A lever-type tuned mass damper with passive adaptive tuning function

Abstract

This invention belongs to the field of vibration control technology, specifically providing a lever-type tuned mass damper with passive adaptive tuning function, including a response sensing component, a trigger driving component, and a tuned mass damping component; the tuned mass damping component includes a first mass block, a first spring, a first damper, and a lever; the trigger driving component includes a response threshold setter, a ratchet, a pawl, and a cam structure; the response sensing component includes a second mass block, a second spring, and a second damper; when vertical displacement is sensed, the response sensing component also includes a negative stiffness unit composed of a third spring, a slide, a pulley, a connecting rod, a first rotating shaft, a second rotating shaft, and a frame; when the vibration displacement of the controlled main structure exceeds the limit, without power supply or intervention, the trigger driving component will move the lever fulcrum, changing the dynamic characteristics of the tuned mass damping component by changing the lever ratio, achieving self-tuning and maintaining high vibration reduction efficiency.

Description

Technical Field

[0001] This invention belongs to the field of vibration control technology and relates to a lever-type tuned mass damper with passive adaptive tuning function. Background Technology

[0002] Engineering structures are often subjected to various external excitation environments during service, making vibration a particularly prominent issue. Tuned mass dampers (TMDs), due to their simple structure and well-defined energy conversion mechanism, are the most commonly used passive vibration reduction devices in engineering. However, traditional TMDs have inherent drawbacks such as narrow damping bandwidth and high sensitivity to tuning accuracy. When design errors, material aging, or time-varying structural parameters cause the natural frequency of the TMD to deviate from the dominant vibration frequency of the main structure, its energy dissipation capacity decreases significantly, making it difficult to guarantee vibration reduction performance. Furthermore, conventional TMDs can only function for a single mode; when external excitation causes multiple modes of the main structure to vibrate sequentially, a single TMD is insufficient to effectively suppress multimodal responses.

[0003] To overcome the aforementioned shortcomings, various semi-active or active damping mechanisms (TMDs) have been proposed in recent years. These mechanisms adjust the dynamic characteristics of the dampers in real time or apply state-dependent control forces to the main structure, enabling them to adapt to changes in external excitation and structural characteristics, thereby maintaining high vibration reduction efficiency. However, such systems generally rely on complex control algorithms and external power supplies, and active control may lead to system stability issues, limiting overall reliability and engineering maintainability.

[0004] Therefore, there is an urgent need to develop a passive adaptive TMD with a simple structure, high reliability, and no need for external power supply, so that it can autonomously respond to changes in external excitation and structural dynamic characteristics, achieve self-tuning in a passive mode, and thus significantly improve the vibration suppression capability of the structure throughout its entire life cycle. Summary of the Invention

[0005] This invention provides a lever-type tuned mass damper with passive adaptive tuning function, including a response sensing component, a trigger driving component, and a tuned mass damping component disposed on the controlled main structure.

[0006] The tuned mass damping assembly includes a first mass block, a first spring, a first damper, a lever, and a lever fulcrum; one end of the first damper is connected to the lower end face of the first mass block, and the other end of the first damper is connected to the controlled main structure; one end of the lever is connected to the side end face of the first mass block, and the other end of the lever extends horizontally and is connected to one end of the first spring; the other end of the first spring extends vertically along the controlled main structure and is connected to the controlled main structure; the lever fulcrum is disposed on the lever.

[0007] The trigger drive assembly includes a cam structure, a ratchet, a pawl, and a response threshold setter; the ratchet is rigidly connected to the cam shaft in the cam structure; one end of the pawl is rigidly connected to the lower rod of the response threshold setter, and the other end of the pawl is engaged with the ratchet; the response threshold setter has an opening for installing the response threshold trigger rod in the response sensing assembly; a connecting shaft is provided on two parallel side faces of the lever fulcrum, and the lever fulcrum is hinged to the cam structure through the connecting shaft;

[0008] The response sensing component is installed on the controlled main structure; and the response sensing component includes a horizontal sensing component and a vertical sensing component; the horizontal sensing component is used to sense the vibration displacement of the main structure in the horizontal direction; the vertical sensing component is used to sense the vibration displacement of the main structure in the vertical direction.

