A wide low-frequency vibration reduction device with non-local particle damping rotating superstructure

Abstract

The present invention discloses a non-local particle damping rotating superstructure wide low-frequency vibration reduction device, comprising a mechanical superstructure and an external cavity; the mechanical superstructure is composed of a plurality of unit cell structures periodically arranged in an XY plane, and the unit cell structure is composed of a non-local connection structure, a matrix damping structure, a connection damping structure and a rod; the matrix damping structure is composed of a particle damping group, a baffle, a partition and a matrix damping cavity; the connection damping structure is composed of a particle damping group, a baffle, a partition and a connection damping cavity; the non-local connection structure is composed of a particle damping group, a partition, a baffle and a non-local cavity; a plurality of layers of particle damping groups are arranged in the matrix damping cavity, the connection damping cavity and the non-local cavity, partitions are provided between each layer of particle damping groups, and baffles are detachably installed in each cavity; the external cavity and the mechanical superstructure are connected to each other by a rotating connection rod, and the bottom of the non-local connection structure in the mechanical superstructure is in a suspended state.

Description

Technical Field

[0001] The present invention belongs to the technical field of engineering vibration isolation and noise reduction, and in particular relates to a two-dimensional rotating periodic superstructure device with non-local characteristics and particle damping wide low-frequency vibration reduction characteristics. Background Art

[0002] Mechanical superstructures and metamaterials are artificially designed structures whose mechanical properties (such as density and elastic modulus) can be precisely controlled by designing their internal structure. The concept of mechanical superstructures and metamaterials originated from the research on electromagnetic metamaterials. The earliest research on superstructures and metamaterials focused on the field of electromagnetic waves, and later the concept was extended to the field of acoustics. In the early 2000s, researchers began to explore the potential applications of acoustic or mechanical superstructures and metamaterials, and gradually developed various design and manufacturing technologies. Unlike natural structures and materials, mechanical superstructures and metamaterials can achieve some mechanical properties that cannot be achieved under conventional circumstances, such as complete band gaps. Mechanical superstructures have broad application prospects. For example, in the field of vibration isolation and noise reduction, compared with traditional structures, mechanical superstructures can more effectively block or absorb sound and elastic waves.

[0003] Particle damping is a passive vibration control technology that uses the relative motion of granular materials within a container and their collision and friction with the container walls to dissipate vibration energy. Granular materials (such as sand and metal balls) collide and rub against each other during vibration, generating internal friction and thus attenuating vibration. The concept of particle damping has been around for decades, but its widespread application and in-depth research have primarily occurred in recent decades. Due to its simple structure and effective damping effect, particularly in high-frequency vibration environments, particle damping technology has garnered widespread attention in fields such as aerospace, mechanical engineering, and civil engineering. For example, incorporating particle damping into mechanical systems can reduce vibration and noise, and can also mitigate wind-induced and earthquake-induced vibrations in high-rise buildings and bridges.

[0004] Mechanical superstructures and particle damping each have unique advantages and application scenarios in the fields of mechanics and vibration control. Mechanical superstructures, with their sophisticated design and controllable mechanical properties, demonstrate tremendous potential in sound insulation, noise reduction, and acoustic wave manipulation. Particle damping, with its simple and efficient energy dissipation mechanism, excels in vibration control and reduction. Research and development in both fields has not only enriched the theoretical foundations of mechanics and vibration control but also promoted innovation and advancement in practical applications. Summary of the Invention

[0005] The purpose of the present invention is to overcome the shortcomings of the prior art and provide a non-local particle damping rotating superstructure wide low-frequency vibration reduction device, which combines the advantages of the rotating structure and the particle damper to achieve wide low-frequency vibration and noise reduction;

[0006] The object of the present invention is achieved through the following technical solutions:

[0007] A non-local particle damping rotating superstructure wide low-frequency vibration reduction device comprises a mechanical superstructure and an external cavity; the mechanical superstructure is a planar periodic structure formed by a plurality of unit cell structures arranged periodically in an XY plane, and the unit cell structure is composed of a non-local connection structure, a matrix damping structure, a connection damping structure, and rods;

[0008] The matrix damping structure is composed of a particle damping group, a baffle, a partition and a matrix damping cavity; the connection damping structure is composed of a particle damping group, a baffle, a partition and a connection damping cavity; the non-local connection structure is composed of a particle damping group, a partition, a baffle and a non-local cavity; the matrix damping cavity, the connection damping cavity and the non-local cavity are each provided with several layers of particle damping groups, with partitions provided between each layer of particle damping groups, and the matrix damping cavity, the connection damping cavity and the non-local cavity are each detachably provided with baffles;

[0009] The outer cavity and the mechanical superstructure are connected to each other through a rotating connecting rod, and the bottom of the non-local connection structure in the mechanical superstructure is in a suspended state.

