Metamaterial vibration reduction platform and manufacturing method thereof

Abstract

The invention belongs to the technical field of vibration reduction, and relates to a metamaterial vibration reduction platform and a manufacturing method thereof. The manufacturing method comprises the steps that S1, the performance requirement of a vibration isolation component is determined according to the application working condition requirement of the metamaterial vibration reduction platform; s2, based on performance requirements, the vibration isolation component is designed to be of a core sandwich structure, a three-dimensional model of the vibration isolation component is constructed, and a core layer of the core sandwich structure in the three-dimensional model is generated by a minimum curved surface controlled by an implicit function and a multi-point array field; s3, based on the three-dimensional model, a metal framework in the shape of a multi-minimum-curved-surface dot matrix metamaterial is obtained through an additive manufacturing technology, and then pores of the metal framework are filled with flexible materials to form a vibration isolation component in the form of a multiphase material; and S4, the vibration isolation component is supported on the platform support through a buffer, and the metamaterial vibration reduction platform is manufactured. The metamaterial vibration reduction platform prepared by the invention has good vibration suppression performance.

Description

Technical Field

[0001] This application belongs to the field of vibration reduction technology and relates to a metamaterial vibration reduction platform and its manufacturing method. Background Technology

[0002] A vibration damping platform is a load-bearing and vibration-damping device used to block or weaken the transmission of vibrations and protect target objects (such as precision equipment) from vibration interference. Its core function is to absorb, dissipate, or isolate the vibration energy generated by vibration sources (such as rotating parts or fluid pulsations) through a specific structure, so as to avoid vibration causing performance degradation, fatigue damage, or functional failure of the target object on the platform.

[0003] With the development of experimental techniques, especially for various spaceborne payloads (i.e., equipment carried by satellites), such as astronomical telescopes, satellite antennas, space interferometers, and laser communication devices, higher requirements have been placed on the accuracy and stability of payload pointing. In particular, isolating spaceborne payloads from frequent environmental vibrations is crucial to ensuring sufficient performance. However, in many cases, vibration isolation of these spaceborne payloads is achieved by using expensive and unreliable active vibration isolation platforms. Furthermore, these active vibration isolation platforms often lack excellent vibration suppression performance in the broadband low-frequency domain and time domain, resulting in poor vibration suppression capabilities. Summary of the Invention

[0004] In response to the deficiencies or improvement needs of existing technologies, this application provides a metamaterial vibration damping platform and its manufacturing method, aiming to solve the problem of poor vibration suppression performance of vibration isolation platforms.

[0005] This application provides a method for manufacturing a metamaterial vibration damping platform, comprising the following steps: S1. Determine the performance requirements of the vibration isolation components based on the application conditions of the metamaterial vibration reduction platform; S2. Based on performance requirements, the vibration isolation component is designed as a core sandwich structure, and a three-dimensional model of the vibration isolation component is constructed. In this three-dimensional model, the core layer of the core sandwich structure is generated by a minimal surface controlled by an implicit function and a multi-point array field. S3. Based on the three-dimensional model, a metal skeleton in the form of a multi-minimal curved surface lattice metamaterial is manufactured using additive manufacturing technology. Then, flexible material is filled into the pores of the metal skeleton to form a vibration isolation component in the form of a multiphase material. S4. Vibration isolation components are supported on the platform bracket by a buffer to obtain a metamaterial vibration reduction platform.

[0006] As a further preferred embodiment, in step S2, constructing a three-dimensional model of the vibration isolation component based on the performance requirements includes: S21. A lattice structure is adopted as the basic configuration of the vibration isolation components; S22. Using a three-period minimal surface design for the unit cell of the lattice structure, construct the dynamic performance function expression between the mechanical and vibrational properties of the three-period minimal surface structure; S23. Based on the dynamic performance function expression and performance requirements, combine the periodic implicit function surface generating formula to construct a lattice structure model that obtains a three-period minimum surface; S24. Using the lattice structure model as a framework, a digital model of filling its pores with flexible material is obtained to obtain a multiphase material model containing a lattice framework phase and a flexible filling phase. S25. Add panel models to the upper and lower ends of the composite material model to form a three-dimensional design model of the vibration isolation component.

[0007] As a further preferred embodiment, the periodic implicit function surface generator includes the Gyroid surface generator, the IWP surface generator, and the Primitive surface generator.

[0008] As a further preferred embodiment, in step S23, when the weight-bearing requirement has a higher priority than the vibration reduction requirement in the performance requirements, the dynamic performance function expression is combined with the Gyroid surface generation formula, which includes: ; in, Represents a time variable. Indicates the size of the unit cell. , and Represents spatial coordinates.

[0009] As a further preferred embodiment, in step S23, when the priority of the load-bearing requirement is lower than that of the vibration reduction requirement in the performance requirements, the dynamic performance function expression is combined with the IWP surface generation formula. The IWP surface structure control equation generation formula includes: ; in, Represents a time variable. , and Represents spatial coordinates, This represents the side length of a single cube cell.

[0010] As a further preferred embodiment, in step S23, when the priority of load-bearing requirements and vibration reduction requirements are the same in the performance requirements, the dynamic performance function expression is combined with the Primitive surface generation formula. The Primitive surface structure control equation generation formula includes: ; in, Represents a time variable. Indicates the size of the unit cell. , and Represents spatial coordinates.

[0011] As a further preferred option, in step S23, after constructing the lattice structure model with a three-period minimum surface, the lattice structure model is verified and iterated based on the equivalent force and vibration relationship model function equations, so that the lattice structure corresponding to the lattice structure model meets the requirements.

[0012] As a further preferred embodiment, in step S4, when the vibration isolation component is supported on the platform support by the buffer, the platform, connecting plate, bottom surface and side plate are first installed on the vibration isolation component to form the platform body, and then the platform body is supported on the platform support by the buffer.