[0009] Furthermore, the cam structure includes a barrel-shaped cam and a slider that mesh with each other; the slider is configured as a U-shaped structure, with its open end hinged to the lever fulcrum through two connecting shafts, and its closed end provided with a connecting hole that meshes with the barrel-shaped cam; when the barrel-shaped cam rotates, the slider is driven to slide along the central axis of the barrel-shaped cam, thereby converting the rotation of the barrel-shaped cam into the translation of the slider.

[0010] Two sets of spiral grooves with opposite directions are provided on the outer circumferential surface of the barrel cam. The two sets of spiral grooves are connected to each other through a smooth transition section at the two side end faces of the barrel cam. When the slider moves to the end of the barrel cam along one of the spiral grooves, it moves to the other spiral groove through the smooth transition section, so that the slider can automatically turn when sliding on the barrel cam, and thus the slider can move back and forth on the barrel cam.

[0011] Furthermore, the response threshold setter includes an integrally formed connecting part, an upper rod, and a lower rod; the connecting part is hinged to the camshaft of the barrel cam; one end of the upper rod is fixedly connected to the connecting part, and the other end of the upper rod extends outward; one end of the lower rod is fixedly connected to the connecting part, and the other end of the lower rod extends outward and is set at an angle to the upper rod to form an opening for installing the response threshold trigger rod in the response sensing component;

[0012] The ratchet is rigidly connected to the camshaft of the barrel cam;

[0013] One end of the pawl is rigidly connected to the lower rod, and the other end of the pawl is engaged with the ratchet.

[0014] Furthermore, the response sensing component includes a second mass block, a second spring, and a second damper;

[0015] One end of the second spring is connected to the second mass block, and the other end of the second spring extends along the vertical direction of the controlled main structure and is connected to the position in the controlled main structure that needs to sense the response.

[0016] One end of the second damper is connected to the second mass block, and the other end of the second damper extends along the vertical direction of the controlled main structure and is connected to the position in the controlled main structure that needs to sense the response.

[0017] Furthermore, the second spring and the second damper are connected in parallel.

[0018] Furthermore, when the response to be sensed is vertical vibration displacement, in order to prevent the second spring from elongating too much under the gravity of the second mass block, the response sensing component also includes a negative stiffness unit. The negative stiffness unit also includes a groove and a pulley. The groove in the negative stiffness unit is located on the inner side of the upper end face of the frame and has two pieces arranged side by side along the elongation and compression direction of the third spring.

[0019] The pulley is connected to the third spring, and there are two pulleys. Each pulley is matched with a single groove and slides within the groove, thereby guiding and limiting the direction of action of the third spring.

[0020] Furthermore, in the initial state, the response threshold trigger lever is located at the center of the opening;

[0021] When the vibration response of the controlled main structure exceeds the limit, the displacement of the second mass block relative to the controlled main structure will exceed the set threshold range of the response threshold setter. The response threshold trigger rod will reciprocate up and down to strike the upper and lower rods of the response threshold setter. When the response threshold trigger rod strikes the lower rod, the response threshold setter rotates counterclockwise, which in turn drives the pawl to rotate counterclockwise, further driving the ratchet and barrel cam to rotate counterclockwise, and finally driving the slider and lever fulcrum to move horizontally, starting the self-tuning process. When the response threshold trigger rod strikes the upper rod, the response threshold setter rotates clockwise, returning the response threshold setter to near its initial position, while simultaneously driving the pawl to rotate clockwise along the ratchet teeth, and the ratchet does not rotate.