[0010] Furthermore, the mechanical superstructure is divided into two layers, the upper layer being the matrix damping structure and the connection damping structure, and the lower layer being the non-local connection structure; the non-local connection structures of the lower layer are interconnected by long connecting rods, and the top of the non-local connection structure in each unit cell structure is connected to the matrix damping structure by a short connecting rod.

[0011] Furthermore, the matrix damping structure and the connection damping structure within the mechanical superstructure are arranged alternately, presenting periodic characteristics on the plane, thereby realizing the Bragg band gap characteristics and achieving the effect of vibration isolation in a specific frequency domain.

[0012] Furthermore, the matrix damping cavity is a rectangular cavity structure with an open top, the cross-section of the matrix damping cavity is a square structure with a side length of 60 mm, and the depth of the matrix damping cavity is 45 mm; the side wall and bottom thickness of the matrix damping cavity are both 5 mm; the normal direction of the side wall of the matrix damping cavity is 45 degrees to the X direction or the Y direction.

[0013] Furthermore, the connecting damping cavity is a rectangular cavity structure with an open top, the cross-section of the connecting damping cavity is a square structure with a side length of 40 mm, and the depth of the connecting damping cavity is 45 mm; the side wall and bottom surface thicknesses of the connecting damping cavity are both 5 mm; the normal direction of the side wall of the connecting damping cavity is parallel to the X direction or the Y direction.

[0014] Furthermore, the normal directions of the adjacent side wall surfaces between two adjacent matrix damping cavities and the connecting damping cavity are at a 45-degree angle to each other, and the matrix damping cavity and the connecting damping cavity are connected to each other by a rotating connecting rod, so that the unit cell structure composed of the two cavities has the property of mirror non-overlapping, realizing the selective response of the unit cell structure in the mechanical superstructure to circular polarization, and realizing the control of vibration in a specific frequency range.

[0015] Furthermore, the particle damping group is composed of a plurality of solid circular particles, and the distance between the partitions is greater than the maximum diameter of the solid circular particles; the partitions connecting the damping cavity and the matrix damping cavity are fixed on the side wall of the cavity or freely placed on the surface of the particle damping group; when the partitions are fixed, the solid circular particles are installed and removed by disassembling the baffles; the partitions in non-local cavities are not fixed;

[0016] The diameter of the solid circular particles is 9 mm, and the layer height between each layer of particle damping group is 10 mm;

[0017] Vertical grooves are provided on the two opposite inner walls of the base damping cavity and the connecting damping cavity, and the baffle is detachably connected to the base damping cavity and the connecting damping cavity through the vertical grooves; horizontal grooves are provided on the two opposite inner walls of the non-local cavity, and the baffle is detachably connected to the non-local cavity through the horizontal grooves.

[0018] Furthermore, the non-local cavity is a cubic cavity structure, the cross-section of the non-local cavity is a square structure with a side length of 40 mm, and the depth of the non-local cavity is 40 mm; a baffle is detachably provided on the top of the non-local cavity, and the side wall and bottom thickness of the non-local cavity are both 5 mm.

[0019] Furthermore, the particle damping group in the matrix damping cavity and the connection damping cavity occupies 1 / 5 to 1 / 2 of the cavity volume; the particle damping group in the non-local cavity occupies 1 / 3 to 2 / 3 of the non-local cavity volume.

[0020] Furthermore, the non-local connection structure realizes the direct connection of two matrix damping cavities that are not directly connected to each other, realizes the direct transmission of vibration of the two matrix damping cavities, changes the vibration mode, and strengthens the local resonance band gap characteristics; and a non-local cavity is set in the non-local connection structure to further dissipate the vibration energy of the superstructure wide low-frequency vibration reduction device; the mechanical superstructure is often obtained using 3D printing technology.

[0021] Compared with the prior art, the technical solution of the present invention has the following beneficial effects:

[0022] 1. The device of the present invention is based on a periodic mechanical superstructure, and is designed in combination with a matrix damping structure, a connection damping structure, a non-local connection structure, and a particle damping group. It has a two-dimensional periodic form and Bragg scattering band gap characteristics. At the same time, the non-local connection structure connecting different matrix damping cavities has a cavity structure, which can act as a local oscillator, so that the device has a local resonance band gap characteristic, thereby making the device have a wide low-frequency vibration isolation characteristic. The matrix damping cavity and the connection damping cavity are connected by a rotating connecting rod to form a rotating connection structure. By changing the angle of the rotating connection, the vibration reduction and isolation frequency range can be adjusted. Combined with the energy dissipation characteristics of the particle damping group, the purpose of vibration reduction and isolation can be achieved to the greatest extent. Compared with traditional phononic crystal isolators, it has a wider and lower low-frequency band gap characteristic and a better vibration isolation effect.