[0013] The second aspect of this application provides a metamaterial vibration damping platform using the following technical solution: A metamaterial vibration damping platform, manufactured using the method described in the first aspect, includes vibration isolation components, a buffer, and a platform support, wherein: The vibration isolation components are supported on the platform support by several buffers; The vibration isolation component is a core sandwich structure, including a core layer and two panels. The core layer includes a metal skeleton in the shape of a multi-point array structure with extremely small curved surfaces. The pores of the metal skeleton are filled with flexible material. The two panels are respectively disposed at the upper and lower ends of the core layer.

[0014] As a further preferred embodiment, the metamaterial vibration damping platform also includes an upper platform, a connecting plate, a lower bottom surface, and side plates. The upper platform and the connecting plate are fixed to the top of the vibration isolation component, and the connecting plate is located between the upper platform and the vibration isolation component. The side plates are located on the outer periphery of the vibration isolation component, and the lower bottom plate is fixed to the bottom of the vibration isolation component.

[0015] In summary, compared with the prior art, the technical solutions conceived in this application have the following main technical advantages: 1. This application breaks through the traditional honeycomb sandwich support structure of vibration reduction platforms, abandoning the traditional concept of relying on thin-walled hexagonal unit cells to provide bending stiffness and out-of-plane buckling resistance. Instead, it introduces the local resonance mechanism into the lattice structure through flexible materials, enabling the vibration isolation units in the vibration isolation components to actively utilize the internal resonant microstructure (i.e., flexible materials) to enhance vibration attenuation. Simultaneously, by designing the sandwich structure in the vibration isolation components with a lattice cavity, the structural density can be reduced while ensuring load-bearing performance, achieving a coupling of lightweight and vibration isolation performance. Moreover, the hollow cavity provides topological stiffness. During the design and modeling process, by adjusting the beam thickness, cavity diameter, filling material, and mass distribution of local resonant units in the sandwich structure, the natural frequency of vibration isolation can be reduced, enabling low-frequency vibration isolation while maintaining platform stability and load-bearing capacity.

[0016] 2. In this design, the vibration isolation components can be highly customized as needed. Its core structure employs a multi-scale collaborative system of lightweight lattice-multiphase material-core sandwich, with the overall geometry precisely controlled by implicit function equations, enabling automatic generation and topological transformation within a virtually infinite parameter space. Specifically, in this design, through multi-level decomposition and nested configuration recombination, the system can generate metamaterial units with different cell topologies, spatial densities, and functional gradients. This method expands the structural design freedom, allowing lattice-related parameters to be flexibly adjusted in a continuous design space. Furthermore, controlling the implicit function parameters can rapidly generate various lattice sandwich structures and customize optimization according to engineering constraints. Compared to traditional regular cell parametric modeling, this method offers a wider design domain, finer microstructure controllability, and more flexible material function gradient capabilities, meeting the diverse needs of vibration isolation systems across various fields for vibration isolation performance, structural strength, and lightweighting. Attached Figure Description

[0017] Figure 1 This is a flowchart illustrating a method for manufacturing a metamaterial vibration damping platform according to an embodiment of this application; Figure 2 These are schematic diagrams of the unit cell structures corresponding to the Gyroid surface, IWP surface, and Primitive surface provided in the embodiments of this application. Figure 3 This is a schematic diagram of the vibration isolation component based on the IWP surface provided in the embodiments of this application; Figure 4 This is a schematic diagram of the structure of the vibration isolation component based on the Gyroid surface provided in the embodiments of this application; Figure 5 This is a flowchart illustrating the fabrication process of the vibration isolation component provided in the embodiments of this application; Figure 6 This is a schematic diagram of the design, processing, and application process of the vibration reduction platform provided in the embodiments of this application; Figure 7This is a structural schematic diagram of a metamaterial vibration damping platform provided in an embodiment of this application; Figure 8 This is an exploded view of the metamaterial vibration damping platform provided in the embodiments of this application; Figure 9 This is a front view of the metamaterial vibration reduction platform provided in the embodiments of this application; Figure 10 This is a partial structural schematic diagram of the metamaterial vibration reduction platform provided in the embodiments of this application; Figure 11 This is a cross-sectional view of the metamaterial vibration reduction platform provided in the embodiments of this application.

[0018] In all the accompanying drawings, the same reference numerals are used to denote the same elements or structures, wherein: 1. Upper platform; 2. Isolation cup; 3. Lower bottom surface; 4. Vibration isolation components; 5. Side plate; 6. Connecting plate; 7. Fastening bolts; 8. Positioning pins; 9. Damping buffer; 10. Platform support. Detailed Implementation

[0019] To make the objectives, technical solutions, and advantages of this application clearer, the following detailed description is provided in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the scope of this application.

[0020] The following is in conjunction with the appendix Figures 1-11 This application will be described in further detail.

[0021] This application discloses a method for manufacturing a metamaterial vibration damping platform. (Refer to...) Figure 1 The manufacturing method of this metamaterial vibration damping platform includes the following steps: S1. Determine the performance requirements of the vibration isolation components based on the application conditions of the metamaterial vibration reduction platform.

[0022] S2. Based on performance requirements, the vibration isolation component is designed as a core sandwich structure, and a three-dimensional model of the vibration isolation component is constructed. In this three-dimensional model, the core layer of the core sandwich structure is generated by a minimal surface controlled by an implicit function and a multi-point array field.

[0023] S3. Based on the three-dimensional model, a metal skeleton in the form of a multi-minimal curved surface lattice metamaterial is manufactured using additive manufacturing technology. Then, flexible material is filled into the pores of the metal skeleton to form a vibration isolation component in the form of a multiphase material.

[0024] S4. Vibration isolation components are supported on the platform bracket by a buffer to obtain a metamaterial vibration reduction platform.

[0025] Furthermore, in step S1, based on the application requirements of the metamaterial vibration reduction platform (such as the application scenarios of installing spectral analysis devices, electron microscopes, CNC machine tools, etc.), the performance requirements of the vibration isolation components are analyzed and determined. These performance requirements include vibration isolation effect requirements and vibration isolation frequency bands.