[0022] When the vibration response of the controlled main structure exceeds the limit, the lever fulcrum will be moved, the lever ratio will change, and the tuned mass damping component will be retuned. When the effective natural frequency of the retuned structure is reached... When the control mode frequency is approximately equal to that of the controlled main structure, the vibration response of the controlled main structure will be less than the given threshold. The displacement of the second mass block relative to the position where the response needs to be sensed is within the set threshold range of the response threshold setter, and the self-tuning process ends.

[0023] Furthermore, the vibration differential equation of the second mass block is:

[0024] ;

[0025] in: This represents the absolute vibration displacement of the main structure within the inertial frame. This represents the mass of the second mass block. This is expressed as the total vertical stiffness of the second and third springs. This is expressed as the damping coefficient of the second damper. This is expressed as the displacement of the second mass block relative to the controlled main structure; It represents the absolute vibration acceleration of the main structure in the inertial frame; This is expressed as the velocity of the second mass block relative to the controlled main structure; It is expressed as the acceleration of the second mass block relative to the controlled main structure.

[0026] Furthermore, when the natural frequency of the second mass block... satisfy At that time, the displacement amplitude of the second mass block relative to the controlled main structure Approximately equal to the absolute vibration displacement amplitude of the controlled main structure ,Right now ; This is expressed as the damping ratio of the second damper;

[0027] When the natural frequency of the second mass block satisfy At that time, the ratio of the displacement amplitude of the second mass block relative to the controlled main structure to the vibration acceleration amplitude of the controlled main structure is approximately equal to a constant.

[0028] Furthermore, let the effective natural frequency of the tuned mass damping component be... ;

[0029] in: Let be the nominal natural frequency of the tuned mass damping component, and , Let this be the mass of the first mass block. This is expressed as the stiffness of the first spring; Expressed as leverage ratio, This is expressed as the distance from the fulcrum of the lever to the first spring. This is expressed as the distance from the fulcrum of the lever to the first mass block;

[0030] For a given first mass block and first spring, the nominal natural frequency of the tuned mass damping assembly remains constant. .

[0031] Compared with the prior art, the present invention has the following beneficial effects:

[0032] (1) The present invention provides a lever-type tuned mass damper, including a response sensing component, a trigger driving component and a tuned mass damper component; the response sensing component is connected to the controlled main structure and is used to sense the vibration response of the controlled main structure; when the response of the controlled main structure is greater than a given threshold, the response sensing component impacts and drives the trigger driving component to rotate, and further, the rotation of the trigger driving component drives the lever fulcrum of the tuned mass damper component to move, changing the lever ratio, thereby changing the dynamic characteristics of the tuned mass damper component, realizing the self-tuning of the tuned mass damper component, and the device is simple and reliable.

[0033] (2) The lever-type tuned mass damper provided by the present invention has a wide range of applications. Compared with the existing passive / active / semi-active vibration dampers, it can automatically sense the vibration response of the controlled main structure without external power supply and human intervention, and self-tune the tuned mass damping component to adapt to changes in external excitation and maintain high vibration reduction efficiency.

[0034] (3) The lever-type tuned mass damper provided by the present invention can deal with the detuning problem that may gradually occur during the service life of the tuned mass damper.

[0035] (4) The lever-type tuned mass damper provided by the present invention can control the vibration of multi-mode structures under broadband excitation.

[0036] In addition to the objectives, features, and advantages described above, the present invention has other objectives, features, and advantages. The invention will now be described in further detail with reference to the figures. Attached Figure Description

[0037] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. Various modifications and variations can be made to the invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the invention should be included within the scope of protection of the invention. In the drawings:

[0038] Figure 1 This is a schematic diagram of the structure of a lever-type tuned mass damper with passive adaptive tuning function in an embodiment of the present invention;

[0039] Figure 2 yes Figure 1 A schematic diagram of the structure of the response sensing component;

[0040] Figure 3 yes Figure 1 A schematic diagram of the structure of the trigger-driven component;

[0041] Figure 4 yes Figure 1Axonometric schematic diagram of the ratchet element.