[0023] 2. Compared with traditional particle dampers, the matrix damping structure, connection damping structure and non-local connection structure in each unit cell structure of the present invention all adopt the form of multi-layer particle damping groups, which solves the problem of insufficient collision of bottom particle damping under vibration in traditional particle damping, so that each particle damping can fully collide under vibration, further increasing the consumption of vibration energy by the particle damping group.

[0024] 3. Compared to traditional particle dampers, each unit cell structure of the present invention features three differently oriented matrix damping cavities: a matrix damping cavity, a connecting damping cavity, and a non-local cavity. All particle damping groups are housed within these three cavities, providing multi-dimensional vibration reduction and isolation. Furthermore, the solid circular particles are distributed within each cavity with minimal gaps, allowing them to easily collide with each other during vibration, thereby dissipating vibration energy.

[0025] 4. Compared with one-dimensional vibration isolation and noise reduction devices, the present invention can achieve vibration reduction and isolation in different directions within a plane, thereby expanding the scope of vibration reduction and isolation.

[0026] 5. Compared with active vibration isolators, the present invention is a passive vibration isolator, which has the advantages of simple structure, high reliability and low cost.

[0027] 6. The diameter of each solid circular particle in the particle damping group is 9 mm, and the layer height between each layer of particle damping groups is 10 mm. This layered treatment can make the collision between the particle damping group and the solid circular particles more complete, thereby maximizing the dissipated energy.

[0028] 7. Each non-local connection structure is connected to a matrix damping structure, and the non-local connection structures are interconnected, achieving direct connection between two matrix damping structures that are not directly connected to each other. This enables direct transmission of vibration between the two matrix damping cavities, changes the vibration mode of the structure, and further enhances the local resonance band gap characteristics of the structure. Cavity structures are also provided at the non-local connection structures to further dissipate the structure's vibration energy. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] Figure 1 A schematic structural diagram of a vibration isolation device provided in an embodiment of the present invention.

[0030] Figure 2-4 A partial cross-sectional structure and an enlarged schematic diagram of the vibration isolation device provided in an embodiment of the present invention.

[0031] Figure 5 This is a schematic cross-sectional view of a vibration isolation device provided in an embodiment of the present invention.

[0032] FIG6(a) is a front view schematic diagram of the mechanical superstructure portion of the vibration isolation device provided in an embodiment of the present invention; FIG6(b) is a left view schematic diagram of the mechanical superstructure portion of the vibration isolation device provided in an embodiment of the present invention; FIG6(c) is a top view schematic diagram of the mechanical superstructure portion of the vibration isolation device provided in an embodiment of the present invention; FIG6(d) is a three-dimensional schematic diagram of the mechanical superstructure portion of the vibration isolation device provided in an embodiment of the present invention;

[0033] Figure 7 A schematic perspective structural diagram of the mechanical superstructure portion of the vibration isolation device provided by an embodiment of the present invention.

[0034] FIG8( a ) is a schematic diagram of a perspective front view of a unit cell structure provided in an embodiment of the present invention; FIG8( b ) is a schematic diagram of a perspective left view of a unit cell structure provided in an embodiment of the present invention; FIG8( c ) is a schematic diagram of a perspective top view of a unit cell structure provided in an embodiment of the present invention; FIG8( d ) is a schematic diagram of a three-dimensional perspective view of a unit cell structure provided in an embodiment of the present invention;

[0035] Figures 9-12 Schematic diagram of the cross-sectional structure of the unit cell structure provided by the embodiment of the present invention at different viewing angles.

[0036] Figure 13 A schematic diagram of the exploded structure of a unit cell structure provided in an embodiment of the present invention.

[0037] Figure 14 Schematic diagram of the structural details of the base damping cavity baffle of the vibration isolation device provided in an embodiment of the present invention.

[0038] Figure 15A comparison chart of the acceleration responses of a vibration isolation device with particle damping and a vibration isolation device without particle damping within the range of 0-300 Hz provided by an embodiment of the present invention.

[0039] Figure 16 A comparison diagram of the velocity responses of a vibration isolation device with particle damping and a vibration isolation device without particle damping within the range of 0-300 Hz provided by an embodiment of the present invention.

[0040] Figure 17 A comparison diagram of the deformation responses of a vibration isolation device with particle damping and a vibration isolation device without particle damping within the range of 0-300 Hz provided by an embodiment of the present invention.