[0026] Furthermore, in step S2, based on performance requirements, a suitable multiphase material support unit is designed for the vibration isolation component. This multiphase material support unit is preferably formed through a porous multiphase material design and a support unit structure design, and it will serve as the core layer of the vibration isolation component. Then, the remaining parts (such as the panels at the upper and lower ends of the core layer) are designed and installed for the vibration isolation component. Finally, a three-dimensional model is constructed together with the designed multiphase material support unit and the remaining parts.

[0027] At the design level, based on performance requirements, the unit cell topology and multiple nesting methods that should be adopted for the core sandwich structure of the vibration isolation component are first determined. This includes determining the unit cell parameters (unit cell type, unit cell size, unit cell volume fraction) that should be adopted for the lattice structure of the core layer in the core sandwich structure, as well as determining the number of nesting layers of the lattice structure. Then, a preliminary three-dimensional model of the porous structure is generated in the multi-surface software.

[0028] Then, the selected porous structure 3D model is filled with a digital model of flexible material, and FEA (modal analysis + vibration isolation support coupling analysis) simulation is performed in the software. Based on the simulation results, the selected unit cell parameters and multiple nesting methods are optimized again, and a stable porous structure solid model in the vibration isolation component is reconstructed so that the solid model can meet the vibration isolation effect and load-bearing capacity required by the vibration isolation component under the stated working conditions.

[0029] Research has found that honeycomb core materials have high in-plane stiffness. The panels bear the principal bending stiffness, while the honeycomb core bears the vertical shear deformation. This shear deformation exhibits damping and hysteresis, forming a dynamic structure similar to a "spring + damping" system, preventing energy from being effectively transferred from the panels to the other side. Therefore, when designing the core sandwich of vibration isolation components, a honeycomb structure is selected for the core layer, with panels on both sides. The honeycomb structure of the core significantly increases the secondary modulus of the panels during out-of-plane bending, preventing structural resonance of the platform in the low-frequency range. The design concept is to adjust the height and unit size of the honeycomb structure in the core sandwich according to the stiffness requirements of the vibration isolation platform. By adjusting the honeycomb height and unit ratio, the modal distribution and damping characteristics of the core sandwich can be controlled to obtain the desired damping effect. Subsequently, a single honeycomb structure is cut from the complete multiphase material, and the multiphase material is then subjected to a preset wall thickness increase to match the size of the vibration isolation platform, ultimately obtaining a three-dimensional model of the single load-bearing unit in the lightweight lattice-multiphase material-core sandwich structure.

[0030] Next, the individual load-bearing units in the lightweight lattice-multiphase material-core sandwich structure are arrayed to obtain a large-scale three-dimensional model, which is then subjected to detailed processing. This detailed processing includes: adding top and bottom panels to the large-scale three-dimensional model to facilitate the installation and handling of the overall structure; checking for any defects in the connections between the individual load-bearing units; and removing or thickening some individual load-bearing units to match the dimensions of the vibration damping platform. Finally, a complete, adapted three-dimensional design model of the vibration isolation component with the lightweight lattice-multiphase material-core sandwich structure is obtained.

[0031] At the model building level, constructing the 3D model of the vibration isolation components includes: S21. A lattice structure is adopted as the basic configuration of the vibration isolation components; S22. A unit cell of a lattice structure is designed using a three-period minimal surface, and a dynamic performance function expression is constructed to represent the mechanical and vibrational properties of the three-period minimal surface structure. S23. Based on the dynamic performance function expression and performance requirements, combine the periodic implicit function surface generating formula to construct a lattice structure model that obtains a three-period minimum surface; S24. Using the lattice structure model as a framework, a digital model of filling its pores with flexible material is obtained to obtain a multiphase material model containing a lattice framework phase and a flexible filling phase. S25. Add panel models to the upper and lower ends of the composite material model to form a three-dimensional design model of the vibration isolation component.

[0032] Specifically, based on the change in stress distribution from linear stress concentration to uniform annular stress distribution under load in a lattice structure, the gradient design within the lattice structure allows the main load-bearing side (the part with the greatest stress) to simultaneously possess stronger toughness, larger crack propagation space, and lower principal stress. Through simulation analysis of the fatigue performance of the lattice structure and its fatigue-resistant design and manufacturing methods, it is concluded that these advantages combined ultimately improve the fatigue resistance of the lattice structure (making it more resistant to repeated stress and less prone to failure). Therefore, the lattice structure was selected as the skeleton in the vibration isolation component.

[0033] Then, in view of the problem that conventional truss-type lightweight structures are prone to stress concentration and poor service performance due to sharp corners, the three-period minimal surface (TPMS) design lattice structure is preferred to ensure that the skeleton in the vibration isolation component (i.e. the lattice structure adopted) meets the performance requirements (such as meeting the required structural characteristics and related force and vibration performance).

[0034] The equivalent force and vibration relation model function equations required to construct a force and vibration constitutive model based on material and structural inhomogeneities are as follows: ; ; ; in, It is the displacement acceleration of the damping block over time. It is the displacement velocity of the damping block over time. It is the displacement of the damping block over time. c It is the damping coefficient. k It is the elasticity coefficient. A Indicates the vibration coefficient. The equivalent model material strength; , , These are all weighting coefficients, representing the proportion of each component's contribution to the equivalent strength. Specifically, This indicates the proportion of the matrix material's contribution to the equivalent strength. This indicates the proportion of contribution to enhancing the relative equivalent strength. This indicates the proportion of the interface's relative equivalent strength that it contributes. This represents the elastic modulus of the matrix material. This indicates the volume fraction of the matrix material. E sp This represents the elastic modulus of the reinforcing phase (such as particles, fibers, etc.). V sp This indicates the volume fraction of the reinforcing phase. E inter This represents the elastic modulus of the interface phase. V inter This indicates the volume fraction of the interfacial phase. For the vibration parameters in the force-vibration relationship model, The damping coefficient representing the matrix energy, The damping coefficient representing the energy of space. The damping coefficient represents the energy of the interaction. , , It is a constant, representing the weights of these damping terms, specifically... This indicates the proportion of the matrix material's contribution to the equivalent damping. This indicates the proportion of contribution to enhancing the relative equivalent damping. This indicates the proportion of the interface's contribution to the relative equivalent damping. t Represents a time variable. Indicates the real-time frequency.

