Three-dimensional vibration isolation superstructure with impact resistance function, preparation method and application thereof

Abstract

The application discloses a three-dimensional vibration isolation superstructure with an anti-impact function and a preparation method and application thereof. The three-dimensional vibration isolation superstructure with the anti-impact function is formed by a plurality of three-dimensional concave cells arranged periodically along three mutually orthogonal spatial directions and connected with each other; each three-dimensional concave cell comprises three groups of hollow tubular member units and eight groups of strut units, and the axes of the hollow tubular member units are arranged along the three mutually orthogonal spatial directions; each group of hollow tubular member units comprises two hollow tubular members arranged coaxially and oppositely; each group of strut units comprises three struts, one end of the three struts is connected integrally and forms a connecting node, the other end of the three struts is connected to three adjacent and mutually orthogonal hollow tubular members respectively, and no geometric intersection occurs between each strut and the hollow tubular member not connected. The application can form a local resonance band gap without setting an independent concentrated mass block, and is compatible with anti-impact deformation.

Description

Technical Field

[0001] This invention relates to the field of mechanical metamaterials technology, and in particular to a three-dimensional vibration isolation superstructure with impact resistance, its preparation method, and its application. Background Technology

[0002] Aerospace engines, pumps, compressors, precision instruments, and vehicle-mounted equipment continuously input vibrations into their supporting foundations during operation. Vibration isolators typically need to block vibration propagation while maintaining sufficient static load-bearing capacity within a small installation space and with low added mass. Under conditions of transport collisions, drops, landings, or abnormal impacts, the isolating components must not experience brittle failure and must be able to dissipate impact energy. Traditional solutions often separate the spring-damped isolator, the load-bearing frame, and the energy-absorbing buffer components, which can easily increase system mass, installation height, and connection interfaces. More importantly, vibration isolation and impact resistance have mutually restrictive requirements on structural stiffness: achieving lower frequencies or wider bandgap usually requires a larger equivalent modal mass or more flexible connections, while impact resistance and reliable load-bearing capacity require high structural stiffness and a stable collapse path. Therefore, achieving effective vibration isolation with a single lightweight structure while retaining impact resistance is a key issue in the design of vibration isolators and damping devices.

[0003] Traditional chiral structures typically consist of a central circular or polygonal ring (as a rigid node) and tangential ligaments arranged in a plane. Several tangential ligaments rotate around the central node, primarily relying on the rotation of the central node to generate compressive-shear coupling or negative Poisson's ratio. The specific response is predominantly in-plane. Traditional concave structures typically consist of straight or curved rods forming an in-plane concave angle, further stretched along the thickness direction if necessary. They primarily rely on the in-plane bending of the support rods to generate lateral contraction and buffer energy absorption (negative Poisson's ratio deformation). Related 2.5D structures typically consist of the above-mentioned two-dimensional unit cells arranged in a plane and then stretched along the thickness direction (e.g., ...). Figure 1 (As shown). Existing chiral structures and concave negative Poisson's ratio structures mostly focus on compressive-shear coupling, lateral contraction, and energy absorption. For example, existing technologies report the use of polygonal ring structures and connecting rods to form two-dimensional unit cells, which are then arrayed in a planar plane and stretched outwards to form a 2.5-dimensional structure. Its main performance characteristics are in-plane compressive-shear coupling and tensile energy absorption. Existing technologies also report the embedding of chiral units within curved concave structures, forming a dual-material energy-absorbing structure through mirrored arrangement, arraying, and outward stretching of two-dimensional unit cells. Its main objectives remain collision energy absorption and controlled collapse. All of these structures are based on two-dimensional or 2.5-dimensional configurations. The specific chiral or concave responses are mainly concentrated in the in-plane direction, while the out-of-plane direction primarily provides ordinary thickness support, offering limited improvement in vibration isolation and impact resistance.

[0004] Therefore, how to achieve a wide local resonant bandgap in a lightweight three-dimensional vibration isolation structure without increasing the number of independent concentrated mass blocks, while maintaining the necessary static bearing capacity and forming a stable progressive buckling and energy dissipation path under impact or large compressive loads, and breaking through the bottleneck of the difficulty in balancing the mass-stiffness matching required for vibration isolation and the bearing-collapse stability required for impact resistance, remains a technical problem that urgently needs to be solved in this field. Summary of the Invention

[0005] The purpose of this invention is to overcome the above-mentioned technical deficiencies and propose a three-dimensional vibration isolation superstructure with both impact resistance and its preparation method and application, thereby solving the technical problem in the prior art of balancing the mass-stiffness matching required for vibration isolation with the load-bearing-collapse stability required for impact resistance.

[0006] In a first aspect, the present invention provides a three-dimensional vibration isolation superstructure with impact resistance, which is formed by multiple three-dimensional concave unit cells arranged periodically along three mutually orthogonal spatial directions and interconnected with each other; each three-dimensional concave unit cell includes three sets of hollow tubular component units and eight sets of support rod units, and the axes of the hollow tubular component units are arranged along three mutually orthogonal spatial directions; each set of hollow tubular component units includes two coaxial and relatively spaced hollow tubular components; each set of support rod units includes three support rods, one end of the three support rods is connected as a whole to form a connection node, and the other end of the three support rods is respectively connected to three adjacent and mutually orthogonal hollow tubular components, and there is no geometric intersection between each support rod and the unconnected hollow tubular components.