[0041] Figure 18 A stress response comparison diagram of a vibration isolation device with particle damping and a vibration isolation device without particle damping within the range of 0-300 Hz provided by an embodiment of the present invention.

[0042] Figure 19 A comparison chart of acceleration responses of a vibration isolation device provided in an embodiment of the present invention within the range of 0-300 Hz, showing a vibration isolation device with one layer of particle damping and a vibration isolation device with three layers of particle damping.

[0043] Figure 20 A comparison diagram of the velocity responses of a vibration isolation device provided in an embodiment of the present invention within the range of 0-300 Hz, a vibration isolation device with one layer of particle damping and a vibration isolation device with three layers of particle damping.

[0044] Figure 21 A comparison diagram of the deformation responses of a vibration isolation device provided in an embodiment of the present invention within the range of 0-300 Hz, with a vibration isolation device having one layer of particle damping and a vibration isolation device having three layers of particle damping.

[0045] Figure 22 A stress response comparison diagram of a vibration isolation device provided in an embodiment of the present invention within the range of 0-300 Hz, showing a vibration isolation device with one layer of particle damping and a vibration isolation device with three layers of particle damping.

[0046] Figure numerals: 1-external cavity, 2-mechanical superstructure, 3-particle damping group, 4-partition, 5-matrix damping cavity, 6-baffle, 7-non-local cavity, 8-particle damping group, 9-partition, 10-long connecting rod, 11-baffle, 12-baffle, 13-rotating connecting rod, 14-connecting damping cavity, 15-partition, 16-particle damping group, 17-short connecting rod. DETAILED DESCRIPTION

[0047] The following is a detailed description of embodiments of the present invention. Examples of these embodiments are shown in the accompanying drawings, in which the same or similar reference numerals represent the same or similar elements or elements having the same or similar functions. These examples are provided for illustrative purposes only and are not to be construed as limiting the present invention.

[0048] The width and position of the elastic band gap can be manipulated by adjusting the rotation angle of the rotating connection structure formed between the base damping cavity and the connecting damping cavity, the geometric parameters of the mechanical superstructure, and the number of particle damping cluster layers in each cavity. This embodiment provides a wide-band, low-frequency vibration reduction device using a non-local particle damping rotating superstructure. By leveraging the vibration energy dissipation of discrete particles and the band gap characteristics of the artificial periodic structure, it can achieve vibration and noise reduction at specific frequencies on a two-dimensional plane.

[0049] The solution adopted by the non-local particle damping rotating superstructure wide low-frequency vibration reduction device of the embodiment of the present invention is: the planar device that needs vibration isolation is fitted with the external cavity of the embodiment of the present invention. The form of the external cavity can be appropriately changed so that the structure that needs vibration isolation is tightly connected to the embodiment of the present invention. Through the device composed of the mechanical superstructure and the internal particle damping spheres, in the elastic waves transmitted in the two-dimensional plane, the band gap characteristics of the periodic mechanical structure and the local resonance characteristics caused by the non-local connection structure achieve the effect of vibration isolation and vibration reduction in a specific frequency band. At the same time, during the transmission of the elastic wave, the circular particles in the same layer collide with each other, greatly dissipating the elastic energy, thereby achieving vibration reduction and noise reduction within the entire frequency band.

[0050] The structure of the non-local particle damping rotating superstructure wide low frequency vibration reduction device according to the embodiment of the present invention is as follows: Figures 1 to 5 As shown, it mainly includes an outer cavity 1 and a mechanical superstructure 2, wherein the outer cavity 1 and the mechanical superstructure 2 are connected by a rotating connecting rod 13, and the non-local connection structure part at the bottom of the mechanical superstructure 2 is not connected to the outer cavity 1, and the non-local connection structure is in a suspended state. The mechanical superstructure part is mainly composed of a cavity, a rod and a particle damping group. The mechanical superstructure is a two-dimensional periodic form, that is, it presents a two-dimensional periodic form in the XY plane. Each unit cell structure has three cavities, and there are a number of particle damping groups in the cavity. The particle damping group is composed of a plurality of solid circular particles. The particle damping group is not placed in a stacked form, but a partition is used to separate the particle damping to make the collision between the particle damping more thorough.

[0051] Figures 6(a) to 7A schematic diagram of the mechanical superstructure provided for an example of the present invention is shown in FIG6(c). The mechanical superstructure is a two-dimensional periodic form with five complete periods in both the horizontal and vertical directions. To ensure the symmetry of the boundary connection between the mechanical superstructure 2 and the external cavity 1, as shown in FIG6(c), the mechanical superstructure is further extended by half a periodic structure at the upper and right boundaries of the mechanical superstructure, that is, a matrix damping cavity and a cavity of a non-local connection structure connected thereto are added, so that the boundary forms a symmetrical structure.

