Tuned mass damper parameter design method and device for wind turbine blade hoisting transverse vibration suppression

Abstract

The invention discloses a tuning mass damper parameter design method and device for wind turbine blade hoisting transverse vibration suppression, and relates to the technical field of wind power hoisting. The tuning mass damper parameter design method comprises the steps that a blade hoisting hoisting rope and a blade and clamp assembly of a wind turbine blade are equivalent to a simple pendulum model and then equivalent to a first line spring model; a blade hoisting traction rope is equivalent to a second line spring model, and a multi-line spring motion system is constructed in combination with the first line spring model; constructing a transverse swing kinetic equation of the multi-line spring motion system, and solving and determining a transverse swing inherent frequency; and the mass ratio of the tuned mass damper to the blade and the clamp assembly in the multi-line spring movement system is obtained, and the optimal spring coefficient and the optimal damping of the tuned mass damper are determined by combining the mass of the blade and the clamp assembly and the transverse swing inherent frequency. Based on the scheme, the tuned mass damper obtained through design is installed on the wind turbine blade, and vibration of the structure can be more comprehensively restrained in the hoisting transverse vibration of the wind turbine blade.

Description

Technical Field

[0001] The present invention relates to the technical field of wind power hoisting, and particularly relates to a method and device for designing parameters of a tuned mass damper for suppressing lateral vibration during the hoisting of a wind turbine blade. Background Art

[0002] The blades of a wind turbine are usually installed by split hoisting. During the hoisting process of the wind turbine blade, due to the influence of various factors such as wind load and gravity, lateral vibration is likely to occur. This vibration not only affects the safety and accuracy of hoisting, but also easily causes fatigue damage to the blade, and even leads to more serious structural damage. Therefore, suppressing the lateral vibration during the hoisting of the wind turbine blade is an important link to ensure the safe operation of the wind power generation system.

[0003] Currently, during the single-blade hoisting process, a tuned mass damper (TMD) is mainly installed on the wind turbine blade to suppress the vibration of the blade. However, when setting the parameters of the installed tuned mass damper, only the suppression of the edge vibration of the blade is considered, resulting in poor lateral vibration suppression effect during the hoisting of the wind turbine blade. Summary of the Invention

[0004] The present invention provides a method and device for designing parameters of a tuned mass damper for suppressing lateral vibration during the hoisting of a wind turbine blade, which improves the technical problem that in the single-blade hoisting process, when setting the parameters of the tuned mass damper (TMD) installed on the wind turbine blade, only the suppression of the edge vibration of the blade is considered, resulting in poor lateral vibration suppression effect during the hoisting of the wind turbine blade.

[0005] A method for designing parameters of a tuned mass damper for suppressing lateral vibration during the hoisting of a wind turbine blade provided by the first aspect of the present invention includes:

[0006] After the blade hoisting rope of the wind turbine blade to be hoisted and the blade and fixture assembly are respectively equivalent to the pendulum rope and pendulum ball of a single-pendulum model, they are equivalent to a first linear spring model;

[0007] The blade hoisting traction rope of the wind turbine blade is equivalent to a second linear spring model, and the first linear spring model and the second linear spring model are used to construct a multi-linear spring motion system;

[0008] Based on the Lagrange equation, a lateral swing dynamics equation of the multi-linear spring motion system is constructed, and the lateral swing natural frequency is determined by solving the lateral swing dynamics equation;

[0009] Obtain the mass ratio of the tuned mass damper to the blade and fixture assembly in the multi-linear spring motion system, and calculate the optimal mass, optimal natural frequency ratio and optimal damping ratio of the tuned mass damper in combination with the mass of the blade and fixture assembly;

[0010] Determine the optimal spring coefficient and optimal damping of the tuned mass damper by using the lateral swing natural frequency, the optimal mass, the optimal natural frequency ratio, and the optimal damping ratio.

[0011] The lateral swing dynamic equation includes:

[0012] ;

[0013] In the formula, is the mass of the blade and fixture assembly, is the lateral swing acceleration of the multi-wire spring motion system, is the spring stiffness of the first-line spring model, is the spring stiffness of the first second-line spring model, is the spring stiffness of the second second-line spring model, is the lateral swing displacement of the multi-wire spring motion system.

