A torsional quasi-zero stiffness vibration absorber

Abstract

The application discloses a torsional quasi-zero stiffness vibration absorber and relates to the technical field of vibration control, which is used for being installed on a vibration receiving shaft to suppress torsional vibration of the shaft and comprises a bearing ring, a bearing ring, a positive stiffness mechanism, a negative stiffness mechanism and an inertial mass block. The bearing ring is fixedly installed on the vibration receiving shaft. The bearing ring is coaxially arranged with the bearing ring and is connected with the positive stiffness mechanism and the negative stiffness mechanism between the bearing ring and the bearing ring. The positive stiffness mechanism is used for providing positive stiffness elastic restoring force, and the negative stiffness mechanism is used for providing negative stiffness effect. The inertial mass block is detachably installed on the bearing ring and is used for providing rotational inertia. Therefore, the problems that the traditional linear vibration absorber cannot simultaneously consider low-frequency vibration suppression performance and static bearing capacity, the structure is not compact enough and the wide-frequency low-frequency torsional vibration cannot be effectively suppressed can be solved.

Description

Technical Field

[0001] This invention relates to the field of vibration control technology, and in particular to a torsional quasi-zero stiffness vibration absorber. Background Technology

[0002] Rotating machinery is the core of modern industry, and its shaft systems (such as engine crankshafts, ship propulsion shafts, and fan main shafts) inevitably generate torsional vibrations during operation. This periodic angular displacement around the axis not only causes gear meshing errors and accelerates bearing wear, but in severe cases, it can lead to shaft fatigue fracture, threatening equipment safety. Traditionally, linear dynamic vibration absorbers are used to suppress torsional vibrations. The principle is to add a "mass, spring, and damping" subsystem tuned to a specific frequency to the main shaft, utilizing the phase reversal characteristics at resonance to achieve efficient energy transfer and dissipation near the target frequency.

[0003] However, traditional linear torsional vibration absorbers have inherent drawbacks. First, the frequency response characteristics of linear systems fundamentally limit their application boundaries—their effective damping bandwidth is strictly constrained by the system's damping ratio, exhibiting a sharp peak characteristic centered on the natural frequency. This means that when the excitation frequency deviates from the design point, the absorber's effectiveness will experience a precipitous decline, and may even produce a negative amplification effect at the new frequency. This inherent "narrow band" characteristic makes traditional linear vibration absorbers exhibit significant adaptability deficiencies when facing wide-bandwidth excitation or variable-frequency operating conditions. Second, the effective damping bandwidth of a linear vibration absorber is always centered on its natural frequency. To achieve low-frequency vibration suppression, the absorber's natural frequency must be designed to be sufficiently low, which usually means significantly reducing torsional stiffness or increasing rotational inertia. Reducing stiffness weakens the system's static load-bearing capacity, leading to excessive static deformation under gravity or steady-state torque, affecting equipment accuracy or even causing malfunction. Conversely, increasing inertia results in a dramatic increase in volume and weight, contradicting the demands of modern lightweight and compact equipment, and is virtually impractical in space-constrained environments (such as automotive powertrains and wind turbine nacelles). Therefore, traditional linear design presents an irreconcilable contradiction between "low-frequency performance," "compact structure," and "static stiffness."

[0004] Therefore, how to provide a torsional quasi-zero stiffness vibration absorber, which addresses the inherent limitations of traditional linear torsional vibration absorbers in simultaneously achieving deep low-frequency suppression and effective wide-band coverage due to their inherent frequency characteristics, and solves the problem of low-frequency vibration in shaft systems, is a technical problem that needs to be solved by those skilled in the art. Summary of the Invention

[0005] The purpose of this invention is to provide a torsional quasi-zero stiffness vibration absorber that can solve the problems of traditional linear vibration absorbers being unable to simultaneously achieve low-frequency vibration suppression performance and static load-bearing capacity, and having an insufficiently compact structure and being unable to effectively suppress wideband low-frequency torsional vibrations.

