A self-tuning vibration absorber
By designing a self-tuning vibration absorption device, the natural frequency of the vibration absorption device is adjusted by utilizing the sway of the main counterweight and the centrifugal force of the secondary sliding mass block. This solves the problem of the increasing gap between the vibration absorption effect and the frequency of forging vibration in the existing technology, and achieves a better vibration reduction effect.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- XI AN SINOBERUN HEAVY IND TECH CO LTD
- Filing Date
- 2026-04-09
- Publication Date
- 2026-05-29
AI Technical Summary
The existing vibration-absorbing structure has a fixed natural frequency, which makes it difficult to adapt to the decreasing frequency of forging impact vibration, resulting in a gradual deterioration of the vibration absorption effect.
A self-tuning vibration absorption device was designed. By the swaying of the main counterweight and the centrifugal force of the secondary sliding mass block, the natural frequency of the vibration absorption device is dynamically adjusted to adapt to the change of forging impact vibration frequency. The device includes a combination structure of a base, a central support shaft, a main counterweight, and a secondary sliding mass block.
It effectively reduces the gap between the natural frequency of the vibration absorption device and the forging vibration frequency, improves the vibration absorption effect, and ensures the vibration reduction performance during the forging process.
Smart Images
Figure CN122107044A_ABST
Abstract
Description
Technical Field
[0001] This invention relates to the field of heavy forging equipment technology, and more specifically, to a self-tuning vibration damping device. Background Technology
[0002] During the operation of a forging manipulator, the periodic impact load of the forging press will induce strong vibrations in the manipulator structure. This vibration not only affects the machining accuracy but also leads to structural fatigue damage and shortens the service life of the equipment.
[0003] Common vibration reduction measures include increasing the structural stiffness of the forging manipulator and adding damping materials to the vibration area of the manipulator. However, the vibration generated by forging impact is broadband and multimodal. High-frequency components are absorbed or disappear first due to rapid damping, while low-frequency components persist longer. Therefore, during the vibration decay process after each impact, the dominant frequency gradually decreases over time. It is well known that the vibration absorption effect of a vibration-absorbing structure is optimal when the natural frequency equals the excitation frequency; the greater the deviation, the worse the absorption effect. Existing vibration-absorbing structures have a fixed natural frequency. As time progresses and high-frequency vibrations decay, the gap between the natural frequency of the vibration-absorbing structure and the gradually decreasing dominant frequency widens, resulting in a worse vibration absorption effect. This makes it difficult to adapt to the decreasing frequency of forging impact vibration and ensure effective vibration absorption.
[0004] Therefore, how to provide an adaptive vibration absorption device that can automatically tune and gradually reduce its own natural frequency to adapt to the frequency reduction of forging impact vibration and ensure the vibration absorption effect has become an urgent problem to be solved by those skilled in the art. Summary of the Invention
[0005] The purpose of this invention is to provide a self-tuning vibration absorption device to solve the aforementioned technical problems.
[0006] To achieve the above objectives, the present invention provides the following technical solution: A self-tuning vibration absorption device, comprising: Base, central support shaft, main counterweight, and secondary sliding mass block; The base is used to connect the vibration-absorbing equipment. The base is equipped with a central support shaft. The base and the central support shaft vibrate with the vibration of the equipment. The main counterweight is rotatably connected to the central support shaft. The main counterweight is equipped with a guide rail. The secondary sliding mass block slides linearly on the guide rail. The center of mass of the secondary sliding mass block slides on a first straight line. The first straight line is perpendicular to the axis of the central support shaft. The first straight line, the axis of the central support shaft, and the center of mass of the main counterweight block are located on a first plane.
[0007] Optionally, the secondary sliding mass is mounted on the guide rail via a linear bearing and slides linearly along the extension direction of the guide rail.
[0008] Optionally, the guide rail has a friction plate assembly at the end of the track. When the secondary sliding mass block slides to the end and hits its friction plate assembly, the friction plates of the friction plate assembly rub against each other to dissipate energy.
[0009] Optionally, the main counterweight is rotatably connected to the central support shaft via a set of angular contact ball bearings.
[0010] Optionally, the base has a housing, a central support shaft is installed inside the housing, and the base is connected to the vibration-absorbing device on one side along the axial direction of the central support shaft. The main counterweight and its secondary sliding mass block rotate inside the housing.
[0011] Optionally, the two ends of the central support shaft are fixed to the opposite ends of the housing.
[0012] Optionally, the housing is equipped with a heat dissipation structure.
