Vibration reduction superstructure of combined type inerter light beam pipe system

Abstract

The invention discloses a vibration reduction superstructure of a composite inerter light beam pipe system, and particularly relates to the field of mechanical vibration control, the vibration reduction superstructure comprises a beam pipe main body and a plurality of resonance units periodically arranged on the beam pipe main body; the rhombic four-bar mechanism converts infinitesimal displacement in the vertical direction into large-amplitude displacement in the horizontal direction, and first-stage inertia amplification is achieved; the screw-nut type inerter device converts axial translation of a nut into large-amplitude rotating motion of a steel hollow flywheel, and second-stage inertia amplification is achieved. According to the invention, through a series two-stage amplification mechanism, the system generates equivalent inertia which is far greater than the physical mass of the system while keeping extremely light physical mass, so that the inherent frequency of the system is obviously reduced, a wide vibration band gap is formed in an ultra-low frequency range, and propagation of bending waves is effectively inhibited; the technical problem of a traditional light superstructure in the aspect of ultralow-frequency broadband vibration control is solved, and unification of light weight and efficient ultralow-frequency broadband vibration reduction is achieved.

Description

Technical Field

[0001] This invention relates to the field of mechanical vibration control technology, and more specifically, to a composite inertial-capacity lightweight beam-pipe system vibration reduction superstructure. Background Technology

[0002] With the rapid development of modern high-end equipment towards ultra-high speed, ultra-precision, extreme dimensions, and lightweight design, its structural dynamics are becoming increasingly complex. Vibration has become a key factor restricting the performance, reliability, and safety of equipment. Beam and tubular structures, as core components in engineering equipment that integrate load-bearing and function (such as aircraft frames, vehicle chassis beams, and fluid transport pipelines), directly determine the vibration response and operational stability of the overall system due to their dynamic characteristics. These structures typically feature lightweight, large spans, and high flexibility, resulting in low resonant frequencies and sensitivity to external excitations. Severe resonance is particularly likely in the low-frequency (10-200Hz) and ultra-low-frequency (0-10Hz) ranges, leading to structural fatigue damage, connection failures, and functional loss.

[0003] Ultra-low frequency vibrations, due to their long wavelength, strong penetration, and slow energy decay, are difficult to effectively suppress using conventional damping materials or localized weight increases. Traditional vibration control technologies are divided into active control and passive control. While active control offers superior performance, it suffers from system complexity, high cost, and stringent environmental requirements. Passive control, on the other hand, is more widely used in engineering due to its simple structure, high reliability, and lack of external power requirements.

[0004] The emergence of periodic metamaterials / metastructures has provided a new paradigm for passive vibration control. These artificial structures possess vibration bandgap characteristics not found in natural materials, meaning that elastic waves cannot propagate within a specific frequency range (bandgap) and are thus suppressed. The formation of the bandgap is mainly based on two mechanisms: Bragg scattering and local resonance. The Bragg bandgap depends on the periodic size of the structure; achieving a low-frequency bandgap requires a large-size structure, leading to increased mass and hindering lightweight design. The local resonance bandgap, by embedding resonant units, achieves "small-size control of large wavelengths," overcoming the limitations of Bragg scattering and becoming a research hotspot for low-frequency vibration control.

[0005] However, to achieve a low-frequency bandgap in traditional local resonant superstructures, large mass blocks or extremely low-stiffness elastic elements are typically required, which contradicts the requirements of lightweight and high-stiffness equipment. To overcome this bottleneck, the principle of inertial amplification was introduced. Specifically, a linkage-type inertial amplification mechanism amplifies equivalent inertia through geometric motion coupling; while the inertial container, as a mechanical element, converts linear motion into the rotation of a hollow steel flywheel through mechanisms such as ball screws or racks, generating an "apparent mass" (inertial capacitance coefficient) far greater than its own physical mass.

[0006] Despite the potential of inertial amplification technology, existing techniques still have significant shortcomings: single linkage-type inertial amplification structures have limited amplification factors and often require additional mass blocks to achieve low-frequency bandgap, hindering ultra-lightweight design; while independent inertial capacitance damping devices can achieve significant apparent mass, their integration into the main structure as independent components is complex, and their effective isolation bandwidth is typically narrow, making them unsuitable for broadband vibration environments. Combining inertial containers with superstructures is an effective approach to resolving these contradictions, but current research is mostly theoretical, lacking concrete, efficient, and easily engineering-implementable physical structural solutions.

