A pendulum type variable damping device and vibration reduction configuration method thereof

Abstract

The present invention provides a pendulum-type variable damping device and a vibration reduction configuration method thereof. The device includes a mass unit, a swing arm unit and an energy consuming unit. The permanent magnet assembly of the energy consuming unit includes a plurality of annular permanent magnets. The conductor plate of the energy consuming unit is an inwardly concave curved plate. The center of the annular permanent magnet is arranged relative to the center of the inwardly concave curved plate. The method includes calculating the optimal value of the initial damping constant of the energy consuming unit according to the configuration parameters of the device, setting the curvature of the conductor plate in the energy consuming unit to 0, making the initial damping constant generated by the energy consuming unit consistent with the optimal value of the initial damping constant through finite element simulation, determining the optimal number and spacing of annular permanent magnets, and the minimum spacing between the annular permanent magnet and the conductor plate; continuously adjusting the curvature of the conductor plate surface in the finite element model, making the damping force generated by the energy consuming unit consistent with the theoretical damping force generated by the energy consuming unit, and determining the optimal curvature of the conductor plate surface. The present invention has the advantages of adjustable damping, high safety and reliability, etc.

Description

Technical Field

[0001] The invention relates to the field of damping and vibration reduction, and in particular to a pendulum-type variable damping device and a vibration reduction configuration method thereof. Background Art

[0002] Tuned mass damping (TMD) is one of the effective implementation methods to solve the vibration problem of large structures such as wind turbines, bridges, and high-rise buildings. For controlled structures with limited internal installation space (such as wind turbine towers), pendulum mass damping devices are usually used, and eddy current damping is used to reduce vibration and dissipate energy to avoid mechanical friction and leakage problems in traditional oil damping energy dissipation.

[0003] However, the existing pendulum mass damping devices have problems such as poor vibration reduction effect, poor safety and stability when the internal installation space of the controlled structure (such as land or offshore wind turbine towers, etc.) is limited. Specifically, the internal space of the controlled structure is small. In sudden or extreme load environments such as strong winds and strong earthquakes, the mass block often exceeds the pre-set range and collides with the controlled structure or the device limit components, which seriously weakens the vibration reduction effect of the damping device and poses a collision safety hazard. In particular, when the offshore wind turbine is affected by the marine environment and the motion response is complex, the stroke of the mass block is very easy to exceed the limit and there is a risk of lateral collision. At the same time, there is currently no vibration reduction configuration method for optimizing the design of the pendulum damping device, making the pendulum damping device difficult to implement in practical applications. Summary of the invention

[0004] The technical problem to be solved by the present invention is to overcome the deficiencies of the prior art and provide a pendulum-type variable damping device with adjustable damping and high safety and reliability and a vibration reduction configuration method thereof.

[0005] In order to solve the above technical problems, the technical solution proposed by the present invention is:

[0006] A pendulum-type variable damping device comprises a mass unit, a swing arm unit and an energy dissipation unit, wherein the mass unit is swingably connected to a controlled structure via the swing arm unit, the energy dissipation unit comprises a permanent magnet assembly and a conductor plate, the permanent magnet assembly is mounted on the mass unit, the permanent magnet assembly comprises a plurality of annular permanent magnets of different diameters and mutually nested; the conductor plate is mounted on the controlled structure, the conductor plate is an inwardly curved plate with a curvature gradually increasing from the center to the outer edge, and the center of the annular permanent magnet is arranged relative to the center of the inwardly curved plate.

[0007] As a further improvement of the above technical solution:

[0008] The swing arm unit includes a rigid swing arm, universal joints arranged at both ends of the rigid swing arm, and a turntable connected to the universal joint. The two ends of the rigid swing arm are rotatably mounted on the controlled structure or the mass unit through the universal joint and the turntable in turn; when the rigid swing arm is set to one, the rigid swing arm is arranged in the middle of the mass unit; when the rigid swing arms are at least two, the rigid swing arms are arranged at intervals along the circumference of the mass unit.

[0009] The swing arm unit is swingably connected to the controlled structure through a force transmission mounting frame, and the force transmission mounting frame includes a force transmission top plate, a connecting piece and a force transmission bottom plate connected in sequence. The swing arm unit is located inside the force transmission mounting frame and is swingably mounted on the force transmission top plate; the force transmission bottom plate is provided with a curved mounting groove adapted to the concave curved plate, and the conductor plate is mounted in the curved mounting groove.

[0010] The bottom surface of the annular permanent magnet is a plane, the concave curved plate is a spherical curved plate, the center of the annular permanent magnet and the center of the spherical curved plate are located on the same vertical line when the mass unit does not swing, and the swing range of the annular permanent magnet as the mass unit swings is located within the spherical curved plate.

[0011] The mass unit includes a mass block, a mass block backplate and a permanent magnet backplate, the energy consumption unit also includes a conductor backplate, the mass block backplate, the mass block, the permanent magnet backplate and the annular permanent magnet are connected in sequence, the swing arm unit is connected to the mass block backplate, and the conductor plate is connected to the controlled structure through the conductor backplate.

[0012] The circular shapes of the annular permanent magnets overlap, the magnetic poles of the annular permanent magnets are alternately arranged along the radial direction of the annular permanent magnets, and each annular permanent magnet includes two annular permanent magnet blocks with different magnetic poles, and the two annular permanent magnets are arranged in a superimposed manner.

[0013] A vibration reduction configuration method for the above-mentioned pendulum-type variable damping device comprises the following steps:

[0014] Step 1) Determine the configuration parameters of the target pendulum variable damping device, wherein the configuration parameters include the mass of the mass unit , the stiffness of the mass unit , the optimal damping ratio of the energy dissipation unit and the travel limits of the mass unit ;

[0015] Step 2) According to the mass of the mass unit , the stiffness of the mass unit , the optimal damping ratio of the energy dissipation unit and the travel limits of the mass unit Calculate the initial damping constant of the energy dissipation unit The optimal value of ;

[0016] Step 3) Construct a finite element model of the target pendulum variable damping device according to the current configuration parameters, and set the curvature of the conductor plate in the energy dissipation unit to 0. Through finite element simulation, the initial damping constant generated by the energy dissipation unit is equal to or close to the initial damping constant. The optimal value of , determine the optimal number and spacing of annular permanent magnets in the permanent magnet assembly of the energy consumption unit, and the minimum spacing between the annular permanent magnets and the conductor plate;

[0017] Step 4) Continuously adjust the curvature of the conductor plate in the finite element model of the target pendulum variable damping device so that the damping force generated by the energy dissipation unit is equal to or close to the theoretical damping force generated by the energy dissipation unit. , determine the optimal conductor plate surface curvature, the theoretical damping force According to the variable damping coefficient of the energy consumption unit It is determined that the variable damping coefficient According to the initial damping constant The optimal value of Definitely got it.

