A vibration reduction and wave energy recovery energy storage system for a floating wind turbine platform

Abstract

The application provides a damping and wave energy recovery energy storage system for a floating wind turbine platform, and belongs to the technical field of marine power generation. The system comprises a floating wind turbine platform and a wave energy conversion device arranged in the floating wind turbine platform. The wave energy conversion device comprises a shell, a tuned mass damper, a transmission mechanism and a power generation and energy storage mechanism arranged in the shell. The tuned mass damper comprises a mass, a spring and a guide rail. The mass is slidably arranged on the guide rail. The mass is connected with the two side plates of the shell through the spring at both ends. The power generation and energy storage mechanism comprises two permanent magnet synchronous motors arranged at both ends of the mass. The mass is drivingly connected with the rotating shafts of the permanent magnet synchronous motors through the transmission mechanism. The mass is configured to reciprocate along the guide rail to drive the rotating shafts of the two permanent magnet synchronous motors to rotate in one direction to generate power. The system provided by the application can solve the problem that the prior art is difficult to consider multi-directional damping and stable power generation and energy storage.

Description

Technical Field

[0001] This invention relates to the field of marine power generation technology, and in particular to a vibration reduction and wave energy recovery storage system for floating wind turbine platforms. Background Technology

[0002] With the rapid development of the deep-sea wind power industry, floating wind turbine platforms, due to their lack of water depth limitations and ability to be deployed in resource-rich deep-sea areas, have become an important direction for offshore wind power development. However, during long-term operation in deep-sea areas, floating wind turbine platforms are continuously subjected to the combined effects of wind, waves, and currents, commonly exhibiting multi-directional oscillations such as longitudinal and transverse oscillations, which seriously threaten structural safety and wind turbine operational stability. Therefore, vibration control technology needs to be introduced. The tuned mass damper (TMD), a classic passive vibration reduction device, consists of a mass, springs, and damping elements. It absorbs and dissipates the kinetic energy of the main structure through the principle of resonance. To improve the vibration reduction effect without significantly increasing the weight of the mass, an inertial capacitive element can be introduced into the TMD to connect the mass to the main structure, forming a tuned mass inertial capacitive damper (TMDI). The output force of the inertial capacitive element is proportional to the relative acceleration at its two ends and the inertial capacitive coefficient. Through proper design, the inertial capacitive coefficient can be made much larger than the physical mass of the element itself, thereby achieving miniaturization and lightweighting of the vibration reduction device, suitable for space-constrained engineering scenarios such as floating wind turbine platforms.

[0003] In existing TMDI devices, common inertial capacitive elements are implemented using ball screw, rack-and-pinion, and hydraulic mechanisms. Their common characteristic is converting the translational displacement of the mass into the rotational motion of the flywheel, utilizing the flywheel's moment of inertia to effectively amplify the inertial capacitive coefficient. During the operation of a traditional TMDI device, the mass reciprocates along the guide structure under the oscillating excitation of the main structure. The flywheel rotates via the transmission mechanism to provide inertial capacitive force, while the vibrational energy is ultimately dissipated as heat by the damping element. Although this design achieves good vibration reduction performance, the damping element only serves to dissipate energy; a large amount of vibrational energy absorbed by the mass is not recovered and utilized. Furthermore, because the mass reciprocates, the flywheel alternates between forward and reverse rotation, resulting in frequent changes in speed and direction, making it impossible to maintain a stable unidirectional rotational state.

[0004] Because existing TMDI devices lack a mechanism to convert vibration energy into usable electrical energy, the vibration energy absorbed by the mass body is dissipated as heat for a long time, resulting in energy waste. If a generator is directly installed on an existing TMDI, the reciprocating motion of the mass body causes the flywheel to rotate alternately in both directions, leading to erratic generator speeds, even reverse rotation, drastic fluctuations in output voltage and current, unstable generator operation, and low energy recovery efficiency. Furthermore, existing systems lack a control strategy that adaptively adjusts electromagnetic damping based on real-time sea conditions, platform vibration status, and battery charge, making it difficult to achieve optimal synergy between vibration reduction and energy recovery under different operating conditions. Simultaneously, if the electromagnetic damping force generated by the generator does not match the optimal damping parameters required by the TMDI system, it will lead to decreased vibration reduction performance or reduced power generation efficiency, making it difficult to achieve synergistic optimization of vibration reduction and energy recovery. In addition, floating wind turbine platforms are deployed in remote areas of deep sea. The power supply for the wind turbine's own monitoring and auxiliary control equipment depends on external lines, which is costly and inconvenient. Although the wave energy contained in the platform's oscillations has a small power and is difficult to utilize by grid connection, if it can be converted and stored on-site, it can meet the above-mentioned low-power electricity demand. Existing technology has not yet provided such an integrated solution that can take into account multi-directional vibration reduction and stable power generation and energy storage in a compact space. Summary of the Invention

[0005] This invention provides a vibration reduction and wave energy recovery storage system for floating wind turbine platforms, which solves the problem in existing technologies of simultaneously achieving multi-directional vibration reduction and stable power generation and energy storage. The technical solution is as follows:

[0006] A vibration reduction and wave energy recovery storage system for a floating wind turbine platform includes: a floating wind turbine platform and a wave energy conversion device;

[0007] The wave energy conversion device is installed inside the floating wind turbine platform. The wave energy conversion device includes a shell and a tuned mass damper, a transmission mechanism and a power generation and storage mechanism installed inside the shell. The shell has a square base plate installed on the floating wind turbine platform and two side plates arranged parallel to each other along the length of the base plate. The side plates are vertically installed on the base plate.

[0008] The tuned mass damper includes a mass, a spring, and a guide rail. The guide rail is disposed on the base plate along the length of the base plate. The mass is slidably disposed on the guide rail. The spring is connected to both ends of the mass and the two side plates.

[0009] The power generation and energy storage mechanism includes two permanent magnet synchronous motors respectively disposed at both ends of the mass body. The mass body is connected to the shaft of the permanent magnet synchronous motor through the transmission mechanism. The mass body is configured to reciprocate along the guide rail to drive the shaft of the two permanent magnet synchronous motors to rotate unidirectionally to generate electricity.

[0010] Optionally, the transmission mechanism includes a rack, a gear, a flywheel, and a ratchet assembly. Two transmission mechanisms are symmetrically arranged on both sides of the mass body along the length direction of the base plate. The rack is arranged along the length direction of the base plate and one end is fixedly connected to the mass body. The gear meshes with the rack. The ratchet assembly includes a ratchet and a pawl. The pawl includes a pawl, a pin, and a torsion spring. The pawl is rotatably mounted on the end face of the gear through the pin. The torsion spring is sleeved on the pin and one end is fixedly connected to the pawl, and the other end is fixedly connected to the gear. The ratchet and the flywheel are coaxially rotatably connected, and the ratchet and the pawl are engaged.

[0011] Optionally, the gear is provided with a plurality of ratchet portions, which are evenly spaced along the circumference of the gear.

[0012] Optionally, the power generation and energy storage mechanism further includes a rectifier bridge, a DC-DC converter, and a battery. The shaft of the permanent magnet synchronous motor is rotatably connected to the flywheel on the same axis. The output end of the permanent magnet synchronous motor is electrically connected to the battery in sequence through the rectifier bridge and the DC-DC converter.

[0013] Optionally, the power generation and energy storage mechanism further includes an energy-consuming resistor disposed between the DC-DC converter and the battery.

[0014] Optionally, the floating wind turbine platform is further equipped with a multi-mode switching control system. The multi-mode switching control system includes a status monitoring module for real-time monitoring of the vibration amplitude of the floating wind turbine platform; a sea state monitoring module for real-time monitoring of the effective wave height of the sea area where the floating wind turbine platform is located; a battery management module for real-time monitoring of the state of charge of the battery; and a judgment and execution module, which is communicatively connected to the status monitoring module, the sea state monitoring module, the battery management module, and the DC-DC converter, respectively, for adjusting the duty cycle of the DC-DC converter to adjust the magnitude of the electromagnetic damping torque of the permanent magnet synchronous motor.

[0015] Optionally, the guide rail is a T-shaped rail, and the bottom of the mass body has a groove along the length direction that matches the guide rail. The mass body is slidably mounted on the guide rail through the groove.

[0016] Optionally, the slide groove is provided with multiple rows of balls, which are arranged along the length of the slide groove, and the slide groove is slidably connected to the guide rail through the balls.

[0017] Optionally, multiple wave energy conversion devices are provided, and the multiple wave energy conversion devices are arranged in a ring within the floating wind turbine platform.

[0018] Optionally, a wind turbine is installed on the floating wind turbine platform, and the power generation and energy storage mechanism is electrically connected to the energy-consuming equipment inside the wind turbine.