[0013] Optionally, on the first plane, a second straight line is drawn through the center of mass of the main counterweight, perpendicular to the first straight line. The main counterweight is provided with two guide rails. Along the radial direction of the central support axis, the guide rail farther from the central support axis is the first guide rail, and the guide rail closer to the central support axis is the second guide rail. The first and second guide rails are symmetrical about the second straight line. Each of the first and second guide rails is slidably connected to a primary sliding mass block. The sliding trajectory of the center of mass of the two primary sliding mass blocks is symmetrical about the second straight line. The two primary sliding mass blocks are connected by a synchronization mechanism on the main counterweight. When the secondary sliding mass block in the first guide rail moves radially outward under centrifugal force, it drives the secondary sliding mass block in the second guide rail to move in the opposite direction and radially inward through the synchronization mechanism. The two primary sliding mass blocks are always symmetrical about the second straight line.
[0014] Optionally, the main counterweight may have only one guide rail.
[0015] This invention features a central support shaft mounted on a base, which is then fixedly installed on the device to be vibration-absorbing (e.g., a forging manipulator). During operation, the device vibrates, causing the connected base and central support shaft to vibrate as well. The vibration direction of the device exhibits anisotropy; by adjusting the installation direction of the self-tuning vibration-absorbing device, the axial direction of the central support shaft is perpendicular to the primary vibration direction of the device. The main counterweight protrudes from the radial outer wall of the central support shaft, with its center of mass far from the axis of the central support shaft. When the vibration direction of the device is along the tangential direction of the main counterweight's rotation around the shaft (or at least has a component in this tangential direction), the central support shaft vibrates synchronously. The central support shaft applies a thrust to the main counterweight via bearings, causing the main counterweight to move laterally synchronously with the shaft. However, the main counterweight, being a counterweight mechanical structure, is relatively heavy and more susceptible to inertial forces. These inertial forces are opposite in direction to the thrust, also having opposing components in the aforementioned tangential direction. Under the influence of these inertial forces, the main counterweight rotates around the shaft. The equipment vibrates reciprocally, and the main counterweight rotates in the opposite direction accordingly. Because the unidirectional rotation angle of this reciprocating rotation often switches back and forth, it can also be called the sway of the main counterweight. Based on this, this application converts the vibration kinetic energy into the rotational kinetic energy of the main counterweight for dissipation. This is the first-stage vibration absorption and energy dissipation strategy of the self-tuning vibration absorption device.
[0016] A secondary sliding mass block is slidably mounted on the guide rail of the main counterweight block, rotating synchronously with the main counterweight block. During the rotation of the main counterweight block, at least one secondary sliding mass block on the main counterweight block is affected by the centrifugal force generated by the rotation, and moves radially outward under the guidance of the guide rail. The moment of inertia of the main counterweight block (carrying the secondary sliding mass block) gradually increases, and the natural frequency of the main counterweight block (carrying the secondary sliding mass block) gradually decreases.
[0017] This application can absorb and dissipate energy through the oscillation of the main counterweight. By gradually reducing the natural frequency of the oscillation energy-absorbing component through the radial outward movement of the secondary sliding mass block on the main counterweight under centrifugal force, compared with the single and unchanging natural frequency of the vibration-absorbing component in the prior art, it is more adaptable to the frequency reduction of forging impact vibration, reduces the risk of the gap between the natural frequency of the vibration-absorbing component and the gradually decreasing main vibration frequency of the forging manipulator becoming larger and larger, and relatively better ensures the vibration absorption effect. Attached Figure Description
[0018] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments and descriptions of the invention are used to explain the invention, but do not constitute an undue limitation of the invention. Obviously, the drawings described below are merely some embodiments, and those skilled in the art can obtain other drawings based on these drawings without creative effort. In the drawings: Figure 1 This is a schematic diagram of the structure of a self-tuning vibration absorption device according to an embodiment of this application; Figure 2 for Figure 1 Cross-sectional view of the self-tuning vibration absorption device in the embodiment; Figure 3 This is a partial structural diagram of the overall rotating body according to an embodiment of this application; Figure 4 for Figure 3 A magnified view of a portion of the image; Figure 5 The diagram shows the working principle of the self-tuning vibration absorption device provided in this application.
