Fan tuned mass inerter damper structure and parameter design method

Abstract

The invention provides a fan tuned mass inerter damper structure and a parameter design method, and belongs to the field of ocean engineering vibration reduction. The structure comprises an engineering structure, an outer sleeve, a roller, an inner sleeve, an additional mass block, four damper spring units and four inerter system units. The engineering structure is fixed with the external sleeve, and a guide rail is formed between the engineering structure and the external sleeve; the additional mass block is arranged in the center of the inner sleeve, the four inerter system units are connected with the damper spring unit and located on the same plane, the other ends of the four inerter system units are connected with the inner wall of the inner sleeve, and each inerter system unit comprises an inerter system spring, a damping unit, a first inerter unit and a second inerter unit. According to the structure, translation-rotation conversion is achieved through the inerter unit, efficient inertia synergy is achieved with small physical mass, and the load of a draught fan is relieved; the four units are symmetrically arranged to ensure omnidirectional vibration suppression; the roller guide rail reduces friction and improves response sensitivity and energy consumption efficiency; according to the parameter design method, parameters are accurately optimized, and broadband vibration reduction performance and engineering reliability are guaranteed.

Description

Technical Field

[0001] This invention relates to the field of vibration reduction technology in marine engineering, specifically to a structure and parameter design method for a tuned mass inertial capacitive damper for wind turbines. Background Technology

[0002] With the rapid development of the global offshore wind power industry, the seismic safety of offshore wind turbines has become increasingly prominent. my country's coastal areas have complex geological conditions, with widespread distribution of areas containing deep overburden, soft soil seabeds, and shallow overburden geological zones. Wind farms located in the Southeast Coastal Seismic Belt and the Circum-Pacific Seismic Belt, in particular, have long faced the threat of seismic activity. To improve the seismic performance of wind turbines, tuned mass dampers (TMDs), as a mainstream energy-absorbing and vibration-damping technology, suppress vibrations at specific frequencies through the principle of mass-spring resonance, demonstrating significant application value in ensuring the safe operation of wind turbines.

[0003] However, traditional TMDs have significant limitations: insufficient frequency domain adaptability, as their narrowband tuning characteristics cannot cover the complex multi-frequency vibration conditions of offshore wind turbines; a single energy dissipation mechanism, mainly relying on viscous damping for energy dissipation, lacking an efficiency-enhancing mechanism, thus limiting control efficiency; and strong mass dependence, requiring large mass blocks to achieve the desired vibration reduction effect, significantly increasing structural load and cost. These shortcomings make it difficult for traditional TMDs to balance vibration reduction efficiency and engineering economy in complex marine environments, restricting their in-depth application in the offshore wind turbine field.

[0004] In summary, how to overcome the limitations of traditional TMDs (Transient Damping Devices) such as narrow bandwidth, single energy dissipation mechanism, and large mass dependence, and develop a new type of vibration reduction device that combines wideband adaptability, high energy dissipation efficiency, and lightweight characteristics has become a key technical challenge for improving the seismic safety of offshore wind turbines. Summary of the Invention

[0005] In view of this, it is necessary to provide a design method for the structure and parameters of a wind turbine tuned mass inertial capacitive damper, in order to solve the problems of high energy dissipation efficiency and insufficient lightweight of traditional tuned mass dampers for offshore wind turbines in the prior art.

[0006] To solve the above-mentioned technical problems, in a first aspect, the present invention provides a wind turbine tuned mass inertial-capacitive damper structure, including an engineering structure, an outer sleeve, rollers, an inner sleeve, an additional mass block, four damper spring units and four inertial-capacitive system units. The engineering structure and the outer sleeve are fixedly connected. A straight guide rail is formed between the outer sleeve and the inner sleeve. Several rollers are provided on the straight guide rail, and the rollers can roll on the straight guide rail. The additional mass block is located at the center of the inner sleeve. The four inertial-capacitance system units are located around the additional mass block and are connected to the additional mass block through corresponding damper spring units. The additional mass block, the four damper spring units, and the four inertial-capacitance system units are on the same horizontal plane. The other end of each inertial-capacitance system unit is connected to the inner wall of the inner sleeve.

[0007] In one possible implementation, each of the inertial capacitive system units includes an inertial capacitive system spring unit, an inertial capacitive system damping unit, a first inertial capacitive unit, and a second inertial capacitive unit. The inertial-capacitive system spring unit, inertial-capacitive system damping unit, and second inertial-capacitive unit are connected in parallel with the first inertial-capacitive unit; the inertial-capacitive system damping unit is connected in parallel with the second inertial-capacitive unit; one end of the inertial-capacitive system spring unit is connected to the damper spring unit, and the other end is connected to one end of the inertial-capacitive system damping unit and one end of the second inertial-capacitive unit; the other end of the inertial-capacitive system damping unit and the other end of the second inertial-capacitive unit are connected to the inner wall of the inner sleeve; one end of the first inertial-capacitive unit is connected to the damper spring unit, and the other end is connected to the inner wall of the inner sleeve.

[0008] In one possible implementation, the damper is a magnetorheological damping element, and the damping magnitude of the magnetorheological damping element is adjustable.

[0009] In one possible implementation, the damper spring unit has different stiffness, length, and deformation than the inertial capacitive system spring unit.

[0010] In one possible implementation, the apparent mass and moment of inertia of the first inertial unit and the second inertial unit are the same.