[0042] in:

[0043] 1. First mass block, 2. First spring, 3. First damper, 4. Lever, 5. Lever fulcrum, 6. Cam structure, 6.1. Barrel cam, 6.2. Slider, 7. Ratchet, 8. Pawl, 9. Response threshold setter, 9.1. Upper rod, 9.2. Lower rod, 10. Second mass block, 11. Third spring, 12. Second spring, 13. Second damper, 14. Slide, 15. Pulley, 16. Response threshold trigger rod, 17. Linkage, 18. First pivot, 19. Second pivot, 20. Frame. Detailed Implementation

[0044] To make the above-mentioned objectives, features, and advantages of the present invention clearer and easier to understand, the specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. It should be noted that the accompanying drawings of the present invention are all in a simplified form and use non-precise proportions, and are only used to facilitate and clearly assist in illustrating the implementation of the present invention; the "several" mentioned in the present invention are not limited to the specific number shown in the examples in the accompanying drawings; the orientations or positional relationships indicated by terms such as "front," "middle," "rear," "left," "right," "up," "down," "top," "bottom," and "center" mentioned in the present invention are all based on the orientations or positional relationships shown in the accompanying drawings of the present invention, and do not indicate or imply that the device or component referred to must have a specific orientation, nor should they be construed as limitations on the present invention.

[0045] Example 1:

[0046] See Figures 1 to 4 As shown, the present invention provides a lever-type tuned mass damper with passive adaptive tuning function, comprising a response sensing component, a trigger driving component, and a tuned mass damping component disposed on the controlled main structure.

[0047] The response sensing component is installed on the controlled main structure and is used to sense the vibration response of the controlled main structure (specifically, the vibration displacement or acceleration of the controlled main structure).

[0048] The trigger drive component uses the kinetic energy of the controlled main structure exceeding a given vibration threshold as the energy source to drive the movement of the lever fulcrum 5 in the tuned mass damping component.

[0049] The tuned mass damping component is used to reduce the vibration response of the controlled main structure (specifically, the vibration displacement or acceleration of the controlled main structure).

[0050] As a further embodiment, the tuned mass damping assembly includes a first mass block 1, a first spring 2, a first damper 3, a lever 4, a lever fulcrum 5, and a cam structure 6.

[0051] One end of the first damper 3 is connected to the lower end face of the first mass block 1, and the other end of the first damper 3 is connected to the controlled main structure.

[0052] One end of the lever 4 is connected to the side end face of the first mass block 1, and the other end of the lever 4 extends horizontally and is connected to one end of the first spring 2.

[0053] The other end of the first spring 2 extends along the vibration direction of the controlled main structure and is connected to the controlled main structure.

[0054] The lever fulcrum 5 is set on the lever 4, and a connecting shaft is provided on each of the two parallel side end faces of the lever fulcrum 5. The lever fulcrum 5 is hinged to the cam structure 6 through the connecting shaft.

[0055] The cam structure 6 includes a barrel-shaped cam 6.1 and a slider 6.2 that mesh with each other; the slider 6.2 is preferably configured as a U-shaped structure, with its open end hinged to the lever fulcrum 5 through two connecting shafts, and its closed end provided with a connecting hole that meshes with the barrel-shaped cam 6.1; when the barrel-shaped cam 6.1 rotates, the slider 6.2 is driven to slide along the central axis of the barrel-shaped cam 6.1, thereby converting the rotation of the barrel-shaped cam 6.1 into the translation of the slider 6.2;

[0056] Preferably, the barrel-shaped cam 6.1 includes an integrally formed cam portion and a camshaft, with the cam portion located in the middle of the camshaft, i.e., camshaft extension ends are provided on both sides of the cam portion;

[0057] Two sets of spiral grooves with opposite directions are provided on the outer circumferential surface of the barrel cam 6.1. The two sets of spiral grooves are connected to each other through a smooth transition section at the two side end faces of the barrel cam 6.1. When the slider 6.2 moves along one of the spiral grooves to the end of the barrel cam 6.1, it moves through the smooth transition section to the other spiral groove to realize the automatic smooth turning of the slider 6.2, thereby enabling the slider 6.2 to reciprocate on the barrel cam 6.1.