[0035] This equation, through a hybridization principle, combines the contributions of the matrix material, reinforcing phase, and interface phase, enabling the calculation of the material strength of the equivalent model. Here, the damping block refers to a general indicator of all material forms that consume system energy. It is worth noting that the equivalent force-vibration relationship model function equation is inserted here as an explanation of the TPMS vibration reduction mechanism. The lattice structure design function model presented later requires this logic of the "equivalent force-vibration relationship model function equation" to verify its performance, and then iteratively derive a lattice structure model that meets the requirements.

[0036] Specifically, the construction process of the lattice structure model includes: constructing a dynamic performance function expression (including model vibration parameters) between the mechanical properties (stiffness, strength, fatigue, etc.) and vibration properties (vibration level difference, natural frequency, damping ratio, etc.) of the three-period minimal surface structure (TPMS) according to the working conditions of the vibration reduction platform; establishing a modeling expression relationship between design and process—microscopic and interface and macroscopic characteristics—force and vibration performance, including Gyroid surface generation formula, IWP surface generation formula, and Primitive surface generation formula. In this process, based on the target focus (i.e., the focus in performance requirements), a required generative formula is selected to construct the lattice structure model (a force-vibration coupled constitutive model based on material and structural inhomogeneity), as detailed below: In performance requirements, when the priority of load-bearing capacity is higher than that of vibration reduction, the dynamic performance function expression is combined with the Gyroid surface generator formula. The Gyroid surface generator formula includes: ; in, This function represents a time variable and changes with time. It changes with the changes. Indicates the size of the unit cell. , and Represents spatial coordinates.

[0037] In performance requirements, when the priority of load-bearing capacity requirements is lower than that of vibration reduction requirements, the dynamic performance function expression is combined with the IWP surface generation formula, which includes: ; in, Represents a time variable. , and Represents spatial coordinates, This represents the side length of a single cube cell.

[0038] In performance requirements, when the priority of load-bearing capacity requirements is the same as that of vibration reduction requirements, the dynamic performance function expression is combined with the Primitive surface generation formula. The Primitive surface generation formula includes: ; in, Represents a time variable. Indicates the size of the unit cell. , and Represents spatial coordinates.

[0039] For ease of understanding, Figure 2 The diagram shows the corresponding unit cell structure, including (a) a cross-sectional view of the rod-shaped Gyroid surface structure, (b) a cross-sectional view of the sheet-shaped Gyroid surface structure, (c) a three-dimensional view of the rod-shaped Gyroid surface structure, (d) a three-dimensional view of the sheet-shaped Gyroid surface structure, (e) a cross-sectional view of the IWP surface structure, (f) a cross-sectional view of the Primitive surface structure, (g) a three-dimensional view of the IWP surface structure, and (h) a three-dimensional view of the Primitive surface structure. Figure 3 This diagram illustrates the structure of a vibration isolation component with a unit cell structure built using an IWP surface. Figure 4 A structural schematic diagram of a vibration isolation component with a unit cell structure constructed using a Gyroid surface is shown.

[0040] When using a lattice structure model as a framework and filling the pores of the framework with flexible material to create a digital model, resulting in a multiphase material model containing both a lattice framework phase and a flexible filling phase, the displacement transfer function is utilized. T The ratio of platform displacement to base displacement is a key quantity for evaluating vibration isolation effectiveness, and its specific expression is as follows: ; in, It is a dimensionless frequency ratio. ζ This indicates the damping ratio.

[0041] when r 1 (i.e., the external excitation frequency is much higher than the system's natural frequency) and the damping is small, the transmission approximately follows 1 and r 2 The natural frequency decreases, therefore setting it lower can achieve significant vibration isolation in frequency bands above the natural frequency. Therefore, adjusting the natural frequency and damping ratio is the core of the model design.

[0042] Research has found that honeycomb core materials have high in-plane stiffness. The panels bear the principal bending stiffness, while the honeycomb core bears the vertical shear deformation. This shear deformation exhibits damping and hysteresis, forming a dynamic structure similar to a "spring + damping" system, preventing energy from being effectively transferred from the panels to the other side. Therefore, this application employs a honeycomb structure design for the obtained multiphase material. The specific quantitative formula for the vibration reduction effect of the designed lightweight lattice-multiphase material-core sandwich is as follows: ; in, T r The transmissibility of vibration, ζ Indicates the damping ratio. ω 0 represents the natural frequency. ω This represents the real-time frequency (which is a function that represents the frequency and time variation).

[0043] It should be noted that in the design scheme of this application, the vibration isolation component is a lightweight lattice-multiphase material-core sandwich structure. That is, in terms of overall structural morphology, the vibration isolation component has a core sandwich structure, which includes two oppositely arranged panels and a core layer located between the two panels; in terms of material properties, the vibration isolation component belongs to a multiphase material; wherein, the core layer includes a porous metal skeleton with a lattice topology, and the metal skeleton is filled with a flexible material.

[0044] Furthermore, such as Figure 5 As shown, in step S3, the designed 3D model is exported as an STL file and sliced ​​and imported into a laser powder bed melting device. Simultaneously, appropriate operating parameters are selected, and LPBF forming is performed under inert gas protection to prepare a metal skeleton, which is a multi-minimal surface lattice metamaterial.

[0045] In some specific embodiments, 316L stainless steel alloy is selected as the forming material for the metal skeleton. Selective laser sintering (SLS) 3D printing technology is used to manufacture the designed lattice structure using a liquid-phase infiltration method with low-melting-point light metals. Under the protection of an argon inert gas atmosphere, the lattice structure in the vibration isolation component is laser-printed using a laser powder bed melting device. The parameters set in the laser powder bed melting device include: laser power of 125W, scanning speed of 600mm / s, layer thickness of 30µm, scanning spacing of 100µm, and spot diameter of 50µm; forming is performed under the protection of an argon inert gas atmosphere.