[0019] The beneficial effects of the technical solutions provided in the embodiments of the present invention include at least the following:

[0020] This invention provides a vibration reduction and wave energy recovery storage system for floating wind turbine platforms. By placing the wave energy conversion device inside the floating wind turbine platform, the entire system is integrated into the platform's internal space, eliminating the need for additional sea surface area. This compact structure is suitable for engineering scenarios where space is limited for floating wind turbine platforms. A tuned mass damper is installed within the shell, utilizing the reciprocating motion of the mass on the guide rail and the elastic restoring force provided by the spring to form a mass-spring vibration system. Based on the resonance principle, the oscillation energy of the floating wind turbine platform under wave action is transferred to the mass, effectively suppressing platform oscillation and ensuring structural safety and wind turbine operational stability. Two permanent magnet synchronous motors are respectively installed at both ends of the mass, and the mass is connected to the shaft of the permanent magnet synchronous motors through a transmission mechanism. This converts the vibration energy absorbed by the tuned mass damper into usable electrical energy, avoiding the vibration energy loss associated with traditional damping devices. The problem of dissipating energy solely as heat has been addressed, thus improving the utilization rate of renewable energy. By configuring the mass body to reciprocate along the guide rail to drive the shafts of two permanent magnet synchronous motors to rotate unidirectionally for power generation, the problems of unstable power generation caused by the reciprocating motion of the mass body, such as sudden changes in generator speed or even reversal, drastic fluctuations in output voltage and current, have been solved in the prior art. This ensures that the permanent magnet synchronous motors can continuously generate electricity in a stable unidirectional rotation state, significantly improving power generation stability and energy recovery efficiency. Furthermore, by setting up a multi-mode switching control system to monitor the platform vibration amplitude, sea state wave height, and battery state of charge in real time, and adjust the electromagnetic damping torque of the permanent magnet synchronous motors accordingly, this system can automatically switch between vibration reduction priority, power generation priority, or balanced working modes under different sea conditions and battery charge levels. This achieves adaptive and synergistic optimization of vibration reduction performance and energy recovery efficiency, significantly improving the overall performance of the system in complex marine environments. Under extreme sea conditions, the system automatically switches to a vibration reduction priority mode, providing a larger electromagnetic damping torque to prioritize suppressing the oscillations of the floating wind turbine platform, ensuring structural safety and turbine operational stability. In low sea states and when battery power is insufficient, the system switches to a power generation priority mode, providing a smaller electromagnetic damping torque to lower the power generation start-up threshold and improve energy capture efficiency in low sea states. This effectively solves the problem of simultaneously achieving multi-directional vibration reduction and stable power generation and energy storage in existing technologies. Attached Figure Description

[0021] To more clearly illustrate the technical solutions in the embodiments of the present invention, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0022] Figure 1 This is a schematic diagram of the overall structure of the system provided in this embodiment of the invention;

[0023] Figure 2 This is a schematic diagram of the wave energy conversion device provided in an embodiment of the present invention;

[0024] Figure 3 This is a schematic diagram of the fit between the mass body and the guide rail provided in an embodiment of the present invention;

[0025] Figure 4 This is a front view schematic diagram of the transmission mechanism and the tuned mass damper provided in an embodiment of the present invention;

[0026] Figure 5 This is a top view schematic diagram of the transmission mechanism, tuned mass damper, and power generation and storage mechanism provided in an embodiment of the present invention;

[0027] Figure 6 This is an exploded view of the transmission mechanism provided in an embodiment of the present invention;

[0028] Figure 7 This is a schematic diagram of the power generation and energy storage mechanism provided in an embodiment of the present invention;

[0029] Figure 8 This is a schematic diagram of signal transmission provided in an embodiment of the present invention.

[0030] In the diagram: 1-Floating wind turbine platform; 2-Wave energy conversion device; 21-Shell; 211-Base plate; 212-Side plate; 213-Fixed bracket; 22-Tuned mass damper; 221-Mass body; 222-Spring; 223-Guide rail; 224-Slide groove; 225-Ball bearing; 23-Transmission mechanism; 231-Rack; 232-Gear; 233-Flywheel; 234-Gear shaft; 235-Common shaft; 24-Power generation and energy storage mechanism; 241-Permanent magnet synchronous motor; 242-Rectifier bridge; 243-Battery; 244-DC-DC converter; 245-Energy dissipating resistor; 246-Coupling; 3-Ratchet assembly; 31-Ratchet; 32-Pawl; 321-Pawl; 322-Pin; 323-Torsion spring; 4-Fan; 5-Multi-mode switching control system; 51-Status monitoring module; 52-Sea state monitoring module; 53-Battery management module; 54-Judgment execution module. Detailed Implementation

[0031] To make the objectives, technical solutions, and advantages of the present invention clearer, the embodiments of the present invention will be described in further detail below with reference to the accompanying drawings.

[0032] Figure 1 This is a schematic diagram of the overall structure of the system provided in this embodiment of the invention; Figure 2 This is a schematic diagram of the wave energy conversion device provided in an embodiment of the present invention; Figure 3 This is a schematic diagram of the fit between the mass body and the guide rail provided in an embodiment of the present invention; Figure 4 This is a front view schematic diagram of the transmission mechanism and the tuned mass damper provided in an embodiment of the present invention; Figure 5 This is a top view schematic diagram of the transmission mechanism, tuned mass damper, and power generation and storage mechanism provided in an embodiment of the present invention; Figure 6 This is an exploded view of the transmission mechanism provided in an embodiment of the present invention; Figure 7 This is a schematic diagram of the power generation and energy storage mechanism provided in an embodiment of the present invention; Figure 8 This is a schematic diagram of signal transmission provided in an embodiment of the present invention. Figures 1 to 8 The system shown is a vibration damping and wave energy recovery and storage system for a floating wind turbine platform, comprising: a floating wind turbine platform 1 and a wave energy conversion device 2; the wave energy conversion device 2 is disposed within the floating wind turbine platform 1, and includes a housing 21 and a tuned mass damper 22, a transmission mechanism 23, and a power generation and storage mechanism 24 disposed within the housing 21; the housing 21 has a square base plate 211 disposed on the floating wind turbine platform 1, and two side plates 212 arranged parallel to each other along the length of the base plate 211, the side plates 212 being vertically disposed on the base plate 211; the tuned mass damper 22 includes a mass body 221, spring 222 and guide rail 223, the guide rail 223 is arranged on the base plate 211 along the length direction of the base plate 211, the mass body 221 is slidably arranged on the guide rail 223, and spring 222 is connected between both ends of the mass body 221 and the two side plates 212; the power generation and energy storage mechanism 24 includes two permanent magnet synchronous motors 241 respectively arranged at both ends of the mass body 221, the mass body 221 is connected to the shaft of the permanent magnet synchronous motor 241 through the transmission mechanism 23, and the mass body 221 is configured to reciprocate along the guide rail 223 to drive the shaft of the two permanent magnet synchronous motors 241 to rotate unidirectionally to generate electricity.

[0033] Exemplarily, in this embodiment of the invention, the housing 21 serves as the supporting frame for the entire wave energy conversion device 2. Its square base plate 211 is fixedly installed on the internal deck of the floating wind turbine platform 1 by bolts or welding. Two side plates 212 are vertically fixed to the long sides of the base plate 211, forming a groove-shaped space extending along the length direction, providing a stable mounting foundation and protective shell for the tuned mass damper 22, the transmission mechanism 23, and the power generation and energy storage mechanism 24. The guide rail 223 is fixedly installed on the base plate 211 along the length direction of the base plate 211. The mass body 221 is assembled on the guide rail 223 through a sliding fit structure at its bottom, and can make reciprocating linear motion in the horizontal direction along the guide rail 223. The spring 222 forms an elastic connection between the mass body 221 and the two end side plates 212, providing elastic restoring force for the mass body 221. When the mass body 221 deviates from the equilibrium position, the restoring force generated by the spring 222 will drive the mass body 221 back to the initial position, thus forming a complete mass-spring vibration system. In practical design, the parameters of the tuned mass damper 22 need to be matched according to the dynamic characteristics of the floating wind turbine platform 1. The stiffness of the spring 222 and the mass of the mass body 221 should meet the tuning condition, that is, the natural frequency of the vibration subsystem composed of the mass body 221 and the spring 222 should be close to or slightly deviate from the natural frequency corresponding to the main oscillation mode of the floating wind turbine platform 1 under wave excitation. The ratio between the two is the tuning frequency ratio. According to the classical Den Hartog optimal tuning theory, the optimal tuning frequency ratio can be determined under a given mass ratio (i.e., the ratio of the mass of the mass body 221 to the equivalent mass of the floating wind turbine platform 1), and then the required stiffness value of the spring 222 can be calculated. Specifically, the optimal tuning frequency ratio decreases as the mass ratio increases. The larger the mass ratio, the more the tuning frequency ratio deviates from 1. During the design, the specific value can be determined by referring to the Den Hartog optimal tuning formula or numerical simulation method. Furthermore, after the flywheel 233 is connected to the mass body 221 through the rack and pinion transmission mechanism 23, its rotational inertia, after being amplified by the transmission ratio, is equivalent to the inertial mass added to the mass body 221. This can further improve the equivalent mass ratio of the damper without increasing the actual mass, which is beneficial for achieving better vibration reduction effect in a limited space. The mass ratio is generally between 0.01 and 0.10, and the specific value can be determined by numerical simulation based on the design parameters of the floating wind turbine platform 1 and the target vibration reduction amplitude. Two permanent magnet synchronous motors 241 are respectively arranged on the outer sides of both ends of the mass body 221, and establish a transmission connection with the mass body 221 through the transmission mechanism 23. When the floating wind turbine platform 1 generates oscillating motions such as swaying or rolling motions under the action of waves, the motion of the platform is transmitted to the shell 21 as an excitation source. Since the mass body 221 has inertia, its motion lags behind the motion of the platform. Therefore, the mass body 221 generates reciprocating linear motion relative to the shell 21 along the guide rail 223.During this process, spring 222 is alternately compressed and stretched, absorbing and storing elastic potential energy. Through resonance, the vibration energy of the main structure is transferred to mass 221, thus achieving platform vibration reduction. Simultaneously, the reciprocating motion of mass 221 is converted into rotational motion via transmission mechanism 23 and transmitted to permanent magnet synchronous motors 241 at both ends. The design of transmission mechanism 23 ensures that regardless of the direction of mass 221's movement, the shaft of the corresponding permanent magnet synchronous motor 241 can be driven to maintain unidirectional rotation, thereby achieving stable and continuous power generation. Driven by the rotation of its shaft, permanent magnet synchronous motor 241 converts mechanical energy into electrical energy for output. Simultaneously, the electromagnetic damping force generated during power generation by permanent magnet synchronous motor 241 is fed back to mass 221 via transmission mechanism 23, serving as the system's damping force to further dissipate vibration energy and enhance vibration reduction performance. Therefore, this system achieves synergistic operation of vibration reduction and wave energy recovery power generation, converting vibration energy originally dissipated as heat into usable electrical energy.