[0007] Therefore, there is an urgent need for an innovative lightweight superstructure design that can deeply integrate the inertial amplification effect with the bandgap characteristics of the superstructure, and achieve efficient vibration suppression at ultra-low frequencies and with a wide bandwidth without increasing the physical mass. Summary of the Invention

[0008] To overcome the aforementioned deficiencies of the prior art, embodiments of the present invention provide a composite inertial-capacitive lightweight beam-tube system vibration-damping superstructure. This structure innovatively couples a rhombic four-bar inertial amplification mechanism with a screw-nut inertial-capacitive mechanism to construct a resonant unit with a two-stage inertial amplification mechanism, and periodically integrates it into the beam-tube body. This achieves excellent vibration reduction performance in the ultra-low frequency broadband range without significantly increasing the structural weight, effectively solving the contradiction between "lightweight" and "large inertia" faced by traditional lightweight superstructures in ultra-low frequency vibration control.

[0009] To achieve the above objectives, the present invention provides the following technical solution: a composite inertial-capacitive lightweight beam-tube system vibration reduction superstructure, comprising a beam-tube body, wherein multiple resonant units are periodically arranged on the beam-tube body, and each resonant unit is provided with a lightweight base plate at its bottom and side; the resonant unit includes a series-coupled rhombic four-bar inertial amplification mechanism and a screw-nut type inertial-capacitive device, forming a two-stage inertial amplification mechanism;

[0010] The rhomboid four-bar inertia amplification mechanism consists of four rigid bars hinged at their intersections via pins to form a rhomboid structure. The upper apex is hinged to a lightweight block at the upper apex via a pin, which is used for fixed connection to the main body of the beam tube. A vertical spring is installed between the upper and lower apexes, serving as the core elastic element of the system. Lateral lightweight blocks are hinged to the two apexes of the rhomboid mechanism, and a lightweight nut is hinged to the lower apex. The function of this mechanism is to input a small vertical displacement from the main body of the beam tube, which, through the geometric deformation of the rhomboid mechanism, is converted into a large horizontal displacement of the lightweight blocks on both sides, thereby achieving a preliminary amplification of the equivalent inertia of the two mass blocks. This is the first stage of inertia amplification.

[0011] The screw-nut type inertial capacity device includes a lightweight screw, a steel hollow flywheel, and a lightweight support base plate. The lightweight screw and the lightweight nut at the lower apex of the rhombic four-bar linkage are engaged by a threaded pair. The steel hollow flywheel (preferably a steel hollow flywheel to reduce weight) is fixedly installed on the lightweight screw. The lower end of the lightweight screw is connected to the lightweight support base plate through a bearing or hinge structure, and the support base plate serves as a fixed end. When the lightweight nut undergoes axial displacement under the drive of the rhombic mechanism, it drives the lightweight screw and the steel hollow flywheel to generate a large rotational motion through the threaded pair, efficiently converting the translational kinetic energy of the system into the rotational kinetic energy of the steel hollow flywheel. The rotational inertia of the steel hollow flywheel generates a huge inertial force, realizing a secondary amplification of the equivalent inertia, which is the second-stage inertial amplification.

[0012] In a preferred embodiment, the resonant unit can be designed as a composite inertial amplification resonant unit. In this configuration, a lightweight nut is hinged to each of the two vertices and the lower vertices of the rhomboid four-bar inertial amplification mechanism. Correspondingly, three screw-nut type inertial capacitive devices are provided, each cooperating with one of the three lightweight nuts. The lightweight screws of the two screw-nut type inertial capacitive devices are connected to a lateral lightweight slider via bearings, and the slider can slide up and down along the side wall of a lightweight base plate. The lower end of the lightweight screw of the lower screw-nut type inertial capacitive device is connected to the base plate of the lightweight base plate via bearings. This composite design can further integrate the motion in multiple directions, improving the inertial amplification effect and bandgap characteristics.

[0013] In a preferred embodiment, the main body of the beam-tube structure can be a beam structure or a pipe structure; the resonant unit is fixedly connected to the main body of the beam-tube structure through processes such as welding, high-strength bonding or integrated casting to form a periodic superstructure with good integrity.