[0058] As a further embodiment, the trigger drive component includes a ratchet 7, a pawl 8, and a response threshold setter 9;

[0059] The response threshold setter 9 includes an integrally formed connecting part, an upper rod, and a lower rod; the connecting part is hinged to the camshaft of the barrel cam 6.1; one end of the upper rod is fixedly connected to the connecting part, and the other end of the upper rod extends outward; one end of the lower rod is fixedly connected to the connecting part, and the other end of the lower rod extends outward and forms an angle with the upper rod to form an opening for installing the response threshold trigger rod 16, the size of which determines the set response threshold.

[0060] The ratchet 7 is rigidly connected to the camshaft of the barrel cam 6.1;

[0061] One end of the pawl 8 is rigidly connected to the lower rod, and the other end of the pawl 8 is engaged with the ratchet 7.

[0062] Preferably, the response sensing component includes a second mass block 10, a second spring 12, and a second damper 13;

[0063] One end of the second spring 12 is connected to the second mass block 10, and the other end of the second spring 12 extends along the vibration direction of the controlled main structure and is connected to the position in the controlled main structure that needs to sense the response.

[0064] One end of the second damper 13 is connected to the second mass block 10, and the other end of the second damper 13 extends along the vibration direction of the controlled main structure and is connected to the position in the controlled main structure where the response needs to be sensed.

[0065] Furthermore, the second spring 12 and the second damper 13 are connected in parallel.

[0066] Preferably, when the response to be sensed is vertical vibration displacement, in order to prevent excessive elongation of the second spring 12 under the gravity of the second mass block 10, the response sensing component further includes a negative stiffness unit. The negative stiffness unit can be specifically configured according to actual needs. Specifically, in this embodiment, the negative stiffness unit includes a third spring 11, a slide 14, a pulley 15, a first connecting rod 17, a first rotating shaft 18, a second rotating shaft 19, and a frame 20.

[0067] The second mass block 10 and the third spring 11 are connected by the first connecting rod 17; the first connecting rod 17 and the second mass block 10 are hinged by the first rotating shaft 18; the first connecting rod 17 and the third spring 11 are hinged by the second rotating shaft 19; the elongation and compression of the third spring 11 are restricted to the horizontal direction by the pulley 15 provided in the slide groove 14; one end of the third spring 11 is fixed to the frame 20, and the frame 20 is fixed at a suitable position on the controlled main structure that needs to sense the response. Specifically, a first connecting seat is provided on the side end face of the second mass block 10; one end of the first connecting rod 17 is hinged to the first connecting seat through the first rotating shaft 18, and the other end of the first connecting rod 17 is hinged to one end of the third spring 11 through the second rotating shaft 19; the other end of the third spring 11 is fixedly connected to the frame 20, and the frame 20 is connected to the position in the controlled main structure that needs to sense the response.

[0068] More preferably, the negative stiffness unit further includes a groove 14 and a pulley 15;

[0069] The slide groove 14 is provided on the inner side of the upper end face of the frame 20, and is provided with two pieces arranged side by side along the elongation and compression direction of the third spring 11.

[0070] The pulley 15 is connected to the third spring 11, and there are two pulleys 15. Each pulley 15 is matched with a single slide groove 14 and slides within the slide groove 14, thereby guiding and limiting the direction of action of the third spring 11.

[0071] More preferably, a response threshold trigger lever 16 is provided on the second mass block 10.

[0072] As a further embodiment, the controlled main structure described in this embodiment includes, but is not limited to, engineering structures that frequently experience vibration, such as bridge structures, building structures, and automobile structures. The lever-type tuned mass damper with passive adaptive tuning function proposed in this invention can be extended to numerous engineering structure vibration control application scenarios.