[0034] This invention provides a vibration reduction and wave energy recovery storage system for a floating wind turbine platform. By placing the wave energy conversion device 2 inside the floating wind turbine platform 1, the entire system is integrated into the platform's internal space, eliminating the need for additional sea surface area. This compact structure is suitable for engineering scenarios where space is limited on the floating wind turbine platform 1. A tuned mass damper 22 is installed within the shell 21, utilizing the reciprocating motion of the mass 221 on the guide rail 223 and the elastic restoring force provided by the spring 222 to form a mass-spring vibration system. Based on the resonance principle, the oscillation energy of the floating wind turbine platform under wave action is transferred to the mass 221, effectively suppressing platform oscillation and ensuring structural safety and wind turbine operational stability. Two permanent magnet synchronous motors 241 are respectively installed at both ends of the mass 221, and the mass 221 is connected to the wave-driven system via a transmission mechanism 23. The shaft drive connection of the permanent magnet synchronous motor 241 converts the vibration energy absorbed by the tuned mass damper 22 into usable electrical energy, avoiding the problem that vibration energy is dissipated only as heat in traditional damping devices, thus improving the utilization rate of renewable energy. By configuring the mass body 221 to reciprocate along the guide rail 223 to drive the shafts of the two permanent magnet synchronous motors 241 to rotate unidirectionally to generate electricity, the problems of generator speed fluctuating or even reversing, output voltage and current fluctuating drastically, and power generation instability caused by the reciprocating motion of the mass body in the prior art are solved. This ensures that the permanent magnet synchronous motor 241 generates electricity continuously in a stable unidirectional rotation state, significantly improving power generation stability and energy recovery efficiency. Thus, it achieves synergistic optimization of vibration reduction and wave energy recovery and storage, effectively solving the problem that it is difficult to balance multi-directional vibration reduction and stable power generation and energy storage in the prior art.

[0035] Optionally, the transmission mechanism 23 includes a rack 231, a gear 232, a flywheel 233, and a ratchet assembly 3. Two transmission mechanisms 23 are symmetrically arranged on both sides of the mass body 221 along the length direction of the base plate 211. The rack 231 is arranged along the length direction of the base plate 211 and one end is fixedly connected to the mass body 221. The gear 232 meshes with the rack 231. The ratchet assembly 3 includes a ratchet 31 and a pawl part 32. The pawl part 32 includes a pawl 321, a pin 322, and a torsion spring 323. The pawl 321 is rotatably mounted on the end face of the gear 232 through the pin 322. The torsion spring 323 is sleeved on the pin 322 and one end is fixedly connected to the pawl 321, and the other end is fixedly connected to the gear 232. The ratchet 31 and the flywheel 233 are coaxially rotatably connected, and the ratchet 31 and the pawl 321 are engaged.

[0036] Exemplary, in embodiments of the present invention, such as Figure 4 and Figure 6 As shown, two transmission mechanisms 23 are arranged symmetrically about the mass body 221. One end of the rack 231 in each transmission mechanism 23 is fixedly connected to the end face of the mass body 221 by bolts or welding. The rack 231 moves in a horizontal reciprocating linear motion synchronously with the mass body 221. A gear 232 meshes with the rack 231. Through the characteristics of meshing transmission, the linear motion of the rack 231 is converted into the rotational motion of the gear 232, thereby increasing the rotational speed. A pawl 321 is hinged to the end face of the gear 232 via a pin 322 and can rotate around the pin 322. A torsion spring 323 is sleeved on the pin 322 to provide a restoring force for the pawl 321, ensuring that the pawl 321 always maintains a tendency to contact and engage with the ratchet 31, thus ensuring the reliability of the transmission. Ratchet 31 and flywheel 233 are fixed on the same rotating shaft and rotate coaxially. When pawl 321 engages with the tooth groove of ratchet 31, the rotational motion of gear 232 is transmitted to ratchet 31 through pawl 321, thereby driving flywheel 233 to rotate synchronously. To prevent accidental reverse rotation, those skilled in the art can selectively set a check pawl according to actual needs; this invention does not limit this. The key is that the transmission directions of the left and right ratchet assemblies 3 are designed to be opposite, so that regardless of whether the mass 221 moves left or right, it only drives the flywheel 233 on the corresponding side to rotate unidirectionally, while the pawl 321 on the other side slides across the ratchet 31 without transmitting power. Specifically, as shown... Figure 4 and Figure 5As shown, the ratchet teeth of the right ratchet 31 are arranged in a clockwise direction along its circumference, that is, the steep locking surface of the ratchet teeth faces the counterclockwise direction, and the gentle guiding slope of the ratchet teeth faces the clockwise direction; the right pawl 321 is installed on the end face of the right gear 232, and the hook end of the pawl 321 faces so that it naturally abuts against the ratchet locking surface of the right ratchet 31 under the elastic force of the torsion spring 323. When the right gear 232 rotates in the clockwise direction, the hook end of the right pawl 321 abuts against the ratchet locking surface, and transmits the rotational torque to the right ratchet 31, driving the right ratchet 31 and the flywheel 233 to rotate in the counterclockwise direction; when the right gear 232 rotates in the counterclockwise direction, the right pawl 321 slides along the ratchet guiding slope without engaging, and the right ratchet 31 is not driven. Correspondingly, the ratchet teeth of the left ratchet 31 are arranged counterclockwise along its circumference, that is, the steep locking surface of the ratchet teeth faces clockwise, and the gentle guiding slope of the ratchet teeth faces counterclockwise; the hook end of the left pawl 321 faces the opposite direction to the right, so that it naturally abuts against the ratchet locking surface of the left ratchet 31 under the elastic force of the torsion spring 323. When the left gear 232 rotates counterclockwise, the left pawl 321 engages with the locking surface of the left ratchet 31, driving the left ratchet 31 and flywheel 233 to rotate clockwise; when the left gear 232 rotates clockwise, the left pawl 321 slides on the ratchet guiding slope without engaging. Since both the left and right racks 231 are fixedly connected to the same mass 221, when the mass 221 moves to the right, both racks 231 move to the right. Under the meshing relationship between the racks 231 and the gears 232, the right gear 232 rotates clockwise, and the left gear 232 rotates clockwise. At this time, the right pawl 321 engages with the right ratchet 31, driving it to rotate counterclockwise, while the left pawl 321 slides across the left ratchet 31. When the mass 221 moves to the left, both gears 232 rotate in opposite directions. The left pawl 321 engages with the left ratchet 31, driving it to rotate clockwise, while the right pawl 321 slides across the right ratchet 31. Through this mirror-symmetric configuration of the tooth direction and the pawl orientation, it is ensured that during the reciprocating motion of the mass 221, the left flywheel 233 is always driven to rotate unidirectionally clockwise, and the right flywheel 233 is always driven to rotate unidirectionally counterclockwise. Figure 4 and Figure 5As shown, when the mass 221 moves to the right, the racks 231 fixed on the left and right sides of the mass 221 move to the right accordingly, driving the gears 232 on the left and right sides to rotate respectively. Taking the right transmission mechanism as an example, the right gear 232 rotates in a specific direction under the drive of the rack 231. At this time, the right pawl 321 is engaged in the tooth groove of the right ratchet 31 under the elastic force of the torsion spring 323. The rotational torque of the gear 232 is transmitted to the ratchet 31 through the pawl 321, driving the right ratchet 31 and the flywheel 233 coaxially connected to it to rotate synchronously in one direction. At the same time, the left gear 232 also rotates under the drive of the rack 231, but the engagement direction between the left pawl 321 and the left ratchet 31 causes the pawl 321 to slide on the tooth surface of the ratchet 31 without engaging. The left flywheel 233 is not driven, but due to the rotational inertia of the flywheel 233 itself, if the left flywheel 233 has been rotating before, it can still continue to rotate by inertia. When the mass 221 moves to its right limit position under the combined force of elastic restoring force, electromagnetic damping force, and its own gravity, and then moves in the opposite direction to the left, the left and right racks 231 move to the left accordingly, and the left and right gears 232 rotate in opposite directions. At this time, the left pawl 321 engages with the left ratchet 31, driving the left flywheel 233 to rotate in one direction; the right pawl 321 slides over the right ratchet 31, and the right flywheel 233 is no longer driven, but it can still continue to rotate due to its inertia, only gradually slowing down due to the electromagnetic damping force generated by the permanent magnet synchronous motor 241 generating electricity. This cycle repeats, and each reciprocating motion of the mass 221 alternately drives the left and right flywheels 233 to rotate. The flywheels 233 store rotational kinetic energy through their own rotational inertia, and under dynamic equilibrium, they maintain continuous rotation within a stable speed range, thereby driving the permanent magnet synchronous motors 241 at both ends to generate electricity alternately and stably, avoiding the problem of generator speed fluctuating or even reversing, and significantly improving power generation stability and energy recovery efficiency.