[0011] On the other hand, the present invention also provides a parameter design method for parameter design of the wind turbine tuned mass inertia-capacitive damper structure described in any of the above implementations, the method comprising: An inertial capacitive unit model is established for the inertial capacitive units that make up the first and second inertial capacitive units. Simulation experiments are then conducted using these models, and the simulation results are compared with theoretical results. This comparison verifies whether the implementation mechanism of the inertial capacitive unit model is equivalent. This verification confirms the reliability of the subsequent modeling of the main wind turbine structure. The main wind turbine structure includes the wind turbine tower, nacelle, and blades. The theoretical results are solved using the motion equations of the inertial capacitive unit model. Modal analysis is performed on the main structure of the wind turbine to obtain the natural frequencies and mode shapes of the main structure under external excitation. Based on the natural frequencies and mode shapes, the installation position of the damper in the wind turbine tower is determined. A model of the main wind turbine structure is established based on the installation position of the main wind turbine structure and the damper on the wind turbine tower, and the motion equation of the main wind turbine structure is established. Based on the motion equation of the main wind turbine structure, the transfer function is derived. The transfer function describes the relationship between the displacement response of the main wind turbine structure and the external excitation. An optimization model of the motion equations of the main structure of the wind turbine is established with the displacement response as the target. The range of values ​​for the parameters in the optimization model is set, and the optimal parameter combination within the range is obtained. Time history analysis is performed on the main structure model of the wind turbine based on the optimal parameter combination to verify its control effect under the target external excitation. If the displacement response meets the requirements, the optimal parameter combination is taken as the optimal solution. If it does not meet the requirements, the range of values ​​is adjusted and the time history analysis is performed again until a parameter combination that meets the displacement response requirements is obtained.

[0012] In one possible implementation, the step of establishing an inertial capacity unit model for the inertial capacity units constituting the first and second inertial capacity units, conducting simulation experiments using the inertial capacity unit model, comparing the simulation results with theoretical results, and verifying whether the implementation mechanism of the inertial capacity unit model is equivalent through the comparison includes: Based on the structure of the inertial capacitive element, an inertial capacitive element model is established in finite element software; Based on the structure of the inertial capacitive unit, the motion equation of the inertial capacitive unit is established; The finite element model of the inertial capacitive element is solved by solving the finite element model, and the theoretical solution of the motion equation of the inertial capacitive element is obtained by solving the differential equation theory. By comparing the finite element solution and the theoretical solution, the equivalence of the implementation mechanism of the inertial capacitive element model is verified based on the comparison. The equivalence refers to the consistency between the physical working principle of the inertial capacitive element model and the real inertial capacitive element in terms of mathematics and function.

[0013] In one possible implementation, the modal analysis of the main wind turbine structure to obtain its natural frequencies and mode shapes under external excitation, and the determination of the damper's installation position on the wind turbine tower based on the natural frequencies and mode shapes, includes: Modal analysis of the main structure of the wind turbine under external excitation is performed to obtain the corresponding natural frequencies and mode shapes. The natural frequencies are several natural frequencies of the main structure of the wind turbine under external excitation, and the several natural frequencies are divided into low-order natural frequencies and high-order natural frequencies. For the vibration modes at low natural frequencies, the damper is installed at the position with the largest amplitude in the wind turbine vibration mode at the low natural frequency.

[0014] In one possible implementation, a model of the main wind turbine structure is established based on the installation positions of the main wind turbine structure and the damper on the wind turbine tower, and the motion equations of the main wind turbine structure are established. Based on these motion equations, a transfer function is derived, which describes the relationship between the displacement response of the main wind turbine structure and external excitation, including: A model of the main structure of the wind turbine is established in finite element software based on the installation position of the main structure of the wind turbine and the damper in the wind turbine tower. The motion equations of the main wind turbine structure are established based on the installation positions of the main wind turbine structure and the damper in the wind turbine tower. By performing a Laplace transform on the motion equations of the main wind turbine structure, the frequency transfer function and acceleration transfer function of the main wind turbine structure are derived.

[0015] In one possible implementation, the optimization model of the wind turbine main structure motion equation is established with the displacement response as the target. The range of parameter values ​​in the optimization model is set, the optimal parameter combination within the range is obtained, and a time history analysis is performed on the wind turbine main structure model based on the optimal parameter combination to verify its control effect under the target external excitation. If the displacement response meets the requirements, the optimal parameter combination is taken as the optimal solution; if not, the range of values ​​is adjusted and the time history analysis is performed again until a parameter combination that meets the displacement response requirements is obtained, including: Based on the wind turbine structure motion equation, an optimization model is established with the goal of minimizing the displacement response of the main wind turbine structure. The parameters to be optimized in the optimization model include: the tuned mass ratio, inertial apparent mass ratio, first stiffness ratio, second stiffness ratio, and damping ratio of the damper. The range of values ​​for the parameters to be optimized is set based on the actual feasibility of the project and the limitations of the physical realization of the damper. A numerical optimization algorithm is used to search within the range of the given values ​​to obtain a set of optimal parameter combinations; Substitute the optimal parameter combination into the main structure model of the wind turbine, perform time history analysis under the target external excitation, and obtain the current displacement response; The current displacement response is compared with a preset displacement response threshold. If the current displacement response is lower than the preset displacement response threshold, the current optimal parameter combination is output as the optimal parameter solution, and the iteration terminates. If the current displacement response is not lower than the preset displacement response threshold, the value range of the parameter to be optimized is adjusted, and the time history analysis is performed iteratively until the displacement response is lower than the preset displacement response threshold and the optimal parameter solution is obtained.