[0018] As a further improvement of the above technical solution:

[0019] In step 2), the coefficient is first determined based on the amplitude of the controlled structure and the installation space. p , then according to the coefficient p and the mass of the mass unit , the stiffness of the mass unit , the optimal damping ratio of the energy dissipation unit and the travel limits of the mass unit The initial damping constant of the energy dissipation unit is calculated according to the following formula: The optimal value of :

[0020] ,

[0021] ,

[0022] in, is a preset coefficient in the range of (0,1], is the ratio between the mass of the mass unit and the modal mass of the target mode of the controlled structure, is the modal mass of the target mode of the controlled structure.

[0023] In step 4), the theoretical damping force generated by the energy dissipation unit is determined according to the following formula: :

[0024] ,

[0025] ,

[0026] in, is the swing amplitude of the mass unit.

[0027] In step 1), the stiffness of the mass unit According to the mass of the mass unit and the vibration frequency of the mass unit The vibration frequency of the mass unit is calculated as According to the frequency of the target mode of the controlled structure And the ratio of the mass of the mass unit to the modal mass of the target mode of the controlled structure The calculation expression is:

[0028] ,

[0029] in, is the modal mass of the target mode of the controlled structure.

[0030] Compared with the prior art, the advantages of the present invention are:

[0031] (1) The conductor plate of the present invention adopts a concave curved plate with a gradually increasing curvature from the center to the outer edge. The center of the annular permanent magnet is arranged relative to the center of the concave curved plate, which makes the gap between the conductor plate and the permanent magnet assembly continuously decrease from the center to the edge. At this time, the damping force generated by the energy dissipation unit is inversely proportional to the gap between the conductor plate and the permanent magnet assembly, that is, when the swing amplitude of the mass block increases, the gap between the conductor plate and the permanent magnet assembly becomes smaller, and the damping coefficient and the damping force generated by the energy dissipation unit become larger; conversely, when the swing amplitude of the mass unit becomes smaller, the gap between the conductor plate and the permanent magnet assembly becomes larger, and the damping coefficient and the damping force generated by the energy dissipation unit become smaller, thereby realizing the function that the damping coefficient of the energy dissipation unit changes continuously with the amplitude of the mass unit.

[0032] It can be seen that the pendulum variable damping device of the present invention can achieve variable damping energy dissipation by changing the gap between the permanent magnet assembly and the conductor plate when the controlled structure has different vibration displacements, thereby ensuring that the damping device has excellent vibration reduction effect at different vibration displacements; at the same time, the variable damping energy dissipation effectively limits the swing stroke of the mass unit, avoiding the occurrence of the mass unit stroke exceeding the limit and colliding with the controlled structure or the device limit parts. While ensuring the safe and reliable operation of the variable damping device, the present invention can be effectively applied to the vibration control of controlled structures with limited space (such as wind turbine towers).

[0033] (2) The permanent magnet assembly includes a plurality of annular permanent magnets, which have different diameters and are mutually nested, so that the energy-consuming unit cuts the magnetic field in each swing direction of the mass unit in a consistent manner. At this time, the energy-consuming unit provides the mass unit with the same damping coefficient at the same swing amplitude and along each vibration direction, so that the damping force provided by the pendulum variable damping device is the same when the mass unit has the same vibration amplitude, which maximizes the vibration reduction control effect of the pendulum variable damping device. At the same time, the annular permanent magnets make the swing stroke of the controlled structure the same at the same amplitude, ensuring that the pendulum variable damping device can avoid over-limit collision in each vibration direction, which further ensures the safe and reliable operation of the pendulum variable damping device.

[0034] (3) The method of the present invention first determines the optimal value of the initial damping constant of the energy-consuming unit according to the configuration parameters of each unit, and combines the finite element simulation method to simulate the target pendulum-type variable damping device when the curvature of the conductor plate is 0. According to the optimal value of the initial damping constant of the energy-consuming unit, the optimal number and spacing of the annular permanent magnets and the minimum spacing between the annular permanent magnets and the conductor plate are determined. Then, according to the theoretical force determined by the variable damping coefficient, the curvature of the conductor plate surface in the model is continuously adjusted to determine the optimal curvature of the conductor plate surface, which can match the structure of the pendulum-type variable damping device to achieve the optimal configuration, so that the damping and vibration reduction effect of the device can be maximized. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] The present invention will be described in more detail below based on embodiments and with reference to the accompanying drawings, wherein:

[0036] Figure 1 It is a three-dimensional structural schematic diagram of the pendulum type variable damping device of the present invention.

[0037] Figure 2 It is a schematic diagram of the exploded structure of the pendulum type variable damping device of the present invention.

[0038] Figure 3 It is a cross-sectional view of the pendulum type variable damping device of the present invention.

[0039] Figure 4 It is a three-dimensional structural schematic diagram of the swing arm unit of the present invention.

[0040] Figure 5 It is a front view of the permanent magnet assembly of the present invention.

[0041] Figure 6 It is a schematic diagram of the positional relationship between the permanent magnet assembly and the mass block of the present invention.

[0042] Figure 7 It is a structural schematic diagram of the pendulum type variable damping device of the present invention in a specific application.

[0043] Figure 8 yes Figure 7 An enlarged schematic diagram of point A.

[0044] Fig. 9 It is a flow chart of the vibration reduction configuration method of the pendulum type variable damping device of the present invention.

[0045] The symbols in the figure represent:

[0046] 1. Mass unit; 11. Mass block; 12. Mass block back plate; 13. Permanent magnet back plate; 2. Swing arm unit; 21. Rigid swing arm; 22. Universal joint; 221. Cross shaft; 222. Universal joint fork; 23. Turntable; 3. Energy dissipation unit; 31. Ring permanent magnet; 32. Conductor plate; 321. Concave curved plate; 33. Conductor back plate; 4. Controlled structure; 5. Install force transmission frame; 51. Force transmission top plate; 52. Connector; 53. Force transmission bottom plate. DETAILED DESCRIPTION

[0047] The present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments, but the protection scope of the present invention is not limited thereby.