[0073] As a further embodiment, the working principle of the lever-type tuned mass damper with passive adaptive tuning function described above is as follows:

[0074] In the initial state, the response threshold trigger lever 16 is located at the center of the opening of the response sensing component;

[0075] When the vibration response of the controlled main structure exceeds the limit, the displacement of the second mass block 10 relative to the position to be sensed and responded to will exceed the set threshold range of the response threshold setter 9. The response threshold trigger rod 16 will reciprocate up and down to strike the upper and lower rods of the response threshold setter 9. When the response threshold trigger rod 16 strikes the lower rod, the response threshold setter 9 rotates counterclockwise (counterclockwise specifically refers to the rotation based on...). Figure 4 (From the perspective shown), which in turn causes the pawl 8 to engage the teeth of the ratchet 7 and rotate counterclockwise, further causing the ratchet 7 and the barrel cam 6.1 to rotate counterclockwise, and finally causing the slider 6.2 and the lever fulcrum 5 to move horizontally, starting the self-tuning process; when the response threshold trigger rod 16 strikes the upper rod, the response threshold setter 9 rotates clockwise (clockwise specifically refers to based on Figure 4 (From the perspective shown), the response threshold setter 9 is moved back to near its initial position, while the pawl 8 rotates clockwise along the teeth of the ratchet 7, and the ratchet 7 does not rotate.

[0076] When the vibration response of the controlled main structure exceeds the limit, the lever fulcrum 5 will be moved, the lever ratio will change, and the tuned mass damping component will be retuned. When the retuning reaches a suitable frequency, the vibration response of the controlled main structure will be less than the given threshold. The displacement of the second mass block 10 relative to the position to be sensed is within the set threshold range of the response threshold setter 9, and the self-tuning process ends.

[0077] Preferably, the vibration differential equation of the second mass block 10 is:

[0078] ;

[0079] in: This represents the absolute vibration displacement of the main structure within the inertial frame. This is represented by the mass of the second mass block 10. This is expressed as the total vertical stiffness of the second spring 12 and the third spring 11. This is expressed as the damping coefficient of the second damper 13. This is expressed as the displacement of the second mass block 10 relative to the controlled main structure; It is expressed as the absolute vibration acceleration of the controlled main structure in the inertial frame; This is expressed as the velocity of the second mass block 10 relative to the controlled main structure; It is expressed as the acceleration of the second mass block 10 relative to the controlled main structure.

[0080] Preferably, when the natural frequency of the second mass block 10 is... satisfy At that time, the displacement amplitude of the second mass block 10 relative to the controlled main structure Approximately equal to the absolute vibration displacement amplitude of the controlled main structure ,Right now ; This is expressed as the damping ratio of the second damper 13;

[0081] When the natural frequency of the second mass block 10 satisfy At that time, the ratio of the displacement amplitude of the second mass block 10 relative to the controlled main structure to the vibration acceleration amplitude of the controlled main structure is approximately equal to a constant.

[0082] Preferably, the effective natural frequency of the tuned mass damping component is set to... ,in: Let be the nominal natural frequency of the tuned mass damping component, and , Let the mass of the first mass block 1 be represented. This is expressed as the stiffness of the first spring 2; Expressed as leverage ratio, This is expressed as the distance from the lever fulcrum 5 to the first spring 2. This is expressed as the distance from the lever fulcrum 5 to the first mass block 1;

[0083] For a given first mass block 1 and first spring 2, the nominal natural frequency of the tuned mass damping assembly remains constant. ;

[0084] When the lever fulcrum 5 is in different positions, the effective natural frequency of the tuned mass damping component Different. When the effective natural frequency of the tuned mass damping component... When the frequency is approximately equal to the control mode frequency of the controlled main structure, the tuned mass damping component can effectively control the vibration displacement or acceleration of the controlled main structure.