[0016] The beneficial effects of this invention are as follows: The wind turbine tuned mass-capacitive damper structure provided by this invention includes an engineering structure, an outer sleeve, rollers, an inner sleeve, an additional mass block, four damper spring units, and four inertial-capacitive system units; the engineering structure and the outer sleeve are fixedly connected, wherein the fixed connection allows the vibration of the wind turbine tower to be directly transmitted to the outer sleeve of the damper without loss or delay, providing an efficient path for the input of vibration energy; a straight guide rail is formed between the outer sleeve and the inner sleeve, and several rollers are arranged on the straight guide rail, wherein the rollers-straight guide rail... The linear guide rails convert sliding friction into rolling friction, significantly reducing motion resistance. The additional mass block is located at the center of the inner sleeve, and the four inertial-capacitive system units are located around the additional mass block and connected to it through corresponding damper spring units. The additional mass block, the four damper spring units, and the four inertial-capacitive system units are on the same horizontal plane. The other end of each inertial-capacitive system unit is connected to the inner wall of the inner sleeve. The fact that the four inertial-capacitive system units are located around the additional mass block and on the same horizontal plane allows the damper to respond completely uniformly to horizontal vibrations in any direction. Each of the aforementioned inertial-capacitive system units includes an inertial-capacitive system spring unit, an inertial-capacitive system damping unit, a first inertial-capacitive unit, and a second inertial-capacitive unit. The inertial-capacitive system spring unit, the inertial-capacitive system damping unit, and the second inertial-capacitive unit are connected in parallel with the first inertial-capacitive unit, and the inertial-capacitive system damping unit is connected in parallel with the second inertial-capacitive unit. One end of the inertial-capacitive system spring unit is connected to the damper spring unit, and the other end is connected to one end of the inertial-capacitive system damping unit and one end of the second inertial-capacitive unit. The other end of the inertial-capacitive system damping unit and the other end of the second inertial-capacitive unit are connected to the inner wall of the inner sleeve. The first inertial-capacitive unit is connected to the damper spring unit, and the other end is connected to the inner wall of the inner sleeve. The inertial-capacitive unit can convert linear motion into rotational motion and amplify the moment of inertia through the internal flywheel, generating an apparent mass far exceeding its own physical weight. This significantly reduces the damper's requirement for additional mass blocks and greatly reduces the load on the wind turbine structure.

[0017] The above description is merely an overview of the technical solution of the present invention. In order to better understand the technical means of the present invention and to implement it in accordance with the contents of the specification, the preferred embodiments of the present invention are described in detail below. Attached Figure Description

[0018] 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.

[0019] Figure 1 A schematic diagram of an embodiment of the wind turbine tuned mass inertia-capacitive damper structure provided by the present invention; Figure 2 A schematic diagram of an embodiment of the inertial capacitive system unit structure provided by the present invention; Figure 3 A schematic flowchart illustrating an embodiment of the parameter design method provided by the present invention; Figure 4 Provided by the present invention Figure 3 A schematic diagram of an embodiment of S301; Figure 5 A schematic diagram of an embodiment of the tuned viscous mass damper provided by the present invention; Figure 6 A schematic diagram of an embodiment of the inertial capacity unit model provided by the present invention; Figure 7 A schematic diagram illustrating an embodiment comparing simulation results and theoretical results of the inertial capacity unit model provided by the present invention; Figure 8 Provided by the present invention Figure 3 A schematic diagram of an embodiment of S302; Figure 9 Provided by the present invention Figure 3 A schematic diagram of an embodiment of S303; Figure 10 Provided by the present invention Figure 3 A schematic diagram of an embodiment of S304; Figure 11 A schematic diagram of an embodiment of the structural parameter design for the wind turbine tuned mass inertia-capacitive damper provided by the present invention. Detailed Implementation

[0020] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of them. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative effort are within the scope of protection of the present invention.

[0021] In the description of the embodiments of the present invention, unless otherwise stated, "multiple" means two or more. "And / or" describes the relationship between related objects, indicating that there can be three relationships. For example, A and / or B can represent three situations: A exists alone, A and B exist simultaneously, and B exists alone.

[0022] The terms "first," "second," etc., used in the embodiments of this invention are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a technical feature defined with "first" or "second" may explicitly or implicitly include at least one of that feature.

[0023] In this document, the term "embodiment" means that a particular feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of the invention. The appearance of this phrase in various places throughout the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment mutually exclusive with other embodiments. It will be explicitly and implicitly understood by those skilled in the art that the embodiments described herein can be combined with other embodiments.

[0024] Before demonstrating the embodiments, the following terms will be explained.

[0025] Engineering structure: refers to the wind turbine tower itself or the mounting base rigidly connected to the tower. It is the mounting foundation for the damper and the vibration transmission carrier. The vibration of the wind turbine itself is transmitted to the damper through it, and the control force generated by the damper also reacts to the wind turbine structure through it.

[0026] Outer and inner sleeves: the core frame structure of the damper. The outer sleeve is fixedly connected to the engineering structure, serving as the outer shell. The inner sleeve, through rollers, forms a relatively sliding connection with the outer sleeve, acting as the mounting platform for internal moving parts. Together, they constitute the basic skeleton and motion guiding mechanism of the damper.

[0027] Roller and linear guide: This is a low-friction motion mechanism. It consists of rollers positioned between the outer and inner sleeves and their running track (i.e., linear guide). Its core function is to allow the inner sleeve to slide relative to the outer sleeve with almost no friction, transforming traditional sliding friction into rolling friction, which greatly improves the damper's starting sensitivity and energy transfer efficiency.

[0028] Additional mass block: The core component in the damper that provides inertial mass. It is typically a heavy metal block, and the ratio of its mass to the main structural mass (i.e., the tuned mass ratio) is a key optimization parameter. The inertial force it generates during vibration is one of the main sources of damping force.

[0029] Damper spring unit: An elastic element connecting the added mass block and the inertial-capacitive system unit. Its main function is to store energy and provide restoring force to the added mass block; its stiffness is one of the key parameters determining the system's tuning frequency.

[0030] Inertial-capacitive system unit: A flywheel or gear generates a huge moment of inertia, thereby effectively amplifying its inertial effect (i.e., producing apparent mass). It can achieve the effect of inertial force with a very small physical weight, which traditionally requires a large mass.

[0031] Inertial-capacitive system spring unit and inertial-capacitive system damping unit: The inertial-capacitive system spring unit is an elastic element inside the inertial-capacitive system, connected in parallel with the inertial-capacitive unit, and together they determine the dynamic characteristics of the subsystem. The inertial-capacitive system damping unit is an energy-consuming intelligent material damper, whose damping value can be adjusted in real time, continuously, and reversibly through an external magnetic field, thereby achieving adaptive control.