[0014] This invention also includes a vibration reduction method for a composite inertial-capacity lightweight beam-pipe system vibration reduction superstructure, the specific steps of which are as follows:

[0015] When the main body of the beam tube is subjected to external vibration excitation, the rhomboid four-bar inertial amplification mechanism of the driving resonant unit moves, converting the small vertical displacement into a large horizontal displacement, thus completing the first stage of inertial amplification.

[0016] At the same time, the motion of the lower vertex of the rhomboid four-bar inertial amplification mechanism drives the lightweight nut to generate axial displacement, which in turn drives the lightweight screw and the steel hollow flywheel to rotate through the threaded pair, converting translational kinetic energy into rotational kinetic energy and completing the second stage of inertial amplification;

[0017] This secondary inertial amplification mechanism generates a huge equivalent inertia in the system, significantly reducing the natural frequency, thereby forming a vibration bandgap in the ultra-low frequency range and suppressing the propagation of elastic waves in the beam-tube body.

[0018] The technical effects and advantages of this invention are as follows:

[0019] 1. This invention achieves a two-stage inertial amplification mechanism by series coupling of a rhombic four-bar linkage and a screw-nut type inertial capacitance device. It can generate an equivalent inertia of hundreds of times or even higher than the physical mass with extremely light physical mass, fundamentally solving the problem that traditional local resonant superstructures rely on large mass blocks to achieve low-frequency band gaps.

[0020] 2. Due to the second-order inertial amplification mechanism, the present invention greatly reduces the equivalent natural frequency of the system, enabling the superstructure constructed therefrom to generate a wide vibration bandgap in the ultra-low frequency range; within this bandgap frequency range, bending wave vibration is significantly suppressed, thereby achieving efficient control of the challenging ultra-low frequency broadband vibration in engineering.

[0021] 3. All inertial amplification elements in this invention are made of lightweight materials and have a hollow design. The entire resonant unit is directly and periodically integrated on the main body of the beam tube as a functional structure. There is no need to install independent and bulky vibration damping devices, which realizes the integration of load-bearing and vibration damping functions, perfectly meeting the requirements of modern equipment for lightweight and compactness.

[0022] 4. This invention successfully transforms the inertial container from a traditional independent vibration damping element into an intrinsic functional unit of a superstructure, solving the problems of narrow frequency band and complex integrated design when used independently. The superstructure is mainly composed of common rods, springs, screws, nuts, steel hollow flywheels and pins, and can be manufactured using conventional machining processes, resulting in relatively low cost and good prospects for engineering applications and marketization. Attached Figure Description

[0023] Figure 1 This is a three-dimensional schematic diagram of the overall structure of the composite inertial-capacity beam-tube superstructure, which is a preferred embodiment of the present invention.

[0024] Figure 2 This is a schematic diagram of a composite beam-pipe system superstructure unit, which is a preferred embodiment of the present invention.

[0025] Figure 3 This is a three-dimensional schematic diagram of the overall structure of the composite inertial-capacity beam-pipe system superstructure of the present invention.

[0026] Figure 4 This is a schematic diagram of the composite inertial compressive beam-pipe system superstructure unit of the present invention.

[0027] Figure 5 This is a schematic diagram of the resonant unit structure of the present invention.

[0028] Figure 6 This is a schematic diagram of the rhomboid four-bar inertial amplification mechanism of the present invention.

[0029] Figure 7This is a schematic diagram of the screw-nut inertial capacitive mechanism of the present invention.

[0030] Figure 8 This is a schematic diagram of the inertial capacitive mechanism structure provided in the lateral orientation of the present invention.

[0031] Figure 9 This is a diagram of the superstructure energy band structure of the composite inertial-capacitance lightweight beam-tube system of the present invention.

[0032] Figure 10 The diagram shows the superstructure band structure of the composite inertial-capacitance lightweight beam-pipe system, which is a preferred embodiment of the present invention.

[0033] The attached diagram is labeled as follows: 1. Beam-tube main body, 2. Resonant unit, 3. Rhomboid four-bar inertial amplification mechanism, 4. Screw-nut type inertial capacitance mechanism, 5. Lightweight base plate;

[0034] 31 Pin, 32 Rigid rod, 33 Light block at the top vertex, 34 Vertical spring, 35 Lateral light block;

[0035] 41 Lightweight screw, 42 Lightweight nut, 45 Steel hollow flywheel, 46 Lightweight support base plate, 47 Lateral lightweight slider, 48 Lightweight flywheel. Detailed Implementation

[0036] 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.

