Pendulum-type tuned mass damper

Abstract

Provided in the present invention is a pendulum-type tuned mass damper, comprising a mass unit, a pendulum arm unit and an energy dissipation unit, wherein the mass unit comprises an upper mass block and a lower mass block, the upper mass block is oscillatingly connected to a controlled structure by means of the pendulum arm unit, and the lower mass block is horizontally movably supported on the controlled structure by means of a horizontal guide assembly; and the energy dissipation unit comprises a linear damping assembly and a non-linear damping assembly, the linear damping assembly is arranged at the bottom of the lower mass block, the non-linear damping assembly comprises linear dampers symmetrically arranged on two sides of the mass unit, and the upper mass block and the lower mass block are connected to each other by means of the linear dampers. The present invention has the advantages of a reduced occupied space under the condition of the same vibration frequency and effective mass of the mass unit, a good damping effect, etc.

Description

A pendulum-type tuned mass damper Technical Field

[0001] This invention relates to the field of damping and vibration reduction, and more particularly to a pendulum-type tuned mass damper. Background Technology

[0002] Tuned mass dampers (TMDs) are widely used for vibration suppression and attenuation in large structures such as bridges. They mainly consist of mass elements, stiffness elements, and damping elements, achieving vibration reduction by tuning their own frequency to be close to the vibration frequency of the structure. Among them, the pendulum-type tuned mass damper is a commonly used type. Its stiffness element (pendulum arm element) has a long pendulum length, resulting in a large damper size. When applied to space-constrained vibration reduction applications such as wind turbines (where internal facilities are numerous and space is compact) and high-rise buildings, the effective stroke of the pendulum-type tuned mass damper is limited, thus failing to achieve excellent vibration reduction effects. Furthermore, existing tuned mass dampers typically use linear damping for energy dissipation, which makes it difficult to simultaneously meet energy dissipation and vibration reduction requirements under normal and extreme conditions. There is a risk of lateral collision between the mass element and the controlled structure under extreme conditions, and the pendulum-type tuned mass damper exhibits poor safety and stability in extreme environments. Summary of the Invention

[0003] The technical problem to be solved by the present invention is to overcome the shortcomings of the prior art and provide a pendulum tuned mass vibration damper that reduces the space occupied and has excellent vibration reduction effect while having the same vibration frequency and effective mass of the same mass unit.

[0004] To solve the above-mentioned technical problems, the technical solution proposed by this invention is as follows:

[0005] A pendulum-type tuned mass damper includes a mass unit, a swing arm unit, and an energy dissipation unit. The mass unit includes an upper mass block and a lower mass block. The upper mass block is oscillatingly connected to a controlled structure via the swing arm unit, and the lower mass block is horizontally movable and supported on the controlled structure via a horizontal guide assembly. The energy dissipation unit includes a linear damping assembly and a nonlinear damping assembly. The linear damping assembly is located at the bottom of the lower mass block, and the nonlinear damping assembly includes linear dampers symmetrically arranged on both sides of the mass unit. The upper mass block and the lower mass block are connected via the linear dampers.

[0006] As a further improvement to the above technical solution:

[0007] The pendulum-type tuned mass damper also includes a vertical guide assembly, which includes an axial guide sleeve and a guide rod that are nested together. The axial guide sleeve is vertically installed on the upper mass block, and the guide rod is fixed to the lower mass block. The top end of the guide rod passes through the axial guide sleeve, and the top end of the guide rod is provided with an upper limit part to prevent the upper mass block and the lower mass block from separating from each other.

[0008] The pendulum-type tuned mass damper also includes a limiting spring to prevent the mass unit from colliding beyond its limit. The guide rod is provided with a lower limiting part that can move along the axial direction of the guide rod. The limiting spring is installed between the upper limiting part and the lower limiting part. An over-limit collision space is left between the axial guide sleeve and the lower limiting part to allow them to contact each other when the upper mass block's displacement exceeds the limit.

[0009] The pendulum-type tuned mass damper also includes an upper mass block mounting bracket, wherein the upper mass block is placed on the upper part of the upper mass block mounting bracket, and a guide mounting space is provided at the lower part of the upper mass block mounting bracket. The axial guide sleeve is located in the guide mounting space and is mounted on the upper mass block mounting bracket through a horizontal mounting bracket.

[0010] The upper mass block mounting frame includes an upper frame for placing the upper mass block, a lower frame for providing a guide mounting space, and a horizontal connecting plate connecting the upper frame and the lower frame. The swing arm unit includes a swing arm and a fixed connector. The horizontal connecting plate is provided with a hinge hole with an arc-shaped inner sidewall. The swing arm passes through the hinge hole and is fixed to the lower frame by the fixed connector.