[0032] First and second inertial units: These refer to two inertial units connected in parallel within the inertial system. Both have the same apparent mass and moment of inertia, meaning that their dynamic characteristics must be completely identical during design and manufacturing to ensure the system's symmetry and stability, and to avoid unbalanced forces caused by parameter differences.

[0033] Apparent mass: The core performance parameter of the inertial capacitance unit. It is not the actual gravitational mass, but refers to the equivalent inertial effect exhibited by the inertial capacitance unit through its internal "translational-rotational" conversion mechanism. Its value is usually much greater than its own physical mass, achieving lightweight efficiency and is the key to solving the bottleneck of "mass accumulation" in traditional dampers.

[0034] Modal analysis: a structural dynamics analysis method. It is used to determine the inherent dynamic characteristics of the main structure of a wind turbine (tower, nacelle, blades), including its natural frequencies (frequencies at which the structure tends to vibrate) and mode shapes (vibration patterns at the corresponding frequencies).

[0035] Transfer function: a core concept in control system theory. In this paper, it specifically refers to the frequency transfer function, which quantitatively describes the mathematical relationship between the wind turbine structure under external excitation (input) and the resulting displacement or acceleration response (output). Derived through the Laplace transform, it forms the theoretical basis for parametric optimization design.

[0036] Time history analysis: an advanced dynamic response analysis method. It involves inputting a real, time-varying external excitation (such as seismic wave or wind load time history) into the structural model and solving for the detailed response (such as displacement and acceleration) of the structure throughout the entire time history by step-by-step integration.

[0037] Tuned mass ratio, apparent inertial-capacitive mass ratio, stiffness ratio, and damping ratio: all are dimensionless key design parameters. The tuned mass ratio is the ratio of the mass of the added mass block to the mass of the main structure; the apparent inertial-capacitive mass ratio is the ratio of the apparent inertial-capacitive mass to the mass of the main structure; the stiffness ratio is the ratio of the damper spring stiffness or the spring stiffness of the inertial-capacitive system to the stiffness of the main structure; and the damping ratio is a dimensionless parameter characterizing the magnitude of damping.

[0038] This invention provides a structure and parameter design method for a wind turbine tuned mass inertia capacitive damper, which will be described in detail below.

[0039] Figure 1 This is a schematic diagram of an embodiment of the wind turbine tuned mass inertia-capacitive damper structure provided by the present invention, as shown below. Figure 1 As shown, the structure of the wind turbine tuned mass inertial-capacitive damper includes an engineering structure 1, an outer sleeve 2, a roller 3, an inner sleeve 4, an additional mass block 5, four damper spring units 6, and four inertial-capacitive system units 7. The engineering structure 1 and the outer sleeve 2 are fixedly connected. A straight guide rail is formed between the outer sleeve 2 and the inner sleeve 4. Several rollers 3 are provided on the straight guide rail and can roll on the straight guide rail. The additional mass block 5 is located at the center of the inner sleeve 4. Four inertial capacitive system units 7 are located around the additional mass block 5 and are connected to the additional mass block 5 through corresponding damper spring units 6. The additional mass block 5, the four damper spring units 6 and the four inertial capacitive system units 7 are on the same horizontal plane. The other end of each inertial capacitive system unit 7 is connected to the inner wall of the inner sleeve 4.

[0040] In some embodiments of the present invention, each inertial capacitive system unit 7 includes an inertial capacitive system spring unit 71, an inertial capacitive system damping unit 72, a first inertial capacitive unit 73, and a second inertial capacitive unit 74. The inertial-capacitive system spring unit 71, the inertial-capacitive system damping unit 72, and the second inertial-capacitive unit 74 are connected in parallel with the first inertial-capacitive unit 73, and the inertial-capacitive system damping unit 72 is connected in parallel with the second inertial-capacitive unit 74; one end of the inertial-capacitive system spring unit 71 is connected to the damper spring unit 6, and the other end is connected to one end of the inertial-capacitive system damping unit 72 and one end of the second inertial-capacitive unit 74; the other end of the inertial-capacitive system damping unit 72 and the other end of the second inertial-capacitive unit 74 are connected to the inner wall of the inner sleeve 4; one end of the first inertial-capacitive unit 73 is connected to the damper spring unit 6, and the other end is connected to the inner wall of the inner sleeve 4.

[0041] In some embodiments of the present invention, a schematic diagram of the inertial capacitive system unit structure is shown below. Figure 2 As shown.

[0042] In some embodiments of the present invention, the damper is a magnetorheological damping element, and the damping magnitude of the magnetorheological damping element is adjustable.

[0043] In some embodiments of the present invention, the damper spring unit 6 has different stiffness, length and deformation than the inertial capacitive system spring unit 71.

[0044] In some embodiments of the present invention, the apparent mass and moment of inertia of the first inertial capacity unit 73 and the second inertial capacity unit 74 are the same.

[0045] It should be noted that the fixed connection allows the vibration of the wind turbine tower to be directly transmitted to the outer sleeve of the damper without loss or delay; the roller-linear guide rail combination converts sliding friction into rolling friction, which can significantly reduce motion resistance; the four inertial capacitive system units are located around the additional mass block and are on the same horizontal plane, which allows the damper to make a completely consistent response to horizontal vibrations in any direction; the inertial capacitive unit can convert linear motion into rotational motion, and through the internal flywheel, it amplifies the moment of inertia to generate an apparent mass far exceeding its own physical weight, which significantly reduces the damper's demand on the additional mass block and greatly reduces the load on the wind turbine structure.