[0052] like Figures 8(a) to 13 The unit cell structure of the mechanical superstructure provided in the examples of the present invention is generally composed of a matrix damping structure, a connection damping structure, a non-local connection structure portion, and a rod. The matrix damping structure includes a matrix damping cavity 5, a partition 4, a particle damping group 3, and a baffle 11. The bottom of the matrix damping cavity remains horizontal, and the normal direction of any cavity wall in the matrix damping cavity 5 is 45 degrees to the X direction or the Y direction. One of the cavity walls is hollowed out and provided with a groove structure, so that the matrix baffle 11 can move up and down within the groove structure. The detailed structural diagram of the groove is shown in FIG. Figure 14 As shown; by moving the baffle 11 up and down, the particle damping group can be taken out and installed; a partition is set in the matrix damping cavity, and the partition 4 can be fixed or allowed to move freely. The particle damping group is placed between the partitions. When the partition is fixed, the distance between the partitions is slightly larger than the diameter of the largest solid circular particle in the particle damping group; the number of partition layers and the number of particle damping layers are determined by the particle damping diameter and the depth of the matrix damping cavity. The top of the cavity can be capped or not.

[0053] The connecting damping structure includes a connecting damping cavity 14, a partition 15, a particle damping group 16, and a baffle 12. The bottom of the connecting damping cavity is also horizontal, and the normal direction of any cavity wall in the connecting damping cavity 14 is parallel to the X-direction or the Y-direction. The groove of the connecting damping cavity is configured to be consistent with that of the base damping cavity, and a baffle 12 is vertically and detachably installed in the groove. Each layer of particle damping group 16 is separated by a partition 15. In this embodiment of the present invention, the side length of the connecting damping cavity is slightly smaller than that of the base damping cavity, and the depth of the two cavities is the same.

[0054] The non-local connection structure consists of a non-local cavity 7, a long connecting rod 10, a short connecting rod 17, a baffle 6, a particle damping group 8, and a partition 9. The non-local cavity 7 is connected to the base damping cavity using four short connecting rods 17 to ensure more complete vibration transmission between the two cavities. In this embodiment, the four short connecting rods 17 are respectively arranged at the four corners of the top of the non-local cavity 7. The non-local cavities 7 are connected using long connecting rods 10. The grooves in the non-local cavity 7 are arranged transversely on the two inner walls opposite to each other at the top, and the baffles 6 are detachably installed in the grooves transversely. The partitions 9 inside the non-local cavity 7 are not fixed on the cavity wall, but are placed above the particle damping group 8 and move with the solid circular particles.

[0055] The working principle of the non-local particle damping rotating superstructure wide low-frequency vibration reduction device of the above-mentioned invention embodiment includes:

[0056] The mechanical superstructure in this embodiment has an elastic wave bandgap characteristic as one of its important characteristics; an elastic wave bandgap refers to the presence of a forbidden state or bandgap within the frequency range of elastic waves in the mechanical superstructure, i.e., a frequency range in which elastic waves cannot propagate. The formation of an elastic wave bandgap is based on the periodic form and material properties of the mechanical superstructure, as well as the wave nature of elastic waves. Mechanical superstructures are typically composed of periodically arranged microstructures, the periodicity of which leads to Bragg scattering of elastic waves in the structure. In crystallography, this scattering leads to the formation of elastic wave energy bands, in which there is a forbidden region of elastic wave energy, i.e., an elastic wave bandgap.

[0057] In each unit cell structure, the matrix damping cavity and the connecting damping cavity are connected by a rotating connecting rod to form a rotating structural type. When this rotating unit presents a specific periodicity and symmetry in the periodic structure, it can achieve vibration control within a specific frequency range; this rotating structural type will present a non-overlapping mirror relationship of spatial symmetry, so that the structure has special mechanical properties; by changing the design of the rotating structural type between the matrix damping cavity and the connecting damping cavity, the direction and speed of the wave field can be controlled, and the vibration or elastic wave can be controlled to achieve the effect of vibration isolation.

[0058] The unit cell structure exhibits particle damping. When subjected to external forces, friction and collisions occur between particles. When vibrations act on the particle damping system, these friction and collisions dissipate vibration energy. Specifically, the particles are subject to external forces during vibration, resulting in relative displacement and velocity between particles, which in turn generates friction and collision forces. These forces convert vibration energy into heat, gradually reducing the amplitude of the vibration system. The effectiveness of particle damping and vibration isolation is generally related to the vibration frequency. In low-frequency vibrations, friction between particles plays a primary role, while in high-frequency vibrations, particle collisions become the primary means of energy dissipation.