[0037] Optionally, the gear 232 is provided with a plurality of pawl portions 32, which are evenly spaced along the circumference of the gear 232.

[0038] Exemplary, in embodiments of the present invention, such as Figure 4 and Figure 6 As shown, multiple pawl portions 32 are mounted at equal angular intervals on the end face of the gear 232 along the circumferential direction of the gear 232, such as... Figure 4As shown, this embodiment has two pawl portions 32, each including a pawl 321, a pin 322, and a torsion spring 323. The structure and installation method of each pawl portion 32 on each gear 232 are identical, and the orientation of each pawl 321 is consistent, ensuring that all pawls 321 can engage with the ratchet 31 in the same direction. The uniform spacing of the multiple pawl portions 32 reduces the angular distance between adjacent pawls 321, thereby reducing the idle angle between the pawl 321 disengaging from the ratchet 31 tooth groove and re-engaging in the next tooth groove during the rotation of the gear 232. When the mass body 221 changes its direction of motion, and the corresponding gear 232 changes from an idle state to a state requiring the ratchet 31 to rotate, the pawl 321 closest to the gear 232 will engage in the ratchet 31 tooth groove first. Because multiple pawls 32 are evenly spaced, the angular distance between adjacent pawls 321 is small. The gear 232 only needs to rotate a very small angle to engage the pawl 321 with the ratchet 31. This greatly shortens the response time and idle stroke between the start of the movement of the mass body 221 and the start of the rotation of the flywheel 233, improves the timeliness and efficiency of energy transfer, reduces energy loss during the switching of the direction of movement, and enables the flywheel 233 to be accelerated more quickly, thereby ensuring the continuity and stability of power generation.

[0039] Optionally, the power generation and energy storage mechanism 24 also includes a rectifier bridge 242, a DC-DC converter 244 and a battery 243. The shaft of the permanent magnet synchronous motor 241 is coaxially rotatably connected to the flywheel 233. The output end of the permanent magnet synchronous motor 241 is electrically connected to the battery 243 in sequence through the rectifier bridge 242 and the DC-DC converter 244.

[0040] Exemplary, in embodiments of the present invention, such as Figure 7As shown, the shaft of the permanent magnet synchronous motor 241 is coaxially rotatably connected to the flywheel 233. When the flywheel 233 rotates unidirectionally under the drive of the ratchet assembly 3, the shaft of the permanent magnet synchronous motor 241 rotates synchronously with the flywheel 233, converting the rotational kinetic energy of the flywheel 233 into three-phase AC output. The input terminal of the rectifier bridge 242 is electrically connected to the three-phase output terminal of the permanent magnet synchronous motor 241, and is used to convert the three-phase AC power into DC power. The input terminal of the DC-DC converter 244 is electrically connected to the DC output terminal of the rectifier bridge 242, and the output terminal is electrically connected to the battery 243. This DC-DC converter 244 has a dual function: firstly, it filters and stabilizes the rectified DC power, removing noise and ripple, and adjusting the voltage to a stable value suitable for charging the battery 243; secondly, its duty cycle can be adjusted in real time by the multi-mode switching control system 5 to change the equivalent load impedance of the permanent magnet synchronous motor 241, thereby adjusting the magnitude of the electromagnetic damping torque and achieving coordinated switching between vibration reduction and power generation modes. The battery 243 stores the processed DC energy. The flywheel 233, driven by the ratchet assembly 3, rotates unidirectionally, continuously rotating the shaft of the permanent magnet synchronous motor 241 to generate electricity. The permanent magnet synchronous motor 241 outputs three-phase AC power with frequency and amplitude varying with rotational speed. This three-phase AC power first enters the rectifier bridge 242 and is converted into pulsating DC power after full-bridge rectification. The pulsating DC power then enters the DC-DC converter 244, where the pulsating component is removed by filtering. The voltage is then adjusted to match the charging voltage of the battery 243, outputting stable DC power to charge the battery 243, thus achieving stable energy storage. The electromagnetic damping torque generated by the permanent magnet synchronous motor 241 during power generation is related to the motor's load current, which in turn is regulated by the operating parameters of the DC-DC converter 244. According to basic motor principles, the electromagnetic damping torque of the permanent magnet synchronous motor 241 is positively correlated with its output current: the larger the output current, the larger the electromagnetic damping torque. The output current is regulated by the duty cycle D of the DC-DC converter 244: the larger the duty cycle D, the smaller the equivalent load impedance of the permanent magnet synchronous motor 241, the larger the output current, and the larger the electromagnetic damping torque. Therefore, the duty cycle D is positively correlated with the electromagnetic damping torque, and the magnitude of the damping torque can be linearly adjusted by adjusting D. During the system design phase, the required optimal damping coefficient can be calculated based on the optimal damping ratio of the tuned mass damper 22. Then, by combining the rack-and-pinion transmission ratio and parameters such as the torque constant and back electromotive force coefficient of the permanent magnet synchronous motor 241, the required equivalent load resistance value of the permanent magnet synchronous motor 241 can be derived, thereby determining the basic operating parameters of the DC-DC converter 244. Furthermore, in actual operation, the judgment and execution module 54 of the multi-mode switching control system 5 adjusts the duty cycle of the DC-DC converter 244 in real time based on the state of charge of the battery 243, the platform vibration amplitude, and sea state parameters. This ensures that the system maintains a near-optimal damping operating state under different operating conditions, achieving synergistic optimization of vibration reduction performance and power generation efficiency.Specifically, the rated power of the permanent magnet synchronous motor 241 can be estimated based on the expected oscillation amplitude and frequency of the floating wind turbine platform 1 under the design sea conditions. Taking a typical semi-submersible floating wind turbine platform as an example, under common sea conditions with a significant wave height of 2 to 4 meters and a wave period of 8 to 12 seconds, the peak reciprocating speed of the mass body 221 in a single wave energy conversion device 2 is typically in the range of 0.4 to 0.7 meters per second. Correspondingly, after the rack 231 drives the gear 232 to rotate and the speed is amplified by the transmission ratio, the rotational speed range of the flywheel 233 and the shaft of the permanent magnet synchronous motor 241 is approximately 100 to 600 revolutions per minute. Accordingly, the rated power of each permanent magnet synchronous motor 241 can be selected in the range of 10 to 200 kilowatts, and the rated speed matches the aforementioned flywheel speed range. The rectifier bridge 242 can adopt a three-phase uncontrolled full-bridge rectifier circuit, consisting of six rectifier diodes with a withstand voltage not less than twice the peak value of the maximum line voltage of the permanent magnet synchronous motor 241. The DC-DC converter 244 can be selected from either a buck or buck-boost topology. The specific type is determined by the relationship between the output voltage range of the rectifier bridge 242 and the charging voltage of the battery 243: a buck converter is selected when the rectified DC voltage is consistently higher than the battery's rated voltage; a buck-boost converter is selected when the rectified voltage may be lower than the battery's rated voltage. The battery 243 can be a 400V lithium iron phosphate battery pack. Its capacity is determined based on the average daily power consumption of the wind turbine's monitoring and auxiliary equipment, as well as the required operating time. Typically, a capacity range of 20 to 200 Ah is selected to ensure sufficient energy storage capacity to power the wind turbine's auxiliary equipment even under continuous low sea state conditions. The resistance value of the energy-dissipating resistor 245 can be calculated based on the difference between the maximum allowable charging voltage of the battery 243 and the maximum output voltage of the DC-DC converter 244 under extreme sea conditions, as well as the maximum charging current. Typically, a power-type wire-wound resistor or an aluminum-cased resistor is selected, with a rated power not lower than the maximum power dissipated under extreme operating conditions. The entire circuit system achieves efficient conversion from fluctuating three-phase AC power to stable DC power, ensuring that even when the speed of flywheel 233 fluctuates due to the reciprocating motion of mass 221, it can still provide a stable and reliable charging current for battery 243, improving energy recovery efficiency and power quality. At the same time, through the active adjustment of the duty cycle of DC-DC converter 244 by the multi-mode switching control system 5, the system can adaptively optimize the comprehensive performance of vibration reduction and power generation under different sea conditions and battery status.