[0014] Optionally, the calculation process of the optimal mass includes:

[0015] ;

[0016] In the formula, is the optimal mass, is the mass ratio, is the mass of the blade and fixture assembly.

[0017] Optionally, the calculation process of the optimal natural frequency ratio includes:

[0018] ;

[0019] In the formula, is the optimal mass, is the mass ratio.

[0020] Optionally, the calculation process of the optimal damping ratio includes:

[0021] ;

[0022] In the formula, is the optimal damping ratio, is the mass ratio.

[0023] Optionally, the determination process of the optimal spring coefficient and optimal damping includes:

[0024] ;

[0025] ;

[0026] Wherein, is the optimal spring coefficient, is the optimal mass, is the mass ratio, is the optimal damping, is the optimal damping ratio.

[0027] A tuned mass damper parameter design device for suppressing the lateral vibration of a wind turbine blade during hoisting provided by the second aspect of the present invention includes:

[0028] An equivalent module, which is used to respectively equivalent the blade hoisting rope of the wind turbine blade to be hoisted and the blade and fixture assembly to the pendulum rope and pendulum ball of a simple pendulum model, and then equivalent it to a first-line spring model;

[0029] A hoisting system simplification module, which is used to equivalent the blade hoisting traction rope of the wind turbine blade to a second-line spring model, and construct a multi-line spring motion system by using the first-line spring model and the second-line spring model;

[0030] A swing analysis module, which is used to construct a lateral swing dynamic equation of the multi-line spring motion system based on the Lagrange equation, and solve the lateral swing dynamic equation to determine the lateral swing natural frequency;

[0031] A damper intermediate parameter determination module, which is used to obtain the mass ratio of the tuned mass damper to the blade and fixture assembly in the multi-line spring motion system, and calculate the optimal mass, optimal natural frequency ratio and optimal damping ratio of the tuned mass damper in combination with the mass of the blade and fixture assembly;

[0032] A damper target parameter determination module, which is used to determine the optimal spring coefficient and optimal damping of the tuned mass damper by using the lateral swing natural frequency, the optimal mass, the optimal natural frequency ratio and the optimal damping ratio.

[0033] A computer device provided by the third aspect of the present invention includes a memory and a processor. When the computer program stored in the memory is executed by the processor, the processor executes the steps of the method for designing the parameters of the tuned mass damper for suppressing the lateral vibration of the wind turbine blade during hoisting as described in any one of the above.

[0034] A computer-readable storage medium provided by the fourth aspect of the present invention stores a computer program thereon. When the computer program is executed, it implements the method for designing the parameters of the tuned mass damper for suppressing the lateral vibration of the wind turbine blade during hoisting as described in any one of the above.

[0035] A computer program product provided by the fifth aspect of the present invention includes a computer program / instructions, and when the computer program / instructions are executed by a processor, the method for designing parameters of a tuned mass damper for suppressing lateral vibration during hoisting of a wind turbine blade as described in any one of the above is implemented.

[0036] As can be seen from the above technical solutions, the present invention has the following advantages:

[0037] The above solution of the present invention provides a method for designing parameters of a tuned mass damper for suppressing lateral vibration during hoisting of a wind turbine blade, including: after respectively equivalenting the blade hoisting rope of the wind turbine blade to be hoisted and the blade and the fixture assembly to the pendulum rope and the pendulum ball of a single pendulum model, it is equivalented to a first linear spring model; the blade hoisting traction rope of the wind turbine blade is equivalented to a second linear spring model, and a multi-linear spring motion system is constructed by using the first linear spring model and the second linear spring model; based on the Lagrange equation, the lateral swing dynamic equation of the multi-linear spring motion system is constructed, and the lateral swing natural frequency is determined by solving the lateral swing dynamic equation; the mass ratio of the tuned mass damper to the blade and the fixture assembly in the multi-linear spring motion system is obtained, and the optimal mass, optimal natural frequency ratio and optimal damping ratio of the tuned mass damper are calculated in combination with the mass of the blade and the fixture assembly; the optimal spring coefficient and optimal damping of the tuned mass damper are determined by using the lateral swing natural frequency, optimal mass, optimal natural frequency ratio and optimal damping ratio. Based on the above solution, the blade hoisting system of the wind turbine blade is equivalented to a single pendulum and a linear spring to determine a simplified multi-linear spring motion system, and then the free vibration equation in the lateral direction of the simplified model of the blade hoisting system, that is, the lateral swing dynamic equation, is derived by using the Lagrange equation. Then, combined with the optimal calculation theory of the tuned mass damper, parameter design is carried out to determine the optimal spring coefficient and optimal damping of the tuned mass damper. By means of the simplified model, the parameter design time of the tuned mass damper can be greatly shortened. At the same time, since the multi-linear spring motion system simplifies the model for the entire hoisting system, the designed tuned mass damper installed on the wind turbine blade can more comprehensively suppress the vibration of the structure during the lateral vibration of the wind turbine blade hoisting. Description of the Drawings