[0007] Secondly, the present invention provides a method for preparing a three-dimensional vibration isolation superstructure with impact resistance, comprising the following steps: A three-dimensional concave unit cell model is constructed using 3D modeling software; The three-dimensional concave unit cell model is periodically arrayed in three-dimensional space to construct a three-dimensional overall model of a three-dimensional vibration isolation superstructure with shock resistance function. The overall three-dimensional model of the three-dimensional vibration isolation superstructure with impact resistance is imported into slicing software for layer-by-layer slicing and printing path generation. The 3D printing equipment is then used to form the superstructure layer by layer according to the printing path to obtain the three-dimensional vibration isolation superstructure with impact resistance.

[0008] Thirdly, the present invention provides an application of a three-dimensional vibration isolation superstructure with impact resistance, which is applied in the field of vibration reduction.

[0009] Compared with the prior art, the beneficial effects of the present invention include: This invention utilizes the relative vibration of a hollow tubular component and a support rod to form a local resonant bandgap. The bandgap has local resonance, load transfer, and impact-resistant deformation paths in three orthogonal directions, primarily functioning as vibration isolation. Impact resistance is achieved through progressive buckling of the support rod. Simultaneously, the cavity of the hollow tubular component reduces mass while distributing it away from the neutral axis, providing geometric space for adjusting the mass of the local resonant modes. This allows for the formation of a local resonant bandgap without the need for independent concentrated mass blocks, while also supporting impact-resistant deformation. Attached Figure Description