[0011] A limiting buffer is provided at the lower center of the lower mass block, and the limiting buffer cooperates with the horizontal guide component to limit the movement of the lower mass block to a preset limit position.

[0012] The horizontal guide assembly includes a dual guide rail assembly or multiple bullseye bearings;

[0013] The dual-rail assembly includes an upper rail component and a lower rail component. The lower rail component has four lower rails arranged in a cross shape. The lower slider of the lower rail component is perpendicularly connected to the upper slider of the upper rail component. The lower mass block is mounted on the upper rail of the upper rail component via a lower mounting bracket. The limiting buffer is located at the center of the cross-shaped lower rails. The linear damping components are located at the four corners of the lower mounting bracket.

[0014] When the horizontal guide assembly includes multiple bullseye bearings, the linear damping assembly is arranged offset from the bullseye bearings in the lower mounting bracket.

[0015] The mass unit is connected to the controlled structure via a force transmission frame. The force transmission frame includes a mounting frame body sleeved on the outside of the mass unit, a horizontal mounting plate located at the bottom of the mounting frame body, and a force transmission frame body connecting the mounting frame body and the controlled structure. The swing arm unit is connected to the controlled structure in sequence via the mounting frame body and the force transmission frame body. The horizontal guide assembly and the linear damping assembly are installed between the lower mass block and the horizontal mounting plate.

[0016] The mounting force transmission frame also includes a height adjustment component for adjusting the height of the swing arm unit. The height adjustment component includes a lifting adjustment frame, a lifting adjustment rope, and a rope fixing frame. The swing arm unit is hinged to the lifting adjustment frame. The lifting adjustment frame is vertically slidably mounted on the mounting frame. The rope fixing frame is located above the lifting adjustment frame. The bottom end of the lifting adjustment rope is fixedly connected to the lifting adjustment frame. The top end of the lifting adjustment rope is height-adjustably connected to the rope fixing frame through a rope clamping limiter.

[0017] The linear damping component is an eddy current damping component, which includes an energy-dissipating magnet and a conductor plate. The energy-dissipating magnet and the conductor plate are arranged opposite to each other between the lower mass block and the controlled structure.

[0018] Compared with the prior art, the advantages of the present invention are as follows:

[0019] (1) This invention is the first to split the mass unit into an upper mass block and a lower mass block. After the split setting, the swing arm length is directly proportional to the proportion of the upper mass block in the total mass of the mass unit. When the mass unit needs a specific vibration frequency, by reducing the mass proportion of the upper mass block, the swing arm length can be shorter than that of the existing single mass block swing arm. Therefore, under the same mass unit vibration frequency and the same effective mass, this invention can effectively reduce the swing arm length of the swing arm unit by splitting the upper mass block and lower mass block and adjusting the proportion of the upper mass block and lower mass block, which greatly reduces the vertical space occupied by the vibration damper. It can be applied to the vibration reduction of space-constrained structures such as wind turbines, which are mainly characterized by wind-induced vibration (with horizontal vibration as the main feature, low vibration frequency and large vibration amplitude).

[0020] (2) Based on the structure of the mass block being set up separately, this invention effectively achieves excellent vibration reduction and energy dissipation effects of the vibration damper under normal and extreme working conditions by combining linear damping components and nonlinear damping components. Specifically: the damping magnitude of the nonlinear damping component has a nonlinear relationship with the horizontal displacement of the mass block. Under normal operating conditions, the horizontal displacement of the mass unit is small, and the damping provided by the nonlinear damping component is negligible. It can achieve excellent vibration reduction effect mainly by providing damping force through the linear damping component. Under extreme working conditions, when the amplitude exceeds the preset stroke (such as earthquakes, extreme winds, or sudden stops that may cause impact), the horizontal displacement of the mass unit is large, causing the damping of the nonlinear damping component to increase nonlinearly. At this time, the nonlinear damping component starts to work. The combination of linear damping components and nonlinear damping components effectively reduces the vibration amplitude of the mass block under extreme working conditions and reduces the probability of lateral collision between the mass unit and the controlled structure.

[0021] It is evident that the vibration damper achieves excellent damping and vibration reduction effect within its design stroke through the linear damping component. Under extreme working conditions and when the amplitude exceeds the preset stroke, the vibration damper achieves excellent damping and vibration reduction effect through the combined action of the nonlinear damping component and the linear damping component. This reduces the amplitude of the tuned mass vibration damper under extreme working conditions such as earthquakes, extreme winds, or sudden stops, effectively preventing the vibration damper from over-limit collisions.