[0085] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A lever-type tuned mass damper with passive adaptive tuning function, characterized in that, This includes a response sensing component, a trigger driving component, and a tuned mass damping component installed on the controlled main structure; The tuned mass damping assembly includes a first mass block (1), a first spring (2), a first damper (3), a lever (4), and a lever fulcrum (5); one end of the first damper (3) is connected to the lower end face of the first mass block (1), and the other end of the first damper (3) is connected to the controlled main structure; one end of the lever (4) is connected to the side end face of the first mass block (1), and the other end of the lever (4) extends horizontally and is connected to one end of the first spring (2); the other end of the first spring (2) extends vertically along the controlled main structure and is connected to the controlled main structure; the lever fulcrum (5) is located on the lever (4); The trigger drive assembly includes a cam structure (6), a ratchet (7), a pawl (8), and a response threshold setter (9); the ratchet (7) is rigidly connected to the cam shaft in the cam structure (6); one end of the pawl (8) is rigidly connected to the lower rod of the response threshold setter (9), and the other end of the pawl (8) is engaged with the ratchet (7); a connecting shaft is provided on two parallel side end faces in the lever fulcrum (5), and the lever fulcrum (5) is hinged to the cam structure (6) through the connecting shaft; The response sensing component is installed on the controlled main structure, and the response sensing component includes a horizontal sensing component and a vertical sensing component; the horizontal sensing component is used to sense the vibration displacement of the controlled main structure in the horizontal direction; the vertical sensing component is used to sense the vibration displacement of the controlled main structure in the vertical direction. The cam structure (6) includes a barrel cam (6.1) and a slider (6.2) that mesh with each other; the slider (6.2) is configured as a U-shaped structure, with its open end hinged to the lever fulcrum (5) through two connecting shafts, and its closed end provided with a connecting hole that meshes with the barrel cam (6.1); when the barrel cam (6.1) rotates, the slider (6.2) is driven to slide along the central axis of the barrel cam (6.1), thereby converting the rotation of the barrel cam (6.1) into the translation of the slider (6.2); Two sets of helical grooves with opposite directions are provided on the outer circumferential surface of the barrel cam (6.1). The two sets of helical grooves are connected to each other through a smooth transition section at the two side end faces of the barrel cam (6.1). When the slider (6.2) moves along one of the helical grooves to the end of the barrel cam (6.1), it moves through the smooth transition section to the other helical groove, thereby causing the slider (6.2) to reciprocate on the barrel cam (6.1). The response threshold setter (9) includes an integrally formed connecting part, an upper rod, and a lower rod; the connecting part is hinged to the camshaft of the barrel cam (6.1); one end of the upper rod is fixedly connected to the connecting part, and the other end of the upper rod extends out; one end of the lower rod is fixedly connected to the connecting part, and the other end of the lower rod extends out and is set at an angle to the upper rod. The response threshold trigger lever (16) is located at the center of the opening of the response threshold setter (9), and the response threshold trigger lever (16) is mounted on the second mass block (10). The ratchet (7) is rigidly connected to the camshaft of the barrel cam (6.1); One end of the pawl (8) is rigidly connected to the lower rod, and the other end of the pawl (8) is engaged with the ratchet (7); The response sensing component includes a second mass block (10), a second spring (12), and a second damper (13). One end of the second spring (12) is connected to the second mass block (10), and the other end of the second spring (12) extends along the vertical direction of the controlled main structure and is connected to the position in the controlled main structure that needs to sense the response. One end of the second damper (13) is connected to the second mass block (10), and the other end of the second damper (13) extends along the vertical direction of the controlled main structure and is connected to the position in the controlled main structure that needs to sense the response. The second spring (12) and the second damper (13) are connected in parallel.

2. The lever-type tuned mass damper with passive adaptive tuning function according to claim 1, characterized in that, When the response to be sensed is vertical vibration displacement, the response sensing component also includes a negative stiffness unit, which further includes a groove (14) and a pulley (15). The groove (14) in the negative stiffness unit is located on the inner side of the upper end face of the frame (20) and is provided with two pieces arranged side by side along the elongation and compression direction of the third spring (11). The pulley (15) is connected to the third spring (11), and there are two pulleys (15). The single pulley (15) is matched with the single slide groove (14) and slides in the slide groove (14) to guide and limit the direction of action of the third spring (11).