[0041] Optionally, the power generation and energy storage mechanism 24 also includes an energy-consuming resistor 245, which is disposed between the DC-DC converter 244 and the battery 243.

[0042] Exemplary, in embodiments of the present invention, such as Figure 7As shown, the energy-dissipating resistor 245 is connected in series with the battery 243 in the circuit. That is, after the current outputs from the DC-DC converter 244, it flows sequentially through the energy-dissipating resistor 245 and the battery 243, forming a complete charging circuit. A bypass switch element, which can be a relay or a power MOSFET, is also connected in parallel in the branch containing the energy-dissipating resistor 245. Under normal operating conditions, when the output voltage of the DC-DC converter 244 is within the rated charging voltage range of the battery 243, the bypass switch element is turned on, and the current flows directly into the battery 243 for charging. The energy-dissipating resistor 245 does not participate in the operation, avoiding unnecessary energy loss. When the system detects that the output voltage of the DC-DC converter 244 exceeds a preset safety threshold, the bypass switch element is turned off, and the charging current is forced to flow through the energy-dissipating resistor 245. The energy-dissipating resistor 245 shares the excess voltage drop and dissipates the excess energy as heat, thereby limiting the charging voltage of the battery 243 within a safe range. The on / off control of voltage detection and bypass switching elements can be achieved by a simple voltage comparison protection circuit. When the detected voltage exceeds the upper threshold, the bypass switching element is disconnected, allowing the energy-consuming resistor 245 to connect to the circuit. When the detected voltage falls back to the normal range, the bypass switching element is re-closed. Thus, the energy-consuming resistor 245 only operates under overvoltage conditions and does not consume energy under normal conditions, balancing energy recovery efficiency and battery safety protection. Under normal operating conditions, the energy-consuming resistor 245 functions as a voltage divider and current limiter. When the system voltage is too high, the energy-consuming resistor 245 dissipates excess energy as heat by sharing part of the voltage, preventing the battery 243 from being subjected to excessively high charging voltage, thus preventing overcharging damage and ensuring the safety and lifespan of the battery 243. During system operation, when sea conditions are severe and wave excitation is strong, the amplitude of motion of the mass body 221 increases, the speed of the flywheel 233 increases, and the output voltage of the permanent magnet synchronous motor 241 increases accordingly. Even after voltage regulation by the DC-DC converter 244, the system voltage may still be too high. In this situation, the energy-dissipating resistor 245 acts as a voltage divider, transferring excess voltage exceeding the rated charging voltage of the battery 243 across the resistor 245. This excess energy is dissipated as heat, ensuring that the charging voltage of the battery 243 remains within a safe range. Simultaneously, the electromagnetic damping force generated by the energy dissipated by the resistor 245 also participates in the vibration reduction process as part of the system damping, contributing to the dissipation of vibration energy. The resistance value of the energy-dissipating resistor 245 can be designed to match the rated parameters of the permanent magnet synchronous motor 241, the charging voltage and capacity of the battery 243, etc., to ensure safe and stable operation of the system under different sea conditions.

[0043] Optionally, the floating wind turbine platform 1 is also equipped with a multi-mode switching control system 5. The multi-mode switching control system 5 includes a status monitoring module 51 for real-time monitoring of the vibration amplitude of the floating wind turbine platform 1; a sea state monitoring module 52 for real-time monitoring of the effective wave height of the sea area where the floating wind turbine platform 1 is located; a battery management module 53 for real-time monitoring of the state of charge of the battery 243; and a judgment and execution module 54, which is communicatively connected to the status monitoring module 51, the sea state monitoring module 52, the battery management module 53, and the DC-DC converter 244, respectively, for adjusting the duty cycle of the DC-DC converter 244 to adjust the magnitude of the electromagnetic damping torque of the permanent magnet synchronous motor 241.

[0044] Exemplary, in embodiments of the present invention, such as Figure 8 As shown, to further improve the adaptability and overall performance of this system under different operating conditions and sea states, a multi-mode switching control system 5 is also installed inside the floating wind turbine platform 1. This multi-mode switching control system 5 automatically switches between vibration reduction priority mode, power generation priority mode, and balance mode based on the real-time vibration state of the floating wind turbine platform 1, the energy storage state of the battery 243, and the current sea state parameters, achieving coordinated optimization of vibration reduction and power generation. The state monitoring module 51 can be an accelerometer, installed on key structural parts of the floating wind turbine platform 1, to acquire in real-time the vibration amplitude A (unit: m / s) of the floating wind turbine platform 1 in the sway or roll direction. 2 The system can accurately reflect the intensity of the platform's oscillation response under wave excitation. The sea state monitoring module 52 can be a wave sensor, installed on the floating wind turbine platform 1, to monitor the effective wave height Hs (unit: meters) of the sea area where the floating wind turbine platform 1 is located in real time. The wave sensor can be in the form of wave radar or an inertial navigation system, etc., and obtains the effective wave height Hs through statistical analysis of the wave surface height signal, serving as a quantitative indicator of the current sea state severity. The battery management module 53 is electrically connected to the battery 243, monitoring parameters such as voltage, current, and temperature of the battery 243 in real time, and calculating and outputting the state of charge (SOC) (percentage) of the battery 243, providing real-time data on the battery's energy storage status to the judgment execution module 54. The judgment and execution module 54 is communicatively connected to the state monitoring module 51, the sea state monitoring module 52, and the battery management module 53. It receives real-time signals such as vibration amplitude A, significant wave height Hs, and state of charge (SOC). Based on preset judgment logic, it determines the current operating mode and adjusts the duty cycle D of the DC-DC converter 244 according to the determined operating mode, thereby changing the equivalent load impedance and electromagnetic damping torque of the permanent magnet synchronous motor 241. The judgment and execution module 54 can be implemented using a microcontroller or a programmable logic controller, integrating mode judgment and mode execution functions.