[0059] Figure 15 The simulation calculation results of the acceleration response of the vibration isolation device provided in the embodiment of the present invention in the frequency range of 0-300 Hz are shown. The boundary condition is that acceleration excitation is applied to one end of the mechanical superstructure and acceleration signal monitoring is performed at the other end. The solid line in the figure is the acceleration response diagram of the response end when there is no particle damping, and the dotted line is the acceleration response diagram of the response end when there is particle damping. It can be clearly seen that at the four frequencies of 60 Hz, 120 Hz, 175 Hz, and 250 Hz, the acceleration frequency response without particle damping is much greater than the calculated result with particle damping, and in other frequency bands, the acceleration response with particle damping is also slightly lower than the calculated result without particle damping. The simulation calculation results show that the vibration isolator with particle damping has better vibration isolation and vibration reduction effects.

[0060] Figure 16 The simulation calculation results of the velocity response of the vibration isolation device provided in the embodiment of the present invention in the frequency range of 0-300 Hz are calculated. The boundary condition is that acceleration excitation is applied to one end of the mechanical superstructure and velocity signal monitoring is performed on the other end. The solid line in the figure is the velocity response diagram of the response end when there is no particle damping, and the dotted line is the velocity response diagram of the response end when there is particle damping. It can be clearly seen that at the four frequencies of 60 Hz, 120 Hz, 175 Hz, and 250 Hz, the velocity frequency response without particle damping is much greater than the calculated result with particle damping, and in other frequency bands, the velocity response with particle damping is also slightly lower than the calculated result without particle damping. The simulation calculation results show that the vibration isolator with particle damping has better vibration isolation and vibration reduction effects.

[0061] Figure 17 The simulation calculation results of the deformation response of the vibration isolation device provided in the embodiment of the present invention in the frequency range of 0-300 Hz are shown. The boundary condition is that acceleration excitation is applied to one end of the mechanical superstructure and deformation signal monitoring is performed on the other end. The solid line in the figure is the deformation response diagram of the response end when there is no particle damping, and the dotted line is the deformation response diagram of the response end when there is particle damping. It can be clearly seen that at the four frequencies of 60 Hz, 120 Hz, 175 Hz, and 250 Hz, the deformation frequency response without particle damping is much greater than the calculated result with particle damping, and in other frequency bands, the deformation response with particle damping is also slightly lower than the calculated result without particle damping. The simulation calculation results show that the vibration isolator with particle damping has better vibration isolation and vibration reduction effects.

[0062] Figure 18The stress response simulation calculation results of the vibration isolation device provided in the embodiment of the present invention in the frequency range of 0-300 Hz are shown. The boundary condition is that acceleration excitation is applied to one end of the mechanical superstructure and stress signal monitoring is performed on the other end. The solid line in the figure is the stress response diagram of the response end when there is no particle damping, and the dotted line is the stress response diagram of the corresponding end when there is particle damping. It can be clearly seen that at the five frequencies of 60 Hz, 120 Hz, 175 Hz, 200 Hz, and 250 Hz, the stress frequency response without particle damping is much greater than the calculated result with particle damping, and in other frequency bands, the stress response with particle damping is also slightly lower than the calculated result without particle damping. The simulation calculation results show that the vibration isolator with particle damping has better vibration isolation and vibration reduction effects.

[0063] Figure 19 The simulation calculation results of the acceleration response of the vibration isolation device provided in the embodiment of the present invention within the frequency range of 0-300 Hz are shown. The boundary condition is that acceleration excitation is applied to one end of the mechanical superstructure and acceleration signal monitoring is performed at the other end. The solid line in the figure is the acceleration response diagram of the response end when there is one layer of particle damping, and the dotted line is the acceleration response diagram of the response end when there are three layers of particle damping. It can be clearly seen that at the three frequencies of 60 Hz, 130 Hz, and 175 Hz, the acceleration frequency response of the device with one layer of particle damping is greater than the calculated result of the device with three layers of particle damping. In addition, in other frequency bands, the acceleration response of the device with three layers of particle damping is also slightly lower than the calculated result of the device with one layer of particle damping. The simulation calculation results show that increasing the number of layers of particle damping can enhance the vibration isolation and vibration reduction effect of the vibration isolator.