[0048] Figures 1 to 3 The embodiment of the pendulum variable damping device of the present invention is shown, which can be applied to vibration reduction of large structures such as wind turbine towers, bridges and high-rise buildings. The wind turbine towers, bridges and high-rise buildings are controlled structures 4 of the pendulum variable damping device. In this embodiment, the pendulum variable damping device includes a mass unit 1, a swing arm unit 2 and an energy dissipation unit 3. Among them, the mass unit 1 is swingably connected with the controlled structure 4 through the swing arm unit 2, and the energy dissipation unit 3 includes a permanent magnet assembly and a conductor plate 32. The permanent magnet assembly includes a plurality of annular permanent magnets 31, and the plurality of annular permanent magnets 31 have different diameters and are mutually sleeved. The annular permanent magnets 31 are installed on the mass unit 1; the conductor plate 32 is installed on the controlled structure 4, and the conductor plate 32 is an inwardly curved plate 321 with a curvature gradually increasing from the center to the outer edge. The center of the annular permanent magnet 31 is arranged relative to the center of the inwardly curved plate 321, and the structure is simple and the cost is low.

[0049] The conductor plate 32 of the present invention adopts a concave curved plate 321 with a gradually increasing curvature from the center to the outer edge, and the center of the annular permanent magnet 31 is arranged relative to the center of the concave curved plate 321, which makes the gap between the conductor plate 32 and the permanent magnet assembly continuously decrease from the center to the edge. At this time, the damping force generated by the energy consumption unit 3 is inversely proportional to the gap between the conductor plate 32 and the permanent magnet assembly, that is, when the swing amplitude of the mass block 11 increases, the gap between the conductor plate 32 and the permanent magnet assembly becomes smaller, and the damping coefficient and the damping force generated by the energy consumption unit 3 become larger; on the contrary, when the swing amplitude of the mass unit 1 becomes smaller, the gap between the conductor plate 32 and the permanent magnet assembly becomes larger, and the damping coefficient and the damping force generated by the energy consumption unit 3 become smaller, thereby realizing the function that the damping coefficient of the energy consumption unit 3 changes continuously with the amplitude of the mass unit 1.

[0050] It can be seen that the pendulum variable damping device of the present invention can realize variable damping energy dissipation by changing the gap between the permanent magnet assembly and the conductor plate 32 when the controlled structure 4 has different vibration displacements, thereby ensuring that the damping device has excellent vibration reduction effect at different vibration displacements; at the same time, the variable damping energy dissipation effectively limits the swing stroke of the mass unit 1, avoiding the occurrence of the mass unit 1 exceeding the stroke limit and colliding with the controlled structure 4 or the device limit parts. While ensuring the safe and reliable operation of the variable damping device, the present invention can be effectively applied to the vibration control of the controlled structure 4 (such as the wind turbine tower) with limited space.

[0051] At the same time, the permanent magnet assembly includes a plurality of annular permanent magnets 31, and the diameters of the plurality of annular permanent magnets 31 are different and they are mutually nested, which makes the energy consumption unit 3 cut the magnetic field in each swing direction of the mass unit 1 in a consistent manner. At this time, the energy consumption unit 3 provides the mass unit 1 with the same damping coefficient in the same swing amplitude and along each vibration direction, so that the damping force provided by the pendulum variable damping device is the same when the mass unit 1 has the same vibration amplitude, which maximizes the vibration reduction control effect of the pendulum variable damping device. At the same time, the annular permanent magnet 31 makes the swing stroke of the controlled structure 4 limited to the same at the same amplitude, ensuring that the pendulum variable damping device can avoid over-limit collision in each vibration direction, which further ensures the safe and reliable operation of the pendulum variable damping device.

[0052] Furthermore, if Figure 4 As shown, the swing arm unit 2 includes a rigid swing arm 21, a universal joint 22 and a turntable 23. The universal joint 22 is arranged at both ends of the rigid swing arm 21 to transmit power at a variable angle when the mass unit 1 swings, so that the mass unit 1 can swing at multiple angles; the turntable 23 is connected to the universal joint 22, and the setting of the turntable 23 allows the rigid swing arm 21 to rotate flexibly when the swing arm unit 2 swings, so as to avoid the rigid swing arms 21 interfering with each other and hindering the swing of the mass unit 1. The two ends of the rigid swing arm 21 are rotatably mounted on the controlled structure 4 or the mass unit 1 through the universal joint 22 and the turntable 23 in turn, so that the mass unit 1 can swing in any horizontal direction, providing a structural basis for the vibration reduction and energy consumption of the controlled structure 4 in any direction.

[0053] In this embodiment, there are four rigid swing arms 21, which are arranged at intervals along the circumference of the mass unit 1, and can effectively bear the gravity of the mass unit 1, so that the stability and reliability of the mass unit 1 during swinging are high. In other embodiments, the number of rigid swing arms 21 can be adjusted according to the load-bearing requirements of the mass unit 1, such as one, two, five, etc. When the rigid swing arm 21 is set to one, the rigid swing arm 21 is arranged in the middle of the mass unit 1.

[0054] In this embodiment, the universal joint 22 is a cross-axis universal joint, which includes a cross shaft 221 and two universal joint forks 222. One universal joint fork 222 is connected to the rigid swing arm 21, and the other universal joint fork 222 is connected to the turntable 23; the universal joint fork 222 is a Y-shaped fork structure, and the open end of the Y-shaped fork structure is sleeved on the journal of the cross shaft 221. The universal joint 22 has a simple structure and enables the mass unit 1 to swing at multiple angles. In other embodiments, the form of the universal joint 22 can be any as long as it can ensure that the mass unit 1 can swing at multiple angles, such as a three-pin universal joint, a ball-fork universal joint, etc.