[0046] The innovative design of the wind turbine tuned mass inertial-capacitive damper structure in this invention provides the physical basis and possibility for achieving efficient vibration reduction. However, to ensure it remains in optimal working condition under complex and variable offshore wind loads and wave excitation, a precise and scientific parameter design method is required, such as... Figure 3 As shown, this embodiment of the invention also provides a parameter design method for designing the parameters of a wind turbine tuned mass inertia-capacitive damper structure. The method includes: S301. Establish inertial capacitive unit models for the inertial capacitive units that make up the first inertial capacitive unit 73 and the second inertial capacitive unit 74. Conduct simulation experiments using the inertial capacitive unit models, and compare the simulation results with the theoretical results to verify whether the implementation mechanism of the inertial capacitive unit models is equivalent. Verify the reliability of the subsequent modeling of the main wind turbine structure. The main wind turbine structure includes the wind turbine tower, wind turbine nacelle, and wind turbine blades. Solve the theoretical results using the motion equations of the inertial capacitive unit models. S302. Perform modal analysis on the main structure of the wind turbine to obtain the natural frequency and mode shape of the main structure of the wind turbine under external excitation, and determine the installation position of the damper in the wind turbine tower based on the natural frequency and mode shape. S303. Establish a model of the main structure of the wind turbine based on the installation positions of the main structure and damper in the wind turbine tower, and establish the motion equation of the main structure of the wind turbine. Derive the transfer function based on the motion equation of the main structure of the wind turbine. The transfer function describes the relationship between the displacement response of the main structure of the wind turbine and the external excitation. S304. Establish an optimization model of the motion equation of the main structure of the wind turbine with displacement response as the target, set the range of parameter values ​​in the optimization model, obtain the optimal parameter combination within the range, and perform time history analysis on the main structure model of the wind turbine based on the optimal parameter combination to verify its control effect under the target external excitation. If the displacement response meets the requirements, the optimal parameter combination is taken as the optimal solution. If it does not meet the requirements, adjust the range of values ​​and re-perform the time history analysis until the parameter combination that meets the displacement response requirements is obtained.

[0047] In some embodiments of the present invention, such as Figure 4 As shown, step S301 includes: S401. Establish an inertial capacitive element model in finite element software based on the structure of inertial capacitive elements; S402. Establish the motion equation of the inertial capacitive element based on the structure of the inertial capacitive element; S403. Solve the inertial-capacitive element model using the finite element model to obtain the finite element solution of the inertial-capacitive element model, and solve the motion equations of the inertial-capacitive element using differential equation theory to obtain the theoretical solution of the motion equations of the inertial-capacitive element. S404. By comparing the finite element solution and the theoretical solution, the equivalence of the realization mechanism of the inertial capacitive element model is verified based on the comparison. Equivalence means that the physical working principle of the inertial capacitive element model and the real inertial capacitive element are consistent in mathematics and function.

[0048] It should be noted that, unlike traditional mass elements, inertial capacitance is a two-endpoint element that is related to the relative acceleration between the two ends. Due to the special nature of its internal structure, this invention takes into account its internal structure and the "translational-rotational" conversion mechanism.

[0049] In some embodiments of the present invention, a tuned viscous mass damper (TVMD) is taken as an example. Figure 5 If the inertial capacity unit If we consider it as a simple mass component, then the following three problems exist: 1) The magnitude of the provided inertial force cannot be correlated with the acceleration at both ends of the inertial capacity; 2) The provided inertial force is not achieved through rotational inertia, meaning that inertial enhancement cannot be achieved. 3) If the inertial-compression element at point B is considered a simple mass block, and A and B, and B and C are connected with infinite stiffness, then no relative displacement can occur between A and C, and consequently the damper... The inability to function directly contradicts the working mechanism of the inertial capacity unit's energy consumption efficiency enhancement.

[0050] To solve the above problems, the inertial-capacitive unit was modified in the ABAQUS software. The relationship between points A, B, and C is handled as follows: 1) For inertial compressive units Imparting rotational inertia Ignoring the mass of the inertial capacity unit itself, its gravitational mass is assigned a value of 0; 2) Assign translational degrees of freedom (degree of freedom 2) to points A and C in the Y direction, and rotational degrees of freedom (degree of freedom 6) to point B in the Z direction, and establish the constraints as shown in the following formula to link the rotational degrees of freedom of the component at point B with the translational degrees of freedom at points A and C, as shown in Formula 1. (1) In the formula, the subscripts A, B, and C represent point numbers, while the superscripts represent degree of freedom numbers.

[0051] 3) Attach TVMD to a single-degree-of-freedom structure and input a simple harmonic wave to excite the structure's vibration at the bottom. The equation of motion for the structure is shown in Equation 2-3: (2) (3) In the formula, , and These are the mass, damping, and stiffness of the main structure, respectively. For the damping of the inertial-capacitive system, For the stiffness of the inertial-compressive system, For the apparent quality of the inertial capacitive system, , and These represent the distance, velocity, and acceleration of the inertial capacitive system being pulled apart, respectively. , and These are the displacement, velocity, and acceleration of the main structure, respectively. The bottom input is a simple harmonic excitation.

[0052] In some embodiments of the present invention, ABAQUS software is used to establish inertial capacitance unit models, such as... Figure 6 As shown, ， ， Three points constitute an inertial capacitive system. Point and Set springs between points and assign them stiffness , The point is considered as a simple harmonic wave input to the ground that excites structural vibration. Dot and The floor was just touched. (The rest of the text appears to be incomplete and unrelated.) Dot and The translational degrees of freedom of a point are transformed into The rotational degrees of freedom of the point are constrained as shown in Equation 4. The moment of inertia is assigned to a point for calculation.

[0053] (4) In the formula, the subscripts 3, 2, and 1 represent point numbers, while the superscripts represent degree-of-freedom numbers. The motion equations in equation 2-3 were calculated using MATLAB differential equation theory. A comparison was then made between the MATLAB differential equation theoretical solution and the results obtained using the ABAQUS finite element model. Figure 7 The results show that the results are consistent (there are small, fixed differences between each peak point, but the values ​​are stable and do not change with frequency, so they are judged to be stable calculation errors), which verifies the equivalence of the ABAQUS implementation mechanism of this inertial capacitive unit. That is, it is feasible and reliable to use the inertial capacitive unit in TVMD in subsequent wind turbine main structure modeling, modal analysis and parameter optimization.