[0046] After printing, residual powder inside the metal skeleton is cleaned, and the skeleton is then wire-cut to obtain a metal skeleton without flexible material filling. Post-processing is then performed, including: removing the metal skeleton after processing, and then performing in-situ annealing and sandblasting to relieve thermal stress and provide surface treatment, respectively. Finally, flexible material is filled into the pores of the treated metal skeleton to form vibration-damping components.

[0047] It is important to note that after printing, the laser and other options of the printing equipment should be turned off by clicking the button, the pressure relief valve of the argon cylinder should be closed, and the exhaust button should be opened to remove the argon gas from the chamber before removing the metal skeleton from the printing chamber.

[0048] Because silicone exhibits a significant frequency dependence, and the periodic structure of TPMS can generate a low-frequency bandgap, the combination of the two can simultaneously achieve: shielding of vibrations at specific frequencies and dissipation of residual amplitude. Therefore, silicone is preferred as the flexible material to be filled. During filling, an acrylic sheet is preferably used to make a mold, and the silicone material (generally silicone with a hardness of 25) is filled into the pores of the lattice-structured metal skeleton. After filling, the silicone will gradually solidify under ultraviolet light, forming a composite material tightly bonded to the metal skeleton. After curing, demolding yields a complete lightweight lattice-multiphase material-core sandwich structure.

[0049] Then, the obtained lightweight lattice-multiphase material-core sandwich structure undergoes post-processing to remove excess silicone impurities. A thin viscoelastic layer is then added to the bottom panel of the lightweight lattice-multiphase material-core sandwich structure as a method of fixing the vibration isolation component to the vibration damping platform. The thin viscoelastic layer converts the strain energy generated by panel bending into viscoelastic energy dissipation, which can improve damping efficiency. Butyl rubber is the most widely used material and has excellent high- to mid-frequency damping properties; therefore, butyl rubber is used as the thin viscoelastic layer added to the vibration isolation component.

[0050] Furthermore, in step S4, the vibration isolation component is supported on the platform support by a buffer, thus obtaining the metamaterial vibration damping platform. In some embodiments, the metamaterial vibration damping platform also includes other supporting components to improve its practical performance. That is, in step S4, when supporting the vibration isolation component on the platform support by a buffer, a platform, a connecting plate, a bottom surface, and a side plate are first installed on the vibration isolation component to form a platform body, and then the platform body is supported on the platform support by a buffer. For ease of understanding, Figure 6 A fabrication flowchart of a metamaterial vibration damping platform is shown.

[0051] Furthermore, such as Figures 7-11As shown, the components that need to be assembled in the vibration damping platform include the upper platform 1, isolation cup 2, lower bottom surface 3, vibration isolation component 4, side plate 5, connecting plate 6, fastening bolt 7, positioning pin 8, damping buffer 9, and platform support 10.

[0052] The upper platform 1, as the direct load-bearing object, needs to ensure high rigidity, high structural modality, and appropriate damping to avoid local bending. Preferably, the upper platform 1 is a rigid thin panel MHS (metal honeycomb sandwich). Preferably, the damper is a bidirectional damping damper 9, and four bidirectional damping dampers 9 are used to connect the vibration damping platform and the platform support 10 for further buffering and vibration reduction. Preferably, four holes are provided on the lower bottom surface 3, and the connection between the vibration isolation component 4 and the lower bottom surface 3 is fixed by fastening bolts 7, and the connection between the vibration isolation component 4 and the upper platform 1 is fixed by fastening bolts 7.

[0053] In some embodiments, the vibration isolation component 4 is an integral sandwich honeycomb structure, connected to the lower platform using a welding process (not adhesive bonding). This design ensures that the assembled component is free from loosening, cracking, or detachment. The upper platform 1 is made of 400 series ferromagnetic stainless steel, which has good corrosion resistance. M6 threaded holes are evenly distributed on the platform at a 25mm × 25mm spacing for subsequent installation of the vibration isolation component 4 and the adjustment component (connecting plate). To ensure flatness between the platform tops, a connecting plate 6 is provided. The connecting plate 6 is a set of precision-ground matching steel materials, aligned with the side plates 5 using locating pins 8. Isolation cups 2 are also evenly distributed within the connecting plate at a 25mm × 25mm spacing. The isolation cups 2 are bowl-shaped structures that collect dust that seeps into the platform through the threaded holes, protecting the inner core of the vibration isolation component 4 from contamination.

[0054] In some embodiments, the platform support 10 adopts an integrally welded four-support structure (six supports for 3 meters and above). Buffers are introduced above the support legs of the platform support 10, and damping vibration isolation pads are used below the support legs. This design gives the platform support 10 excellent vibration isolation performance, with a natural frequency designed between 5Hz and 20Hz, making it suitable for use in environments with high vibration isolation requirements.

[0055] In some embodiments, the assembly steps of the metamaterial vibration isolation platform include: (1) Fix the platform bracket 10 on the assembly station or the ground, ensure that the mounting surface of the platform bracket 10 is flat and that the positioning holes are consistent with the arrangement of the buffers. Install 4 buffers on the bracket (using anti-loosening washers and thread locking agent), and align the output direction of the buffers with the future installation position of the vibration isolation component 4 according to the design requirements.

[0056] (2) Align the side of the vibration isolation component 4 with the thin viscoelastic layer on the mounting hole on the bottom surface 3, ensuring that the viscoelastic layer faces the upper surface 1 (i.e., the viscoelastic layer is located on the upper interface, which is beneficial for bonding and buffering effect), and gently place it in place. First, insert the fastening bolts 7 from the bottom through the screw holes on the bottom surface 3, and add washers to fix it; first, hand-tighten until the component has initial contact with the bottom surface 3 but is not completely tightened. Use the positioning pins 8 to calibrate the vibration isolation component 4 in terms of level and angle, ensuring that the hole positions are coaxial and the surface contact is uniform.