[0037] Example 1: Rhomboid connecting rod-screw inertial-capacity lightweight beam-pipe system vibration reduction superstructure

[0038] Reference Figures 1-3 This embodiment provides a composite inertial-capacitance lightweight beam-tube system vibration-damping superstructure. The structure includes a beam-tube main body 1 (a beam structure in this example) serving as the load-bearing foundation, and multiple resonant units 2 periodically arranged on the beam-tube main body 1. The secondary inertial amplification resonant units are as follows: Figure 5 As shown, through the coupling of a rhombic four-bar linkage ( Figure 6 (as shown) and screw-nut type inertial capacity ( Figure 7 As shown, this constitutes a two-stage series inertial amplification mechanism;

[0039] like Figures 4-6Each resonant unit 2 is the core of the vibration reduction function; it is fixedly connected to the main body of the beam tube 1 through the upper vertex lightweight block 33; the resonant unit 2 is composed of a rhomboid four-bar inertial amplification mechanism 3 and a screw-nut type inertial capacitance device 4 coupled in series; the rhomboid four-bar inertial amplification mechanism 3 is composed of four rigid rods 32 hinged into a rhombus shape through pins 31; the upper vertex is hinged to the upper vertex lightweight block 33 and fixed to the beam; a vertical spring 34 is connected between the upper and lower vertices; lateral lightweight blocks 35 are hinged to the two side vertices; and a lightweight nut 42 is hinged to the lower vertex;

[0040] like Figures 7-8 The lightweight screw 41 and lightweight nut 42 of the screw-nut type inertial capacity device 4 are engaged by a threaded pair; a steel hollow flywheel 45 is fixed on the lightweight screw 41; the lower end of the lightweight screw 41 is mounted on the lightweight support base plate 46 through a bearing.

[0041] The first-stage inertial amplification mechanism is a rhomboid four-bar linkage inertial amplification mechanism 3, mainly composed of rigid rods 32, vertical rubber springs 34, and lightweight blocks 33. The four rigid rods 32 are hinged at their intersections by pins 31 to form a rhomboid mechanism. The upper apex is hinged to the top lightweight block 33 by pins 31, which is used to fix the connection to the main beam or pipe. The upper and lower apexes are connected by a hinge through the vertical springs 34 and pins 31, serving as the core elastic element of the system. Lateral lightweight blocks 35 are hinged to the two side apexes to transmit and amplify horizontal and vertical displacements. The lower apex is hinged to a lightweight nut 42 by pins 31, serving as the power output end of the first-stage mechanism.

[0042] The second-stage inertial amplification mechanism is a screw-nut type inertial-capacitance amplification device 4, mainly composed of a lightweight screw 41, a steel hollow flywheel 45, and a lightweight support base plate 46. The lightweight screw 41 and the lightweight nut 42 are connected by a threaded connection, converting the axial motion of the nut into the rotational motion of the screw, realizing the conversion between translational and rotational motion. The steel hollow flywheel 45 is fixed to the lower end of the screw by welding or high-strength adhesive, serving as the core carrier of rotational inertia. The lower end of the screw is connected to the lightweight support base plate 46 through a bearing or hinge structure. The support base plate 46 serves as a fixed end to constrain the vertical displacement of the screw, thus forming a complete inertial-capacitance system.

[0043] The completed secondary inertial amplification resonant unit 2 is fixedly connected to the beam-tube body 1 to form a beam / tube system superstructure unit with inertial amplification characteristics. Figure 4 As shown); subsequently, the unit is periodically arranged along the x-axis, and a beam / pipe system vibration-damping superstructure with good integrity is formed through processes such as welding, high-strength bonding, or integral casting. Figure 3 As shown); this structure, while maintaining its lightweight and simple structure, exhibits significant ultra-low frequency broadband vibration bandgap characteristics (as shown). Figure 9 As shown in the figure, it can effectively suppress the propagation of elastic waves in a specific frequency band and can be widely used in practical engineering vibration reduction;