[0055] like Figure 1 and Figure 6 As shown, the swing arm unit 2 is swingably connected to the controlled structure 4 through a force transmission frame 5. The force transmission frame 5 is set so that the force of the controlled structure 4 can be evenly and effectively transmitted to the device, ensuring the vibration reduction and energy consumption effect of the device. At the same time, the force transmission frame 5 includes a force transmission top plate 51, a connecting member 52 and a force transmission bottom plate 53 connected in sequence, wherein the swing arm unit 2 is located inside the force transmission frame 5, and the swing arm unit 2 is swingably mounted on the force transmission top plate 51; the force transmission bottom plate 53 is provided with a curved surface mounting groove adapted to the concave curved plate 321, and the conductor plate 32 is installed in the curved surface mounting groove; the connecting member 52 is a plurality of connecting rods, and the plurality of connecting rods are arranged at intervals along the outer periphery of the force transmission top plate 51 and the force transmission bottom plate 53. It ensures the effective transmission of the force of the controlled structure 4, and the layout structure is compact and occupies a small space. In other embodiments, the setting of the connecting member 52 is sufficient as long as it can ensure the effective transmission of the force, such as it can also be set as a connecting sleeve.

[0056] In this embodiment, the bottom surface of the annular permanent magnet 31 is a plane, and the concave curved plate 321 is a spherical curved plate. The center of the annular permanent magnet 31 and the center of the spherical curved plate are located on the same vertical line when the mass unit is not swinging, and the swing range of the annular permanent magnet 31 with the swing of the mass unit 1 is located within the spherical curved plate. The spherical curved plate with continuous symmetry of the arc makes the gap between the conductor plate 32 and the permanent magnet assembly symmetrical, and the gap continuously decreases from the center to the edge, which further improves the energy consumption and vibration reduction effect of the device; at the same time, the spherical curved plate simplifies the configuration method of the configuration parameters and improves the configuration efficiency of the device. In other embodiments, the shape of the concave curved plate 321 can be a structure in which the curvature gradually increases from the center to the outer edge, and the gap between the conductor plate 32 and the permanent magnet assembly decreases from the center to the edge. For example, the concave curved plate 321 can also be set as an elliptical surface or a parabolic plate body.

[0057] More preferably, the mass unit 1 includes a mass block 11, a mass block back plate 12 and a permanent magnet back plate 13, and the energy dissipation unit 3 also includes a conductor back plate 33; the mass block back plate 12, the mass block 11, the permanent magnet back plate 13 and the annular permanent magnet 31 are connected in sequence. Among them, the mass block back plate 12 is connected to the swing arm unit 2; the permanent magnet back plate 13 and the conductor back iron are both made of high magnetic permeability materials to reduce the magnetic resistance and leakage of the magnetic circuit, enhance the magnetic flux density and heat transfer efficiency in the permanent magnet assembly and the conductor plate 32, and have high energy dissipation density and good heat dissipation effect; the conductor plate 32 is connected to the controlled structure 4 through the conductor back plate 33, and the conductor plate 32 is usually made of non-ferromagnetic materials with high electrical conductivity (such as copper, aluminum, etc.) to increase the intensity of eddy currents in the conductor plate 32. The arrangement of the mass block back plate 12 and the permanent magnet back plate 13 of the present invention further improves the energy dissipation and vibration reduction effect of the device, and has a compact structure and occupies a small space.

[0058] In this embodiment, the mass block back plate 12, the mass block 11 and the permanent magnet back plate 13 are connected in series through screws and fixed to each other through nuts located on the mass block back plate 12; the permanent magnet back plate 13 is fixedly connected to the annular permanent magnet 31. In other embodiments, the connection between the mass block 11, the mass block back plate 12 and the permanent magnet back plate 13 only needs to ensure that the components are directly and reliably connected to each other.

[0059] More preferably, if Figure 5 and Figure 6 As shown, the circular shapes of the annular permanent magnets 31 overlap, the magnetic poles of the annular permanent magnets 31 are alternately arranged along the radial direction of the annular permanent magnets 31, and each annular permanent magnet 31 includes two annular permanent magnet blocks, the two annular permanent magnet blocks have different magnetic poles, and are arranged in a superimposed manner. The alternating radial magnetic poles of the annular permanent magnets 31 and the superimposed arrangement of the annular permanent magnet blocks with different magnetic poles further improve the energy consumption and vibration reduction effect of the device.

[0060] Figure 7 and Figure 8 The installation relationship between the pendulum variable damping device of the present invention and the controlled structure 4 is shown. Taking the application to the wind turbine tower as an example, the force transmission bottom plate 53 of the force transmission frame 5 is fixed to the connection platform inside the wind turbine tower by fasteners. In other embodiments, the connection and fixing position of the force transmission frame 5 and the controlled structure 4 (wind turbine tower) can be installed as long as the force of the controlled structure 4 is effectively transmitted to the device, such as the force transmission top plate 51 of the force transmission frame 5 can also be connected to the connection platform inside the tower.

[0061] When the wind turbine tower is vibrated by external load, the mass unit 1 will swing, which will drive the permanent magnet assembly and the conductor plate 32 to move relative to each other, thereby cutting the magnetic flux lines and generating eddy currents in the conductor plate 32. The eddy currents generate an electromagnetic field with the opposite polarity to the magnetic field of the permanent magnet assembly itself. The two electromagnetic fields with opposite polarities hinder each other's movement, generating an eddy current damping effect, so that the swing of the mass unit 1 is converted into heat energy generated by the eddy current, and the heat energy is consumed through conduction through the air. Under the action of the eddy current damping effect, the swing speed of the mass unit 1 becomes slower and slower, and the angle becomes smaller and smaller until it stops. Thus, the purpose of energy consumption and vibration reduction is achieved.

[0062] At the same time, when the swing amplitude of the mass block 11 increases, the gap between the conductor plate 32 and the permanent magnet assembly becomes smaller, the damping coefficient and the damping force generated by the energy dissipation unit 3 become larger, and its vibration reduction and energy dissipation capacity is improved; conversely, when the swing amplitude of the mass unit 1 becomes smaller, the gap between the conductor plate 32 and the permanent magnet assembly becomes larger, the damping coefficient and the damping force generated by the energy dissipation unit 3 become smaller, and its vibration reduction and energy dissipation capacity is reduced, ensuring that the damping device has excellent vibration reduction effect at different vibration displacements.