[0045] Specifically, in this embodiment, the judgment execution module 54 compares the vibration amplitude A with a preset safety threshold A. safeThe state of charge (SOC) is compared with a preset minimum threshold SOC. min A comparison is made, and based on the comparison result, the current working mode is determined and the corresponding duty cycle adjustment is performed. Among these, the safety threshold A... safe The value can be determined based on the structural design parameters and safety standards of the floating wind turbine platform 1, for example, set to 0.5 m / s. 2 Minimum threshold SOC min This can be determined based on the minimum power supply requirements of the auxiliary equipment of fan 4, for example, set to 20%. The specific judgment and execution logic of the judgment execution module 54 is as follows: when the vibration amplitude A ≥ A safe When the current sea conditions are severe, such as typhoons or giant waves, the judgment execution module 54 determines that the structural safety of the floating wind turbine platform 1 and the operational stability of the wind turbine 4 are threatened, and the vibration reduction demand far exceeds the power generation demand. Therefore, the judgment execution module 54 switches to a vibration reduction priority mode. In this mode, the judgment execution module 54 adjusts the duty cycle D of the DC-DC converter 244 to its maximum value, for example, D=0.95, to minimize the equivalent load impedance of the permanent magnet synchronous motor 241 and maximize the electromagnetic damping torque. This provides the maximum damping force to the mass body 221, prioritizing the suppression of the oscillation motion of the floating wind turbine platform 1 and ensuring structural safety and wind turbine operational stability. In this mode, power generation is a secondary objective; the system sacrifices some power generation efficiency for maximum vibration reduction performance. When the state of charge (SOC) ≤ SOC min And the vibration amplitude A < 0.5 × A safe When the judgment execution module 54 determines that the battery 243 has insufficient power and the sea state is relatively stable, it is necessary to replenish the battery 243 with power as soon as possible to meet the power supply requirements of the wind turbine 4 auxiliary equipment. The judgment execution module 54 then switches to the power generation priority mode. In the power generation priority mode, the judgment execution module 54 adjusts the duty cycle D of the DC-DC converter 244 to its theoretical optimal value, for example, D is in the range of 0.6 to 0.8. The specific value can be pre-calibrated based on parameters such as the torque constant of the permanent magnet synchronous motor 241 and the rated voltage of the battery 243. Under this optimal duty cycle, the permanent magnet synchronous motor 241 operates near its maximum power point, with the highest energy recovery efficiency, and can quickly charge the battery 243, restoring the battery 243's stored power to a level sufficient for the normal power supply of the wind turbine 4 auxiliary equipment. When neither of the above two conditions is met, i.e., the vibration amplitude A < A safe Furthermore, it does not meet the power generation priority condition (i.e., battery state of charge (SOC) > SOC). min or although SOC≤SOC min However, the vibration amplitude A ≥ 0.5 × A safeWhen the system operates under normal sea conditions, it needs to simultaneously consider vibration reduction and power generation. Therefore, the judgment execution module 54 switches to a balanced mode. In balanced mode, the judgment execution module 54 dynamically adjusts the duty cycle D of the DC-DC converter 244 based on the significant wave height Hs provided by the sea state monitoring module 52, achieving a dynamic balance between vibration reduction and power generation. Specifically, when the significant wave height Hs is low, for example, within the range of 2 to 4 meters, the sea state is stable, the oscillation amplitude of the floating wind turbine platform 1 is small, and the vibration reduction requirement is relatively low. In this case, the judgment execution module 54 appropriately reduces the duty cycle D and decreases the electromagnetic damping torque, thereby lowering the power generation start-up threshold and improving the energy capture efficiency under low sea states. When the significant wave height Hs is high, for example, within the range of 4 to 6 meters, the sea state gradually worsens, the oscillation of the floating wind turbine platform 1 intensifies, and the vibration reduction requirement increases. In this case, the judgment execution module 54 appropriately increases the duty cycle D and increases the electromagnetic damping torque, prioritizing the vibration reduction effect while still maintaining a certain level of power generation efficiency. Through the above design, the balanced mode achieves the function of adaptive damping adjustment under sea conditions, integrating it into the balanced framework of vibration reduction and power generation. This ensures the system's adaptability under different sea conditions while avoiding excessive complexity in the control logic. To prevent the system from frequently switching near critical values, which could lead to operational instability, the judgment execution module 54 employs hysteresis comparison logic: the threshold for entering the vibration reduction priority mode from the safe state is A≥A. safe The threshold for returning to a safe state from the vibration reduction priority mode is A < 0.8 × A. safe A hysteresis interval is formed between the two thresholds to ensure the stability of mode switching. Duty cycle adjustment in all three modes is achieved by sending a PWM control signal to the DC-DC converter 244 via the judgment execution module 54. Since the response time of the DC-DC converter 244 is typically in the millisecond range, much faster than the wave cycle (generally 8 to 12 seconds), the multi-mode switching control system 5 can respond to changes in operating conditions and sea conditions in real time, achieving smooth mode switching and damping adjustment. The multi-mode switching control system 5 of this invention has a close synergistic relationship with the aforementioned mechanical structure; the two are not simply superimposed but rather interdependent and work together. In terms of mechanical structure, this invention adopts a symmetrical design with opposite transmission directions of the ratchet assemblies 3 on both sides, ensuring that the mass body 221 can drive the corresponding permanent magnet synchronous motor 241 to maintain unidirectional rotation regardless of whether it moves left or right, completely avoiding the drastic voltage and current fluctuations caused by the alternating forward and reverse rotation of the motor in traditional solutions. Meanwhile, the flywheel 233, coaxially fixed with the ratchet 31, stores rotational kinetic energy using its large moment of inertia, smoothing out the speed fluctuations caused by the reciprocating motion of the mass 221, and maintaining the speed of the permanent magnet synchronous motor 241 within a relatively stable range. This combination of mechanical unidirectional rectification and inertial speed stabilization ensures that the electromagnetic damping torque output by the permanent magnet synchronous motor 241 is continuous in time, constant in direction, and stable in amplitude, providing a stable and predictable execution environment for the fine adjustment of the judgment execution module 54.

[0046] The aforementioned mechanical structure provides key support for the multi-mode switching control system 5 in several aspects. Firstly, it improves the response speed of mode switching. Since the permanent magnet synchronous motor 241 always rotates in one direction, there is no reverse acceleration delay due to forward rotation, stopping, or reversal. When a sudden high sea state necessitates a rapid switch from the balance mode to the vibration reduction priority mode, the judgment and execution module 54 can adjust the duty cycle to its maximum value within milliseconds, instantly increasing the electromagnetic damping torque. This rapid response directly ensures the system's ability to switch to the vibration reduction priority mode promptly when platform oscillations intensify, which is a core guarantee of structural safety. Secondly, it achieves stepless continuous adjustment. Because the electromagnetic damping torque continuously changes in the same direction, there is no stepless adjustment. During the zero-crossing dead zone of alternating forward and reverse rotation, smooth stepless adjustment from minimum to maximum value can be achieved. This is a prerequisite for the balanced mode to dynamically adjust damping according to the effective wave height and achieve continuous, non-jumping operation. Finally, it ensures the predictability and repeatability of the response. The same duty cycle input produces the same electromagnetic damping effect at any time, with consistent direction and magnitude. The adjustment result of the judgment execution module 54 is predictable and repeatable, which makes it possible to reliably achieve precise control objectives such as the maximum duty cycle corresponding to the maximum damping in vibration reduction priority mode and the optimal duty cycle corresponding to the highest efficiency in power generation priority mode. In terms of control logic, the judgment execution module 54 dynamically adjusts the duty cycle of the DC-DC converter 244 by receiving monitoring data provided by the status monitoring module 51, sea state monitoring module 52, and battery management module 53 in real time, thereby changing the equivalent load impedance and electromagnetic damping torque of the permanent magnet synchronous motor 241. This control action not only optimizes power generation efficiency, but more importantly, it actively alters the system's damping characteristics, enabling the originally passively responding tuned mass damper 22 to adaptively adjust its damping force according to operating conditions and sea conditions, significantly expanding the system's effective operating range. Without the active intervention of the multi-mode switching control system 5, the mechanical structure could only operate with a fixed damping coefficient, unable to adapt to the changing marine environment, and its vibration reduction and power generation performance would be limited. The mechanical structure and the multi-mode switching control system 5 together constitute a complete closed-loop optimization system. The mechanical structure provides a stable unidirectional rotational power source and an adjustable actuator. The judgment and execution module 54 calculates the optimal damping target based on the real-time feedback state signal and achieves this target by adjusting the duty cycle of the DC-DC converter 244. The signal flow and energy flow between the two form a closed loop: mechanical motion generates electrical energy, the judgment and execution module 54 adjusts the damping, the damping reacts to the mechanical motion to suppress vibration and affect power generation, and the power generation affects the state of charge (SOC) of the battery 243. The SOC is fed back to the judgment and execution module 54 through the battery management module 53 and then used as one of the inputs for control decisions. Through this multi-physics field coupling closed-loop optimization of mechanical, electrical and control systems, this system can achieve optimal synergy between vibration reduction and stable power generation and energy storage under different sea conditions and operating conditions.

[0047] Optionally, the base plate 211 has two fixed supports 213 arranged parallel to each other along the width direction. The transmission mechanism 23 also includes a gear shaft 234 and a common shaft 235 arranged along the width direction of the base plate 211. The gear shaft 234 and the common shaft 235 are rotatably mounted on the fixed supports 213. The gear 232 is fixed on the gear shaft 234. The flywheel 233 and the ratchet 31 are fixed on the common shaft 235. One end of the common shaft 235 is provided with a coupling 246. The common shaft 235 is coaxially rotatably connected to the shaft of the permanent magnet synchronous motor 241 through the coupling 246.

[0048] Exemplary, in embodiments of the present invention, such as Figure 5 As shown, two fixed brackets 213 are fixedly installed on the base plate 211 at parallel intervals along the width direction of the base plate 211, providing a stable support foundation for each rotating shaft in the transmission mechanism 23. The gear shaft 234 is arranged horizontally along the width direction of the base plate 211, and its two ends are rotatably mounted on the two fixed brackets 213 respectively. The gear 232 is fixedly mounted on the gear shaft 234 and rotates synchronously with the gear shaft 234, ensuring smooth and reliable meshing transmission between the gear 232 and the rack 231. The common shaft 235 is arranged parallel to the gear shaft 234, and its two ends are also rotatably mounted on the fixed brackets 213. The flywheel 233 and the ratchet 31 are both fixedly mounted on the common shaft 235, and the three are coaxially rotatably connected. When the pawl 321 engages with the ratchet 31 and drives the ratchet 31 to rotate, the flywheel 233 rotates synchronously with the ratchet 31 on the common shaft 235. One end of the common shaft 235 is connected to the shaft of the permanent magnet synchronous motor 241 via a coupling 246. The coupling 246 is used to achieve coaxial transmission between the common shaft 235 and the shaft of the permanent magnet synchronous motor 241, while also compensating for minor deviations in the shaft and buffering torque fluctuations, protecting the permanent magnet synchronous motor 241 from damage caused by impact loads. When the mass 221 reciprocates, the rack 231 drives the gear 232 to rotate on the gear shaft 234. The rotation of the gear 232 is transmitted to the ratchet 31 through the pawl 32 on its end face. The ratchet 31 drives the common shaft 235 to rotate, which in turn drives the flywheel 233 fixed on the common shaft 235 to rotate synchronously. The flywheel 233 utilizes its large moment of inertia to store rotational kinetic energy and maintain a stable rotational state. The rotational motion of the common shaft 235 is transmitted to the shaft of the permanent magnet synchronous motor 241 via the coupling 246, driving the permanent magnet synchronous motor 241 to rotate and generate electricity. The fixed bracket 213 provides rigid support for the gear shaft 234 and the common shaft 235, preventing shaft offset, vibration or shaking caused by load changes during transmission. It ensures the meshing accuracy between the rack 231 and the gear 232 and the matching accuracy between the pawl 321 and the ratchet 31, ensuring the efficient operation of the entire transmission chain and the stable maintenance of the constant speed range of the flywheel 233.