[0006] To achieve the above objectives, the present invention provides the following technical solution: A torsional quasi-zero stiffness vibration absorber, used for mounting on a vibrating shaft to suppress its torsional vibration, comprising: The bearing ring is fixedly installed on the vibrating shaft; The bearing ring is a ring-shaped structure. The bearing ring is coaxially arranged with the bearing ring. A positive stiffness mechanism and a negative stiffness mechanism are connected between the bearing ring and the bearing ring. The positive stiffness mechanism is used to provide positive stiffness elastic restoring force, and the negative stiffness mechanism is used to provide negative stiffness effect. An inertial mass block, detachably mounted on the bearing ring, is used to provide rotational inertia.

[0007] In one possible implementation, the negative stiffness mechanism includes: A pair of cam structures are symmetrically arranged inside the bearing ring, and the cam structures have working surfaces with specific profiles. A pair of elastic elements, one end of which is fixed to the bearing ring, and the other end is provided with a rotatable roller structure, the roller structure abutting against the cam structure.

[0008] In one possible implementation, the working surface of the cam structure is a convex arc surface with a semi-circular structure.

[0009] In one possible implementation, the elastic element has a hexagonal structure and includes several first spring plates connected end to end. A connecting portion is provided on the elastic element, and the connecting portion is symmetrically arranged with the roller structure. The connecting portion is used to be inserted into the bearing ring.

[0010] In one possible implementation, the positive stiffness mechanism includes a pair of second spring plates, the two ends of which are fixed to the bearing ring, and the two second spring plates are symmetrical about the elastic element.

[0011] In one possible implementation, the inner side of the bearing ring is provided with symmetrical slots, and the two ends of the second spring sheet are respectively embedded and fixed in the slots.

[0012] In one possible implementation, a shaped connector is further included, one end of which is fixedly connected to the bearing ring, and the other end is provided with a guide structure. The second spring sheet passes through the guide structure and can slide relative to the guide structure along its length.

[0013] In one possible implementation, the guide structure consists of two sets of pulleys disposed at the end of the irregular connector, with the second spring plate inserted between the two pulleys and both sides of the second spring plate abutting against the pulleys respectively.

[0014] In one possible implementation, the bearing ring is provided with a plurality of mounting holes uniformly arranged circumferentially for mounting the inertial mass block.

[0015] In one possible implementation, the elastic element is a spring.

[0016] Compared with the above-mentioned background technology, the torsional quasi-zero stiffness vibration absorber provided by the present invention has at least the following beneficial effects: The vibration absorber provided in this application achieves near-zero stiffness by arranging positive and negative stiffness mechanisms, as well as a negative stiffness mechanism, in parallel between the bearing ring and the load-bearing ring. The dynamic stiffness of these two mechanisms near their static equilibrium positions cancels each other out, resulting in an extremely low equivalent dynamic stiffness and a significant decrease in the natural frequency. This effectively suppresses ultra-low frequency torsional vibrations that traditional vibration absorbers cannot handle. In a static state, the positive stiffness mechanism provides high stiffness to support the inertial mass block and bear static loads, ensuring the stability and load-bearing capacity of the structure. In a dynamic state, the negative stiffness mechanism cancels out the positive stiffness, achieving low dynamic stiffness and excellent low-frequency vibration reduction. Furthermore, the vibration absorber adopts a ring-shaped coaxial layout, highly integrating the functional modules, resulting in a compact structure that facilitates installation on space-constrained shaft systems. The detachable inertial mass block design allows for flexible adjustment of the moment of inertia to adapt to the vibration suppression requirements of different shaft systems and operating conditions, making it highly practical. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the provided drawings without creative effort.

[0018] Figure 1 This is a three-dimensional structural diagram of an embodiment of the present invention; Figure 2 This is a schematic diagram of the bearing ring structure provided in an embodiment of the present invention; Figure 3 This is a schematic diagram of the elastic element structure provided in an embodiment of the present invention; Figure 4 This is a schematic diagram of the bearing ring structure provided in an embodiment of the present invention; Figure 5 This is a schematic diagram of the irregularly shaped connector structure provided in an embodiment of the present invention; Figure 6 This is a schematic diagram of the positive stiffness mechanism structure provided in an embodiment of the present invention; Figure 7This is a schematic diagram of the pulley structure of the irregularly shaped connector provided in an embodiment of the present invention; Figure 8 The diagram shows the low-frequency vibration absorption effect of the torsional quasi-zero stiffness vibration absorber provided in the embodiment of the present invention.