[0063] like Fig. 9 As shown, in the vibration reduction configuration method of the pendulum variable damping device as described above, the method of the present invention first determines the initial damping constant of the energy consumption unit 3 according to the configuration parameters of each unit. The optimal value of , combined with the finite element simulation method, the target pendulum variable damping device is simulated when the radian of the conductor plate 32 is 0, according to the initial damping constant of the energy dissipation unit 3 The optimal value of Determine the optimal number and spacing of the annular permanent magnets 31, as well as the minimum spacing between the annular permanent magnets 31 and the conductor plate 32, and then adjust the damping coefficient according to the variable damping coefficient. c Determine the theoretical damping force generated by energy dissipation unit 3 , continuously adjust the curvature of the conductor plate 32 in the model, and determine the optimal curvature of the conductor plate 32, which can match the structure of the pendulum-type variable damping device to achieve the optimal configuration, so as to maximize the damping and vibration reduction effect of the device.

[0064] Since the conductor plate 32 of the variable damping device of the present invention is set as a concave curved plate 321, and the permanent magnet assembly is set as a plurality of annular permanent magnets 31, how to select the configuration parameters of the improved components (such as the number and spacing of the annular permanent magnets 31, the spacing between the annular permanent magnets 31 and the conductor plate 32, and the curvature of the concave curved plate 321) becomes the basis for ensuring the variable damping function of the device. The present invention sets a vibration reduction configuration method on the basis of the improved variable damping device to optimize the configuration parameters of the pendulum variable damping device, so that the improved pendulum variable damping device can be actually applied and implemented, and the damping vibration reduction effect of the present invention can be maximized by optimizing the configuration parameters.

[0065] The present invention optimizes the configuration of the number of annular permanent magnets 31, the spacing between the annular permanent magnets 31, and the spacing between the annular permanent magnets 31 and the conductor plate 32 in the configuration parameters. The process is: finite element simulation is performed on the pendulum-type variable damping device, and the curvature of the conductor plate 32 is set to 0 (i.e., a flat plate) during the finite element simulation process. The curvature of the conductor plate 32 does not participate in the numerical simulation of the above configuration parameters, which avoids the influence of the curvature of the conductor plate 32 on the confirmation of the above configuration parameters, so as to obtain the optimal configuration parameter configuration and finally obtain the optimal damping and vibration reduction effect; and because the curvature of the conductor plate 32 is set to zero, the complexity of the device simulation is reduced and the simulation efficiency is improved.

[0066] At the same time, the initial damping constant of energy consumption unit 3 is calculated based on the configuration parameters of each unit. The optimal value of In the simulation process of finite element simulation, the initial damping constant of energy consumption unit 3 is made close to the initial damping constant by continuous simulation. The optimal value of , thereby obtaining the optimal number and spacing of the annular permanent magnets 31 , as well as the minimum spacing between the annular permanent magnets 31 and the conductor plate 32 .

[0067] After setting the parameters such as the number and spacing of the annular permanent magnets 31, the minimum spacing between the annular permanent magnets 31 and the conductor plate 32, etc., further according to the theoretical damping force generated by the energy dissipation unit 3 Determine the optimal curvature of the conductor plate 32, that is, when simulating, the damping force generated by the energy dissipation unit 3 is equal to the theoretical damping force. The present invention simulates the configuration parameters of the permanent magnet unit and the configuration parameters of the conductor plate 32 in a hierarchical manner, which can simplify the simulation process and greatly improve the configuration efficiency.

[0068] See also Fig. 9 The specific steps of the vibration reduction configuration method of the pendulum variable damping device of the present invention are:

[0069] Step 1), determine the mass of mass unit 1 , Stiffness of mass unit 1 , the optimal damping ratio of energy dissipation unit 3 and the travel limit of mass unit 1 .

[0070] Among them, the mass of mass unit 1 It can be determined according to the overall bearing capacity of the controlled structure 4 and the local bearing capacity of the installation location, and the installation space of the controlled structure 4. For example, the mass unit 1 The mass unit 1 is set within the bearing capacity of the controlled structure 4 and meets the installation requirements according to the installation space of the controlled structure 4. The mass unit 1 has a mass of It includes the total mass of the mass block back plate 12 , the mass block 11 and the permanent magnet back plate 13 .

[0071] Among them, the optimal damping ratio of energy consumption unit 3 is It can be determined according to the energy consumption demand of the controlled structure 4. For example, the optimal damping ratio of the energy consumption unit 3 is The fixed point method can be used to determine the optimal damping ratio of the energy consuming unit 3. The principle of the fixed point method is to convert the recursive formula of the series into a geometric series or an arithmetic series, thereby simplifying the solution of the problem. It can be applied to occasions where the energy consumption demand of the controlled structure 4 is low, and quickly obtain the optimal damping ratio of the energy consuming unit 3. .

[0072] The optimal damping ratio of energy-consuming unit 3 is determined by using the fixed point method. The optimal formula is:

[0073] ,

[0074] in, is a preset coefficient in the range of (0,1], is the ratio between the mass of mass unit 1 and the modal mass of the target mode of the controlled structure 4, is the modal quality of the target mode of the controlled structure 4. Before the damping device is set, it can be determined according to the type of the controlled structure 4.

[0075] When the When , it corresponds to the optimal damping ratio of energy dissipation unit 3 calculated by the traditional fixed point method. .

[0076] Preferably, the optimal damping ratio of the energy consumption unit 3 is It can also be determined by using the improved fixed point method, for example , that is, according to Determining the Optimal Damping Ratio , which can further improve the convergence speed and accuracy of the iteration.

[0077] More preferably, the optimal damping ratio of the energy consumption unit 3 is It can also be determined by the maximum modal damping ratio method, for example, ,according to Determining the Optimal Damping Ratio , further improve the optimal damping ratio of energy consumption unit 3 The accuracy of the energy dissipation unit 3 is thus further improved. When the preset coefficient Select large, the optimal damping ratio of energy dissipation unit 3 The accuracy is higher and the damping and vibration reduction ability of the device is better.

[0078] In this embodiment, the stiffness of mass unit 1 is The mass of mass unit 1 can be , the vibration frequency of mass unit 1 It is calculated that, at the same time, the vibration frequency of mass unit 1 is The ratio of the mass of mass unit 1 to the modal mass of the target mode of the controlled structure 4 can be used. , and the frequency of the target mode of the controlled structure 4 Optionally, the stiffness of mass unit 1 is determined by calculation The calculation formula is:

[0079] ,

[0080] in, is the vibration frequency of mass unit 1, is the frequency of the target mode of the controlled structure 4, the frequency of the target mode of the controlled structure 4 is the natural frequency of the controlled structure 4, is the ratio between the mass of mass unit 1 and the modal mass of the target mode of the controlled structure 4, is the modal mass of the target mode 4 of the controlled structure.