[0010] Figure 1 This is a schematic diagram of a traditional 2.5-dimensional chiral structure; Figure 2 This is a schematic diagram of an embodiment of the single-phase three-dimensional non-chiral concave unit cell and the three-dimensional vibration isolation superstructure with shock-resistant function provided by the present invention. Figure 3 This is a schematic diagram of an embodiment of the single-phase three-dimensional chiral concave unit cell and the resulting three-dimensional vibration isolation superstructure with shock resistance provided by the present invention. Figure 4 This is a schematic diagram of an embodiment of the biphase three-dimensional non-chiral concave unit cell and the resulting three-dimensional vibration isolation superstructure with shock resistance provided by the present invention. Figure 5 This is a schematic diagram of an embodiment of the biphasic three-dimensional chiral concave unit cell and the resulting three-dimensional vibration isolation superstructure with shock resistance provided by the present invention. Figure 6 This is a schematic diagram showing the positional relationship between the struts and the cross-section in a three-dimensional non-chiral concave unit cell provided by the present invention; Figure 7 This is a schematic diagram showing the positional relationship between the struts and the cross-section in a three-dimensional chiral concave unit cell provided by the present invention; Figure 8 This is a schematic diagram of an embodiment of the positional relationship between the vibration isolation base and the engine or rotating equipment of the three-dimensional vibration isolation superstructure with both impact resistance function provided by the present invention. Figure 9 This is a band gap distribution diagram of a single-phase three-dimensional non-chiral concave unit cell provided by the present invention; Figure 10 This is a band gap distribution diagram of a single-phase three-dimensional chiral concave unit cell provided by the present invention; Figure 11 This is a band gap distribution diagram of a biphasic three-dimensional non-chiral concave unit cell provided by the present invention; Figure 12 This is a band gap distribution diagram of a biphasic three-dimensional chiral concave unit cell provided by the present invention; Figure 13This is a local vibration mode diagram of the upper and lower boundaries of the main band gap of a two-phase three-dimensional chiral concave unit cell provided by the present invention; Figure 14 The transmission loss curve of a three-dimensional vibration isolation superstructure with shock resistance function formed by a biphasic three-dimensional chiral concave unit cell provided by the present invention is shown. Figure 15 This is a diagram of the compression deformation process of a three-dimensional vibration isolation superstructure with impact resistance, formed by different unit cells. Figure 16 It is a quasi-static compressive stress-strain curve of a three-dimensional vibration isolation superstructure with impact resistance formed by different unit cells; Figure 17 This is a diagram showing the specific stiffness of a three-dimensional vibration isolation superstructure with impact resistance, formed by different unit cells. Figure 18 This is a diagram showing the total energy absorption effect of a three-dimensional vibration isolation superstructure with impact resistance, formed by different unit cells. Figure 19 The diagram shows the band gap and total energy absorption effect of a three-dimensional vibration isolation superstructure with shock resistance, formed by biphase three-dimensional chiral concave unit cells under different relative densities. Figure 20 The stress-strain curves of a three-dimensional vibration isolation superstructure with shock resistance, formed by biphase three-dimensional chiral concave unit cells under different relative densities; Figure 21 This is a diagram showing the band gap and total energy absorption effect of a three-dimensional vibration isolation superstructure with shock resistance, formed by two-phase three-dimensional chiral concave unit cells with different support radii. Figure 22 The stress-strain curves of a three-dimensional vibration isolation superstructure with impact resistance, formed by two-phase three-dimensional chiral concave unit cells with different support radii; Figure 23 The diagram shows the band gap and total energy absorption effect of a three-dimensional vibration isolation superstructure with impact resistance, formed by two-phase three-dimensional chiral concave unit cells with different Young's modulus ratios of hollow tubular components / supports. Figure 24 The stress-strain curves of a three-dimensional vibration isolation superstructure with impact resistance is formed by two-phase three-dimensional chiral concave unit cells with different Young's modulus ratios of hollow tubular components / supports. Figure 25 This is a diagram showing the band gap and total energy absorption effect of a three-dimensional vibration isolation superstructure with impact resistance, formed by two-phase three-dimensional chiral concave unit cells with different hollow tubular component / support mass ratios. Figure 26 The stress-strain curves of a three-dimensional vibration isolation superstructure with impact resistance is formed by two-phase three-dimensional chiral concave unit cells with different hollow tubular component / support mass ratios. Figure 27The diagram shows the band gap and total energy absorption effect of a three-dimensional vibration isolation superstructure with shock resistance, formed by biphase three-dimensional non-chiral concave unit cells under different relative densities. Figure 28 The stress-strain curves of a three-dimensional vibration isolation superstructure with shock resistance, formed by biphase three-dimensional non-chiral concave unit cells under different relative densities; Figure 29 This is a diagram showing the band gap and total energy absorption effect of a three-dimensional vibration isolation superstructure with shock resistance, formed by two-phase three-dimensional non-chiral concave unit cells with different support radii. Figure 30 The stress-strain curves of a three-dimensional vibration isolation superstructure with impact resistance are formed by two-phase three-dimensional non-chiral concave unit cells with different support radii. Figure 31 The diagram shows the band gap and total energy absorption effect of a three-dimensional vibration isolation superstructure with impact resistance, formed by two-phase three-dimensional non-chiral concave unit cells with different Young's modulus ratios of hollow tubular components / supports. Figure 32 The stress-strain curves of a three-dimensional vibration isolation superstructure with impact resistance is formed by two-phase three-dimensional non-chiral concave unit cells with different Young's modulus ratios of hollow tubular components / supports. Figure 33 This is a diagram showing the band gap and total energy absorption effect of a three-dimensional vibration isolation superstructure with impact resistance, formed by two-phase three-dimensional non-chiral concave unit cells with different hollow tubular component / support mass ratios. Figure 34 The stress-strain curves of a three-dimensional vibration isolation superstructure with impact resistance is formed by two-phase three-dimensional non-chiral concave unit cells with different hollow tubular component / support mass ratios. Figures 2-5 In 8, 100, a three-dimensional vibration isolation superstructure with impact resistance, 110, a three-dimensional concave unit cell, 120, a hollow tubular component unit, 130, a support rod unit, 121, a hollow tubular component, 131, a support rod, 200, an upper mounting plate, and 300, a lower support plate. Figures 2-5 In the diagram, L represents the side length of the unit cell, H represents the effective height of the hollow tubular component, d1 represents the radius of the support rod, d2 represents the outer diameter of the hollow tubular component, and d3 represents the inner diameter of the hollow tubular component. Figures 16-18 In this context, FEA represents finite element analysis, and EXP represents experiment. Detailed Implementation

[0011] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the invention.

[0012] Please see Figures 2-5 In a first aspect, the present invention provides a three-dimensional vibration isolation superstructure 100 with impact resistance, which is formed by a plurality of three-dimensional concave unit cells 110 arranged periodically along three mutually orthogonal spatial directions and interconnected with each other; each three-dimensional concave unit cell 110 includes three sets of hollow tubular component units 120 and eight sets of support rod units 130, and the axes of the hollow tubular component units 120 are arranged along three mutually orthogonal spatial directions; each set of hollow tubular component units 120 includes two coaxial and relatively spaced hollow tubular components 121; each set of support rod units 130 includes three support rods 131, one end of the three support rods 131 is connected as a whole to form a connection node, and the other end of the three support rods 131 is respectively connected to three adjacent and mutually orthogonal hollow tubular components 121, and there is no geometric intersection between each support rod 131 and the unconnected hollow tubular component 121.

[0013] In this invention, a three-dimensional concave unit cell 110 is constructed using six hollow tubular components 121 and twenty-four support rods 131. The hollow tubular components 121 are arranged in pairs at intervals along three mutually orthogonal spatial directions. One end of each of the three support rods 131 is connected to form a connection node, and the other end of each of the three support rods 131 is connected to three adjacent and mutually orthogonal hollow tubular components 121 respectively. There is no geometric intersection between each support rod 131 and the unconnected hollow tubular components 121. The relative vibration of the hollow tubular components 121 and the support rods 131 forms a local resonant bandgap, and the three orthogonal directions all have local resonance, load transfer, and impact-resistant deformation paths. The main function is vibration isolation, and the support rods are progressively buckled to accommodate impact resistance. At the same time, the cavity of the hollow tubular components 121 can reduce the mass while making the mass distribution away from the neutral axis, and provide geometric space for adjusting the mass of the local resonant modal. Among them, the hollow tubular component 121 mainly provides the modal mass required for local resonance and participates in structural bearing, while the support rod 131 mainly provides the modal stiffness of local resonance and controls the preferential buckling position and progressive collapse path under compression or impact loads.