[0022] (3) The nonlinear damping component includes linear dampers symmetrically arranged on both sides of the mass unit. The linear dampers decouple the vertical motion of the upper mass block and the lower mass block, that is, release the vertical relative motion constraint between the upper mass block and the lower mass block. At this time, the lower mass block will not move vertically synchronously with the swing of the upper mass block. The lower mass block still maintains the motion in the original horizontal plane. At this time, the gap between the lower mass block and the controlled structure remains unchanged. The lower mass block can be supported on the controlled structure by moving freely in the plane through the horizontal guide component. This makes the gap of the linear damping component set at the gap unchanged, which can maintain the linear damping vibration reduction effect of the linear damping component and ensure the reliable operation of the vibration reduction function of the linear damping component.

[0023] After vertical motion decoupling, the damper's restoring force (elastic force) will be solely provided by the gravity of the upper mass block, while the gravity of the lower mass block will be entirely borne by the horizontal guide component, which does not provide a restoring force. Simultaneously, the linear damper couples the horizontal motion of the upper and lower mass blocks, meaning they move together in the horizontal direction. The damper's horizontal inertial force (the effective mass of the mass unit) is the sum of the upper and lower mass blocks, and the effective mass of the mass unit remains unchanged from that of a traditional single mass block. In other words, the upper and lower mass blocks move vertically relative to each other without affecting each other, and move together in the horizontal direction. This achieves the goal of effectively shortening the swing arm length at the same frequency and with the same effective mass, making it a necessary structural feature for shortening the swing arm length of the shock absorber and the fundamental principle of a separated mass pendulum damper.

[0024] (4) In extreme working conditions such as the breakage of the swing arm unit, the horizontal guide component can support the overall structure of the shock absorber, and the linear damper can provide buffer during the fall of the upper mass block, so that the upper mass block falls smoothly on the lower mass block, ensuring the safety of the shock absorber in extreme environments. Attached Figure Description

[0025] The invention will now be described in more detail with reference to embodiments and the accompanying drawings.

[0026] Figure 1 is a schematic diagram of the structure of the pendulum-type tuned mass vibration damper of the present invention in a specific application;

[0027] Figure 2 is the front view of Figure 1;

[0028] Figure 3 is the left view of Figure 2;

[0029] Figure 4 is a three-dimensional structural diagram of a pendulum tuned mass damper.

[0030] Figure 5 is the front view of Figure 4;

[0031] Figure 6 is a cross-sectional view of AA in Figure 5;

[0032] Figure 7 is a three-dimensional sectional view at point AA in Figure 5;

[0033] Figure 8 is a schematic diagram of a pendulum-type tuned mass damper.

[0034] Figure 9 is a three-dimensional structural diagram of the horizontal guide component.

[0035] The labels in the diagram represent:

[0036] 1. Mass Unit; 11. Upper Mass Block; 12. Lower Mass Block; 121. Lower Mounting Frame; 2. Swing Arm Unit; 21. Swing Arm; 22. Fixed Connector; 3. Energy Dissipation Unit; 31. Linear Damping Assembly; 311. Energy Dissipating Magnet; 312. Conductor Plate; 32. Nonlinear Damping Assembly; 321. Linear Damper; 4. Controlled Structure; 5. Horizontal Guide Assembly; 51. Double Guide Rail Assembly; 511. Lower Guide Rail; 512. Lower Slider; 513. Upper Slider; 514. Upper Guide Rail; 52. Bullseye Bearing; 6. Vertical Guide Assembly; 61. Axial Guide Sleeve; 62. Guide Rod; 621. 622. Upper limit position; 63. Lower limit position; 7. Over-limit collision space; 7. Limiting component; 71. Limiting spring; 72. Limiting buffer; 8. Upper mass block mounting frame; 81. Guide mounting space; 82. Horizontal mounting frame; 83. Upper frame; 84. Lower frame; 85. Horizontal connecting plate; 9. Force transmission frame; 91. Mounting frame; 92. Horizontal mounting plate; 93. Force transmission frame; 931. Mounting ring; 932. Force transmission mounting rod; 10. Height adjustment component; 101. Lifting adjustment frame; 102. Lifting adjustment rope; 103. Rope fixing frame; 104. Rope clamping limit component. Detailed Implementation

[0037] The present invention will now be described in further detail with reference to the accompanying drawings and specific embodiments, but this does not limit the scope of protection of the present invention.

[0038] Figures 1 to 8 illustrate embodiments of the pendulum-type tuned mass damper of the present invention. The pendulum-type tuned mass damper includes a mass unit 1, a swing arm unit 2, and an energy dissipation unit 3. The mass unit 1 includes an upper mass block 11 and a lower mass block 12. The upper mass block 11 is oscillatingly connected to the controlled structure 4 via the swing arm unit 2, and the lower mass block 12 is horizontally movably supported on the controlled structure 4 via a horizontal guide component 5. The energy dissipation unit 3 includes a linear damping component 31 and a nonlinear damping component 32. The linear damping component 31 is located at the bottom of the lower mass block 12, and the nonlinear damping component 32 includes linear dampers 321 symmetrically arranged on both sides of the mass unit 1. The upper mass block 11 and the lower mass block 12 are connected via the linear dampers 321. Its structure is simple and compact, and occupies little space.