[0019] in: 100 - Bearing ring, 110 - Mounting groove; 200 - Load-bearing ring, 210 - Slot, 220 - Mounting hole; 300 - Positive stiffness mechanism; 400 - Negative stiffness mechanism, 410 - Cam structure, 420 - Elastic element, 430 - Roller structure, 440 - Connecting part; 500-Inertial Mass Block; 600 - Irregularly shaped connector, 610 - Pulley. Detailed Implementation

[0020] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0021] To enable those skilled in the art to better understand the present invention, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0022] In the description of this invention, it should be understood that the terms "upper", "lower", "front", "rear", "left" and "right" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the position or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations of this invention.

[0023] The purpose of this invention is to provide a torsional quasi-zero stiffness vibration absorber that can solve the problems of traditional linear vibration absorbers being unable to simultaneously achieve low-frequency vibration suppression performance and static load-bearing capacity, and having an insufficiently compact structure and being unable to effectively suppress wideband low-frequency torsional vibrations.

[0024] To achieve the above objectives, the present invention provides the following technical solution: Please see Figures 1 to 8This embodiment provides a torsional quasi-zero stiffness vibration absorber for installation on a vibrating shaft to suppress its torsional vibration. It includes: a bearing ring 100, a load-bearing ring 200, a positive stiffness mechanism 300, a negative stiffness mechanism 400, and an inertial mass block 500. The bearing ring 100 is fixedly installed on the vibrating shaft. The load-bearing ring 200 has a ring-shaped structure and is coaxially arranged with the bearing ring 100. The positive stiffness mechanism 300 and the negative stiffness mechanism 400 are connected between the load-bearing ring 200 and the bearing ring 100. The positive stiffness mechanism 300 provides positive stiffness elastic restoring force, and the negative stiffness mechanism 400 provides negative stiffness effect. The inertial mass block 500 is detachably installed on the load-bearing ring 200 to provide rotational inertia.

[0025] Specifically, the bearing ring 200 is a ring-shaped structural component, serving as the main load-bearing component and installation reference of the system, used to fix the inertial mass block 500 and the positive stiffness mechanism 300. The bearing ring 200 has a detachable inertial mass block 500 installed inside. By adjusting the mass or number of inertial mass blocks 500, the rotational inertia of the entire vibration absorber can be adjusted to meet the needs of different low-frequency vibration suppression. The inertial mass block 500 is made of cylindrical cast iron, and its mass distribution is adjustable. By adding or removing counterweights or replacing mass blocks of different sizes, the overall rotational inertia of the system can be precisely adjusted to match the vibration suppression requirements of different frequencies.

[0026] The bearing ring 100 is directly fitted and fixed on the vibrating long shaft, serving as the mechanical interface between the vibration absorber and the vibrating body. It is responsible for transmitting torque and vibration, and at the same time provides an installation base for the negative stiffness mechanism 400. The positive stiffness mechanism 300 is connected to the bearing ring 200, providing the basic elastic restoring force of the system. Its stiffness parameters can be designed and adjusted according to the actual working conditions to work in conjunction with the negative stiffness mechanism 400 to form a quasi-zero stiffness zone near the equilibrium position.

[0027] When torsional resonance occurs in the shaft system, the bearing ring 100 rotates with the shaft, driving the connected positive stiffness mechanism 300 and negative stiffness mechanism 400 to move, thereby generating angular displacement relative to the bearing ring 200 and the inertial mass block 500. During this process, the negative stiffness and positive stiffness generated by the system cancel each other out near the equilibrium position, causing the system to exhibit quasi-zero stiffness characteristics in this range, thereby significantly reducing the natural frequency of the vibration absorber and effectively suppressing low-frequency torsional vibration. Figure 8 As can be seen from the vibration response curves shown, after adding the vibration absorber provided in this embodiment, the resonance peak value of the system in the low-frequency range is significantly reduced, indicating that the device has good low-frequency vibration suppression capability.