[0054] In some embodiments of the present invention, such as Figure 8 As shown, step S302 includes: S801. Perform modal analysis on the main structure of the wind turbine under external excitation to obtain the corresponding natural frequencies and mode shapes. The natural frequencies are several natural frequencies of the main structure of the wind turbine under external excitation. The several natural frequencies are divided into low-order natural frequencies and high-order natural frequencies. S802. For the vibration mode at the low-order natural frequency, select the position where the damper has the largest amplitude in the vibration mode of the wind turbine at the low-order natural frequency.

[0055] It's important to note that natural frequencies are inherent physical properties of a structure, determined by its mass and stiffness distribution. Like the "natural pitch" of an object, each structure has several specific natural frequencies (such as first, second, etc.). Resonance occurs when the dominant frequency of external excitation approaches or coincides with one of the structure's natural frequencies. In this case, the structure absorbs a large amount of energy, causing a sharp amplification of the amplitude (vibration amplitude), potentially leading to rapid structural fatigue or even failure. Therefore, the primary goal of damper installation is to suppress excessive vibrations caused by resonance. The first step in the analysis is to identify the lower-order natural frequencies of the wind turbine structure (especially the tower) through dynamic analysis and examine whether these frequency components are included in the external environmental loads (such as local wind and wave spectra). If there is a risk of overlap, vibration control must be implemented targeting that frequency.

[0056] It should be noted that modal analysis is typically performed on the main structure at low-order frequencies. Since the total vibration of a structure during dynamic response can be considered as the superposition of vibrations of various modes, and low-order frequencies (especially the first and second orders) usually account for the majority of the total vibration energy of the system, controlling the vibration of low-order modes addresses the main problem and solves most of the vibration issues. The response amplitudes of higher-order modes are usually very small, and their impact on structural safety and comfort is far less than that of low-order modes. Therefore, investing limited design and manufacturing resources (such as the size and cost of dampers) in controlling the first and second-order modes offers the best cost-effectiveness.

[0057] In some embodiments of the present invention, the main structure of the wind turbine can be divided into three common structures: tripod-type foundation wind turbine main structure, gravity-type foundation wind turbine main structure, and jacket-type foundation wind turbine main structure. Modal analysis was performed on these three types of wind turbine main structures, and the experimental results show that: preferably, the wind turbine tuned mass inertial-capacitive damper is installed at the top of the wind turbine tower.

[0058] In some embodiments of the present invention, such as Figure 9 As shown, step S303 includes: S901. Based on the installation positions of the main wind turbine structure and dampers in the wind turbine tower, establish a model of the main wind turbine structure in finite element software. S902. Establish the motion equations of the main wind turbine structure based on the installation positions of the main wind turbine structure and dampers in the wind turbine tower. S903. Perform a Laplace transform on the motion equations of the main structure of the wind turbine to derive the frequency transfer function and acceleration transfer function of the main structure of the wind turbine.

[0059] In some embodiments of the present invention, the motion equation of the main structure of the wind turbine is shown in Equation 5: (5) In the formula, 、 、 These represent the displacement, velocity, and acceleration responses of the wind turbine tower, respectively. 、 、 These represent the displacement, velocity, and acceleration responses of the actual mass of the damper, respectively. 、 、 This represents the displacement, velocity, and acceleration response of the inertial-compressive element; This represents the normalized generalized external excitation. To simplify the motion equations of the main wind turbine structure, dimensionless parameters are defined as shown in Equation 6-12: (6) (7) (8) (9) (10) (11) (12) In the formula, Additional mass of the damper m t With the quality of the main structure m The ratio; Apparent quality of inertial compressive unit m in With the quality of the main structure m The ratio; ; Indicates the stiffness of the tuning spring k t and main structural stiffness k stiffness ratio; Indicates the stiffness of the spring element in an inertial-capacitive system k in and main structural stiffness k stiffness ratio; The inherent damping ratio of the main structure; This is the nominal damping ratio of the inertial capacitive system unit.

[0060] Based on the above dimensionless parameters, the equation of motion for the single-degree-of-freedom system of the inertial-compressive system with an added tuned mass damper can be expressed as Equation 13: (13) The matrix form of Equation 13 is shown in Equations 14-18: (14) (15) (16) (17) (18) Applying a Laplace transform to Equation 13, it can be rewritten as shown in the following equation regarding... 、 、 The system of equations, where 、 、 The ones are respectively 、 、 Laplace transform, for The Laplace transform. After the Laplace transform, the resulting system of equations is shown in Equation 19.

[0061] (19) It should be noted that the fundamental purpose of performing the Laplace transform is to transform a differential equation problem that is difficult to solve directly in the time domain into an algebraic equation problem that is easy to handle in the complex frequency domain.

[0062] After derivation using Equation 19, the frequency transfer function of the main structure displacement is obtained. and acceleration transfer function It can be obtained from Equation 20: (20) In the formula, It is a complex number used to describe a purely oscillating signal and is central to frequency domain analysis. w and Both represent angular frequency (the unit is rad / s). s Compare More generally, it is a complex frequency variable, which can be represented as s = σ + iw , actual part σ The imaginary part represents the rate of increase or decrease of a signal. This represents the oscillation frequency of the signal.

[0063] In some embodiments of the present invention, such as Figure 10 As shown, step S304 includes: S1001. Based on the wind turbine structure motion equation, with the minimization of the displacement response of the main wind turbine structure as the optimization objective, an optimization model is established. The parameters to be optimized in the optimization model include: the tuned mass ratio, inertial capacitance apparent mass ratio, first stiffness ratio, second stiffness ratio, and damping ratio of the damper. It should be noted that the tuning mass ratio is the ratio of the additional tuning mass of the damper to the mass of the main structure of the wind turbine; the apparent mass ratio is the ratio of the apparent mass of the inertial capacitance unit to the mass of the main structure; the first stiffness ratio is the stiffness ratio of the damping spring unit to the main structure of the wind turbine; the second stiffness ratio is the stiffness ratio of the spring unit of the inertial capacitance system to the main structure of the wind turbine; and the damping ratio is the nominal damping ratio of the damping unit of the inertial capacitance system.