[0038] In order to more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the following will briefly introduce the drawings required for use in the description of the embodiments or the prior art. Obviously, the following drawings are only some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained according to these drawings.

[0039] Figure 1 It is a flowchart of the steps of a method for designing parameters of a tuned mass damper for suppressing lateral vibration during hoisting of a wind turbine blade provided by an embodiment of the present invention;

[0040] Figure 2 Schematic diagram of the blade hoisting system provided by the embodiment of the present invention;

[0041] Figure 3 Schematic diagram of the pendulum system provided by the embodiment of the present invention;

[0042] Figure 4 Plan view of the simplified model of the blade hoisting system provided by the embodiment of the present invention;

[0043] Figure 5 TMD mechanical model provided by the embodiment of the present invention;

[0044] Figure 6 Structural block diagram of a device for designing parameters of a tuned mass damper for suppressing lateral vibration of a wind turbine blade hoisting provided by the embodiment of the present invention. Detailed implementation manners

[0045] The embodiment of the present invention provides a method and a device for designing parameters of a tuned mass damper for suppressing lateral vibration of a wind turbine blade hoisting, which are used to improve the technical problem that in the process of single blade hoisting, when setting parameters for the existing tuned mass damper (TMD) in the installation of wind turbine blades, only the suppression of the vibration at the edge of the blade is considered, resulting in poor effect of suppressing the lateral vibration of the wind turbine blade during hoisting.

[0046] In order to make the invention purpose, features and advantages of the present invention more obvious and understandable, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention. Obviously, the embodiments described below are only a part of the embodiments of the present invention, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts shall fall within the protection scope of the present invention.

[0047] Please refer to Figure 1 , Figure 1 Flowchart of the steps of a method for designing parameters of a tuned mass damper for suppressing lateral vibration of a wind turbine blade hoisting provided by the embodiment of the present invention.

[0048] A method for designing parameters of a tuned mass damper for suppressing lateral vibration of a wind turbine blade hoisting provided by the present invention includes:

[0049] Step 101: After respectively equivalenting the blade hoisting rope of the wind turbine blade to be hoisted and the blade and fixture assembly to the pendulum rope and pendulum ball of the single pendulum model, it is equivalented to the first linear spring model.

[0050] It should be noted that in the actual hoisting process of a single wind turbine blade, such as Figure 2As shown, the components of the involved blade hoisting system generally include at least a crane, a blade hoisting rope, a wind turbine blade, a blade fixture, and a blade hoisting towing rope. Among them, the crane is connected to the rope, the first end of the wind turbine blade is connected to the rope through the blade fixture, and the second end of the wind turbine blade is connected to the towing rope near the ground. The towing rope is used to control the attitude and position of the blade during the blade hoisting process and is usually operated by ground personnel;

[0051] In this embodiment, regarding the wind turbine blade and the blade as a rigid structure fixedly connected, that is, the blade and the fixture assembly, the blade hoisting part can be simplified into a two-dimensional simple pendulum model for dynamic analysis. The simplified simple pendulum model is as shown in Figure 3 ; For the lateral vibration suppression analysis of the blade hoisting system, to design the optimal parameters of the tuned mass damper TMD for blade hoisting, a dynamic equation with simplified degrees of freedom is established. The following basic assumptions need to be made during the analysis:

[0052] 1) The position of the top of the crane remains unchanged. Without loss of generality, we assume that the position of the center of gravity plane after simplifying the model is ;

[0053] 2) Only consider the three planar motions of the simplified model, namely flapping (in the X-axis direction), waving (in the Y-axis direction), and rotation (the degree of its torsion is described by the rotation angle θ in the blade hoisting system);

[0054] 3) During the hoisting process, the angular velocity of the blade is small, that is, the angular velocity of the simplified model is small;

[0055] 4) The motion of the center of gravity of the simplified model in different degrees of freedom is independent;

[0056] Based on the above relevant assumptions, the decoupled three-degree-of-freedom single-blade hoisting dynamic equation can be expressed as follows:

[0057] For the simple pendulum system, apply the Lagrange equation:

[0058]

[0059]

[0060] In the formula, is the Lagrange function, is the total kinetic energy of the system, is the total potential energy of the system, is the generalized coordinate, is the generalized velocity, is time, is the th degree of freedom;

[0061] Figure 3 The total kinetic energy corresponding to the simple pendulum system shown , total potential energy are respectively:

[0062]

[0063]

[0064] In the formula, is the mass of the blade and fixture assembly, is the length of the simple pendulum rope (determined by the distance from the crane to the center of mass of the blade and fixture), is the rotation angle of the simple pendulum, is the angular velocity of the simple pendulum rotation, is the acceleration due to gravity (take 9.8 s 2 ); Substituting formula (3) and formula (4) into formula (1), the motion equation of the simple pendulum system can be obtained:

[0065]

[0066] In the formula, is the angular acceleration of the simple pendulum rotation; Because the rotation angle of the simple pendulum is very small, then , it can be obtained:

[0067] , ;

[0068] According to the above results, the simple pendulum can be simplified into a linear spring connected to the center of mass and coinciding with the center of mass, and thus the first linear spring model is obtained, is the spring stiffness of the first linear spring model.

[0069] Step 102, Equivalent the blade hoisting traction rope of the wind turbine blade to the second linear spring model, and construct a multi-linear spring motion system by using the first linear spring model and the second linear spring model.

[0070] It should be noted that in this embodiment, the blade hoisting traction rope is simplified into a linear spring, and thus the second linear spring model is obtained. Therefore, the blade hoisting system can be simplified into a multi-linear spring motion system composed of the first linear spring model and the second linear spring model.

[0071] Step 103: Construct the lateral swing dynamics equation of the multi-wire spring motion system based on the Lagrange equation, and solve the lateral swing dynamics equation to determine the natural frequency of lateral swing.

[0072] The natural frequency of lateral swing refers to the frequency at which the multi-wire spring motion system vibrates on its own without external excitation when swinging laterally (in the X-axis direction).

[0073] It should be noted that in this embodiment, taking two blade hoisting tow ropes as an example, two second-wire spring models are obtained, and their corresponding spring stiffnesses are and , respectively. The blade hoisting system is simplified into a planar system with three wire springs, that is, a multi-wire spring motion system. Its planar system is as shown in Figure 4 . Based on the planar diagram of the multi-wire spring motion system shown in Figure 4 , dynamic analysis is carried out: after the system rotates, the positions of specific points A, B, and C in the system change, generating kinetic energy and elastic potential energy. Among them, , and represent the initial points of the system at A, B, and C respectively, , and represent the end points of A, B, and C after the system moves. The distances between A and B and C in the X-axis and Y-axis are respectively expressed as , , and . Applying the Lagrange equation, the total kinetic energy T and total potential energy V are respectively:

[0074]

[0075]

[0076]

[0077] In the formula, is the velocity of the center of gravity position point C of the system in the X-axis direction, is the velocity of the center of gravity position point C of the system in the Y-axis direction, is the moment of inertia of the blade and fixture assembly in the Y-axis, is the angular velocity of the blade hoisting system, that is, the multi-wire spring motion system, is the transformation matrix from the main body fixed frame to the global frame; substituting the above formulas into formula (1) and formula (2), the lateral swing dynamics equation of the blade hoisting can be obtained, including:

[0078]

[0079] In the formula, is the mass of the blade and the fixture assembly, is the lateral swing acceleration of the multi-wire spring motion system, is the spring stiffness of the first-line spring model, is the spring stiffness of the first second-line spring model, is the spring stiffness of the second second-line spring model, is the lateral swing displacement of the multi-wire spring motion system;

[0080] Based on the above lateral swing dynamic equation, according to the general structural form of the motion equation of the free vibration system, the lateral swing natural frequency can be solved as:

[0081] .