[0044] Working principle: When the main body 1 of the beam tube is subjected to external vertical vibration excitation, it drives the light block 33 at the upper vertex to generate a vertical displacement; the rhomboid mechanism deforms accordingly, amplifying the small vertical displacement into a large horizontal displacement of the lateral light block 35, completing the first stage of inertial amplification; at the same time, the light nut 42 at the lower vertex generates a significant axial displacement, driving the light screw 41 and the steel hollow flywheel 45 to rotate at high speed, converting translational kinetic energy into rotational kinetic energy, and using the huge rotational inertia of the steel hollow flywheel 45 to generate a huge inertial force, completing the second stage of inertial amplification; these two stages of series amplification enable the resonant unit 2 to exhibit huge equivalent inertia under extremely light weight, significantly reducing the natural frequency of the system;

[0045] Multiple such resonant units 2 are periodically arranged on the main body of the beam tube 1 (see...). Figure 1 ), forming a superstructure; its band structure is calculated using the finite element method, such as Figure 9 As shown, the structure produces a significant bandgap (shaded area) in the frequency range of 6.47-103.30Hz; within this bandgap, bending waves of the corresponding frequency cannot propagate in the structure.

[0046] Example 2: Vibration-reducing superstructure of rhombic connecting rod-three-screw composite inertial-capacity lightweight beam-pipe system

[0047] Reference Figures 4-6 This embodiment provides a composite structure with stronger inertial amplification effect; its core difference lies in the fact that the resonant unit 2 is a composite design.

[0048] The rhomboid four-bar linkage 3 of the composite resonant unit 2 is hinged with a lightweight nut 42 at each of its two vertices and the lower vertices; correspondingly, it is equipped with three independent screw-nut type inertial capacitance devices 4; the lightweight screws 41 of the inertial capacitance devices 4 on both sides are connected to the lateral lightweight sliders 47 through bearings, and the sliders 47 can slide along the side wall of the lightweight base plate 5; the lower end of the lightweight screw 41 of the lower inertial capacitance device 4 is connected to the base plate of the lightweight base plate 5 through bearings; the lightweight base plate 5 serves as the support and encapsulation of the entire unit;

[0049] Working principle: When the main body 1 of the beam tube vibrates, the rhomboid mechanism 3 not only drives the light nut 42 at the lower apex to move, but also drives the lateral light blocks 35 on both sides to move horizontally; the light nut 42 and the lateral light blocks 35 respectively drive the corresponding screw 41, the steel hollow flywheel 45 and the light flywheels 48 on both sides to rotate; this makes the vibration energy from the beam more fully converted into the rotational kinetic energy of the steel hollow flywheel 45 and the light flywheel 48, realizing more extreme inertial amplification and energy dissipation;

[0050] This composite resonant unit 2 is periodically arranged on the main body of the beam tube 1 (see...). Figure 4 Its band structure is as follows Figure 10 As shown, a very concentrated bandgap was generated in the ultra-low frequency band of 4.69-7.32Hz.

[0051] In summary, this invention, through the ingenious design of a two-stage inertial amplification resonant unit, creates a beam-tube structure that combines lightweight, ultra-low frequency, and broadband vibration reduction characteristics. It is particularly suitable for ultra-low frequency broadband vibration suppression of beam and tube structures in aerospace, vehicle engineering, shipbuilding, and other fields, and has significant engineering application value.

[0052] Finally, the following points should be noted: First, in the description of this application, it should be noted that, unless otherwise specified and limited, the terms "installation", "connection", and "linkage" should be interpreted broadly, and can be mechanical or electrical connections, or internal connections between two components, or direct connections. "Up", "down", "left", "right", etc. are only used to indicate relative positional relationships. When the absolute position of the described object changes, the relative positional relationship may change.

[0053] Secondly: The accompanying drawings of the embodiments disclosed in this invention only involve the structures involved in the embodiments disclosed in this invention. Other structures can refer to the general design. In the absence of conflict, the same embodiment and different embodiments of this invention can be combined with each other.

[0054] In conclusion, the above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A composite inertial-capacitance lightweight beam-tube system vibration-damping superstructure, comprising a beam-tube main body (1), characterized in that: Multiple resonant units (2) are periodically arranged on the main body (1) of the beam tube, and each resonant unit (2) is provided with a lightweight base plate (5) at the bottom and side. The resonant unit (2) includes a series-coupled rhomboid four-bar inertial amplification mechanism (3) and a screw-nut type inertial capacitance device (4), forming a two-stage inertial amplification mechanism; The rhomboid four-bar inertial amplification mechanism (3) is used to convert the input displacement in the vertical direction into the amplified displacement in the horizontal direction, thereby realizing the first stage of inertial amplification. The screw-nut type inertial capacitance device (4) is used to convert the translational displacement output by the first-stage inertial amplification into the rotational motion of the steel hollow flywheel (45), thereby realizing the second-stage inertial amplification.