[0028] In summary, the vibration absorber provided in this application, by arranging the positive and negative stiffness mechanisms 400 and the negative stiffness mechanism 400 in parallel between the bearing ring 200 and the bearing ring 100, allows the dynamic stiffness of the two mechanisms near the static equilibrium position to cancel each other out, resulting in a quasi-zero stiffness characteristic of the entire vibration absorber system. This leads to extremely low equivalent dynamic stiffness and a significant decrease in the natural frequency, effectively suppressing ultra-low frequency torsional vibrations that traditional vibration absorbers cannot handle. In a static state, the positive stiffness mechanism 300 provides high stiffness to support the inertial mass block 500 and bear static loads, ensuring the stability and load-bearing capacity of the structure. In a dynamic state, the negative stiffness mechanism 400 cancels out the positive stiffness, achieving low dynamic stiffness and obtaining excellent low-frequency vibration reduction effect. Furthermore, the vibration absorber adopts a ring-shaped coaxial layout, highly integrating the functional modules, resulting in a compact structure that facilitates installation on space-constrained shaft systems. Moreover, the detachable inertial mass block 500 design allows for flexible adjustment of the moment of inertia to adapt to the vibration suppression requirements of different shaft systems and working conditions, making it highly practical.

[0029] In one possible implementation, the negative stiffness mechanism 400 includes: a pair of cam structures 410 and a pair of elastic elements 420; the cam structures 410 are symmetrically arranged inside the bearing ring 200, and the cam structures 410 have a working surface with a specific profile, as shown in the example below. Figure 3 As shown; one end of the elastic element 420 is fixed to the bearing ring 100, and the other end is provided with a rotatable roller structure 430, which abuts against the cam structure 410, as detailed below. Figure 2 As shown.

[0030] Specifically, when the bearing ring 200 and the bearing ring 100 undergo relative torsion, the roller structure 430 rolls along the working surface of the cam structure 410, forcing the elastic element 420 to bend and deform. Through the specific profile of the working surface of the cam structure 410 and the deformation of the elastic element 420, a torque is generated in the same direction as the relative torsion, i.e., a negative stiffness effect, which is coupled with the positive stiffness mechanism 300 to achieve a quasi-zero stiffness state, thereby significantly reducing the equivalent stiffness of the system and widening the low-frequency vibration absorption frequency band. The symmetrical structure of the cam structure 410 ensures the balance of the system forces, while the roller structure 430 can convert sliding friction into rolling friction, reducing wear and hysteresis and improving the sensitivity and service life of the mechanism.

[0031] In one possible implementation, the working surface of the cam structure 410 is a convex arc surface with a semi-circular structure.

[0032] Understandably, a semi-circular convex arc surface is a profile that is easy to process and design, and can produce smooth and predictable nonlinear force and displacement relationships. This is beneficial for accurately achieving the required negative stiffness characteristics and matching with the positive stiffness mechanism 300, thereby forming an ideal quasi-zero stiffness zone near the equilibrium position.

[0033] In one possible implementation, the elastic element 420 has a hexagonal structure and includes several first spring sheets connected end to end. A connecting part 440 is provided on the elastic element 420, and the connecting part 440 is symmetrically arranged with the roller structure 430. The connecting part 440 is used to be inserted into the bearing ring 100.

[0034] Specifically, such as Figure 5 As shown, the elastic element 420 has an overall rhomboid structure, composed of several first spring plates, forming an elastic unit with controllable stiffness. This structure ensures sufficient strength while possessing excellent elastic deformation capacity, effectively storing and releasing deformation energy. The symmetrical arrangement of the connecting part 440 and the roller structure 430 makes the force transmission more direct and balanced; furthermore, as... Figure 2 As shown, the bearing ring 100 is provided with a mounting groove 110 that mates with the connecting part 440. After the connecting part 440 is inserted into the mounting groove 110, it is fixed by bolts. The plug-in connection method facilitates subsequent installation and maintenance.

[0035] In one possible implementation, the positive stiffness mechanism 300 includes a pair of second spring plates, the two ends of which are fixed to the bearing ring 200, and the two second spring plates are symmetrical about the elastic member 420.

[0036] Specifically, such as Figure 4 As shown, the second spring plate is used as the positive stiffness element, which has a simple and reliable structure. Its two ends are fixed on the bearing ring 200 to form a stable elastic support. The two spring plates are symmetrically arranged about the elastic element 420, which ensures that the stiffness characteristics of the whole system in the torsional direction are uniform and avoids additional coupling vibration caused by structural asymmetry.