[0014] In this invention, the three-dimensional concave unit cell 110 includes a three-dimensional non-chiral concave unit cell and / or a three-dimensional chiral concave unit cell.

[0015] Further, please refer to Figure 6 Take the plane perpendicular to the tube axis and passing through the junction of the support rod 131 and the hollow tubular component 121 as the cross section. In the three-dimensional non-chiral concave unit cell, the extension line of the orthographic projection of the axis of the support rod 131 on the cross section passes through the intersection of the cross section and the tube axis (i.e., the center of the hollow tube on the cross section shown in the figure).

[0016] Further, please refer to Figure 7Taking a plane perpendicular to the tube axis and passing through the junction of the support rod 131 and the hollow tubular member 121 as the cross-section, in the three-dimensional chiral concave unit cell, the extension of the orthographic projection of the axis of the support rod 131 onto the cross-section does not pass through the intersection of the cross-section and the tube axis (i.e., the center of the hollow tube on the cross-section shown in the figure), and the direction of the orthographic projection on the cross-section is the same as the tangent direction of the circle centered at the intersection of the cross-section and the tube axis, so that all the support rods constitute a left-handed or right-handed spatial connection. Through the above-mentioned chiral bias, the support rod generates bending-torsional coupling during vibration, and forms a controllable buckling and lateral deformation path during compression, instead of only undergoing in-plane bending.

[0017] In some specific embodiments of the present invention, please refer to Figure 7 Take a plane perpendicular to the tube axis and passing through the junction of the support rod 131 and the hollow tubular component 121 as the cross section. In the three-dimensional chiral concave unit cell, the orthographic projection of the axis of the support rod 131 on the cross section is tangent to a median diameter circle of the cross section, and the orthographic projection and the tangent of the median diameter circle have the same rotation direction, so that all the support rods 131 form a left-handed spatial connection or a right-handed spatial connection. The median diameter circle is located between the inner wall and the outer wall of the hollow tubular component 121, is concentric with the inner wall and the outer wall, and is equidistant from both of them radially.

[0018] In this invention, the three-dimensional concave unit cell 110 is a single-phase three-dimensional concave unit cell (including chiral and non-chiral), and the support rod 131 and the hollow tubular component 121 are both made of the first material phase.

[0019] In this invention, the three-dimensional concave unit cell 110 is a two-phase three-dimensional concave unit cell (including chiral and non-chiral phases), and the support rod 131 uses a first material phase, while the hollow tubular component 121 uses a second material phase. The density and Young's modulus of the second material phase are both higher than those of the first material phase. By employing the aforementioned material zoning design, this invention further independently adjusts the density and stiffness of the two types of components, enabling bandgap formation, static load-bearing capacity, and impact energy dissipation to be coordinated within the same unit cell. Specifically, the hollow tubular component 121, using the second material phase, not only has a higher density, increasing local modal mass and reducing the lower boundary of the bandgap, but also a higher modulus, maintaining the static load-bearing capacity of the equipment. The support rod 131, using the first material phase, has a lower modulus, relatively better deformation capacity, reducing local modal stiffness and maintaining progressive buckling during impact.

[0020] In this invention, the density of the first material phase is 0.8~1.2 g / cm³. 3 Further, it was 1.03 g / cm³. 3The Young's modulus is 2000~3000 MPa, and further to 2638.51 MPa. If the support rod is made of a material with too high a modulus, the static load-bearing capacity will increase, but the overall band gap will shift upward; if the support rod is made of a material with too low a modulus, it may buckle prematurely under the weight of the equipment or impact.

[0021] In this invention, the density of the second material phase is 1.5~2 g / cm³. 3 Further, it was 1.75 g / cm³. 3 The Young's modulus is 20,000~40,000 MPa, and further 31,672.1 MPa.

[0022] This invention does not limit the specific types of the first and second material phases, and those skilled in the art can choose according to the actual situation. For example, the first material phase can be an elastomer, a tough polymer, or a tough composite material, and the second material phase can be a particle-reinforced polymer, a metal, or a high-stiffness composite material; the manufacturing method can be additive manufacturing or composite forming processes that can achieve spatial material partitioning.

[0023] In some specific embodiments of the present invention, the first material phase is a photosensitive resin with a density of 1.03 g / cm³. 3 The Young's modulus is 2638.51 MPa; the second material phase is a silicone core-shell particle-reinforced photosensitive resin with a density of 1.75 g / cm³. 3 The Young's modulus is 31672.1 MPa.

[0024] In this invention, the hollow tubular component 121 is a round tube, an elliptical tube, or an approximately tubular component with a hollow cross section, and the support rod 131 is a support rod with a circular or approximately circular cross section. This invention does not impose any restrictions on this.