[0039] This invention, for the first time, splits the mass unit 1 into an upper mass block 11 and a lower mass block 12. After the split configuration, the swing arm 21's length is directly proportional to the proportion of the upper mass block 11 in the total mass of the mass unit 1. When the mass unit 1 requires a specific vibration frequency, by reducing the mass proportion of the upper mass block 11, the swing arm 21's length can be shorter than that of the traditional single-mass-block swing arm 21. Therefore, under the same vibration frequency and effective mass of the mass unit 1, this invention, by splitting the upper mass block 11 and lower mass block 12 and adjusting their mass proportions, can effectively reduce the swing arm 21's length in the swing arm unit 2, significantly reducing the vertical space occupied by the vibration damper. This is applicable to vibration damping of space-constrained structures such as wind turbines, where wind-induced vibration (characterized by predominantly horizontal vibration, low vibration frequency, and large vibration amplitude) is predominant. Specifically, after the split configuration of the upper mass block 11 and lower mass block 12, the vibration frequency of the mass unit 1... 21 swing arm length The proportional relationship between the mass of unit 1 and the mass of mass is:

[0040]

[0041] In the formula, The vibration frequency of mass element 1, This represents the percentage of the total mass of mass block 11 in mass unit 1. It is the acceleration due to gravity. The swing arm is 21 swing length.

[0042] When mass unit 1 requires a specific vibration frequency, the smaller the proportion of the upper mass block 11, the shorter the required swing arm 21 length. It is evident that by adjusting the proportion of the upper and lower mass blocks 11 and 12, the swing arm 21 length can be shortened, reducing the setup space and making it suitable for vibration damping applications in space-constrained environments.

[0043] Based on a structure with a split mass block, this invention effectively achieves excellent vibration reduction and energy dissipation performance of the vibration damper under both normal and extreme operating conditions through a combination of linear damping component 31 and nonlinear damping component 32. Specifically, the damping coefficient of the tuned mass vibration damper... , Linear damping component 31 damping coefficient and nonlinear damping component 32 damping coefficient The relation is:

[0044]

[0045] In the formula, The damping coefficient of the tuned mass damper. The damping coefficient of the linear damping component 31 is given. It is the inherent damping coefficient of the nonlinear damping component. The damping coefficient of the nonlinear damping component 32 applied to the pendulum tuned mass damper is given by, where, The horizontal displacement is 1 unit of mass. The length of the swing arm 21. and Determined based on the characteristics of the damping component itself.

[0046] As shown in the above equation, the damping magnitude of the nonlinear damping component 32 has a nonlinear relationship with the horizontal displacement of the mass unit 1. When the horizontal displacement of the mass unit 1 is 0, the nonlinear damping is 0; as the horizontal displacement of the mass unit 1 increases, the nonlinear damping also gradually increases. The damping coefficient of the linear damping component 31 remains constant as the mass unit 1 moves, and the damping of the linear damping component 31 is directly proportional to the displacement velocity.

[0047] During normal operation, the horizontal displacement of mass unit 1 of the vibration damper is... The value is very small, at this time, The value is very small, so the damping of the nonlinear damping component 32 is negligible. It mainly provides damping through the linear damping component 31, which can achieve excellent vibration reduction effect.

[0048] The greater the vibration of the controlled structure 4, the greater the amplitude of the vibration damper. However, the vibration damper amplitude is limited by the design stroke. When the controlled structure 4 exceeds a certain amplitude, the vibration damper amplitude will exceed the design stroke. Under extreme conditions, when the amplitude exceeds the preset stroke, the preset stroke of the vibration damper is the maximum amplitude set according to the vibration reduction requirements and the size and space of the controlled structure 4. At this time, the horizontal displacement of mass element 1... big, When the value is large, the damping of the nonlinear damping component 32 increases nonlinearly. At this time, the nonlinear damping component 32 begins to provide damping force. The combination of the linear damping component 31 and the nonlinear damping component 32 effectively reduces the vibration amplitude of the mass block under extreme working conditions and reduces the probability of the mass unit 1 colliding with the controlled structure 4.

[0049] It is evident that the vibration damper achieves excellent damping and vibration reduction effect through the linear damping component 31 during normal operation. Under extreme conditions, when the amplitude exceeds the preset stroke, the vibration damper achieves excellent damping and vibration reduction effect through the combined action of the nonlinear damping component 32 and the linear damping component 31. This reduces the amplitude of the tuned mass vibration damper under extreme conditions such as earthquakes, extreme winds, or sudden stops, effectively preventing the vibration damper from over-limit collisions.