[0064] Figure 20 The simulation calculation results of the velocity response of the vibration isolation device provided in the embodiment of the present invention within the frequency range of 0-300 Hz are calculated. The boundary condition is that acceleration excitation is applied to one end of the mechanical superstructure and velocity signal monitoring is performed at the other end. The solid line in the figure is the velocity response diagram of the response end when there is one layer of particle damping, and the dotted line is the velocity response diagram of the response end when there are three layers of particle damping. It can be clearly seen that at the three frequencies of 60 Hz, 130 Hz, and 175 Hz, the velocity frequency response of the device with one layer of particle damping is greater than the calculated result of the device with three layers of particle damping. In other frequency bands, the velocity response of the device with three layers of particle damping is also slightly lower than the calculated result of the device with one layer of particle damping. The simulation calculation results show that increasing the number of layers of particle damping can enhance the vibration isolation and vibration reduction effect of the vibration isolator.

[0065] Figure 21The simulation calculation results of the deformation response of the vibration isolation device provided in the embodiment of the present invention in the frequency range of 0-300 Hz are calculated. The boundary condition is that acceleration excitation is applied to one end of the mechanical superstructure and deformation signal monitoring is performed at the other end. The solid line in the figure is the deformation response diagram of the response end when there is one layer of particle damping, and the dotted line is the deformation response diagram of the response end when there are three layers of particle damping. It can be clearly seen that at the three frequencies of 60 Hz, 130 Hz, and 175 Hz, the deformation frequency response of the device with one layer of particle damping is greater than the calculated result of the device with three layers of particle damping. In other frequency bands, the deformation response of the device with three layers of particle damping is also slightly lower than the calculated result of the device with one layer of particle damping. The simulation calculation results show that increasing the number of layers of particle damping can enhance the vibration isolation and vibration reduction effect of the vibration isolator.

[0066] Figure 22 The stress response simulation calculation results of the vibration isolation device provided in the embodiment of the present invention in the frequency range of 0-300 Hz are calculated. The boundary condition is that acceleration excitation is applied to one end of the mechanical superstructure and stress signal monitoring is performed on the other end. The solid line in the figure is the stress response diagram of the response end when there is one layer of particle damping, and the dotted line is the stress response diagram of the response end when there are three layers of particle damping. It can be clearly seen that at the three frequencies of 60 Hz, 130 Hz, and 180 Hz, the stress frequency response of the one layer of particle damping is greater than the calculated result of the three layers of particle damping, and in other frequency bands, the stress response of the three layers of particle damping is also slightly lower than the calculated result of the one layer of particle damping. The simulation calculation results show that increasing the number of layers of particle damping can enhance the vibration isolation and vibration reduction effect of the vibration isolator.

[0067] In summary, compared with the previous periodic vibration isolation devices, the device of the embodiment of the present invention designs a wide low-frequency superstructure vibration isolation and vibration reduction device in which a non-local connection structure, a matrix damping structure, a connection damping structure and a particle damping group work together. On the basis of the periodic mechanical superstructure, a non-local connection structure and a rotating structure type composed of a matrix damping structure and a connection damping structure are integrated. At the same time, the space of the cavity structure is fully utilized to design a multi-layer particle damping group structure, which strengthens the collision and friction between the particle damping groups, so that the vibration of the structure within a wide frequency range is widely suppressed. The device can be used not only for vibration isolation and vibration reduction in a two-dimensional specific frequency band, but also for vibration isolation and vibration reduction within a wide frequency range. Based on this working condition, a nonlinear vibration isolation and noise reduction device is provided that is easy to manufacture, has significant effects, is simple to operate, has no electromagnetic infection, and has a wide frequency range vibration isolation effect.

[0068] The device in this embodiment is a two-dimensional structure, with only 25 periods and boundary structures designed in the two-dimensional plane to simulate vibration isolation effects over an unlimited range. Furthermore, the structural connecting rods can have different cross-sectional shapes, and the cavity structure can have different structural shapes, such as circular or triangular. Furthermore, the particles that make up the particle damping group can be spherical or cubic.

[0069] The device and system embodiments described above are merely illustrative. The units described as separate components may or may not be physically separate, and the components shown as units may or may not be physical units, i.e., they may be located in one location or distributed across multiple network units. Some or all of these modules may be selected based on actual needs to achieve the objectives of the present embodiments. Persons of ordinary skill in the art will be able to understand and implement the present embodiments without inventive effort.

[0070] It will be understood by those skilled in the art that, unless expressly stated otherwise, the singular forms "a", "an", "said" and "the" used herein may also include the plural forms. It should be further understood that the term "comprising" used in the description of the present invention refers to the presence of the features, integers, steps, operations, elements and / or components, but does not exclude the presence or addition of one or more other features, integers, steps, operations, elements, components and / or groups thereof. It should be understood that when we refer to an element as being "connected" or "coupled" to another element, it may be directly connected or coupled to the other element, or there may be intermediate elements. In addition, "connected" or "coupled" as used herein may include wireless connections or couplings. The term "and / or" used herein includes any unit and all combinations of one or more associated listed items.