[0082] Step 104: Obtain the mass ratio of the tuned mass damper to the mass of the blade and the fixture assembly in the multi-wire spring motion system, and calculate the optimal mass, optimal natural frequency ratio, and optimal damping ratio of the tuned mass damper in combination with the mass of the blade and the fixture assembly.

[0083] It should be noted that the simplified model has three degrees of freedom. Since the TMD can only suppress the motion in one direction, it is necessary to design the TMD for each of the three degrees of freedom. The three degrees of freedom are the X-axis direction, the Y-axis direction, and the rotation about the Y-axis. The design process of the TMD parameters in the three directions is the same, except that the spring for rotation about the Y-axis uses a torsion spring; in this embodiment, the lateral swing is analyzed, and taking the design of the TMD in the X-axis direction as an example, the mechanical model of the TMD is as Figure 5 shown. Using the dynamic law, write the motion equation of the overall dynamic system combining the multi-wire spring motion system (as the main structure) and the TMD (as the sub-structure):

[0084]

[0085] In the formula, is the mass of the main structure, that is, the mass of the blade and the fixture assembly, is the motion acceleration of the main structure, is the damping coefficient of the tuned mass damper, is the motion velocity of the main structure, is the spring stiffness of the tuned mass damper, is the spring stiffness in the lateral direction, that is, the spring stiffness of the main structure, is the displacement of the main structure relative to the ground, is the motion velocity of the tuned mass damper, is the displacement of the tuned mass damper relative to the ground, is the external excitation applied to the main structure, is the mass of the sub-structure, i.e., the mass of the tuned mass damper, is the acceleration of the tuned mass damper; it can be understood that since the mass of the blade hoisting towing rope accounts for a very small proportion of the mass of the blade and the fixture assembly, the mass of the blade hoisting towing rope is negligible, and the mass of the blade and the fixture assembly is regarded as the mass of the blade and the fixture assembly; and the following relevant intermediate symbols are introduced:

[0086]

[0087] In the formula, X is the static deformation of the system, ω0 is the natural frequency of the main structure, i.e., the natural frequency of lateral swing, ω1 is the natural frequency of the sub-structure, i.e., the natural frequency of the tuned mass damper, μ is the mass ratio, f is the ratio of the natural frequencies of the sub-structure and the main structure, is the excitation frequency ratio, ω is the frequency of the external input load, ζ is the damping ratio; substituting into the motion equation and solving, the amplitude magnification factor of the displacement of the main structure, i.e., the steady-state response amplitude X0 of the main structure under the action of the external excitation, is:

[0088]

[0089] Because it mainly suppresses the vibration of the main structure, considering the minimum displacement optimization of the main structure (Den Hartog), Den Hartog takes the minimum steady-state response of the undamped main structure mass under the action of the harmonic load as the design goal, keeps the mass ratio and the natural frequency ratio (f) unchanged, and changes the value of the damping ratio, and the relationship curve between the dynamic magnification factor and the frequency can be obtained. Through the analysis of this curve, two optimization conditions of the TMD damper, i.e., the optimal frequency ratio and the optimal damping ratio, can be deduced. Therefore, the calculation process of the optimal natural frequency ratio and the optimal damping ratio of the tuned mass damper includes:

[0090]

[0091]

[0092] In the formula, is the optimal mass, is the mass ratio, is the optimal damping ratio, is the mass ratio;

[0093] In addition, the calculation process of the optimal mass includes: , in the formula, is the optimal mass, is the mass ratio, is the mass of the blade and fixture assembly.

[0094] Step 105 : Determine the optimal spring constant and optimal damping of the tuned mass damper using the lateral oscillation natural frequency, the optimal mass, the optimal natural frequency ratio, and the optimal damping ratio.