[0064] S1002. Set the value range for the parameters to be optimized based on the actual feasibility of the project and the limitations of the physical realization of the damper. S1003. Use a numerical optimization algorithm to search within the value range to obtain a set of optimal parameter combinations; S1004. Substitute the optimal parameter combination into the main structure model of the wind turbine, perform time history analysis under the target external excitation, and obtain the current displacement response. S1005. Compare the current displacement response with the preset displacement response threshold. If the current displacement response is lower than the preset displacement response threshold, output the current optimal parameter combination as the optimal parameter solution and terminate the iteration. If the current displacement response is not lower than the preset displacement response threshold, adjust the value range of the parameters to be optimized and iterate the time history analysis until the displacement response is lower than the preset displacement response threshold and the optimal parameter solution is obtained.

[0065] In some embodiments of the present invention, the focus is on the tuning quality ratio. This reflects the magnitude of the added tuning quality. Tuning quality ratio To add tuning quality With the main structure quality of the wind turbine The ratio. In the motion equations of the main structure of the wind turbine, the inertial volume element has apparent mass. The apparent mass is much greater than the gravitational mass of the inertial voice unit. The gravitational mass of the inertial voice unit is negligible compared to the overall structural mass and apparent mass. Therefore, the mass of the vibration control system can be considered only for the tuning mass. For vibration damping control of stationary offshore wind turbines, the displacement response of the main structure under external excitation is taken as the primary factor. To minimize the optimization target, the tuning mass ratio of the tuned mass inertial capacitive damper in the main structure of the wind turbine is first determined.

[0066] In some embodiments of the present invention, by utilizing the apparent mass enhancement effect of the inertial capacitive unit, the wind turbine tuned mass inertial capacitive damper can effectively control the structural dynamic response while reducing the required additional tuned mass. To fully leverage the control advantages of the inertial capacitive system, the method for designing the wind turbine tuned mass inertial capacitive damper parameters in this section involves optimizing the design to minimize the additional mass while meeting defined structural performance requirements. The optimized design expressions for the wind turbine tuned mass inertial capacitive damper parameters are shown in Figures 21-25: (twenty one) (twenty two) (twenty three) (twenty four) (25) In the formula, the subscript min Do not specify the lower limit of the parameter values ​​for each component of the wind turbine tuned mass inertia capacitive damper, subscript ， Subscript max, lim The upper limit of the parameter values ​​for each component of the wind turbine tuned mass inertia capacitive damper is as follows: Figure 11 As shown.

[0067] Solve the optimization design equations to obtain the tuning mass ratio. The parameter values ​​are used to derive and determine the... The ratio of the apparent mass of the inertial unit to the mass of the main structure. The nominal damping ratio of the inertial-capacitive system unit; This represents the ratio of the tuning spring frequency to the stiffness of the main structure. The range of parameters representing the stiffness ratio of the unit springs to the main structure of the inertial-capacitive system.

[0068] In some embodiments of the present invention, in the optimization of the parameters of the tuned mass inertial-capacitive damper, the mean square displacement response at the top of the tower is used. To optimize the objective and write its function expression, a genetic algorithm was then used to optimize the four parameters ( , , , The algorithm was optimized using the following parameters: maximum number of generations: 150, population size: 900, crossover probability: 0.8, mutation probability: 0.05, newborn population ratio: 0.25, and computational precision: 1× .

[0069] In some embodiments of the present invention, the tuning mass ratio is studied for tripod-type foundation wind turbine main structures, gravity-type foundation wind turbine main structures, and jacket-type foundation wind turbine main structures. =0.02 and tuning quality ratio =0.05 for two operating conditions. The optimal parameters for each group in the parameter optimization of the tuned mass inertial capacitive damper are shown in Table 1.

[0070] Table 1: Optimal parameters for each group in the parameter optimization of tuned mass-inertial-capacitive dampers

[0071] The above provides a detailed description of the structure and parameter design method of the wind turbine tuned mass inertia capacitive damper provided by the present invention. Specific examples have been used to illustrate the principle and implementation of the present invention. The description of the above embodiments is only for the purpose of helping to understand the method and core idea of ​​the present invention. At the same time, for those skilled in the art, there will be changes in the specific implementation and application scope based on the idea of ​​the present invention. Therefore, the content of this specification should not be construed as a limitation of the present invention.

Claims

1. A fan tuned mass inerter damper structure, characterized by, The engineering structure, the outer sleeve, the plurality of rollers, the inner sleeve, the additional mass block, the four damper spring units and the four inertial mass system units; The engineering structure and the outer sleeve are fixedly connected, a linear guide rail is formed between the outer sleeve and the inner sleeve, a plurality of rollers are arranged on the linear guide rail, and the plurality of rollers can roll on the linear guide rail; the additional mass block is located at the center of the inner sleeve, the four inertial mass system units are located around the additional mass block and are connected with the additional mass block through one-to-one corresponding damper spring units, the additional mass block, the four damper spring units and the four inertial mass system units are located on the same horizontal plane, and the other end of each inertial mass system unit is connected with the inner wall of the inner sleeve.

2. The fan tuned mass inerter damper structure of claim 1, wherein, Each inertial mass system unit comprises an inertial mass system spring unit, an inertial mass system damping unit, a first inertial mass unit and a second inertial mass unit; The inertial mass system spring unit, the inertial mass system damping unit and the second inertial mass unit are connected in parallel with the first inertial mass unit, the inertial mass system damping unit is connected in parallel with the second inertial mass unit, one end of the inertial mass system spring unit is connected with the damper spring unit, the other end of the inertial mass system spring unit is connected with one end of the inertial mass system damping unit and one end of the second inertial mass unit, the other end of the inertial mass system damping unit and the other end of the second inertial mass unit are connected with the inner wall of the inner sleeve, and one end of the first inertial mass unit is connected with the damper spring unit, and the other end of the first inertial mass unit is connected with the inner wall of the inner sleeve.