Claims

1. A non-local particle damping rotating superstructure wide low-frequency vibration reduction device, characterized in that: It includes a mechanical superstructure and an external cavity; the mechanical superstructure is a planar periodic structure formed by a plurality of unit cell structures arranged periodically in an XY plane, and the unit cell structure is composed of a non-local connection structure, a matrix damping structure, a connection damping structure and a rod; The matrix damping structure is composed of a particle damping group, a baffle, a partition and a matrix damping cavity; the connection damping structure is composed of a particle damping group, a baffle, a partition and a connection damping cavity; the non-local connection structure is composed of a particle damping group, a partition, a baffle and a non-local cavity; the matrix damping cavity, the connection damping cavity and the non-local cavity are each provided with several layers of particle damping groups, with partitions provided between each layer of particle damping groups, and the matrix damping cavity, the connection damping cavity and the non-local cavity are each detachably provided with baffles; The outer cavity and the mechanical superstructure are connected to each other via a rotating connecting rod, and the bottom of the non-local connection structure in the mechanical superstructure is in a suspended state; The mechanical superstructure is divided into two layers, the upper layer consisting of a matrix damping structure and a connection damping structure, and the lower layer consisting of a non-local connection structure. The non-local connection structures of the lower layer are interconnected by long connecting rods, and the top of the non-local connection structure in each unit cell structure is connected to the matrix damping structure by a short connecting rod.

2. The non-local particle damping rotating superstructure wide low-frequency vibration reduction device according to claim 1 is characterized in that: The matrix damping structure and the connection damping structure in the mechanical superstructure are arranged alternately, showing periodic characteristics on the plane.

3. The non-local particle damping rotating superstructure wide low-frequency vibration reduction device according to claim 1 is characterized in that: The matrix damping cavity is a rectangular cavity structure with an open top. The cross section of the matrix damping cavity is a square structure with a side length of 60 mm. The depth of the matrix damping cavity is 45 mm. The thickness of the side wall and bottom surface of the matrix damping cavity are both 5 mm. The normal direction of the side wall of the matrix damping cavity is 45 degrees to the X direction or Y direction.

4. The non-local particle damping rotating superstructure wide low-frequency vibration reduction device according to claim 1, characterized in that: The connecting damping cavity is a rectangular cavity structure with an open top. The cross-section of the connecting damping cavity is a square structure with a side length of 40 mm. The depth of the connecting damping cavity is 45 mm. The thickness of the side wall and bottom surface of the connecting damping cavity are both 5 mm. The normal direction of the side wall of the connecting damping cavity is parallel to the X direction or the Y direction.

5. The non-local particle damping rotating superstructure wide low-frequency vibration reduction device according to claim 1, characterized in that: Normal directions of the adjacent sidewall surfaces between two adjacent base damping cavities and the connecting damping cavity form an angle of 45 degrees with each other, and the base damping cavity and the connecting damping cavity are connected to each other by a rotating connecting rod.

6. The non-local particle damping rotating superstructure wide low-frequency vibration reduction device according to claim 1, characterized in that: The particle damping group is composed of several solid circular particles, and the distance between the partitions is greater than the maximum diameter of the solid circular particles. The partitions connecting the damping cavity and the matrix damping cavity are fixed on the side wall of the cavity or freely placed on the surface of the particle damping group. When the partitions are fixed, the solid circular particles can be installed and removed by disassembling the baffles. The partitions in non-local cavities are not fixed. The diameter of the solid circular particles is 9 mm, and the layer height between each layer of particle damping group is 10 mm; Vertical grooves are provided on the two opposite inner walls of the base damping cavity and the connecting damping cavity, and the baffle is detachably connected to the base damping cavity and the connecting damping cavity through the vertical grooves; horizontal grooves are provided on the two opposite inner walls of the non-local cavity, and the baffle is detachably connected to the non-local cavity through the horizontal grooves.

7. The non-local particle damping rotating superstructure wide low-frequency vibration reduction device according to claim 1, characterized in that: The non-local cavity is a cubic cavity structure, the cross-section of the non-local cavity is a square structure with a side length of 40 mm, and the depth of the non-local cavity is 40 mm; a baffle is detachably provided on the top of the non-local cavity, and the side wall and bottom thickness of the non-local cavity are both 5 mm.

8. The non-local particle damping rotating superstructure wide low-frequency vibration reduction device according to claim 1, characterized in that: The particle damping group in the matrix damping cavity and the connection damping cavity occupies 1 / 5 to 1 / 2 of the cavity volume; the particle damping group in the non-local cavity occupies 1 / 3 to 2 / 3 of the non-local cavity volume.

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