[0025] In this invention, the radius of the support rod 131 is 0.2~1.8 mm, including but not limited to 0.2 mm, 0.6 mm, 1 mm, 1.4 mm, 1.8 mm, etc. If the support rod is too thick, the static load-bearing capacity increases but the overall band gap shifts upward; if the support rod is too thin, it may buckle prematurely under the weight of the equipment or impact.

[0026] In this invention, the length of the support rod 131 is 5~20 mm.

[0027] In this invention, the effective height of the hollow tubular component 121 is 8~12 mm, and more specifically 10 mm.

[0028] In this invention, the inner diameter of the hollow tubular component 121 is 2 to 6 mm, and more specifically 4 mm.

[0029] In this invention, the outer diameter of the hollow tubular component 121 is 6-10 mm, and more specifically 8 mm.

[0030] In this invention, the side length of the three-dimensional concave unit cell 110 is 30~40 mm, and more specifically 34 mm.

[0031] In this invention, the relative density of the three-dimensional concave unit cell 110 is 0.06~0.11. The formula for calculating the relative density is: ρ=V s / V c In the formula, V s V is the total volume of a hollow tubular component and supporting solid portion within a single cell. c This represents the volume of the outer envelope of the unit cell.

[0032] In this invention, the Young's modulus ratio of the hollow tubular component 121 to the support rod 131 is 7.2 to 13.3. The formula for calculating the Young's modulus ratio is: R... E =E T / E S Among them, E T E represents the Young's modulus of the material phase used in the hollow tubular component. S The Young's modulus of the material phase used for the support rod.

[0033] In this invention, the mass ratio of the hollow tubular component 121 to the support rod 131 is 2.3 to 4.4. The formula for calculating the mass ratio is: R... M =M T / M S Among them, M T M is the total mass of all hollow tubular components within a single cell. S This represents the total mass of all the supports within the unit cell. Further, M... T =ρ T ×V T M S =ρ S ×V S , where ρ T and ρ S V represents the density of the material phase used in the hollow tubular component and the material phase used in the support rod, respectively. T and V S These represent the solid volumes of all hollow tubular components and all support rods within a single cell.

[0034] Secondly, the present invention provides a method for preparing a three-dimensional vibration isolation superstructure with impact resistance, comprising the following steps: S1. Construct a three-dimensional concave unit cell model using three-dimensional modeling software; S2. Arrange the three-dimensional concave unit cell model in a periodic array in three-dimensional space to construct a three-dimensional overall model of a three-dimensional vibration isolation superstructure with shock resistance function. S3. Import the three-dimensional overall model of the three-dimensional vibration isolation superstructure with impact resistance into the slicing software, slice it layer by layer and generate the printing path. Use 3D printing equipment to form it layer by layer according to the printing path to obtain the three-dimensional vibration isolation superstructure with impact resistance.

[0035] In this invention, during step S3, multi-material photopolymerization 3D printing is used to switch the second material phase and the first material phase according to the spatial position of the hollow tubular component and the support rod, so that the two material phases are integrally formed.

[0036] In this invention, during step S3 of the 3D printing process, the light source wavelength is 350~360 nm, more specifically 355 nm, the single-layer curing time is 10~20 seconds, more specifically 15 seconds, and the layer thickness is 0.05~0.2 mm, more specifically 0.1 mm.

[0037] Thirdly, the present invention provides an application of a three-dimensional vibration isolation superstructure with impact resistance. The aforementioned three-dimensional vibration isolation superstructure with impact resistance is applied in the field of vibration reduction, specifically as a core layer of a vibration isolator, a vibration isolation base, or a load-bearing platform interlayer.

[0038] In this invention, when applied, the local resonant bandgap of the periodic unit cell is preferentially utilized to reduce the transmission of equipment vibration to the foundation; when subjected to transportation collisions, drops, landings, or overload impacts, the support rods undergo progressive buckling, enabling the vibration isolator to simultaneously possess impact-resistant buffering capabilities.

[0039] Specifically, please refer to Figure 8The vibration isolation base includes an upper mounting plate 200, a three-dimensional vibration isolation superstructure 100 with impact resistance provided in the first aspect of the present invention, and a lower support plate 300, wherein the three-dimensional vibration isolation superstructure 100 with impact resistance provided in the first aspect of the present invention is disposed between the upper mounting plate 200 and the lower support plate 300. An engine, pump, compressor, or precision equipment is fixed to the upper mounting plate 200, and the lower support plate 300 connects to the frame, cabin, or foundation. In engineering applications, the band gap position can be adjusted by adjusting the pipe diameter, support rod size, relative density, Young's modulus ratio, and mass ratio. During normal operation, the engine, pump, compressor, or other equipment inputs vibration to the three-dimensional vibration isolation superstructure through the upper mounting plate. The hollow tubular components generate radial, rotational, or bending local resonances near specific frequencies, and the support rods subsequently generate bending-torsional vibrations. When there is no propagation mode between adjacent energy bands, a band gap is formed, and the vibration energy is confined to the first few unit cells near the input end, making it difficult to propagate downwards to the foundation. When equipment or base is subjected to transient impact, the struts preferentially undergo bending, torsion, and buckling. The hollow tubular components maintain overall support in the initial stage of impact. As displacement increases, the multi-layered unit cells successively enter the plateau deformation and densification stages, dispersing the impact energy into multiple struts and multiple unit cells. Since the vibration isolation modal mass is concentrated in the hollow tubular components and the impact deformation is mainly concentrated in the struts, these two functions are divided in different components and different load stages. This avoids insufficient load-bearing capacity due to simply reducing stiffness, and also avoids upward shifting or disappearance of the vibration isolation bandgap due to simply increasing stiffness.