[0019] Reference numerals: 110, housing; 111, heat dissipation fins; 120, mounting flange; 200, angular contact ball bearing; 300, central support shaft; 400, main counterweight; 410, guide rail; 411, first guide rail; 412, second guide rail; 420, bearing housing; 430, first gear; 440, second gear; 450, friction plate assembly; 500, secondary sliding mass block; 510, first linear guide; 610, first rack; 620, second rack. Detailed Implementation
[0020] The technical solutions in the embodiments of the present invention will be clearly and completely described below. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments.
[0021] See Figures 1 to 4 As shown, this invention provides a self-tuning vibration absorption device, including a base, a central support shaft 300, a main counterweight 400, and a secondary sliding mass block 500. The base is used to connect the device to be absorbed. The base has a central support shaft 300, and both the base and the central support shaft 300 vibrate with the vibration of the device. The main counterweight 400 is rotatably connected to the central support shaft 300 and has a guide rail 410. The secondary sliding mass block 500 slides linearly on the guide rail 410. The center of mass of the secondary sliding mass block 500 slides along a first straight line 510, which is perpendicular to the axis of the central support shaft 300. The first straight line 510, the axis of the central support shaft 300, and the center of mass of the main counterweight 400 are located on a first plane. The main counterweight blocks 400 are symmetrically distributed about the first plane.
[0022] This invention features a central support shaft 300 mounted on a base, which is then fixedly installed on the device to be vibration-absorbing (e.g., a forging manipulator). During operation, the device vibrates, causing the connected base and central support shaft 300 to vibrate as well. The vibration direction of the device exhibits anisotropy; by adjusting the installation direction of the self-tuning vibration-absorbing device, the axial direction of the central support shaft 300 is perpendicular to the primary vibration direction of the device. A main counterweight 400 protrudes from the radial outer wall of the central support shaft 300, with its center of mass far from the axis of the central support shaft 300. When the vibration direction of the device is along the tangential direction of the main counterweight 400's rotation around its axis (or at least has a component in that tangential direction), the central support shaft 300 vibrates synchronously. The central support shaft 300 applies a thrust to the main counterweight 400 via bearings, causing the main counterweight 400 to move laterally synchronously with the shaft. However, the main counterweight 400 is a counterweight mechanical structure with a relatively heavy weight, making it more susceptible to inertial forces. These inertial forces are opposite in direction to the thrust, and also have opposing components in the aforementioned tangential direction. Under the action of these inertial forces, the main counterweight 400 rotates around the shaft. As the equipment reciprocates, the main counterweight 400 switches its direction and rotates accordingly. Because the unidirectional rotation angle of this reciprocating rotation frequently switches, it can also be referred to as the yaw of the main counterweight 400. Based on this, this application converts the vibration kinetic energy into the rotational kinetic energy of the main counterweight 400 for dissipation. This is the first-stage vibration absorption and energy dissipation strategy of this self-tuning vibration absorption device.
[0023] A secondary sliding mass block 500 is slidably mounted on the guide rail 410 of the main counterweight block 400 and rotates synchronously with the main counterweight block 400. The main counterweight block 400 bearing the secondary sliding mass block 500 is called the combined structure of the two, also known as the total rotating body.
[0024] During the rotation of the main rotating body, at least one secondary sliding mass block 500 on the main counterweight 400 is affected by the centrifugal force generated by the rotation and moves radially outward under the guidance of the guide rail 410. The rotation radius r of this secondary sliding mass block 500 to the center of rotation is... 次1 Increase (r) 次1 =r 初1 +△r, where △r is the radial outward displacement), and the mass m of the secondary sliding mass block 500. 次1 It remains constant. According to the formula for calculating the moment of inertia: I 总 =I 主 +∑m 次i ·r 次i 2 ; I 总初 =I 主 +∑m 次i ·r 初i 2 ; I 总现 =I主 +∑m 次i ·r 初i 2 ; If there is only one secondary sliding mass block 500, then the secondary sliding mass block 500 will only be moved outward by centrifugal force. The moment of inertia of the total rotating body is calculated as follows: I 总现 =I 主 +m 次1 ·r 次1 2 =I 主 +m 次1 ·(r 初1 +△r) 2 =I 主 +m 次1 ·r 初1 2 +2m 次1 ·r 初1 ·△r+m 次1 ·△r 2 =I 主 +I 初 +2m 次1 ·r 初1 ·△r+m 次1 ·△r 2 =I 总初 +2m 次1 ·r 初1 ·△r+m 次1 ·△r 2 Because 2m 次1 ·r 初1 ·△r+m 次1 ·△r 2 >0, so as time goes on, the secondary sliding mass block 500 moves outward, and the current moment of inertia of the total rotating body I... 总现 Its initial moment of inertia I is always greater than its initial moment of inertia. 总初。