[0050] The nonlinear damping component 32 includes linear dampers 321 symmetrically arranged on both sides of the mass unit 1. The linear dampers 321 decouple the vertical motion of the upper mass block 11 and the lower mass block 12, that is, remove the vertical relative motion constraint between the upper mass block 11 and the lower mass block 12. At this time, the lower mass block 12 will not move vertically synchronously with the swing of the upper mass block 11. The lower mass block 12 still maintains the motion in the original horizontal plane. At this time, the gap between the lower mass block 12 and the controlled structure 4 remains unchanged. The lower mass block 12 can be freely supported on the controlled structure 4 in the plane through the horizontal guide component 5. This makes the gap of the linear damping component 31 set at the gap unchanged, which can maintain the linear damping vibration reduction effect of the linear damping component 31 and ensure the reliable operation of the vibration reduction function of the linear damping component 31.

[0051] After vertical motion decoupling, the restoring force (elastic force) of the damper will be provided solely by the gravity of the upper mass block 11, while the gravity of the lower mass block 12 will be entirely borne by the horizontal guide component 5, which does not provide a restoring force. Simultaneously, the linear damper 321 couples the horizontal motion of the upper mass block 11 and the lower mass block 12, meaning that the mass blocks 11 and 12 move together in the horizontal direction. The horizontal inertial force of the damper (the effective mass of mass unit 1) is the sum of the upper and lower mass blocks 11 and 12, ensuring that the effective mass of mass unit 1 remains unchanged compared to the effective mass of a traditional single mass block. In other words, the vertical relative motion of the upper mass block 11 and the lower mass block 12 is independent, while their horizontal joint motion achieves the goal of effectively shortening the pendulum length of the swing arm 21 at the same frequency and with the same effective mass. This is a necessary structural feature for shortening the pendulum length of the damper's swing arm 21 and is the fundamental principle of a separated mass pendulum damper.

[0052] Finally, in the event of a breakage of the swing arm unit 2, the horizontal guide component 5 can support the overall structure of the shock absorber, and the linear damper 321 can provide a buffering effect during the fall of the upper mass block 11, so that the upper mass block 11 falls smoothly onto the lower mass block 12. The resultant force of gravity is supported by the horizontal guide component 5 and transmitted to the bottom structure of the shock absorber, ensuring the safety of the shock absorber in unexpected extreme environments.

[0053] Furthermore, as shown in Figures 6 and 7, the pendulum-type tuned mass damper also includes a vertical guide assembly 6, which comprises an axial guide sleeve 61 and a guide rod 62. The axial guide sleeve 61 is vertically mounted on the upper mass block 11, and the guide rod 62 is fixed to the lower mass block 12. The axial guide sleeve 61 and the guide rod 62 are sleeved together, with the top end of the guide rod 62 passing through the axial guide sleeve 61. The vertical guide assembly 6 further ensures that the upper mass block 11 and the lower mass block 12 can move vertically relative to each other, and that they can move together in the horizontal direction, thereby further ensuring the effective energy dissipation and reliable operation of the damper when using separate mass blocks. Simultaneously, an upper limit stop 621 is fixedly provided at the top end of the guide rod 62. The upper limit stop 621 effectively prevents the upper mass block 11 from detaching from the lower mass block 12 when it moves to its limit position, improving the safety of the damper.

[0054] Furthermore, the pendulum-type tuned mass damper also includes a limiting spring 71. The guide rod 62 has a lower limiting portion 622 that can move axially along the guide rod 62, and the lower limiting portion 622 is located below the upper limiting portion 621. The limiting spring 71 is installed between the upper limiting portion 621 and the lower limiting portion 622, and the bottom end of the limiting spring 71 is connected to the lower limiting portion 622. An over-limit collision space 63 is provided between the axial guide sleeve 61 and the lower limiting portion 622. The size of the over-limit collision space 63 is set according to the ratio of the horizontal displacement of the mass unit 1 to the corresponding vertical displacement, and the maximum preset horizontal displacement of the mass unit 1. Specifically, based on the ratio of the horizontal displacement of the mass unit 1 to the vertical displacement, the preset vertical displacement of the mass unit 1 at the maximum preset horizontal displacement is obtained, and thus the required height of the over-limit collision space 63 is set according to the preset vertical displacement.

[0055] When mass unit 1 moves in any direction on the horizontal plane and deviates from the center position, the upper mass block 11 moves upward. When the horizontal displacement of the upper mass block 11 reaches the maximum preset horizontal displacement, the axial guide sleeve 61 contacts and collides with the lower limit part 622. At this time, the axial guide sleeve 61 will squeeze the lower limit part 622, and the limiting spring 71 located between the upper limit part 621 and the lower limit part 622 will be compressed. This provides a vertical reaction force to limit the upper mass block 11 in the horizontal direction, further effectively preventing the mass unit 1 from directly colliding with the controlled structure 4 laterally, improving the safety and reliability of the damper, and ensuring the safe operation of the controlled structure 4.