[0040] Example 1: Fabrication of different three-dimensional vibration isolation superstructures with combined impact resistance 3D concave unit cell structure design: Please refer to Figures 2-5A three-dimensional unit cell model was established with a unit cell side length L=34 mm, an effective height H=10 mm for the hollow tubular component (with an inner diameter d3=4 mm and an outer diameter d2=8 mm), a support radius d1=1 mm, and support lengths (non-chiral: 10.57 mm, chiral: 13.89 mm). A three-dimensional concave unit cell 110 was constructed using six hollow tubular components 121 and twenty-four support rods 131. The hollow tubular components 121 were arranged in pairs at intervals along three mutually orthogonal spatial directions. One end of each of the three support rods 131 was connected to form a connection node, and the other end of each support rod 131 was connected to three adjacent and mutually orthogonal hollow tubular components 121, with no geometric intersection between each support rod 131 and any unconnected hollow tubular component 121. A plane perpendicular to the pipe axis and passing through the junction of the support rod 131 and the hollow tubular component 121 is taken as the cross-section. In the non-chiral scheme, the extension of the orthographic projection of the axis of the support rod 131 on the cross-section passes through the intersection of the cross-section and the pipe axis. In the chiral scheme, the orthographic projection of the axis of the support rod 131 on the cross-section is tangent to a median diameter circle of the cross-section, and the orthographic projection and the tangent of the median diameter circle have the same rotation direction, so that all the support rods form a chiral connection. The median diameter circle is located between the inner wall and the outer wall of the hollow tubular component 121, is concentric with the inner wall and the outer wall, and is equidistant from both of them radially.

[0041] In the single-phase three-dimensional non-chiral concave unit cell structure (SS), the single-phase three-dimensional chiral concave unit cell structure (CSS), the biphase three-dimensional non-chiral concave unit cell structure (B-SS), and the biphase three-dimensional chiral concave unit cell structure (B-CSS), the first two structures all use the first material phase; in the latter two structures, the support rod 131 uses the first material phase, and the hollow tubular component 121 uses the second material phase.

[0042] In the aforementioned baseline configurations, SS and B-SS employ the same non-chiral geometry with a relative geometric density of approximately 0.0806; CSS and B-CSS employ the same chiral geometry with a relative geometric density of approximately 0.0927. SS and CSS are single-phase structures, with the hollow tubular components and supports made of the same material, and the two-phase Young's modulus ratio and mass ratio are not used as material zoning design parameters. B-SS and B-CSS are two-phase structures, with the Young's modulus ratio of the hollow tubular components to the supports under their baseline material combinations being approximately 12.0, and the mass ratios of the hollow tubular components to the supports being 3.2 and 3.4, respectively.

[0043] The first material phase is a photosensitive resin (its raw materials include: approximately 15% aliphatic polyurethane acrylate (CN991, Sartomer), approximately 35% bisphenol A epoxy acrylate (CN104NS, Sartomer), approximately 25% multifunctional acrylate monomer (SR454NS, Sartomer), and approximately 25% 4-acryloylmorpholine; in the preparation process, the components are first mixed to form a liquid mixture, and the photoinitiator diphenyl(2,4,6-trimethylbenzoyl)phosphine oxide (TPO) is added, which is then used as a photocurable 3D printing raw material, and is cured layer by layer during the printing process), with a density of 1.03 g / cm³. 3 The Young's modulus is 2638.51 MPa.

[0044] The second material phase is a photosensitive resin reinforced with approximately 5% organosilicon core-shell particles (P52, Wacker) (composed of approximately 5% organosilicon core-shell particles and 95% of the aforementioned photosensitive resin system), with a density of 1.75 g / cm³. 3 The Young's modulus is 31672.1 MPa.

[0045] Fabrication of a three-dimensional vibration-isolation superstructure with impact resistance: A three-dimensional vibration-isolation superstructure with impact resistance was fabricated using multi-material photopolymerization 3D printing. The printing light source wavelength was 355 nm, the single-layer curing time was 15 seconds, and the layer thickness was 0.1 mm.

[0046] The effects of chiral bias and two-phase functional partitioning on vibration isolation bandgap, transmission loss and shock resistance response were verified using the above superstructures. Among them, the sample used for vibration transmission verification adopted a 2×2×4 unit cell array, and the sample used for compression shock resistance verification adopted a 4×4×4 unit cell array.