[0095] It should be noted that the optimal frequency ratio, optimal damping ratio and optimal mass obtained by design, combined with the lateral swing natural frequency, can be used to obtain the optimal spring coefficient and optimal damping of a single TMD. At this point, the TMD parameter design is completed; the process of determining the optimal spring coefficient and optimal damping includes:

[0096]

[0097]

[0098] In the formula, is the optimal spring coefficient, For the best quality, is the mass ratio, For optimal damping, is the optimal damping ratio.

[0099] It can be understood that in the suppression of lateral vibration during the hoisting of wind turbine blades, compared with installing the TMD inside the blade, due to the limited internal space of the blade, the installation and removal of the TMD relies on professional equipment and the ability of technicians, which not only increases the cost of installation and maintenance, but also easily leads to accidental damage during the installation and removal process. In some cases, the blades may need to be partially modified to accommodate the installation of the TMD, which further increases the complexity and cost of the project. Therefore, the tuned mass damper of this embodiment can be installed on a fixture; after the tuned mass damper of this embodiment completes the parameter setting according to the optimal spring coefficient and optimal damping determined in the above steps, it can effectively suppress the vibration of the entire hoisting system, especially when installed at the peak position of the structural vibration corresponding to the wind turbine blade, it can maximize its vibration reduction effect.

[0100] In the embodiment of the present invention, the blade hoisting system of the wind turbine blade is equivalent to a simple pendulum and a wire spring, so as to determine a simplified multi-wire spring motion system. Then, the Lagrange equation is used to derive the free vibration equation of the simplified model of the blade hoisting system in the lateral direction, that is, the lateral swing dynamics equation. Combining with the optimal calculation theory of the tuned mass damper, the parameter design is carried out to determine the optimal spring coefficient and optimal damping of the tuned mass damper. The parameter design by means of the simplified model can greatly shorten the parameter design time of the tuned mass damper. At the same time, since the multi-wire spring motion system simplifies the model for the entire hoisting system, the designed tuned mass damper installed on the wind turbine blade can more comprehensively suppress the vibration of the structure during the lateral vibration of the wind turbine blade hoisting.

[0101] Please refer to Figure 6 , Figure 6 which is the structural block diagram of a device for parameter design of a tuned mass damper for suppressing lateral vibration of a wind turbine blade hoisting provided by an embodiment of the present invention.

[0102] A device for parameter design of a tuned mass damper for suppressing lateral vibration of a wind turbine blade hoisting provided by the present invention includes:

[0103] An equivalent module 601, configured to respectively equivalent the blade hoisting rope of the wind turbine blade to be hoisted and the blade and the fixture assembly to the pendulum rope and the pendulum ball of the simple pendulum model, and then equivalent them to the first wire spring model;

[0104] A hoisting system simplification module 602, configured to equivalent the blade hoisting traction rope of the wind turbine blade to the second wire spring model, and construct a multi-wire spring motion system by using the first wire spring model and the second wire spring model;

[0105] A swing analysis module 603, configured to construct a lateral swing dynamics equation of the multi-wire spring motion system based on the Lagrange equation, and solve the lateral swing dynamics equation to determine the lateral swing natural frequency;

[0106] A damper intermediate parameter determination module 604, configured to obtain the mass ratio of the tuned mass damper to the blade and the fixture assembly in the multi-wire spring motion system, and calculate the optimal mass, optimal natural frequency ratio and optimal damping ratio of the tuned mass damper in combination with the mass of the blade and the fixture assembly;

[0107] A damper target parameter determination module 605, configured to determine the optimal spring coefficient and optimal damping of the tuned mass damper by using the lateral swing natural frequency, the optimal mass, the optimal natural frequency ratio and the optimal damping ratio.

[0108] Further, the lateral swing dynamics equation includes:

[0109] ;

[0110] In the formula, is the mass of the blade and the fixture assembly, is the lateral swing acceleration of the multi-wire spring motion system, is the spring stiffness of the first-line spring model, is the spring stiffness of the first second-line spring model, is the spring stiffness of the second second-line spring model, is the lateral swing displacement of the multi-wire spring motion system.

[0111] Furthermore, the calculation process of the optimal mass includes:

[0112] ;

[0113] In the formula, is the optimal mass, is the mass ratio, is the mass of the blade and the fixture assembly.