[0056] More preferably, a limiting buffer portion 72 is provided at the lower center of the lower mass block 12. When the upper mass block 11 is horizontally displaced and triggers the limiting spring 71 to limit it, the horizontal guide device will limit the movement of the limiting buffer portion 72 when the amplitude of the damper further increases, further preventing over-limit collisions. In this embodiment, the limiting buffer portion 72 is a rubber limiting buffer portion.

[0057] As can be seen, this invention has a four-stage damping function, namely: during normal operation, the linear damping component 31 provides linear damping; when the vibration damper amplitude is too large, the linear damping component 31 provides gradually increasing nonlinear damping; when the vibration damper amplitude increases further, the limiting spring 71 compresses and deforms to provide damping; when the vibration damper amplitude swings to exceed the limit position (i.e., when the outer periphery of the lower mass block 12 swings to the center position when the lower mass block 12 is not swinging), the limiting buffer part 72 plays the final stage of limiting protection. This invention greatly improves the safety of the vibration damper when it exceeds its limit through the four-stage damping of the linear damping component 31, the nonlinear damping component 32, and the limiting component 7 (limiting spring 71 and limiting buffer part 72).

[0058] As shown in Figures 6 and 7, the pendulum-type tuned mass damper also includes an upper mass block mounting frame 8. The upper mass block 11 is placed on the upper part of the upper mass block mounting frame 8; a guide mounting space 81 is provided at the lower part of the upper mass block mounting frame 8. An axial guide sleeve 61 is located within the guide mounting space 81 and is mounted to the upper mass block mounting frame 8 via a horizontal mounting frame 82. This allows the force of the mass unit 1 to be transmitted sequentially through the upper mass block mounting frame 8 and the horizontal mounting frame 82 to the axial guide sleeve 61, enabling the axial guide sleeve 61 to move synchronously with the upper mass block 11, ensuring the reliable operation of the vertical guide assembly 6; and its layout is simple, compact, and occupies little space.

[0059] Furthermore, the upper mass block mounting frame 8 includes an upper frame 83, a lower frame 84, and a horizontal connecting plate 85. The upper frame 83 holds the upper mass block 11; the lower frame 84 provides a guide mounting space 81; and the horizontal connecting plate 85 connects the upper frame 83 and the lower frame 84 to strengthen the upper mass block mounting frame 8. The swing arm unit 2 includes a swing arm 21 and a fixed connector 22. The horizontal connecting plate 85 has a hinge hole with an arc-shaped inner sidewall. The swing arm 21 passes through the hinge hole and is fixed to the lower frame 84 by the fixed connector 22. At this time, the hinge point of the swing arm 21 is located at the hinge hole, and the load-bearing point of the swing arm 21 is located at the connection point of the lower frame 84, thus separating the rotation of the swing arm 21 from the load-bearing function of the mass unit 1, improving the safety, stability, and service life of the swing arm unit 2.

[0060] As shown in Figure 9, the horizontal guide assembly 5 includes a double guide rail assembly 51, which comprises an upper guide rail component and a lower guide rail component. The lower guide rail component has four lower guide rails 511 arranged in a cross shape. The lower slider 512 of the lower guide rail component is perpendicularly connected to the upper slider 513 of the upper guide rail component. The lower mass block 12 is mounted on the upper guide rail 514 of the upper guide rail component via a lower mounting bracket 121. A limiting buffer part 72 is located at the center of the cross-shaped lower guide rails 511. Linear damping components 31 are located at the four corners of the lower mounting bracket 121. The double guide rail assembly 51 is supported on the controlled structure 4. The movement of the lower mass block 12 in any horizontal direction can be achieved by superimposing the movements of the double guide rail assembly 51 in mutually perpendicular directions. It is easy to install, has a compact structure, and occupies little space. In other embodiments, any structure of the horizontal guide component 5 that enables the lower mass block 12 to move in any horizontal direction should be within the protection scope of this invention. For example, it can also be configured as multiple bullseye bearings 52, with the linear damping component 31 and the bullseye bearings 52 installed separately on the lower mounting bracket 121.

[0061] In this embodiment, the linear damping component 31 is an eddy current damping component, which includes an energy-dissipating magnet 311 and a conductor plate 312 arranged opposite to each other. The energy-dissipating magnet 311 is fixed to the lower mass block 12, and the conductor plate 312 is fixed to the controlled structure 4. When the mass unit 1 swings, the energy-dissipating magnet 311 and the conductor plate 312 generate relative motion. At this time, the conductor plate 312 cuts the magnetic field lines, generating an eddy current damping force, so that the energy of the structure vibration is ultimately converted into heat energy from eddy currents, achieving the purpose of energy dissipation and vibration reduction. In other embodiments, the energy-dissipating magnet 311 can also be located on the controlled structure 4, and the conductor plate 312 can be located on the lower mass block 12; the energy-dissipating magnet 311 can also be a permanent magnet of other materials.