[0081] In other embodiments, the optimal damping ratio of the energy consumption unit 3 is and the stiffness of mass element 1 It can also be determined in other ways according to requirements.

[0082] In this embodiment, the travel limit of mass unit 1 is the limit stroke value of the mass unit 1 in the horizontal swing direction, which can be determined according to the actual installation space inside the controlled structure 4. For example, it is based on the standard that the mass unit 1 does not touch the internal components of the controlled structure 4 when it swings to the limit position in the horizontal direction. The safety distance between the limit swing position of the mass unit 1 and the inside of the controlled structure 4 can also be pre-set according to actual conditions.

[0083] Preferably, in step 1), in addition to determining the above parameters, other parameters may also be set, for example, the rigid swing rod length of the swing arm unit 2 may also be determined. L Optionally, determine the rigid swing rod length of the swing arm unit 2 L The principle can be: according to the vibration frequency of the mass unit 1 obtained above Determine the simple pendulum period of swing arm unit 2 T, according to the simple pendulum period of the swing arm unit 2 T Determine the rigid swing rod length of swing arm unit 2 L， The length of the rigid pendulum can be determined by the following formula: L :

[0084] ,

[0085] in, L is the rigid swing rod length of the swing arm unit 2, is the acceleration due to gravity, T is the single pendulum period of the swing arm unit 2, is the vibration frequency of mass unit 1. The frequency of the target mode of the controlled structure 4 is the natural frequency of the controlled structure 4.

[0086] Step 2), according to the mass of mass unit 1 , Stiffness of mass unit 1 , the optimal damping ratio of energy dissipation unit 3 and the travel limit of mass unit 1 Calculate the initial damping constant of energy consumption unit 3 The optimal value of .

[0087] When the amplitude of the controlled structure 4 is large and / or the installation space is small, the required damping of the energy dissipation unit 3 is large, and the corresponding initial damping constant is Correspondingly, when the amplitude of the controlled structure 4 is small and / or the installation space is large, the required damping of the energy dissipation unit 3 is small, and the corresponding initial damping constant is This embodiment uses the above characteristics to further determine the coefficient according to the amplitude of the controlled structure 4 and / or the size of the installation space. p , and then according to the coefficient p Combine various parameters to finally determine the initial damping constant The optimal value of , so that the controlled structure 4 with different amplitudes and different installation spaces can be matched to determine the initial damping constant The optimal value of When the amplitude of the controlled structure 4 is large and / or the installation space is small, a larger initial damping constant is used. Accordingly, when the amplitude of the controlled structure 4 is small and / or the installation space is large, a smaller initial damping constant is used. That is, when the amplitude of the controlled structure 4 is large and / or the installation space is small, the selection coefficient p is a large coefficient, making the initial damping constant The optimal value of The larger the value, the higher the damping of the energy consumption unit 3; when the amplitude of the controlled structure 4 is small or the installation space is large, the coefficientp is a small coefficient, so that the initial damping constant The optimal value of The value is small. At this time, the damping reduction of the energy-consuming unit 3 can also meet the vibration reduction requirements of the controlled structure 4, which reduces energy consumption and saves costs.

[0088] Optionally, the initial damping constant of the energy consumption unit 3 is The optimal value of It can be calculated according to the following formula:

[0089] ,

[0090] in, p It is a coefficient determined in advance according to the amplitude of the controlled structure 4 and the installation space. p In normal cases, the value is 1, which means that the installation space of the controlled structure 4 is sufficient and the amplitude of the controlled structure 4 is within the normal amplitude requirement range; when the installation space of the controlled structure 4 is small and / or the amplitude of the controlled structure 4 is large, the vibration reduction control requirement is high, p Take 2 or 3, p The larger the value, the smaller the initial damping constant. The optimal value of The larger the value is, the better the damping and vibration reduction effect of the energy consumption unit 3 is.

[0091] It can be seen that, based on the above formula, the present invention can adjust the initial damping constant of the energy consumption unit 3 according to the actual installation space and amplitude of the controlled structure 4. The optimal value of , so that the device can obtain the optimal configuration parameter value based on the different installation space, amplitude and damping requirements of the controlled structure 4, meet the damping and vibration reduction requirements of different controlled structures 4, and effectively improve energy utilization and save costs.

[0092] In other embodiments, the optimal initial damping constant of the energy consumption unit 3 is It can also be determined in other ways according to actual circumstances.

[0093] According to the current configuration parameters, the finite element model of the target pendulum variable damping device is constructed, and the radian of the conductor plate 32 in the energy dissipation unit 3 is set to 0. Through finite element simulation, the initial damping constant generated by the energy dissipation unit 3 is equal to or close to the initial damping constant. The optimal value of , determine the optimal number and spacing of the annular permanent magnets 31 in the permanent magnet assembly of the energy consumption unit 3, and the minimum spacing between the annular permanent magnets 31 and the conductor plate 32.

[0094] Finite element simulation is performed on the current pendulum variable damping device. When simulating, based on the mass of mass unit 1 in step 1) , travel limit of mass unit 1 The simulation model of the pendulum variable damping device is established by using various configuration parameters. Through simulation, the initial damping constant generated by the energy consumption unit 3 is equal to or close to the initial damping constant of the energy consumption unit 3. The optimal value of , that is, the initial damping constant generated by energy consumption unit 3 and the initial damping constant The optimal value of The error is within the preset range. At this time, the number and spacing of the annular permanent magnets 31 in the permanent magnet assembly of the energy consumption unit 3, and the spacing between the annular permanent magnets 31 and the conductor plate 32 are the required optimal number and spacing of the annular permanent magnets 31 and the minimum spacing between the annular permanent magnets 31 and the conductor plate 32.