[0025] Without the synchronization mechanism described later, regardless of the total number of guide rails 410 and secondary sliding mass blocks 500 on the main counterweight 400, all secondary sliding mass blocks 500 will only move radially outward due to the centrifugal force generated by rotation. Therefore, as time goes by, the secondary sliding mass blocks 500 move outward, and the current moment of inertia I of the total rotating body... 总现 Its initial moment of inertia I is always greater than its initial moment of inertia. 总初。
[0026] like Figure 3As shown in the embodiment, if a synchronization mechanism described later is provided, such that the self-tuning vibration absorption device contains two secondary sliding mass blocks 500 of equal weight that move in the opposite direction to the rotation of the main rotating body, the secondary sliding mass block 500 with a larger rotation radius moves radially outward, while the one with a smaller rotation radius moves radially inward. The moment of inertia of the main rotating body at this time is calculated as follows: I 总现 =I 主 +m 次1 ·r 次1 2 +m 次1 ·r 次2 2 =I 主 +m 次1 ·(r 初1 +△r) 2 +m 次1 ·(r 初1 -△r) 2 =I 主 +2m 次1 ·r 初1 2 +2m 次1 ·△r(r 初1 -r 初2 )+2m 次1 ·△r 2 =I 总初 +m 次1 ·r 初1 2 +2m 次1 ·△r(r 初1 -r 初2 )+2m 次1 ·△r 2 Because r 初1 >r 初2 Therefore, as time goes by, the two-stage sliding mass blocks 500 move in opposite directions, and the current moment of inertia of the total rotating body is I. 总现 Its initial moment of inertia I is always greater than its initial moment of inertia. 总初。
[0027] The formula for calculating the natural frequency f0 of the entire rotating body is as follows: K θAs the moment of inertia of the total rotating body gradually increases, its natural frequency f0 will gradually decrease. This application can absorb and dissipate energy through the yaw vibration of the main counterweight 400. By gradually reducing the natural frequency of the yaw energy-absorbing component through the radial outward movement of the secondary sliding mass block 500 on the main counterweight 400 under centrifugal force, this method is more adaptable to the decreasing frequency of forging impact vibration compared to the existing technology with a single, unchanging natural frequency of the vibration-absorbing component. It reduces the risk of the gap between the natural frequency of the vibration-absorbing component and the gradually decreasing main vibration frequency of the forging manipulator widening, and thus better ensures the vibration absorption effect.
[0028] The vibration direction of a forging manipulator during operation is complex, involving a combination of horizontal, vertical, and torsional vibrations. During forging (especially with die forging hammers and steam hammers), the reaction force of the hammer impacting the forging is transmitted through the forging to the manipulator's clamping arm, causing the manipulator frame to vibrate horizontally back and forth along the forging direction. Therefore, the core vibration mode of the forging manipulator is horizontal. Thus, the installation direction of the self-tuning vibration damping device can be adjusted before installation so that its central support shaft 300 is vertical. Alternatively, other self-tuning vibration damping devices can be added to the forging manipulator to absorb and dissipate vibration energy in other directions; the number and angle of these devices can be freely set according to actual conditions.
[0029] In one possible implementation, the secondary sliding mass 500 is mounted on the guide rail 410 via a linear bearing and slides linearly along the extension direction of the guide rail 410. Friction plate assemblies 450 are provided at both ends of the guide rail 410. When the secondary sliding mass 500 slides to its end and impacts its friction plate assembly 450, the friction plates of the friction plate assembly 450 rub against each other to dissipate energy.
[0030] In one possible implementation, the main counterweight 400 is rotatably connected to the central support shaft 300 via a set of angular contact ball bearings 200.
[0031] In one possible implementation, such as Figure 2 As shown, the base has a housing 110, and a central support shaft 300 is installed inside the housing 110. The base is connected to the vibration-absorbing device on one side along the axial direction of the central support shaft 300. The main counterweight 400 and its secondary sliding mass block 500 rotate within the housing 110. The two ends of the central support shaft 300 are fixed to opposite ends of the housing 110. Optionally, as... Figure 2As shown, the housing 110 has through holes at opposite ends along the central support shaft 300. The central support shaft 300 is made of high-strength alloy steel, and its axial ends are interference-fitted into the through holes at both ends of the housing 110, rigidly fixed to the housing 110. Alternatively, the housing 110 has through holes at opposite ends along the central support shaft 300, and the axial ends of the central support shaft 300 are rotatably connected to the through holes on both sides of the housing 110 via bearings. Preferably, each axial end of the central support shaft 300 is rotatably connected to the through holes on both sides of the housing 110 via a set of angular contact ball bearings 200, rotating within the housing to improve system rigidity and rotational accuracy. Optionally, as... Figure 1 As shown, a mounting flange 120 is provided on one side of the base and is fixed to the vibrating part of the forging press by bolts. A housing 110 is provided on the other side. The central support shaft 300, the main counterweight 400, the guide rail 410 on the main counterweight 400, the secondary sliding mass block 500, and the synchronization mechanism are installed in the housing 110.