3. The fan-tuned mass-inerter damper structure of claim 1, wherein, The damper is a magneto-rheological damper element, and the damping size of the magneto-rheological damper element is adjustable.

4. The fan-tuned mass-inerter damper structure of claim 1, wherein, The stiffness, length and deformation of the damper spring unit and the inertial mass system spring unit are different.

5. The fan-tuned mass-inerter damper structure of claim 1, wherein, The apparent mass and the moment of inertia of the first inertial mass unit and the second inertial mass unit are the same.

6. A parameter design method for the fan tuned mass inerter damper structure according to any one of claims 1 to 4, characterized in that, The method comprises: An inertial mass unit model is established for the inertial mass units constituting the first inertial mass unit and the second inertial mass unit, a simulation experiment is performed by using the inertial mass unit model, the simulation experiment result is compared with a theoretical result, and whether the implementation mechanism of the inertial mass unit model is equivalent is verified through the comparison; the verification is used to confirm the reliability of subsequent modeling of a fan main structure; the fan main structure comprises a fan tower, a fan cabin and fan blades; the theoretical result is solved by a motion equation of the inertial mass unit model; Modal analysis is performed on the fan main structure to obtain the natural frequency and the mode shape of the fan main structure under external excitation, and the installation position of the damper in the fan tower is determined based on the natural frequency and the mode shape; A fan main structure model is established according to the fan main structure and the installation position of the damper in the fan tower, a fan main structure motion equation is established, a transfer function is derived based on the fan main structure motion equation, and the transfer function describes the relationship between the displacement response of the fan main structure and external excitation. An optimization model of a fan main structure motion equation is established with the displacement response as a target, a value range of parameters in the optimization model is set, an optimal parameter combination in the value range is obtained, a time history analysis is performed on the fan main structure model based on the optimal parameter combination, and a control effect of the fan main structure under a target external excitation is verified; if the displacement response meets a requirement, the optimal parameter combination is taken as an optimal solution, and if the displacement response does not meet the requirement, the value range is adjusted and the time history analysis is performed again until a parameter combination meeting the displacement response requirement is obtained.

7. The parametric design method of claim 6, wherein, The inertance unit model is established for the inertance units constituting the first and second inertance units, simulation experiments are performed by using the inertance unit model, and a comparison is made between simulation experiment results and theoretical results to verify whether an implementation mechanism of the inertance unit model is equivalent, including: An inertance unit model is established in a finite element software based on a structure of the inertance unit; An inertance unit motion equation is established based on the structure of the inertance unit; An inertance unit model finite element solution is obtained by performing finite element model solving on the inertance unit model, and an inertance unit motion equation theoretical solution is obtained by performing differential equation theoretical solving on the inertance unit motion equation; The finite element solution and the theoretical solution are compared, and the equivalence of the implementation mechanism of the inertance unit model is verified based on the comparison, and the equivalence refers to that the physical working principle of the inertance unit model and a real inertance unit are consistent in mathematics and functions.

8. The parametric design method of claim 6, wherein, Modal analysis is performed on the fan main structure to obtain inherent frequencies and vibration modes of the fan main structure under external excitation, and the installation position of the damper in the fan tower is determined based on the inherent frequencies and vibration modes, including: Modal analysis is performed on the fan main structure under external excitation to obtain corresponding inherent frequencies and vibration modes, the inherent frequencies are several inherent frequencies of the fan main structure under external excitation, and the several inherent frequencies include low-order inherent frequencies and high-order inherent frequencies; For the vibration mode under the low-order inherent frequencies, the damper is installed at a position with the largest amplitude in the vibration mode under the low-order inherent frequencies.

9. The parametric design method of claim 6, wherein, A fan main structure model is established based on the installation position of the fan main structure and the damper in the fan tower, a fan main structure motion equation is established, a transfer function is derived based on the fan main structure motion equation, and the transfer function describes a relationship between a displacement response of the fan main structure and external excitation, including: The fan main structure model is established in a finite element software based on the installation position of the fan main structure and the damper in the fan tower; The fan main structure motion equation is established based on the installation position of the fan main structure and the damper in the fan tower; The fan main structure motion equation is subjected to Laplace transformation, and a frequency transfer function and an acceleration transfer function of the fan main structure are derived.

10. The parametric design method of claim 6, wherein, The optimization model of the fan main structure motion equation is established based on the displacement response, the value range of the parameters in the optimization model is set, the optimal parameter combination in the value range is obtained, the time history analysis is performed on the fan main structure model based on the optimal parameter combination, and the control effect under the target external excitation is verified; if the displacement response meets the requirements, the optimal parameter combination is taken as the optimal solution, and if the displacement response does not meet the requirements, the value range is adjusted and the time history analysis is performed again until the parameter combination meeting the displacement response requirements is obtained, comprising: Based on the fan structure motion equation, an optimization model is established to minimize the displacement response of the fan main structure, and the parameters to be optimized in the optimization model include: the tuned mass ratio of the damper, the apparent mass ratio of the inerter, the first stiffness ratio, the second stiffness ratio and the damping ratio; According to the engineering practical feasibility and the limitation of physical realization of the damper, the value range of the parameters to be optimized is set; A numerical optimization algorithm is used to search in the value range to obtain an optimal parameter combination; The optimal parameter combination is substituted into the fan main structure model, and the time history analysis is performed under the target external excitation to obtain the current displacement response; The current displacement response is compared with the preset displacement response threshold value, if the current displacement response is lower than the preset displacement response threshold value, the current optimal parameter combination is taken as the optimal parameter solution, the iteration is terminated, and if the current displacement response is not lower than the preset displacement response threshold value, the value range of the parameters to be optimized is adjusted, the time history analysis is iteratively performed until the displacement response is lower than the preset displacement response threshold value and the optimal parameter solution is obtained.

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