[0062] In this embodiment, the eddy current damping components are arranged at the four corners of the lower mass block 12, offset from the dual guide rail assembly 51. In other embodiments, when the horizontal guide assembly 5 is a bullseye bearing 52, the eddy current damping components can be arranged offset according to the position of the bullseye bearing 52, such as placing the bullseye bearing 52 at the four corners of the lower mass block 12, and placing the eddy current damping components in the central area or the middle area of ​​the four sides of the lower mass block 12.

[0063] In this embodiment, the mass unit 1 is connected to the controlled structure 4 via a force transmission frame 9. The force transmission frame 9 includes a mounting frame 91, a horizontal mounting plate 92, and a force transmission frame 93. The mounting frame 91 is fitted onto the outside of the mass unit 1; the horizontal mounting plate 92 is located at the bottom of the mounting frame 91; and the force transmission frame 93 connects the mounting frame 91 and the controlled structure 4. The swing arm unit 2 is connected to the controlled structure 4 sequentially via the mounting frame 91 and the force transmission frame 93. The vibration of the controlled structure 4 is transmitted to the mass unit 1 sequentially through the force transmission frame 93, the force transmission frame 9, and the swing arm unit 2. The horizontal guide assembly 5 and the linear damping assembly 31 are installed between the lower mass block 12 and the horizontal mounting plate 92, resulting in a simple and compact overall structure.

[0064] In this embodiment, the force transmission frame 93 includes a mounting ring 931 and two force transmission mounting rods 932. The mounting ring 931 is fitted and fixedly connected to the inner wall of the controlled structure 4. The two force transmission mounting rods 932 are parallel to each other, with both ends of the rods fixedly connected to the mounting ring 931. The horizontal mounting plate 92 and the mounting frame 91 are both mounted on the force transmission mounting rods 932, ensuring that the force from the controlled structure 4 can be effectively transmitted to the vibration damper. This design is compact and occupies little space. In other embodiments, the mounting ring 931 can be adjusted according to the shape of the controlled structure 4, as long as it effectively fits the inner wall of the controlled structure 4 and the force is reliably transmitted to the vibration damper.

[0065] More preferably, as shown in Figures 1 to 3, the mounting force transmission frame 9 further includes a height adjustment assembly 10, which includes a lifting adjustment frame 101, a lifting adjustment rope 102, and a rope fixing frame 103. The swing arm 21 of the swing arm unit 2 is connected to the outer periphery of the mass unit 1, and the swing arm 21 is hinged to the lifting adjustment frame 101. The hinge position of the swing arm 21 allows for adjustment of the swing length. The lifting adjustment frame 101 is vertically slidably mounted on the mounting frame 91. The rope fixing frame 103 is located above the lifting adjustment frame 101. The bottom end of the lifting adjustment rope 102 is fixedly connected to the lifting adjustment frame 101, and the top end of the lifting adjustment rope 102 is height-adjustably connected to the rope fixing frame 103 via a rope clamping limiter 104.

[0066] When the height of the swing arm 21 needs to be adjusted, the lifting adjustment rope 102 can be raised or lowered via the rope clamping limiter 104, thereby causing the lifting adjustment frame 101 located at the bottom end of the lifting adjustment rope 102 to rise or fall synchronously, realizing the raising and lowering of the swing arm 21. This invention realizes the lifting and lowering adjustment function of the swing arm 21, thereby flexibly adjusting the vibration frequency and damping coefficient of the mass unit 1, greatly providing effective application of the vibration damper in different situations. In this embodiment, the lifting adjustment rope 102 can be a wire rope or chain, etc.

[0067] In this embodiment, there are two linear dampers 321, which are symmetrically arranged on opposite sides of the mass unit 1. The two ends of each linear damper 321 are hinged to the upper mass block mounting frame 8 and the lower mounting frame 121, respectively. In other embodiments, the number of linear dampers 321 can be adjusted according to actual vibration reduction requirements. For example, linear dampers 321 can be provided on all four sides of the mass unit 1, or one or more linear dampers 321 can be provided on a single side.