[0047] Example 2: Verification of Vibration Isolation Bandgap and Transmission Loss ① Simulation of elastic wave dispersion relation: Apply Bloch periodic boundary conditions to a three-dimensional concave unit cell, scan the wave vector along the boundary of the irreducible Brillouin zone and obtain the eigenfrequency to obtain the dispersion curve, and determine the band gap boundary and band gap width based on the frequency range where there is no eigenfrequency between adjacent energy bands.

[0048] ② Vibration transmission simulation: Apply vibration excitation to one end of a 2×2×4 unit cell array, extract the vibration response at the opposite end, and calculate the transmission loss based on the input response amplitude and the output response amplitude.

[0049] ③ Vibration transmission test: A 2×2×4 unit cell array was used to conduct a 0~15 kHz vibration transmission test. An input acceleration sensor was set at the end of the sample close to the exciter, and an output acceleration sensor was set at the end of the sample opposite to it. The transmission loss was calculated based on the input and output acceleration amplitudes.

[0050] Please see Figures 9-12 The second principal band gap of a single-phase three-dimensional non-chiral concave unit cell is 5815 Hz to 10259 Hz, with a relative band gap width of 55.29% (e.g., Figure 9 As shown); the single-phase three-dimensional chiral concave unit cell ranges from 4935 Hz to 9039 Hz, with a relative band gap width of 58.74% (as shown). Figure 10 As shown); the biphasic three-dimensional non-chiral concave unit cell ranges from 5062 Hz to 12243 Hz, with a relative band gap width of 82.99% (as shown). Figure 11 As shown); the biphasic three-dimensional chiral concave unit cell ranges from 4398 Hz to 11946 Hz, with a relative band gap width of 92.36% (as shown). Figure 12 (As shown). The above results indicate that biphase partitioning and spatial chirality together reduce the lower boundary of the bandgap and expand the main bandgap.

[0051] Please see Figure 13 At the lower boundary of the band gap, paired hollow tubular members mainly undergo radial or rotational local resonance, driving the support rod to bend; at the upper boundary of the band gap, the connecting node and the support rod mainly undergo bending-torsional vibration. These results indicate that the hollow tubular members provide modal mass, while the support rod provides modal stiffness.

[0052] Please see Figure 14 Under 6950 Hz excitation, the vibrational energy is concentrated near the input end. Figure 14 The vertical axis represents the ratio of output to input amplitude in decibels, with a minimum value of approximately -206.98 dB, corresponding to a transmission loss of approximately 206.98 dB. The experimental transmission curve also shows significant attenuation within the predicted bandgap range, and its main attenuation frequency band basically corresponds to the bandgap calculated from the dispersion relationship, proving that this structure can serve as a vibration isolation base to suppress the propagation of equipment vibration to the foundation.

[0053] Example 3: Impact Resistance Verification Quasi-static compression simulation: The numerical simulation uses Abaqus / Explicit for quasi-static compression analysis. The lower pressure plate has all degrees of freedom fixed, while the upper pressure plate is subjected to displacement along the compression direction and constrained in the other directions. Considering the self-contact of the structure and the contact between the structure and the pressure plate, hard contact is adopted in the normal direction, and the tangential friction coefficient is 0.2.

[0054] Quasi-static compression test: A 4×4×4 unit cell array specimen was used and placed between the upper and lower plates of an electronic universal testing machine. The lower plate was fixed, and the upper plate was applied downward at a speed of 5 mm / min until the macroscopic strain reached 50% (e.g., Figure 15 As shown in the figure, the stress-strain curve is obtained, and the initial peak stress, total absorbed energy and specific absorbed energy are calculated based on the stress-strain curve.

[0055] Please see Figure 16The stress-strain curves of both B-SS and B-CSS structures show elastic bearing, post-buckling plateau deformation, and late-stage densification. Under the same two-phase material configuration, the overall stress level of B-SS is higher than that of B-CSS, indicating that chiral connection changes the bending stiffness and compressive response dominated by the strut.

[0056] Please see Figures 17-18 The experimental specific stiffness of the biphase three-dimensional non-chiral concave structure was 37.44 MPa, which is 3.72 times that of the single-phase three-dimensional non-chiral concave structure and 24.79 times that of the single-phase three-dimensional chiral concave structure. The total energy absorption of the biphase three-dimensional non-chiral concave unit cell structure was 165.18 Joules, while that of the single-phase three-dimensional non-chiral concave unit cell structure was 119.16 Joules. This demonstrates that biphase partitioning can improve load-bearing and energy absorption levels. These results prove that the vibration-isolated superstructure still possesses progressive deformation and energy dissipation capabilities under abnormal impact loads, without altering the invention's primary technical objective of vibration isolation.

[0057] Example 4: Effects of Parameter Design ① Taking a two-phase three-dimensional chiral concave unit cell structure as the object, this parameter study adopts a single-factor parameter analysis method. That is, only one research parameter is actively changed in each analysis. Except for the derived geometric quantities directly caused by the change of this parameter, the other independently set structural and material parameters remain unchanged according to the corresponding baseline configuration. The two-phase three-dimensional chiral concave structure was investigated for the following relative densities: 0.07, 0.08, 0.09, 0.10, and 0.11; strut radii: 0.2 mm, 0.6 mm, 1.0 mm, 1.4 mm, and 1.8 mm; Young's modulus ratios of hollow tubular components to struts: 7.2, 8.7, 10.2, 12, and 13.3; and mass ratios: 2.4, 2.9, 3.4, 3.9, and 4.4. The effects of these on the band gap and energy absorption were analyzed.