[0032] In one possible implementation, the housing 110 is provided with a heat dissipation structure, for example, heat dissipation fins (also called heat dissipation fins 111) are provided on the outer surface of the housing 110, thereby increasing the heat dissipation efficiency by increasing the contact area between the housing 110 and the outer surface.
[0033] In one possible implementation, a second straight line is drawn on the first plane through the center of mass of the main counterweight 400. This second straight line is perpendicular to the first straight line 510. The main counterweight 400 is provided with two guide rails 410. Along the radial direction of the central support axis 300, the guide rail farther from the central support axis 300 is the first guide rail 411, and the guide rail closer to the central support axis 300 is the second guide rail 412. The first guide rail 411 and the second guide rail 412 are symmetrical about the second straight line. The first and second guide rails 410... Each of the two primary sliding mass blocks 500 is slidably connected to a secondary sliding mass block 500. The sliding trajectories of the centers of mass of the two secondary sliding mass blocks 500 are symmetrical about the second linear axis. The two secondary sliding mass blocks 500 are connected by a synchronization mechanism on the main counterweight block 400. When the secondary sliding mass block 500 in the first guide rail 411 moves radially outward under centrifugal force, the synchronization mechanism drives the secondary sliding mass block 500 in the second guide rail 412 to move in the opposite direction, radially inward. The two secondary sliding mass blocks 500 are always symmetrical about the second linear axis. Compared with the prior art, this application can increase the moment of inertia while ensuring that the center of mass of the total rotating body does not shift, thereby reducing the natural frequency of the total rotating body, adapting to the wide frequency variation trend of the forging press manipulator, and ensuring the vibration absorption effect.
[0034] In one possible implementation, such as Figure 3As shown, the two ends of the main counterweight 400 along its own rotational circumference form a central angle, which is 270°-350°. Preferably, the main counterweight 400 is generally arc-shaped. The synchronization mechanism includes a gear set (rotatably connected to the main counterweight 400 via a bearing seat 420), a first rack 610 fixed to the secondary sliding mass block 500 in the first guide rail 411, and a second rack 620 fixed to the secondary sliding mass block 500 in the second guide rail 412. The first rack 610 meshes with the first gear 430 in the gear set, and the second rack 620 meshes with the second gear 440 in the gear set. The first gear 430 and the second gear 440 are coaxially connected to form a gear set, and are rotatably connected to the main counterweight 400 via a bearing seat 420. The rotation axis is perpendicular to the first straight line 510 and also perpendicular to the axis of the central support shaft 300. The first rack 610 and the second rack 620 are parallel and located on the same side of the gear set along the axial direction of the central support shaft 300. The gear set is located between the first guide rail 411 and the second guide rail 412. The secondary sliding mass block 500 in the first guide rail 411 is radially moved outward by centrifugal force, and the first rack 610 moves radially outward synchronously, driving the first gear 430 to rotate, which in turn drives the second gear 440 to rotate synchronously. The first gear 430 and the second gear 440 rotate in the same direction, but their tangential pushing directions at the meshing point on the same side of the central support shaft 300 are opposite. Apart from this, the first gear 430 and the second gear 440 are completely identical, including but not limited to having the same gear module, number of teeth, and pressure angle. The first rack 610 and the second rack 620 that match and mesh with them have the same module, number of teeth, and pressure angle. Therefore, the rotation of the second gear 440 will drive the second rack 620 to move linearly in the opposite direction to the first rack 610. The linear displacement speed of the second rack 620 is the same as that of the first rack 610. At any given moment, the linear displacement of the first rack 610 and the second rack 620 is equal in magnitude, so that no matter how the first rack 610 and the second rack 620 move in opposite directions, the center of mass of the combination of the first rack 610 and the second rack 620 does not shift, and the center of mass of the combination of the secondary sliding mass block 500 loaded with the first rack 610 and the secondary sliding mass block 500 loaded with the second rack 620 does not shift.