[0037] Furthermore, specifically as follows Figure 3 As shown, the inner side of the bearing ring 200 is provided with symmetrical slots 210, and the two ends of the second spring sheet are respectively embedded and fixed in the slots 210. The slots 210 provide the second spring sheet with precise positioning and reliable fixing, ensuring the installation accuracy of the spring sheet and its stability during operation, so that it can accurately provide the preset positive stiffness value.

[0038] In one possible implementation, a shaped connector 600 is also included. One end of the shaped connector 600 is fixedly connected to the bearing ring 100, and the other end is provided with a guide structure. The second spring sheet passes through the guide structure and can slide relative to the guide structure along its length.

[0039] Specifically, such as Figure 2 and Figure 6As shown, one end of the irregular connector 600 can be inserted into the mounting groove 110 of the bearing ring 100, and the other end is provided with a U-shaped structure, and a guide structure is provided in the U-shaped structure. Since the bearing ring 200 and the bearing ring 100 rotate relative to each other, if the second spring plate is rigidly connected to the bearing ring 100, unnecessary radial constraints and additional stresses will be generated. The guide structure allows it to slide freely along the length of the second spring plate, which not only ensures that the positive stiffness mechanism 300 can participate in the work, but also releases the excess degrees of freedom, ensuring the accuracy and flexibility of the mechanism's movement, and improving the overall performance and life of the vibration absorber.

[0040] Furthermore, the guide structure consists of two sets of pulleys 610 disposed at the end of the irregular connector 600, with the second spring plate inserted between the two pulleys 610, and both sides of the second spring plate abutting against the pulleys 610 respectively.

[0041] Specifically, such as Figure 7 As shown, two pulleys 610 are arranged side by side in the U-shaped structure at the end of the guide structure via a rotating shaft, and a gap is left between the two sets of pulleys 610 for the second spring plate to pass through. By using pulleys 610 as the guide structure, sliding friction is converted into rolling friction, which greatly reduces the frictional resistance of the irregular connecting piece 600 relative to the second spring plate during the sliding process. This not only improves the response speed of the mechanism, but also reduces energy loss and wear, making the realization of quasi-zero stiffness characteristics more precise and efficient.

[0042] In one possible implementation, the bearing ring 200 is circumferentially provided with a plurality of mounting holes 220 for mounting the inertial mass block 500.

[0043] Understandably, by setting multiple mounting holes 220, different numbers or masses of inertial mass blocks 500 can be conveniently installed as needed, thereby flexibly and precisely adjusting the total rotational inertia of the vibration absorber to meet the vibration suppression requirements of different frequencies; the circumferentially uniform setting ensures the balance of mass distribution and avoids additional vibration caused by mass eccentricity.

[0044] In one possible implementation, the elastic element 420 is a spring.

[0045] Understandably, this provides another specific implementation of the elastic element 420. Standard springs are low-cost, readily available, and have well-defined stiffness characteristics, making them easy to perform theoretical calculations and parameter matching, which can simplify the design and manufacturing process.

[0046] In summary, this application provides a torsional quasi-zero stiffness vibration absorber. When the rotating shaft system undergoes torsional vibration, the bearing ring 100 fixed to it oscillates along with it. Due to the large moment of inertia of the inertial mass block 500, its motion lags behind that of the bearing ring 100. Therefore, a relative angular displacement occurs between the bearing ring 200 and the bearing ring 100. On the one hand, this relative angular displacement causes the positive stiffness mechanism 300, i.e., the second spring plate, fixed to the bearing ring 200, to bend and deform, generating a restoring torque proportional to the angular displacement, i.e., a positive stiffness torque, in the opposite direction to the relative displacement. On the other hand, this relative angular displacement drives the negative stiffness mechanism 400 to operate, and the bearing ring 100 drives the elastic element 42. The roller structure 430 moves relative to the bearing ring 200 and the cam structure 410. The roller structure 430 rolls along the convex arc surface of the cam structure 410, forcing the elastic element 420 to undergo further elastic deformation. The deformation of the elastic element 420 generates a torque, the direction of which is the same as the direction of the relative displacement. Therefore, it exhibits negative stiffness characteristics, that is, it attempts to exacerbate rather than resist this relative motion. Through parameter matching, within a small angle range near the static equilibrium position, the negative torque generated by the negative stiffness mechanism 400 can just offset the positive torque generated by the positive stiffness mechanism 300. At this time, the equivalent dynamic torsional stiffness of the entire vibration absorber system approaches zero, that is, it reaches a quasi-zero stiffness state. According to the principle of dynamics, when the equivalent dynamic stiffness approaches zero, the natural frequency of the vibration absorber also approaches zero. In this way, the vibration absorber can resonate with the main system at extremely low frequencies, thereby transferring the resonance energy of the main system to itself and dissipating it. Therefore, the vibration absorber provided in this application can effectively suppress low-frequency torsional vibrations that traditional linear vibration absorbers cannot handle.