[0114] Furthermore, the calculation process of the optimal natural frequency ratio includes:

[0115] ;

[0116] In the formula, is the optimal mass, is the mass ratio.

[0117] Furthermore, the calculation process of the optimal damping ratio includes:

[0118] ;

[0119] In the formula, is the optimal damping ratio, is the mass ratio.

[0120] Furthermore, the determination process of the optimal spring coefficient and the optimal damping includes:

[0121] ;

[0122] ;

[0123] In the formula, is the optimal spring coefficient, is the optimal mass, is the mass ratio, is the optimal damping, is the optimal damping ratio.

[0124] An embodiment of the present invention further provides a computer device, including a memory and a processor, where a computer program is stored in the memory; when the computer program is executed by the processor, the processor executes the steps of the tuned mass damper parameter design method for suppressing the lateral vibration of the wind turbine blade hoisting as described in any one of the above embodiments.

[0125] An embodiment of the present invention further provides a computer-readable storage medium, on which a computer program / instruction is stored, and when the computer program / instruction is executed by a processor, the steps of the tuned mass damper parameter design method for suppressing the lateral vibration of the wind turbine blade hoisting as described in any one of the above embodiments are implemented.

[0126] An embodiment of the present invention further provides a computer program product, including a computer program / instruction, and when the computer program / instruction is executed by a processor, the steps of the tuned mass damper parameter design method for suppressing the lateral vibration of the wind turbine blade hoisting as described in any one of the above embodiments are implemented.

[0127] Those skilled in the art can clearly understand that for the convenience and brevity of description, the specific working processes of the systems, devices, and units described above can refer to the corresponding processes in the foregoing method embodiments, and will not be described herein again.

[0128] In several embodiments provided by the present application, it should be understood that the disclosed devices and methods can be implemented in other ways. For example, the device embodiments described above are merely illustrative. For example, the division of the units is only a logical function division, and there may be other division methods in actual implementation. For example, multiple units or components can be combined or integrated into another system, or some features can be ignored or not executed. Another point is that the displayed or discussed couplings or direct couplings or communication connections to each other can be through some interfaces, and the indirect couplings or communication connections of the devices or units can be in electrical, mechanical, or other forms.

[0129] The units described as separate components may or may not be physically separated, and the components displayed as units may or may not be physical units, that is, they can be located in one place, or distributed to multiple network units. Some or all of the units can be selected according to actual needs to achieve the purpose of the solution of this embodiment.

[0130] In addition, each functional unit in various embodiments of the present invention can be integrated into one processing unit, or each unit can exist physically alone, or two or more units can be integrated into one unit. The above integrated units can be implemented in the form of hardware or in the form of software functional units.

[0131] If the integrated unit is implemented in the form of a software functional unit and sold or used as an independent product, it can be stored in a computer-readable storage medium. Based on such an understanding, the technical solution of the present invention, in essence, or the part that contributes to the prior art, or all or part of the technical solution, can be embodied in the form of a software product. The computer software product is stored in a storage medium and includes several instructions for causing a computer device (which may be a personal computer, a server, or a network device, etc.) to execute all or part of the steps of the methods described in the various embodiments of the present invention. The aforementioned storage medium includes: various media such as USB flash drives, mobile hard disks, read-only memories (ROM, Read-Only Memory), random access memories (RAM, Random Access Memory), magnetic disks, or optical discs that can store program codes.

[0132] As described above, the above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those of ordinary skill in the art should understand that they can still modify the technical solutions described in the foregoing embodiments or perform equivalent replacements for some of the technical features; and these modifications or replacements do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the various embodiments of the present invention.