[0035] Regarding the attached image... Figure 4 The secondary sliding mass block 500 in the first guide rail 411 moves downward along the arrow and gradually moves away from the central support shaft 300; the secondary sliding mass block 500 in the second guide rail 412 moves upward along the arrow and gradually moves closer to the central support shaft 300. Figure 5 In this context, the shell 110 is referred to as the outer shell, and the secondary sliding mass block 500 is also simply referred to as the secondary mass block or secondary block.
[0036] In another possible implementation, such as Figure 2As shown, the main counterweight 400 has only one guide rail 410.
[0037] In one possible implementation, the self-tuning vibration damping device provided in this application has only one main counterweight 400 rotatably connected to the central support shaft 300. Alternatively, the central support shaft 300 may have multiple main counterweights 400 rotatably connected, and these main counterweights 400 may be arbitrarily spaced circumferentially or axially. Or, the multiple main counterweights 400 may be connected to the central support shaft 300 via the same bearing, and these main counterweights 400 may be circumferentially distributed around the axis of the central support shaft 300.
[0038] The foregoing has shown and described the basic principles, main features, and advantages of the present invention. Those skilled in the art should understand that the present invention is not limited to the above embodiments. The embodiments and descriptions in the specification are merely preferred examples and are not intended to limit the invention. Various changes and modifications can be made to the invention without departing from its spirit and scope, and all such changes and modifications fall within the scope of the present invention as claimed. The scope of protection of the present invention is defined by the appended claims and their equivalents.
Claims
1. A self-tuning vibration absorption device, characterized in that, include: Base, central support shaft, main counterweight, and secondary sliding mass block; The base is used to connect the vibration-absorbing device. The base is provided with a central support shaft. The base and the central support shaft vibrate with the vibration of the device. The main counterweight is rotatably connected to the central support shaft. The main counterweight is provided with a guide rail. The secondary sliding mass block slides linearly on the guide rail. The center of mass of the secondary sliding mass block slides on a first straight line. The first straight line is perpendicular to the axis of the central support shaft. The first straight line, the axis of the central support shaft, and the center of mass of the main counterweight block are located on a first plane.
2. The self-tuning vibration absorption device according to claim 1, characterized in that, The secondary sliding mass block is mounted on the guide rail via a linear bearing and slides linearly along the extension direction of the guide rail.
3. The self-tuning vibration absorption device according to claim 1, characterized in that, The guide rail is provided with a friction plate assembly at the end of the track. When the secondary sliding mass block slides to the end and hits its friction plate assembly, the friction plates of the friction plate assembly rub against each other to consume energy.
4. The self-tuning vibration absorption device according to claim 1, characterized in that, The main counterweight is rotatably connected to the central support shaft via a set of angular contact ball bearings.
5. The self-tuning vibration absorption device according to claim 1, characterized in that, The base is provided with a housing, and the central support shaft is installed inside the housing of the base. The base is connected to the vibration-absorbing device on one side along the axial direction of the central support shaft. The main counterweight and its secondary sliding mass block rotate inside the housing.
6. The self-tuning vibration absorption device according to claim 5, characterized in that, The two ends of the central support shaft are fixed to the opposite ends of the housing.
7. The self-tuning vibration absorption device according to claim 5, characterized in that, The housing is equipped with a heat dissipation structure.
8. The self-tuning vibration absorption device according to claim 1, characterized in that, On the first plane, a second straight line is drawn through the center of mass of the main counterweight, perpendicular to the first straight line. The main counterweight is provided with two guide rails. Along the radial direction of the central support axis, the guide rail farther from the central support axis is the first guide rail, and the guide rail closer to the central support axis is the second guide rail. The first guide rail and the second guide rail are symmetrical about the second straight line. Each of the first and second guide rails is slidably connected to a secondary sliding mass block. The sliding trajectories of the centers of mass of the two secondary sliding mass blocks are symmetrical about the second straight line. The two secondary sliding mass blocks are connected by a synchronization mechanism on the main counterweight. When the secondary sliding mass block in the first guide rail moves radially outward under centrifugal force, it drives the secondary sliding mass block in the second guide rail to move in the opposite direction and radially inward through the synchronization mechanism. The two secondary sliding mass blocks are always symmetrical about the second straight line.
9. The self-tuning vibration absorption device according to claim 1, characterized in that, The main counterweight has only one guide rail.