[0047] It should be noted that in this specification, relational terms such as first and second are used only to distinguish one entity from several other entities, and do not necessarily require or imply any such actual relationship or order between these entities.

[0048] The various embodiments in this specification are described in a progressive manner, with each embodiment focusing on the differences from other embodiments. The same or similar parts between the various embodiments can be referred to each other.

[0049] The embodiments provided by the present invention have been described in detail above. Specific examples have been used to illustrate the principles and implementation methods of the present invention. The descriptions of the embodiments above are merely for the purpose of helping to understand the method and core ideas of the present invention. It should be noted that those skilled in the art can make various improvements and modifications to the present invention without departing from its principles, and these improvements and modifications also fall within the protection scope of the present invention.

Claims

1. A torsional quasi-zero stiffness vibration absorber, used for mounting on a vibrating shaft to suppress its torsional vibration, characterized in that, include: The bearing ring (100) is fixedly installed on the vibrating shaft; The bearing ring (200) is a ring structure. The bearing ring (200) is coaxially arranged with the bearing ring (100). A positive stiffness mechanism (300) and a negative stiffness mechanism (400) are connected between the bearing ring (200) and the bearing ring (100). The positive stiffness mechanism (300) is used to provide positive stiffness elastic restoring force, and the negative stiffness mechanism (400) is used to provide negative stiffness effect. An inertial mass block (500), detachably mounted on the bearing ring (200), is used to provide rotational inertia.

2. The torsional quasi-zero stiffness vibration absorber according to claim 1, characterized in that, The negative stiffness mechanism (400) includes: A pair of cam structures (410) are symmetrically arranged inside the bearing ring (200), and the cam structure (410) has a working surface with a specific profile; A pair of elastic elements (420) have one end fixed to the bearing ring (100) and the other end provided with a rotatable roller structure (430), which abuts against the cam structure (410).

3. The torsional quasi-zero stiffness vibration absorber according to claim 2, characterized in that, The working surface of the cam structure (410) is a convex arc surface with a semi-circular structure.

4. The torsional quasi-zero stiffness vibration absorber according to claim 2, characterized in that, The elastic element (420) has a hexagonal structure and includes several first spring plates connected end to end. A connecting part (440) is provided on the elastic element (420), and the connecting part (440) is symmetrically arranged with the roller structure (430). The connecting part (440) is used to be inserted into the bearing ring (100).

5. The torsional quasi-zero stiffness vibration absorber according to claim 2, characterized in that, The positive stiffness mechanism (300) includes a pair of second spring plates, the two ends of which are fixed to the bearing ring (200), and the two second spring plates are symmetrical about the elastic element (420).

6. The torsional quasi-zero stiffness vibration absorber according to claim 5, characterized in that, The inner side of the bearing ring (200) is provided with symmetrical slots (210), and the two ends of the second spring sheet are respectively embedded and fixed in the slots (210).

7. The torsional quasi-zero stiffness vibration absorber according to claim 5, characterized in that, It also includes a shaped connector (600), one end of which is fixedly connected to the bearing ring (100), and the other end is provided with a guide structure. The second spring sheet passes through the guide structure and can slide relative to the guide structure along its length direction.

8. The torsional quasi-zero stiffness vibration absorber according to claim 7, characterized in that, The guide structure consists of two sets of pulleys (610) disposed at the end of the irregular connector (600), the second spring plate being inserted between the two pulleys (610), and the two sides of the second spring plate abutting against the pulleys (610) respectively.

9. The torsional quasi-zero stiffness vibration absorber according to claim 1, characterized in that, The bearing ring (200) is uniformly provided with a plurality of mounting holes (220) for mounting the inertial mass block (500) in the circumferential direction.

10. The torsional quasi-zero stiffness vibration absorber according to claim 2, characterized in that, The elastic element (420) is a spring.

Images