[0057] (3) Place the connecting plate (with the isolation cup 2 on it) on the upper surface of the vibration isolation component 4, ensuring that the isolation cup 2 corresponds to the reserved boss or positioning hole of the vibration isolation component 4. Insert the positioning pin 8 to precisely align the connecting plate 6 and the vibration isolation component 4. The tolerance of the positioning pin 8 should ensure the accuracy of repeated assembly. At the same time, check whether the edge of the previously installed viscoelastic layer is intact and free from exposed contamination, and confirm that the mating surfaces of the isolation cup 2 and the connecting plate 6 are flat.

[0058] (4) Place the upper platform 1 (rigid thin panel MHS) on the connecting plate 6, ensuring that its bearing surface faces upward and is aligned with the connecting plate 6. Install the fastening bolts 7 in the design sequence, connecting the upper platform 1, the connecting plate 6, and the vibration isolation component 4 through the screw holes; first, use hand force to tighten all bolts in a crisscross pattern to ensure uniform contact between the platform and the connecting plate 6. Use a torque wrench to tighten in stages according to the predetermined torque value. Use a gradual increase in force (e.g., a three-stage tightening method of 30%, 60%, and 100%) to avoid local compression deformation.

[0059] (5) Connect the entire platform to the pre-installed buffer on the platform support 10 (or connect the upper end of the buffer to the corresponding connection points of the connecting plate 6 and the lower bottom surface 3, depending on the design connection scheme). Fix the buffer connector and complete the torque locking as required to ensure that the buffer can provide the expected bidirectional damping behavior in both directions (axial and lateral). Check and adjust the geometric verticality, horizontality and four-corner load distribution of the entire platform. If necessary, achieve platform level by preloading the buffer or adjusting the shims.

[0060] (6) After all tightening is completed, check the torque of all bolts, the positioning accuracy of locating pin 8, the curing status of viscoelastic filler material, and the sealing performance of the joints. Perform static load distribution test, measure the deflection of the upper platform 1 under the specified maximum load, and check whether it meets the design stiffness and deformation limits. Perform preliminary dynamic verification: small amplitude frequency sweep test or hammer impact test, record the acceleration response and FRF of the platform and base, and confirm that the system's natural frequency is consistent with the design target; if the deviation is large, return to steps 2-4 to check the local pre-tightening or filling uniformity. Finally, perform a complete functional acceptance test.

[0061] Under the design of this application, this application has at least the following significant effects: 1. This application uses software modeling to establish a three-dimensional model of the vibration isolation component. Compared with existing vibration isolation components, the vibration isolation component of this application presents a superlattice sandwich structure, which can perform better in broadband vibration attenuation.

[0062] 2. In the design scheme of this application, the vibration isolation component can be highly customized according to different application scenarios. Its core structure adopts a multi-scale collaborative system of lightweight lattice-multiphase material-core sandwich, and the overall geometry is precisely controlled by a set of continuously differentiable implicit function equations, enabling the structure to achieve automatic generation and topological transformation in an almost infinite parameter space. By performing multilevel decomposition and nested topology construction on the implicit field function, the system can generate metamaterial units with different cell topologies, spatial densities, and functional gradients. This method significantly expands the degree of freedom in structural design, allowing the unit cell type, volume fraction, wall thickness distribution, and microstructure arrangement of the lattice to be flexibly adjusted in a continuous design space. Therefore, by controlling the implicit function parameters, various lattice sandwich structures, from dense and load-bearing to high-damping, can be quickly generated, and can be customized and optimized according to engineering constraints such as target frequency range, damping requirements, load paths, and maximum allowable mass. Compared with the parametric modeling of traditional regular cells, this method can obtain a wider design domain, more refined microstructure controllability, and more flexible material function gradient capability, thereby meeting the differentiated requirements of vibration isolation performance, structural strength and lightweight indicators in aerospace, precision equipment, semiconductor equipment and even large mechanical vibration isolation systems.

[0063] 3. This application breaks through the traditional honeycomb sandwich support structure commonly used in vibration reduction platforms, abandoning the concept of relying on thin-walled hexagonal unit cells to provide bending stiffness and out-of-plane buckling resistance. Instead, it directly introduces the local resonance mechanism into the planar square lattice or bulk three-dimensional lattice structure through flexible materials. This allows the vibration isolation unit to actively enhance vibration attenuation by utilizing internal resonant microstructures (i.e., flexible materials) instead of solely relying on structural stiffness to suppress vibration. By embedding tunable local resonators (i.e., flexible materials) in the lattice beams or nodes, this application can form several localized bandgap within the target frequency bandwidth, thereby significantly improving the vibration energy dissipation efficiency. This design strategy also achieves many effects such as increased bending stiffness of the sandwich panel, a significant increase in damping ratio, and a reduction in the overall effective modal mass of the structure. Furthermore, the hollow lattice design effectively reduces structural density while ensuring load-bearing capacity, achieving a virtuous cycle between lightweighting and vibration isolation performance. The hollow cavity provides topological stiffness and lowers the system's natural vibration isolation frequency by adjusting beam thickness, cavity diameter, filling material, and the mass distribution of local resonant units, enabling vibration isolation at lower frequencies while maintaining good platform stability and load-bearing capacity.

[0064] In summary, this application constructs a unified structural system based on the principle of local resonance, characterized by lightweight, high damping, and high stiffness. This system significantly improves the overall vibration isolation effect of the sandwich platform under complex vibration environments, representing a fundamental breakthrough over traditional honeycomb structure support methods. To facilitate understanding of the innovative features of the metamaterial vibration reduction platform proposed in this application, the following specific embodiments are provided for illustration.

[0065] Example 1: (1) According to the engineering requirements, the vibration reduction platform is applied between the high-precision instrument installation foundation and the mechanical equipment base. The goal is to isolate the frequency excitation in the 200Hz~300Hz frequency band. The required vibration reduction effect is 26dB~40dB. The maximum load capacity of the platform is 6t, the rated load is 5t, the minimum working load is 3t, and the design value of the vertical stiffness of the system is 700MPa~1000MPa.