[0095] In the simulation process of this embodiment, the curvature of the conductor plate 32 is set to 0, that is, it is set to a flat plate. At this time, the curvature of the conductor plate 32 does not participate in the numerical simulation, which can effectively reduce the complexity of the simulation without affecting the simulation accuracy, thereby quickly and accurately determining the optimal number of annular permanent magnets 31, the spacing of the annular permanent magnets 31, and the minimum spacing between the annular permanent magnets 31 and the conductor plate 32, and obtaining the optimal damping and vibration reduction effect; and since the curvature of the conductor plate 32 is set to zero, it reduces the complexity of the device simulation and can also improve the simulation efficiency.

[0096] At the same time, when simulating and confirming the above optimal parameters, the initial damping constant of energy consumption unit 3 is used The optimal value of As the confirmation standard of the optimal parameters, that is, during the simulation, the initial damping constant generated by the energy consumption unit 3 is equal to or close to the initial damping constant of the energy consumption unit 3. The optimal value of Determine the optimal configuration parameters, which make the above configuration parameters meet the requirements of damping energy consumption.

[0097] Preferably, in step 3), in addition to determining the above parameters, other parameters may also be determined by simulation, such as the diameter of the concave curved panel 321 and the diameter of the mass unit 1. That is, the diameter of the concave curved panel 321 and the diameter of the mass unit 1 are involved in the simulation, and the optimal value is determined by simulation, so that the initial damping constant generated by the energy consumption unit 3 is equal to the initial damping constant of the energy consumption unit 3. The optimal value of Or the error is within the preset range as standard.

[0098] Step 4), continuously adjust the curvature of the conductor plate 32 in the finite element model of the target pendulum variable damping device so that the damping force generated by the energy dissipation unit 3 is equal to or close to the theoretical damping force generated by the energy dissipation unit 3 , determine the optimal surface curvature of the conductor plate 32, the theoretical damping force According to the variable damping coefficient of energy consumption unit 3 Determine the variable damping coefficient According to the initial damping constant The optimal value of Definitely got it.

[0099] After setting the number and spacing of the annular permanent magnets 31, the spacing between the annular permanent magnets 31 and the conductor plate 32 and other parameters, the above parameters are fixed, and then further based on the theoretical damping force generated by the energy dissipation unit 3 Determine the optimal curvature of the conductor plate 32, that is, make the damping force simulated by the energy dissipation unit 3 equal to the theoretical damping force during simulation. The present invention simulates the configuration parameters of the permanent magnet unit and the configuration parameters of the conductor plate 32 in a hierarchical manner, firstly sets the curvature of the conductor plate 32 to 0 to simulate the optimal number of annular permanent magnets 31, the spacing between the annular permanent magnets 31, and the minimum spacing between the annular permanent magnets 31 and the conductor plate 32, and then further simulates the theoretical damping force generated by the energy dissipation unit 3. Determining the optimal surface curvature of the conductor plate 32 can simplify the simulation process and greatly improve the configuration efficiency. At the same time, it can also effectively ensure the accuracy of the simulation and quickly obtain accurate optimal damping and vibration reduction configuration parameters to achieve the best damping and vibration reduction effect.

[0100] Optionally, the theoretical damping force generated by the energy dissipation unit 3 is calculated The optimal calculation formula is:

[0101] ,

[0102] in, is the swing amplitude of the mass unit. is the oscillation speed of the mass unit, is the variable damping coefficient of the energy dissipation unit.

[0103] Due to the determination of the theoretical damping force generated by the energy dissipation unit 3 Variable damping coefficient The swing amplitude of the mass unit p Second-order correlation ( ), when the coefficient p When the value is large (such as p =2 or 3), variable damping coefficient of energy dissipation unit 3 The exponential increase makes the theoretical damping force generated by the energy dissipation unit 3 The theoretical damping force increases exponentially. As a standard for confirming the optimal curvature of the conductor plate 32, the curvature of the conductor plate 32 is set closer to the damping requirement, and the curvature of the conductor plate 32 is set more accurately, ensuring that the device provides sufficient damping force when the amplitude of the controlled structure 4 is large and / or the installation space is small and the vibration reduction control requirements are high, thereby better meeting the damping and vibration reduction requirements of the device.

[0104] The present invention optimizes the configuration parameters by using different determination criteria. When simulating and confirming the optimal curvature of the conductor plate 32, the theoretical damping force generated by the energy dissipation unit 3 is used. As a confirmation standard, the damping force simulated by the energy consumption unit 3 is equal to the theoretical damping force during the simulation. The optimal value of the curvature of the conductor plate 32 is determined accordingly. When the curvature of the conductor plate 32 is simulated and confirmed, the theoretical damping force generated by the energy dissipation unit 3 is used. As a confirmation criterion, the initial damping constant of the energy consumption unit 3 is compared The optimal value of It is closer to the actual vibration reduction requirements of the controlled unit, so that the curvature of the surface of the conductor plate 32 is more accurate, thereby better ensuring the damping vibration reduction requirements of the device. The curvature of the surface of the conductor plate 32 ultimately meets the damping force requirements of the device, thereby ensuring excellent damping vibration reduction effects.

[0105] It can be seen that based on the above formula, the present invention can adjust the theoretical damping force generated by the energy dissipation unit 3 based on different spaces, amplitudes and different damping requirements. , so that the curvature of the surface of the conductor plate 32 can obtain the optimal value when applied to different controlled structures 4.

[0106] The present invention can adjust the optimal initial damping constant according to the actual conditions such as the installation space and amplitude of the controlled structure 4. and theoretical damping force , and then make corresponding optimal adjustments to the configuration parameters, so as to ensure that the device has the optimal vibration reduction and energy consumption effect when applied to different controlled structures 4, meet the vibration reduction requirements of different controlled structures 4, and effectively improve energy utilization and save costs.

[0107] Preferably, when simulating and determining the curvature of the surface of the conductor plate 32, the curvature is designed by a polynomial parabola formula, and the polynomial parabola may be a quadratic parabola y=ax 2 +bx+c, cubic parabola y=ax 3 +bx 2 +cx+d etc. where x in the parabola formula corresponds to the horizontal distance from the center of the conductor plate 32 to the end point, y corresponds to the spherical height of the spherical curved plate, the value of x can be obtained in advance through finite element simulation, b, c and d are set to 0, and a>0.