Claims

1. A method for designing parameters of a tuned mass damper for suppressing lateral vibration of wind turbine blades during installation, characterized in that: include: After the blade hoisting rope of the wind turbine blade to be hoisted and the blade and the fixture assembly are respectively equivalent to the pendulum rope and the pendulum ball of the simple pendulum model, they are equivalent to the first line spring model; The blade hoisting traction rope of the wind turbine blade is equivalent to a second linear spring model, and the first linear spring model and the second linear spring model are used to construct a multi-linear spring motion system; Constructing a lateral swing dynamics equation of the multi-wire spring motion system based on the Lagrange equation, and solving the lateral swing dynamics equation to determine the lateral swing natural frequency; Obtaining a mass ratio of a tuned mass damper to a blade-to-clamp assembly in the multi-linear spring motion system, and calculating an optimal mass, an optimal natural frequency ratio, and an optimal damping ratio of the tuned mass damper in combination with the mass of the blade-to-clamp assembly; An optimal spring constant and an optimal damping of the tuned mass damper are determined using the lateral oscillation natural frequency, the optimal mass, the optimal natural frequency ratio, and the optimal damping ratio.

2. The method for designing parameters of a tuned mass damper for suppressing lateral vibration of wind turbine blades according to claim 1, characterized in that: The lateral swing dynamic equations include: ； In the formula, is the mass of the blade and fixture assembly, is the lateral swing acceleration of the multi-linear spring motion system, is the spring stiffness of the first line spring model, is the spring stiffness of the first second line spring model, is the spring stiffness of the second wire spring model, is the lateral swing displacement of the multi-linear spring motion system.

3. The method for designing parameters of a tuned mass damper for suppressing lateral vibration of wind turbine blades according to claim 1, characterized in that: The optimal quality calculation process includes: ； In the formula, For the best quality, is the mass ratio, is the mass of the blade and fixture assembly.

4. The method for designing parameters of a tuned mass damper for suppressing lateral vibration of wind turbine blades according to claim 1, characterized in that: The calculation process of the optimal natural frequency ratio includes: ； In the formula, For the best quality, For mass ratio.

5. The method for designing parameters of a tuned mass damper for suppressing lateral vibration of wind turbine blades according to claim 1, characterized in that: The calculation process of the optimal damping ratio includes: ； In the formula, is the optimal damping ratio, For mass ratio.

6. The method for designing parameters of a tuned mass damper for suppressing lateral vibration of wind turbine blades according to claim 1, characterized in that: The process of determining the optimal spring coefficient and optimal damping includes: ； ； In the formula, is the optimal spring coefficient, For the best quality, is the mass ratio, For optimal damping, is the optimal damping ratio.

7. A device for designing parameters of a tuned mass damper for suppressing lateral vibration of wind turbine blades during installation, characterized in that: include: An equivalent module is used to respectively equate the blade hoisting rope of the wind turbine blade to be hoisted and the blade and the fixture assembly to the swing rope and the swing ball of the single pendulum model, and then to the first line spring model; A lifting system simplification module, used for converting the blade lifting traction rope of the wind turbine blade into a second linear spring model, and constructing a multi-linear spring motion system by using the first linear spring model and the second linear spring model; A swing analysis module, used for constructing a lateral swing dynamics equation of the multi-wire spring motion system based on the Lagrange equation, and solving the lateral swing dynamics equation to determine the lateral swing natural frequency; A damper intermediate parameter determination module, used to obtain the mass ratio of the tuned mass damper and the blade and fixture assembly in the multi-wire spring motion system, and calculate the optimal mass, optimal natural frequency ratio and optimal damping ratio of the tuned mass damper in combination with the mass of the blade and fixture assembly; The damper target parameter determination module is used to determine the optimal spring coefficient and optimal damping of the tuned mass damper by using the lateral swing natural frequency, the optimal mass, the optimal natural frequency ratio and the optimal damping ratio.

8. A computer device, characterized in that: It comprises a memory and a processor, wherein a computer program is stored in the memory, and when the computer program is executed by the processor, the processor executes the steps of the method for designing parameters of a tuned mass damper for suppressing lateral vibration of wind turbine blade hoisting as described in any one of claims 1 to 6.

9. A computer-readable storage medium having a computer program / instruction stored thereon, characterized in that: When the computer program / instructions are executed by a processor, the steps of the method for designing parameters of a tuned mass damper for suppressing lateral vibration of wind turbine blade hoisting as described in any one of claims 1 to 6 are implemented.

10. A computer program product comprising a computer program / instructions, characterized in that When the computer program / instructions are executed by a processor, the steps of the method for designing parameters of a tuned mass damper for suppressing lateral vibration of wind turbine blade hoisting as described in any one of claims 1 to 6 are implemented.

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