[0066] Since the damping ratio of the lattice structure increases monotonically with increasing volume fraction, the peak value at resonance is closely related to the damping ratio; the larger the damping ratio, the smaller the peak value at resonance. In the range of 0Hz to 600Hz, the IWP lattice structure has significant vibration isolation capability at around 250Hz to 450Hz. Therefore, a periodically distributed IWP lattice structure is selected as the required lightweight lattice-multiphase material-core sandwich structure.

[0067] The selected IWP lattice matrix material is 316L stainless steel powder with a density of 7900 kg / m³, a Young's modulus of 210 GPa, and a Poisson's ratio of 0.3. According to experimental measurements, the Young's modulus of an IWP lattice structure with a volume fraction of 20% is approximately 485 MPa.

[0068] Based on the target stiffness required by the platform, an IWP lattice structure with a volume fraction of 20%, an equivalent Young's modulus of 850 MPa, and a unit cell size of 10 mm was finally selected. This structure was then covered with a silicone layer with a hardness of 25 degrees to achieve a resonant vibration absorption effect with a target bandgap frequency of 200~300 Hz.

[0069] (2) Based on the implicit modeling parameters of the IWP lattice, a three-dimensional topological model with periodic unit cells is established. An acrylic plate is used to make a mold in the model, and silicone material with a hardness of 25 is filled into the pores of the skeleton. At the same time, it is ensured that the local resonant structure and the lattice are uniformly distributed to meet the overall low-frequency broadband vibration reduction performance requirements of the platform.

[0070] (3) In the nested multi-layer intermediate sandwich structure, the upper and lower sandwich closed structure is used for covering: the upper cover plate is made of Al-7075 with a thickness of 3mm, the lower plate is made of Q235 steel plate with a thickness of 5mm, and the side plates are made of PVC material.

[0071] (4) Export the complete platform sandwich structure and the upper and lower connecting plates and other three-dimensional components as STL files, import them into slicing software for layer processing, and prepare them for hybrid preparation of selective laser sintering (SLS) and metal powder melting manufacturing (LPBF).

[0072] (5) The SLS forming lattice support structure is made of 316L stainless steel powder with a layer thickness of 100μm, a preheating temperature of 150°C, a laser power of 60W, and a scanning speed of 180mm / s. The external structure of the platform (upper and lower cover plates) is made of aluminum alloy and steel, which are processed separately and then assembled.

[0073] (6) After forming, the overall structure undergoes heat treatment and stress reduction process. The lattice structure is heat-treated at 80°C for 6 hours in a constant temperature chamber, while the metal skeleton is subjected to standard annealing to release residual stress. Subsequently, ultrasonic cleaning and sandblasting are used to obtain a clean, complete, and smooth sandwich structure surface.

[0074] (7) The vibration isolation components are assembled with the support frame, bidirectional damper, optical platform and other components to form a complete vibration reduction platform with local resonance-lattice-multiphase material-core sandwich structure. The vibration reduction platform achieves bandwidth vibration suppression effect in the range of 200Hz~450Hz, and the maximum vibration isolation amount can reach 47.44dB, which meets the vibration isolation requirements between high precision equipment and high vibration environment.

[0075] Example 2: (1) According to the environmental requirements of precision optical equipment operation, the vibration reduction platform needs to be set between the interferometer optical platform and the equipment support base to weaken the small vibrations in the range of 10Hz to 60Hz. The vibration isolation target of the platform is 20dB to 30dB, the equipment load is about 300kg, the rated working load is 400kg, the maximum allowable load is 500kg, and the vertical stiffness of the structure should be controlled between 300MPa and 500MPa to ensure that no structural disturbance is generated in the optical path.

[0076] To address this, the matrix material for the vibration isolation components is 316L stainless steel powder with a density of 7900 kg / m³, a Young's modulus of 210 GPa, and a Poisson's ratio of 0.3. The internal flexible material is a 25-degree silicone elastomer (1.5 mm thick, Shore A hardness 25). Based on existing literature and experiments, the constructed Gyroid structure with a volume fraction of 20% has an overall Young's modulus of approximately 520 MPa.

[0077] Based on the target stiffness and bandgap matching results, a Gyroid lattice structure with a volume fraction of 20%, an equivalent Young's modulus of 504 MPa, and a unit cell size of 10 mm was finally selected. The working bandgap is concentrated in the 30 Hz–55 Hz range, effectively avoiding the core frequency band of interferometry.

[0078] (2) Construct a three-dimensional cycloid lattice model and establish a complete structure containing pre-set flexible material cavities using parametric modeling software. Control the volume fraction and spore distribution of the lattice model to meet the design requirements of lightweight structure, strong continuity and uniform stress distribution.

[0079] (3) The Gyroid structure is nested into modules to form a three-dimensional sandwich model. The center of the sandwich is a Gyroid lattice structure. The flexible material filling the lattice structure can be a multiphase material layer (EVA foam + 4mm butyl rubber layer) to enhance the multi-frequency vibration absorption capability. The upper and lower parts of the sandwich structure are an aluminum alloy panel (7075-T6) and a steel plate (Q235 steel plate), respectively. (4) The 3D model was exported as an STL file. The Gyroid lattice part and the flexible material cavity were prepared by FDM (Fused Deposition Modeling) and CNC (Computer Numerical Control Machining) respectively. The multiphase material was prepared by compression molding. Specifically, the lattice part was printed using FDM technology, the material was 316 stainless steel, the nozzle temperature was 240°C, the platform temperature was 90°C, and the layer thickness was 0.15 mm. The elastic connecting layer was cured in situ by injection molding. The upper and lower rigid plates were respectively machined by CNC milling and the rubber layer was hot-pressed.