[0108] When simulating the curvature of the conductor plate 32, different a values ​​are set to simulate different curvature amplitudes of the conductor plate 32 (for example, the larger a is, the smaller the parabola opening is, the steeper the curve is, and the larger the curvature of the curvature is). When the error is within a preset range, the corresponding simulated surface curvature of the conductor plate 32 is used as the optimal surface curvature of the conductor plate 32, and the corresponding a value is determined. Then, y is determined according to the determined a and x. The curved surface curvature of the conductor plate 32 of the present invention is convenient to obtain, efficient, and can obtain a precise curved surface curvature of the conductor plate 32, thereby ensuring the vibration reduction effect of the device.

[0109] Although the present invention has been described with reference to preferred embodiments, various modifications may be made thereto and parts thereof may be replaced by equivalents without departing from the scope of the present invention. In particular, the various technical features mentioned in the various embodiments may be combined in any manner as long as there are no structural conflicts. The present invention is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.

Claims

1. A pendulum-type variable damping device, comprising a mass unit, a swing arm unit and an energy dissipation unit, wherein the mass unit is swingably connected to a controlled structure through the swing arm unit, characterized in that: The energy consumption unit includes a permanent magnet assembly and a conductor plate. The permanent magnet assembly is installed on the mass unit, and the permanent magnet assembly includes a plurality of annular permanent magnets with different diameters and mutually nested; the conductor plate is installed on the controlled structure, and the conductor plate is a concave curved plate with a curvature gradually increasing from the center to the outer edge, and the center of the annular permanent magnet is arranged opposite to the center of the concave curved plate; the bottom surface of the annular permanent magnet is a plane, and the center of the annular permanent magnet and the center of the concave curved plate are located on the same vertical line when the mass unit is not swinging, and the swing range of the annular permanent magnet as the mass unit swings is located within the concave curved plate.

2. The pendulum type variable damping device according to claim 1, characterized in that: The swing arm unit includes a rigid swing arm, universal joints arranged at both ends of the rigid swing arm, and a turntable connected to the universal joint. The two ends of the rigid swing arm are rotatably mounted on the controlled structure or the mass unit through the universal joint and the turntable in turn; when the rigid swing arm is set to one, the rigid swing arm is arranged in the middle of the mass unit; when the rigid swing arms are at least two, the rigid swing arms are arranged at intervals along the circumference of the mass unit.

3. The pendulum type variable damping device according to claim 2, characterized in that: The swing arm unit is swingably connected to the controlled structure through a force transmission mounting frame, and the force transmission mounting frame includes a force transmission top plate, a connecting piece and a force transmission bottom plate connected in sequence. The swing arm unit is located inside the force transmission mounting frame and is swingably mounted on the force transmission top plate; the force transmission bottom plate is provided with a curved mounting groove adapted to the concave curved plate, and the conductor plate is mounted in the curved mounting groove.

4. The pendulum type variable damping device according to any one of claims 1 to 3, characterized in that: The concave curved plate is a spherical curved plate, an ellipsoidal curved plate or a parabolic curved plate.

5. The pendulum type variable damping device according to any one of claims 1 to 3, characterized in that: The mass unit includes a mass block, a mass block backplate and a permanent magnet backplate, the energy consumption unit also includes a conductor backplate, the mass block backplate, the mass block, the permanent magnet backplate and the annular permanent magnet are connected in sequence, the swing arm unit is connected to the mass block backplate, and the conductor plate is connected to the controlled structure through the conductor backplate.

6. The pendulum type variable damping device according to any one of claims 1 to 3, characterized in that: The circular shapes of the annular permanent magnets overlap, the magnetic poles of the annular permanent magnets are alternately arranged along the radial direction of the annular permanent magnets, and each annular permanent magnet includes two annular permanent magnet blocks with different magnetic poles, and the two annular permanent magnets are arranged in a superimposed manner.

7. A vibration reduction configuration method for a pendulum type variable damping device according to any one of claims 1 to 6, characterized in that: The steps include: Step 1) Determine the configuration parameters of the target pendulum variable damping device, wherein the configuration parameters include the mass of the mass unit , the stiffness of the mass unit , the optimal damping ratio of the energy dissipation unit and the travel limits of the mass unit ; Step 2) According to the mass of the mass unit , the stiffness of the mass unit , the optimal damping ratio of the energy dissipation unit and the travel limits of the mass unit Calculate the initial damping constant of the energy dissipation unit The optimal value of ; Step 3) Construct a finite element model of the target pendulum variable damping device according to the current configuration parameters, and set the curvature of the conductor plate in the energy dissipation unit to 0. Through finite element simulation, the initial damping constant generated by the energy dissipation unit is equal to or close to the initial damping constant. The optimal value of , determine the optimal number and spacing of annular permanent magnets in the permanent magnet assembly of the energy consumption unit, and the minimum spacing between the annular permanent magnets and the conductor plate; Step 4) Continuously adjust the curvature of the conductor plate in the finite element model of the target pendulum variable damping device so that the damping force generated by the energy dissipation unit is equal to or close to the theoretical damping force generated by the energy dissipation unit. , determine the optimal conductor plate surface curvature, the theoretical damping force The variable damping coefficient C of the energy consumption unit is determined according to the initial damping constant The optimal value of Definitely got it.

8. The vibration reduction configuration method according to claim 7, characterized in that: In step 2), the coefficient is first determined based on the amplitude of the controlled structure and the installation space. p , then according to the coefficient p and the mass of the mass unit , the stiffness of the mass unit , the optimal damping ratio of the energy dissipation unit and the travel limits of the mass unit The initial damping constant of the energy dissipation unit is calculated according to the following formula: The optimal value of : ， in, is a preset coefficient in the range of (0,1], is the ratio between the mass of the mass unit and the modal mass of the target mode of the controlled structure, is the modal mass of the target mode of the controlled structure.

9. The vibration reduction configuration method according to claim 8, characterized in that: In step 4), the theoretical damping force generated by the energy consuming unit is calculated according to the variable damping coefficient C of the energy consuming unit according to the following formula: : ， in, is the swing amplitude of the mass unit.

10. The vibration reduction configuration method according to claim 7, 8 or 9, characterized in that: In step 1), the stiffness of the mass unit According to the mass of the mass unit and the vibration frequency of the mass unit The vibration frequency of the mass unit is calculated as According to the frequency of the target mode of the controlled structure And the ratio of the mass of the mass unit to the modal mass of the target mode of the controlled structure The calculation expression is: ,in, is the modal mass of the target mode of the controlled structure.

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