) into the vertical displacement of the ball (412) and the transmission rod (41).

9. The adjustable inertial-mass mass damper for a floating wind turbine according to claim 2, characterized in that: The transmission system (2) also includes a bracket (24), a roller (25) disposed on the guide rail (21), and a connecting ring (26) connected to the bowl-shaped slider (22); the guide rail (21) is connected to the outer shell (6) through an elastic element, and the roller (25) enables the guide rail (21) to move vertically along the outer shell (6).

10. An offshore floating wind turbine system, comprising a floating platform, a tower, a nacelle, and wind turbine blades, characterized in that, The nacelle or tower is equipped with an adjustable inertial mass damper for the floating wind turbine according to any one of claims 1 to 9.

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