[0049] Optionally, the guide rail 223 is a T-shaped rail, and the bottom of the mass body 221 is provided with a groove 224 that matches the guide rail 223 along the length direction. The mass body 221 is slidably mounted on the guide rail 223 through the groove 224.

[0050] Exemplary, in embodiments of the present invention, such as Figure 2 and Figure 3 As shown, the guide rail 223 adopts a T-shaped cross-section track structure and is fixedly installed on the upper surface of the base plate 211, extending along the length of the base plate 211. The bottom of the mass body 221 has a groove 224 along its length that matches the cross-section of the T-shaped track. The cross-sectional shape of the groove 224 complements the T-shaped track. The mass body 221 is fitted onto the guide rail 223 through the groove 224 and can slide freely along the length of the guide rail 223. A lateral and longitudinal constraint relationship is formed between the lateral flange of the T-shaped track and the corresponding groove of the groove 224. This allows the mass body 221 to reciprocate linearly along the length of the guide rail 223 while restricting its displacement perpendicular to the guide rail, preventing lateral deviation or longitudinal derailment during movement and ensuring that the mass body 221 always moves along a predetermined trajectory. When the floating wind turbine platform 1 oscillates under wave action, the mass body 221 reciprocates relative to the shell 21 along the guide rail 223 due to inertia. The cooperation between the T-shaped guide rail 223 and the slide 224 constrains the movement of the mass 221 to a straight trajectory in a single direction. The lateral flange of the T-shaped guide rail provides an upward constraint force on the mass 221, preventing it from detaching from the guide rail 223 when the floating wind turbine platform 1 experiences complex movements such as heaving or pitching. This guiding constraint ensures the accuracy and reliability of the mass 221's movement, enabling it to continuously and stably transmit reciprocating motion to the power generation and energy storage mechanism 24 through the transmission mechanism 23. This avoids transmission failure or structural damage caused by derailment or offset, improving the safety and stability of the system during long-term operation in complex sea conditions.

[0051] Optionally, multiple rows of balls 225 are provided in the slide groove 224, and the multiple rows of balls 225 are arranged along the length of the slide groove 224. The slide groove 224 is slidably connected to the guide rail 223 through the balls 225.

[0052] Exemplary, in embodiments of the present invention, such as Figure 3As shown, multiple rows of balls 225 are arranged sequentially along the length of the groove 224 and installed on the contact surface between the groove 224 and the guide rail 223. The balls 225 are embedded between the inner wall of the groove 224 and the outer surface of the T-shaped guide rail 223. When the mass 221 slides along the guide rail 223, the balls 225 roll between the inner wall of the groove 224 and the surface of the guide rail 223, converting the sliding friction between the mass 221 and the guide rail 223 into rolling friction, significantly reducing frictional resistance. A ball retaining frame is also provided between the groove 224 and the guide rail 223. The ball retaining frame is made of wear-resistant engineering plastic or copper alloy and extends along the length of the groove 224. Multiple circular receiving holes are evenly distributed along the length of the frame. The diameter of each receiving hole is slightly larger than the diameter of the balls 225, allowing the balls 225 to roll freely within the receiving holes without falling out. The ball retainer frame is embedded in the gap between the inner wall of the groove 224 and the outer surface of the guide rail 223. Axial and radial constraints are provided by limiting bosses on the inner wall of the groove 224, preventing significant displacement of the ball retainer frame relative to the groove 224. When the mass 221 reciprocates along the guide rail 223, the balls 225 roll in place within the receiving holes or move slightly within a certain range with the ball retainer frame, always maintaining a preset uniform distribution. This prevents the balls 225 from accumulating at one end or dislodging from the groove 224 during reciprocating motion, ensuring a stable and reliable rolling friction connection between the mass 221 and the guide rail 223 during long-term operation. Multiple rows of balls 225 are evenly distributed along the length of the groove 224, allowing the load of the mass 221 to be evenly transferred to the guide rail 223, avoiding stress concentration and improving the load-bearing capacity and service life of the guide structure. When the mass body 221 reciprocates along the guide rail 223 under wave excitation, multiple rows of balls 225 in the groove 224 roll on the surface of the guide rail 223, transforming the original sliding friction into rolling friction, significantly reducing motion resistance and friction loss. The reduction in friction means that a larger proportion of the vibration energy absorbed by the mass body 221 is effectively transferred to the transmission mechanism 23 and the power generation and storage mechanism 24, rather than being lost as heat energy in sliding friction, thereby improving the energy transfer efficiency and power generation efficiency of the entire system. Simultaneously, the rolling motion of the balls 225 reduces wear on the guide rail 223 and the groove 224, extending the service life of the guiding structure, reducing maintenance frequency, and making the system more suitable for long-term unattended operation in deep-sea environments.

[0053] Optionally, multiple wave energy conversion devices 2 are provided, and the multiple wave energy conversion devices 2 are arranged in a ring inside the floating wind turbine platform 1.

[0054] Exemplary, in embodiments of the present invention, such as Figure 1As shown, multiple wave energy conversion devices 2 are arranged in a ring array within the internal space of the floating wind turbine platform 1. The guide rails 223 of each wave energy conversion device 2 are oriented differently, including at least two wave energy conversion devices 2 arranged along two mutually perpendicular horizontal directions, such as wave energy conversion devices 2 arranged along the platform's longitudinal sway direction and wave energy conversion devices 2 arranged along the platform's transverse sway direction. The ring arrangement ensures that the wave energy conversion devices 2 are evenly distributed within the floating wind turbine platform 1, making full use of the limited space inside the platform and resulting in a more balanced mass distribution of the system, without adversely affecting the center of gravity and stability of the floating wind turbine platform 1. When the floating wind turbine platform 1 operates in deep-sea environments, it is simultaneously subjected to the combined excitation of wind, waves, and currents from different directions. The platform will not only oscillate in the longitudinal direction but also oscillate in the transverse direction and other directions. Since the multiple wave energy conversion devices 2 are arranged in different directions, when the platform oscillates in any direction, the mass body 221 in the wave energy conversion device 2 arranged along that direction or its component will be effectively excited, generating reciprocating motion and driving the power generation and energy storage mechanism 24 to generate electricity. When waves arrive directly in front of the platform, causing sway vibrations, the mass 221 in the wave energy conversion device 2 arranged along the sway direction is maximally excited and generates electricity efficiently. Simultaneously, if lateral wave components cause transverse sway vibrations, the wave energy conversion device 2 arranged along the transverse sway direction can also synchronously capture the vibration energy in that direction and generate electricity. Multiple multi-directionally arranged wave energy conversion devices 2 work together to capture and recover the omnidirectional oscillation energy of the floating wind turbine platform 1, while providing vibration damping forces to the platform from multiple directions, significantly improving the system's vibration reduction effect and energy recovery capability, enabling the system to adapt to the complex and variable sea conditions of the deep sea. Specifically, the number and orientation of the wave energy conversion devices 2 can be determined based on the main wave direction statistics of the target deployment area of ​​the floating wind turbine platform 1 and the platform's structural form. As a typical arrangement, multiple wave energy conversion devices 2 are arranged at equal angular intervals along the circumference inside the floating wind turbine platform 1, with the guide rails 223 of each device extending radially along the circumference, forming a radial ring array. For example, when four wave energy conversion devices 2 are installed, the guide rails between adjacent devices are angled at 45 degrees, i.e., arranged along four directions: 0 degrees (swell direction), 45 degrees, 90 degrees (swell direction), and 135 degrees, respectively, which can cover all major oscillation direction components in the horizontal plane. When six wave energy conversion devices 2 are installed, the guide rails between adjacent devices are angled at 30 degrees, resulting in more uniform and detailed directional coverage. If the main wave direction in the target sea area is relatively concentrated, the number of wave energy conversion devices 2 arranged along the main wave direction and its vicinity can be appropriately increased, while the number arranged along secondary directions can be reduced, in order to maximize energy capture efficiency and vibration reduction effect under limited space and cost conditions.Each wave energy conversion device 2 has its base plate 211 independently fixed to the corresponding mounting base on the inner deck of the floating wind turbine platform 1 using its own mounting bolts. They are mechanically independent and do not interfere with each other, each operating independently. The batteries 243 of the power generation and storage mechanisms 24 of each device can be connected in parallel through a combiner circuit to jointly supply power to the energy-consuming equipment of the wind turbine 4, or they can independently store energy and supply power.

[0055] Optionally, a wind turbine 4 is installed on the floating wind turbine platform 1, and the power generation and energy storage mechanism 24 is electrically connected to the energy-consuming equipment inside the wind turbine 4.