3. The lever-type tuned mass damper with passive adaptive tuning function according to claim 2, characterized in that, The negative stiffness unit is provided in two sets symmetrically arranged on both sides of the second mass block (10).

4. The lever-type tuned mass damper with passive adaptive tuning function according to claim 3, characterized in that, In the initial state, the response threshold trigger lever (16) is located at the center of the opening of the response sensing component; When the vibration response of the controlled main structure exceeds the limit, the displacement of the second mass block (10) relative to the controlled main structure will exceed the set threshold range of the response threshold setter (9). The response threshold trigger rod (16) will repeatedly strike the upper and lower rods of the response threshold setter (9). When the response threshold trigger rod (16) strikes the lower rod, the response threshold setter (9) rotates counterclockwise, which in turn drives the pawl (8) to lock the teeth of the ratchet (7) to rotate counterclockwise, further driving the ratchet (7) and the barrel cam (6.1) to rotate counterclockwise, and finally driving the slider (6.2) and the lever fulcrum (5) to move horizontally and start the self-tuning process. When the response threshold trigger rod (16) strikes the upper rod, the response threshold setter (9) rotates clockwise, returning the response threshold setter (9) to the initial position, while driving the pawl (8) to rotate clockwise along the teeth of the ratchet (7), and the ratchet (7) does not rotate. When the vibration response of the controlled main structure exceeds the limit, the lever fulcrum (5) will be moved, the lever ratio will change, and the tuned mass damping component will be retuned. When the effective natural frequency of the retuned structure is... The vibration response of the controlled main structure will be less than the given threshold when the frequency of the control mode is approximately equal to that of the controlled main structure. The displacement of the second mass block (10) relative to the position where the response needs to be sensed is within the set threshold range of the response threshold setter (9), and the self-tuning process ends.

5. The lever-type tuned mass damper with passive adaptive tuning function according to claim 4, characterized in that, The vibration differential equation of the second mass block (10) is: ； in: It represents the absolute vibration displacement of the controlled main structure within the inertial frame. Let the mass be represented as that of the second mass block (10). This is expressed as the total vertical stiffness of the second spring (12) and the third spring (11). The damping coefficient of the second damper (13) is expressed as follows. This is represented as the displacement of the second mass block (10) relative to the controlled main structure; It is expressed as the absolute vibration acceleration of the controlled main structure in the inertial frame; This is represented as the velocity of the second mass block (10) relative to the controlled main structure; It is represented as the acceleration of the second mass block (10) relative to the controlled main structure.

6. The lever-type tuned mass damper with passive adaptive tuning function according to claim 5, characterized in that, When the natural frequency of the second mass block (10) satisfy At that time, the displacement amplitude of the second mass block (10) relative to the controlled main structure Approximately equal to the absolute vibration displacement amplitude of the controlled main structure ,Right now ; The damping ratio of the second damper (13) is expressed as follows; When the natural frequency of the second mass block (10) satisfy At that time, the ratio of the displacement amplitude of the second mass block (10) relative to the controlled main structure to the vibration acceleration amplitude of the main structure is approximately equal to a constant.

7. The lever-type tuned mass damper with passive adaptive tuning function according to claim 6, characterized in that, Let the effective natural frequency of the tuned mass damping component be... ; in: Let be the nominal natural frequency of the tuned mass damping component, and , Let the mass be represented by the mass of the first mass block (1). The stiffness is expressed as that of the first spring (2); Expressed as leverage ratio, This is expressed as the distance from the lever fulcrum (5) to the first spring (2). It is expressed as the distance from the lever fulcrum (5) to the first mass block (1); For a given first mass block (1) and first spring (2), the nominal natural frequency of the tuned mass damping assembly remains constant. .

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