[0068] Although the invention has been described with reference to preferred embodiments, various modifications can be made and components can be replaced with equivalents without departing from the scope of the invention. In particular, the technical features mentioned in the various embodiments can be combined in any manner as long as there is no structural conflict. The 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 tuned mass damper, comprising a mass unit, a pendulum arm unit, and an energy dissipation unit, characterized in that, The mass unit includes an upper mass block and a lower mass block. The upper mass block is oscillatingly connected to the controlled structure via the swing arm unit, and the lower mass block is horizontally supported on the controlled structure via a horizontal guide assembly. The energy dissipation unit includes a linear damping assembly and a nonlinear damping assembly. The linear damping assembly is located at the bottom of the lower mass block, and the nonlinear damping assembly includes linear dampers symmetrically arranged on both sides of the mass unit. The upper mass block and the lower mass block are connected via the linear dampers.

2. The pendulum-type tuned mass damper according to claim 1, characterized in that, It also includes a vertical guide assembly, which includes an axial guide sleeve and a guide rod that are nested together. The axial guide sleeve is vertically installed on the upper mass block, and the guide rod is fixed to the lower mass block. The top end of the guide rod passes through the axial guide sleeve, and the top end of the guide rod is provided with an upper limit part to prevent the upper mass block and the lower mass block from separating from each other.

3. The pendulum-type tuned mass damper according to claim 2, characterized in that, It also includes a limiting spring to prevent the mass unit from over-limiting collision. The guide rod is provided with a lower limiting part that can move along the guide rod axis. The limiting spring is installed between the upper limiting part and the lower limiting part. An over-limit collision space is left between the axial guide sleeve and the lower limiting part to allow them to contact each other when the upper mass block displacement exceeds the limit.

4. The pendulum-type tuned mass damper according to claim 3, characterized in that, It also includes an upper mass block mounting bracket, the upper mass block is placed on the upper part of the upper mass block mounting bracket, the lower part of the upper mass block mounting bracket is provided with a guide mounting space, the axial guide sleeve is located in the guide mounting space and is mounted on the upper mass block mounting bracket through a horizontal mounting bracket.

5. The pendulum-type tuned mass damper according to claim 4, characterized in that, The upper mass block mounting frame includes an upper frame for placing the upper mass block, a lower frame for providing a guide mounting space, and a horizontal connecting plate connecting the upper frame and the lower frame. The swing arm unit includes a swing arm and a fixed connector. The horizontal connecting plate is provided with a hinge hole with an arc-shaped inner sidewall. The swing arm passes through the hinge hole and is fixed to the lower frame by the fixed connector.

6. The pendulum-type tuned mass damper according to any one of claims 1 to 5, characterized in that, A limiting buffer is provided at the lower center of the lower mass block, and the limiting buffer cooperates with the horizontal guide component to limit the movement of the lower mass block to a preset limit position.

7. The pendulum-type tuned mass damper according to claim 6, characterized in that, The horizontal guide assembly includes a dual guide rail assembly or multiple bullseye bearings; The dual-rail assembly includes an upper rail component and a lower rail component. The lower rail component has four lower rails arranged in a cross shape. The lower slider of the lower rail component is perpendicularly connected to the upper slider of the upper rail component. The lower mass block is mounted on the upper rail of the upper rail component via a lower mounting bracket. The limiting buffer is located at the center of the cross-shaped lower rails. The linear damping components are located at the four corners of the lower mounting bracket. When the horizontal guide assembly includes multiple bullseye bearings, the linear damping assembly is arranged offset from the bullseye bearings in the lower mounting bracket.

8. The pendulum-type tuned mass damper according to any one of claims 1 to 5, characterized in that, The mass unit is connected to the controlled structure via a force transmission frame. The force transmission frame includes a mounting frame body sleeved on the outside of the mass unit, a horizontal mounting plate located at the bottom of the mounting frame body, and a force transmission frame body connecting the mounting frame body and the controlled structure. The swing arm unit is connected to the controlled structure in sequence via the mounting frame body and the force transmission frame body. The horizontal guide assembly and the linear damping assembly are installed between the lower mass block and the horizontal mounting plate.

9. The pendulum-type tuned mass damper according to claim 8, characterized in that, The mounting force transmission frame also includes a height adjustment component for adjusting the height of the swing arm unit. The height adjustment component includes a lifting adjustment frame, a lifting adjustment rope, and a rope fixing frame. The swing arm unit is hinged to the lifting adjustment frame. The lifting adjustment frame is vertically slidably mounted on the mounting frame. The rope fixing frame is located above the lifting adjustment frame. The bottom end of the lifting adjustment rope is fixedly connected to the lifting adjustment frame. The top end of the lifting adjustment rope is height-adjustably connected to the rope fixing frame through a rope clamping limiter.

10. The pendulum-type tuned mass damper according to any one of claims 1 to 5, characterized in that, The linear damping component is an eddy current damping component, which includes an energy-dissipating magnet and a conductor plate. The energy-dissipating magnet and the conductor plate are arranged opposite to each other between the lower mass block and the controlled structure.

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