[0056] Exemplary, in embodiments of the present invention, such as Figure 1 As shown, wind turbine 4 is installed at the upper center of floating wind turbine platform 1, and includes a tower, nacelle, blades, and related control and monitoring systems. During operation, wind turbine 4 requires power for various energy-consuming devices, including but not limited to operating status monitoring sensors, yaw control system, auxiliary power supply for pitch control system, communication equipment, navigation lights, and other auxiliary control equipment. The batteries in the power generation and storage mechanism 24 are electrically connected to the aforementioned energy-consuming devices within wind turbine 4 via cables, transmitting the stored electrical energy to each device to power it. Floating wind turbine platform 1 is deployed in remote, deep-sea areas, and the low-power devices of wind turbine 4, such as its monitoring and auxiliary control systems, typically require a continuous power supply. Relying entirely on external power lines would not only be costly to lay, but also compromise the reliability of power supply in harsh sea conditions. In this system, the wave energy conversion device 2 converts the wave energy contained in the oscillation of the floating wind turbine platform 1 into electrical energy and stores it in batteries. Although the power recovered by the wave energy conversion device 2 is relatively small and difficult to integrate into the power grid, it is sufficient to meet the power needs of low-power equipment such as the monitoring and auxiliary control of the wind turbine 4. The electrical energy stored in the batteries is supplied to the energy-consuming equipment of the wind turbine 4 nearby through electrical connection lines, realizing the on-site conversion and utilization of wave energy. There is no need to lay additional power supply lines, which reduces operation and maintenance costs and improves the power supply reliability and self-sufficiency of the wind turbine 4 during long-term operation in remote sea areas. At the same time, this system is independent of the main power generation system of the wind turbine 4 and does not interfere with each other. It does not affect the normal power generation operation of the wind turbine 4, and can indirectly improve the operational stability and service life of the wind turbine 4 through its own vibration reduction function.

[0057] Because this system is installed inside the floating wind turbine platform 1, it is exposed to the corrosive environment of high humidity and high salt spray in the deep sea for extended periods. To ensure the system can operate reliably under these harsh conditions, corresponding anti-corrosion and sealing protection measures have been implemented for each component. The bottom plate 211 and side plates 212 of the shell 21 are made of marine-grade stainless steel or hot-dip galvanized carbon steel, with a marine anti-corrosion coating. The guide rails 223, racks 231, gears 232, flywheels 233, gear shafts 234, common shafts 235, and ratchet 31 are all made of marine corrosion-resistant alloy steel and are chrome-plated or nitrided to enhance corrosion resistance and wear resistance. The springs 222 are made of corrosion-resistant spring steel and are phosphated or sprayed with an anti-corrosion coating. The balls 225 are made of stainless steel or ceramic to balance corrosion resistance and wear resistance. The sliding surfaces of the guide rails 223 and the slide grooves 224 are periodically coated with an appropriate amount of salt spray resistant grease to reduce frictional resistance and form an anti-corrosion isolation layer. The permanent magnet synchronous motor 241 is selected with an IP65 or higher protection rating. Its casing is sealed, the internal stator windings are impregnated with moisture-resistant insulating varnish, and the rotor permanent magnet surface is coated with an anti-corrosion protective layer. The circuit boards of the rectifier bridge 242 and the DC-DC converter 244 are coated with conformal coating (moisture-proof, salt spray-proof, and mildew-proof) and encapsulated in a sealed protective box. The battery 243 is a lithium iron phosphate battery or a marine-specific battery with good sealing performance, and the casing has a moisture-proof sealed structure. The cable connection joints use waterproof sealed connectors. A waterproof sealed cover can be installed on the top of the housing 21 to form a relatively sealed space inside the housing 21, reducing the intrusion of external moisture and salt spray gases.

[0058] Unless otherwise defined, the technical or scientific terms used herein shall have the ordinary meaning as understood by one of ordinary skill in the art to which this invention pertains. The terms “first,” “second,” and similar terms used in this patent application specification and claims do not indicate any order, quantity, or importance, but are merely used to distinguish different components. Similarly, the terms “an” or “a” and similar terms do not indicate a quantity limitation, but rather indicate the presence of at least one. The terms “comprising” or “including” and similar terms mean that the elements or objects preceding “comprising” or “including” encompass the elements or objects listed following “comprising” or “including” and their equivalents, and do not exclude other elements or objects. The terms “connected” or “linked” and similar terms are not limited to physical or mechanical connections, but can include electrical connections, whether direct or indirect. The terms “upper,” “lower,” “left,” and “right” are used only to indicate relative positional relationships; when the absolute position of the described object changes, the relative positional relationship may also change accordingly.

[0059] The above description is merely an optional embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A vibration reduction and wave energy recovery storage system for a floating wind turbine platform, characterized in that, include: Floating wind turbine platform (1) and wave energy conversion device (2); The wave energy conversion device (2) is installed inside the floating wind turbine platform (1). The wave energy conversion device (2) includes a shell (21) and a tuned mass damper (22), a transmission mechanism (23) and a power generation and energy storage mechanism (24) installed inside the shell (21). The shell (21) has a square base plate (211) installed on the floating wind turbine platform (1) and two side plates (212) arranged parallel to each other along the length of the base plate (211). The side plates (212) are vertically installed on the base plate (211). The tuned mass damper (22) includes a mass (221), a spring (222), and a guide rail (223). The guide rail (223) is disposed on the base plate (211) along the length direction of the base plate (211). The mass (221) is slidably disposed on the guide rail (223). The two ends of the mass (221) are connected to the two side plates (212) by the spring (222). The power generation and energy storage mechanism (24) includes two permanent magnet synchronous motors (241) respectively disposed at both ends of the mass body (221). The mass body (221) is connected to the shaft of the permanent magnet synchronous motor (241) through the transmission mechanism (23). The mass body (221) is configured to reciprocate along the guide rail (223) to drive the shaft of the two permanent magnet synchronous motors (241) to rotate unidirectionally to generate electricity. The transmission mechanism (23) includes a rack (231), a gear (232), a flywheel (233), and a ratchet assembly (3). Two transmission mechanisms (23) are symmetrically arranged on both sides of the mass body (221) along the length of the base plate (211). The rack (231) is arranged along the length of the base plate (211) and one end is fixedly connected to the mass body (221). The gear (232) meshes with the rack (231). The ratchet assembly (3) includes a ratchet (31) and a pawl (32). The pawl part (32) includes a pawl (321), a pin (322), and a torsion spring (323). The pawl (321) is rotatably mounted on the end face of the gear (232) via the pin (322). The torsion spring (323) is sleeved on the pin (322), with one end fixedly connected to the pawl (321) and the other end fixedly connected to the gear (232). The ratchet (31) and the flywheel (233) are coaxially connected, and the ratchet (31) is engaged with the pawl (321). The gear (232) is provided with a plurality of ratchet portions (32), which are evenly spaced along the circumference of the gear (232).

2. The vibration reduction and wave energy recovery storage system for floating wind turbine platforms according to claim 1, characterized in that, The power generation and energy storage mechanism (24) also includes a rectifier bridge (242), a DC-DC converter (244) and a battery (243). The shaft of the permanent magnet synchronous motor (241) is coaxially connected to the flywheel (233). The output end of the permanent magnet synchronous motor (241) is electrically connected to the battery (243) through the rectifier bridge (242) and the DC-DC converter (244) in sequence.

3. The vibration reduction and wave energy recovery storage system for floating wind turbine platforms according to claim 2, characterized in that, The power generation and energy storage mechanism (24) also includes an energy-consuming resistor (245), which is disposed between the DC-DC converter (244) and the battery (243).

4. The vibration reduction and wave energy recovery storage system for floating wind turbine platforms according to claim 2, characterized in that, The floating wind turbine platform (1) is also equipped with a multi-mode switching control system (5). The multi-mode switching control system (5) includes a status monitoring module (51) for real-time monitoring of the vibration amplitude of the floating wind turbine platform (1); a sea state monitoring module (52) for real-time monitoring of the effective wave height of the sea area where the floating wind turbine platform (1) is located; a battery management module (53) for real-time monitoring of the state of charge of the battery (243); and a judgment execution module (54) for communication connection with the status monitoring module (51), the sea state monitoring module (52), the battery management module (53), and the DC-DC converter (244), respectively, for adjusting the duty cycle of the DC-DC converter (244) to adjust the magnitude of the electromagnetic damping torque of the permanent magnet synchronous motor (241).

5. The vibration reduction and wave energy recovery storage system for floating wind turbine platforms according to claim 1, characterized in that, The guide rail (223) is a T-shaped rail. The bottom of the mass body (221) is provided with a groove (224) that matches the guide rail (223) along the length direction. The mass body (221) is slidably mounted on the guide rail (223) through the groove (224).

6. The vibration reduction and wave energy recovery storage system for a floating wind turbine platform according to claim 5, characterized in that, The groove (224) is provided with multiple rows of balls (225), which are arranged along the length of the groove (224). The groove (224) is slidably connected to the guide rail (223) through the balls (225).

7. The vibration reduction and wave energy recovery storage system for floating wind turbine platforms according to claim 1, characterized in that, Multiple wave energy conversion devices (2) are provided, and the multiple wave energy conversion devices (2) are arranged in a ring inside the floating wind turbine platform (1).

8. The vibration reduction and wave energy recovery storage system for floating wind turbine platforms according to claim 1, characterized in that, A wind turbine (4) is installed on the floating wind turbine platform (1), and the power generation and energy storage mechanism (24) is electrically connected to the energy-consuming equipment inside the wind turbine (4).

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