2. The composite inertial-capacity lightweight beam-pipe system vibration-damping superstructure according to claim 1, characterized in that: The rhomboid four-bar inertial amplification mechanism (3) includes four rigid rods (32) that are hinged at each other to form a rhomboid structure by means of pins (31), a light block (33) at the upper vertex of the rhomboid mechanism and fixedly connected to the main body of the beam tube (1), a vertical spring (34) between the upper vertex and the lower vertex, and lateral light blocks (35) respectively hinged to the two vertices of the rhomboid mechanism.

3. The composite inertial-capacitance lightweight beam-pipe system vibration-damping superstructure according to claim 2, characterized in that: The screw-nut inertial capacity device (4) includes a lightweight nut (42) hinged to the lower apex of the rhomboid mechanism, a lightweight screw (41) that engages with the lightweight nut (42) via a threaded pair, a steel hollow flywheel (45) fixedly installed on the lightweight screw (41), and a lightweight support base plate (46) for supporting the lower end of the lightweight screw (41). The lower end of the lightweight screw (41) is connected to the lightweight support base plate (46) via a bearing or hinge structure.

4. The composite inertial-capacitance lightweight beam-pipe system vibration-damping superstructure according to claim 3, characterized in that: The steel hollow flywheel (45) is configured as a steel hollow flywheel.

5. The composite inertial-capacitance lightweight beam-pipe system vibration-damping superstructure according to claim 1, characterized in that: The resonant unit (2) is configured as a composite inertial amplification resonant unit, with a lateral lightweight block (35) hinged at both vertices of its rhomboid four-bar inertial amplification mechanism (3) and a lightweight nut (42) hinged at the lower vertices. Correspondingly, three screw-nut type inertial capacity devices (4) are provided at the corresponding positions of the lateral lightweight block (35) and the lightweight nut (42); The lightweight screws (41) of the screw-nut type inertial capacity devices (4) on both sides are connected to the lateral lightweight sliders (47) that can slide up and down along the side wall of the lightweight base plate (5) through bearings. The lower end of the lightweight screws (41) of the screw-nut type inertial capacity devices (4) on the lower side is connected to the base plate of the lightweight base plate (5) through bearings.

6. The composite inertial-capacitance lightweight beam-pipe system vibration-damping superstructure according to claim 5, characterized in that: The lightweight base plate (5) serves as the support and encapsulation structure for the composite inertial amplification resonant unit.

7. The composite inertial-capacitance lightweight beam-pipe system vibration-damping superstructure according to claim 1, characterized in that: The main body of the beam-pipe (1) is a beam structure or a pipe structure.

8. The composite inertial-capacitance lightweight beam-pipe system vibration-damping superstructure according to claim 1, characterized in that: The resonant unit (2) is fixedly connected to the beam tube body (1) by welding, high-strength bonding or integrated casting process.

9. A vibration reduction method applicable to the composite inertial-capacity lightweight beam-pipe system vibration reduction superstructure according to any one of claims 1-8, characterized in that, The specific steps are as follows: When the main body of the beam tube (1) is subjected to external vibration excitation, the rhomboid four-bar inertial amplification mechanism (3) of the resonant unit (2) moves, converting the small displacement in the vertical direction into a large displacement in the horizontal direction, and completing the first stage of inertial amplification. At the same time, the motion of the lower vertex of the rhomboid four-bar inertial amplification mechanism (3) drives the lightweight nut (42) to generate axial displacement, which in turn drives the lightweight screw (41) and the steel hollow flywheel (45) to rotate through the thread pair, converting translational kinetic energy into rotational kinetic energy and completing the second stage of inertial amplification; The secondary inertial amplification mechanism generates a huge equivalent inertia in the system, significantly reducing the natural frequency, thereby forming a vibration band gap in the ultra-low frequency range and suppressing the propagation of elastic waves in the beam tube body (1).

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