[0080] (5) After all components are formed, the lattice structure is heat-treated (80°C for 6 hours) to remove residual stress and is subjected to low-frequency vibration test in a vacuum chamber; after the vibration isolation components are assembled, they are encapsulated with glue and sandblasted to make the surface smooth. The final assembly of the vibration damping platform is controlled within ±0.2 mm.

[0081] (6) The assembled Gyroid lattice-multiphase material-core sandwich vibration damping platform. Low-frequency vibration tests showed that the platform achieved an average vibration reduction of 26.4 dB within the 30Hz–55Hz range, exhibiting characteristics of wide bandwidth, low frequency, lightweight, and high performance. Field testing showed that after application to a laser interferometric optical platform, the platform's vibration peak decreased by 82%, significantly improving the accuracy of optical interferometry measurements and meeting the stability requirements of the market for vibration damping platforms at the time.

[0082] It should be understood that expressions such as "comprising" and "may include" as used in this application indicate the existence of the disclosed functions, operations, or constituent elements, and do not limit one or more additional functions, operations, and constituent elements. In this application, terms such as "comprising" and / or "having" are to be interpreted as indicating a particular characteristic, number, operation, constituent element, component, or combination thereof, but not to exclude the existence or possibility of adding one or more other characteristics, numbers, operations, constituent elements, components, or combinations thereof.

[0083] It should be understood that the terms “center,” “upper,” “lower,” “front,” “rear,” “left,” “right,” “vertical,” “horizontal,” “inner,” “outer,” “clockwise,” “counterclockwise,” “axial,” “radial,” and “circumferential” indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device 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 on this application.

[0084] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0085] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0086] Those skilled in the art will readily understand that the above description is merely a preferred embodiment of this application and is not intended to limit this application. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A method for manufacturing a metamaterial vibration damping platform, characterized in that, Includes the following steps: S1. Determine the performance requirements of the vibration isolation components based on the application conditions of the metamaterial vibration reduction platform; S2. Based on performance requirements, the vibration isolation component is designed as a core sandwich structure, and a three-dimensional model of the vibration isolation component is constructed. In this three-dimensional model, the core layer of the core sandwich structure is generated by a minimal surface controlled by an implicit function and a multi-point array field. S3. Based on the three-dimensional model, a metal skeleton in the form of a multi-minimal curved surface lattice metamaterial is manufactured using additive manufacturing technology. Then, flexible material is filled into the pores of the metal skeleton to form a vibration isolation component in the form of a multiphase material. S4. Vibration isolation components are supported on the platform bracket by a buffer to obtain a metamaterial vibration reduction platform.

2. The manufacturing method as described in claim 1, characterized in that, In step S2, based on the performance requirements, constructing a three-dimensional model of the vibration isolation component includes: S21. A lattice structure is adopted as the basic configuration of the vibration isolation components; S22. Using a three-period minimal surface design for the unit cell of the lattice structure, construct the dynamic performance function expression between the mechanical and vibrational properties of the three-period minimal surface structure; S23. Based on the dynamic performance function expression and performance requirements, combine the periodic implicit function surface generating formula to construct a lattice structure model that obtains a three-period minimum surface; S24. Using the lattice structure model as a framework, a digital model of filling its pores with flexible material is obtained to obtain a multiphase material model containing a lattice framework phase and a flexible filling phase. S25. Add panel models to the upper and lower ends of the composite material model to form a three-dimensional design model of the vibration isolation component.

3. The manufacturing method as described in claim 2, characterized in that, The periodic implicit function surface generators include Gyroid surface generators, IWP surface generators, and Primitive surface generators.

4. The manufacturing method as described in claim 3, characterized in that, In step S23, when the weight-bearing requirement has a higher priority than the vibration reduction requirement in the performance requirements, the dynamic performance function expression is combined with the Gyroid surface generation formula, which includes: ； in, Represents a time variable. Indicates the size of the unit cell. , and Represents spatial coordinates.

5. The manufacturing method as described in claim 3, characterized in that, In step S23, when the weight-bearing requirement has a lower priority than the vibration reduction requirement in the performance requirements, the dynamic performance function expression is combined with the IWP surface generation formula, which includes: ； in, Represents a time variable. and Represents spatial coordinates, This represents the side length of a single cube cell.

6. The manufacturing method as described in claim 3, characterized in that, In step S23, when the priority of the load-bearing requirement is the same as the priority of the vibration reduction requirement in the performance requirements, the dynamic performance function expression is combined with the Primitive surface generation formula, which includes: ； in, Represents a time variable. Indicates the size of the unit cell. , and Represents spatial coordinates.

7. The manufacturing method as described in claim 2, characterized in that, In step S23, after constructing the lattice structure model with a three-period minimum surface, the lattice structure model is verified and iterated based on the equivalent force and vibration relationship model function equations to ensure that the lattice structure corresponding to the lattice structure model meets the requirements.

8. The manufacturing method as described in claim 1, characterized in that, In step S4, when the vibration isolation component is supported on the platform support by the buffer, the platform, connecting plate, bottom surface and side plate are first installed on the vibration isolation component to form the platform body, and then the platform body is supported on the platform support by the buffer.

9. A metamaterial vibration damping platform, manufactured by the method described in any one of claims 1-8, characterized in that: Includes vibration isolation components, buffers, and platform supports, among which: The vibration isolation components are supported on the platform support by several buffers; The vibration isolation component is a core sandwich structure, including a core layer and two panels. The core layer includes a metal skeleton in the shape of a multi-point array structure with extremely small curved surfaces. The pores of the metal skeleton are filled with flexible material. The two panels are respectively disposed at the upper and lower ends of the core layer.

10. The metamaterial vibration damping platform as described in claim 9, characterized in that, The metamaterial vibration damping platform also includes an upper platform, a connecting plate, a lower bottom surface, and side plates. The upper platform and the connecting plate are fixed to the top of the vibration isolation component, and the connecting plate is located between the upper platform and the vibration isolation component. The side plates are located on the outer periphery of the vibration isolation component, and the bottom of the vibration isolation component is connected to the buffer through the lower bottom plate.

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