[0058] Please see Figures 19-20 When the relative density increases from 0.07 to 0.11, the initial peak stress of the two-phase three-dimensional chiral concave unit cell increases from 0.08 MPa to 0.22 MPa; the first band gap expands from 2232~2466 Hz to 4040~4545 Hz; the second band gap expands from 3078~9788 Hz to 5782~13221 Hz; and the total energy absorption increases from 56.6 J to 171.8 J.

[0059] Please see Figures 21-22When the strut radius increased from 0.2 mm to 1.8 mm, the initial peak stress of the two-phase three-dimensional chiral concave unit cell structure increased from 0.03 MPa to nearly 0.73 MPa; the total energy absorption increased from 13.8 J to 425.0 J; and the specific energy absorption increased from approximately 0.052 J / g to approximately 0.959 J / g. These results demonstrate that the strut radius can significantly control the load-bearing capacity, collapse plateau, and energy absorption efficiency.

[0060] Please see Figures 23-24 When the Young's modulus ratio of the hollow tubular component to the support rod increases from 7.2 to 13.3, the stress-strain curve of the two-phase three-dimensional chiral concave unit cell structure shows relatively small overall changes, with initial peak stress fluctuations of less than 15%. The frequency positions and bandgap widths of the first and second bandgaps change only slightly, with bandgap characteristic frequency fluctuations of less than 3%. Simultaneously, the total energy absorption changes by less than 5%. These results indicate that within the scope of this study, the Young's modulus ratio has a relatively limited impact on the structural bandgap position, load-bearing response, and total energy absorption, and can be used as an auxiliary adjustment parameter for vibration isolation and impact resistance performance.

[0061] Please see Figures 25-26 When the mass ratio of the hollow tubular component to the support rod increases from 2.4 to 4.4, the stress-strain curves of the two-phase three-dimensional chiral concave unit cell structure basically coincide, and the initial peak stress changes little; the frequency ranges of the first and second band gaps only fluctuate slightly, the band gap characteristic frequency changes by less than 3%, and the total energy absorption changes by less than 5%. These results indicate that within the scope of this study, changes in the mass ratio do not significantly alter the overall compression deformation mode and absolute band gap distribution of the structure, and can be used to assist in adjusting the local modal mass and vibration isolation performance of the structure.

[0062] comprehensive Figures 19-26 It is known that for a two-phase three-dimensional chiral concave unit cell structure, relative density and strut radius are the main parameters affecting the vibration isolation bandgap, load-bearing capacity, and energy absorption performance. Increasing the relative density can stably widen the multi-order bandgap and increase the total energy absorption, while increasing the strut radius can significantly improve the load-bearing capacity and total energy absorption, while also causing changes in the width of the multi-order bandgap. In contrast, within the scope of this implementation, the Young's modulus ratio and mass ratio have relatively small effects on the absolute bandgap position, compressive response, and total energy absorption; the frequency fluctuations of each order bandgap are less than 3%, and the variation in total energy absorption is less than 5%. Therefore, in the structural design process, the main vibration isolation and impact resistance performance can be adjusted primarily through relative density and strut radius, and then the bandgap and material configuration can be adjusted auxiliaryly through Young's modulus ratio and mass ratio.

[0063] ② Taking a biphasic three-dimensional achiral concave unit cell structure as the object, this group also adopted a single-factor parameter analysis method. Only one research parameter was actively changed in each group, while other independently set parameters remained unchanged according to the corresponding baseline configuration. The effects of the following on band gap and energy absorption were investigated for the biphasic three-dimensional achiral concave structure: relative density of 0.06, 0.07, 0.08, 0.09, and 0.10; strut radius of 0.2 mm, 0.6 mm, 1.0 mm, 1.4 mm, and 1.8 mm; Young's modulus ratio of hollow tubular component to strut of 7.2, 8.7, 10.2, 12, and 13.3; and mass ratio of 2.3, 2.7, 3.2, 3.7, and 4.1.

[0064] Please see Figures 27-28 When the relative density increases from 0.06 to 0.10, the initial peak stress of the two-phase three-dimensional non-chiral concave unit cell structure increases from 0.10 MPa to 0.27 MPa, and the total absorbed energy increases from 68.7 J to 183.9 J.

[0065] Please see Figures 29-30 When the support rod radius increases from 0.2 mm to 1.8 mm, the initial peak stress of the two-phase three-dimensional non-chiral concave unit cell structure increases from about 0.04 MPa to nearly 0.83 MPa, and the total energy absorption increases from 2.4 J to 482.3 J.

[0066] Please see Figures 31-32 When the Young's modulus ratio of the hollow tubular component to the support rod increases from 7.2 to 13.3, the stress-strain curve of the two-phase three-dimensional non-chiral concave unit cell structure shows relatively small overall changes, with initial peak stress fluctuations below 5%. The frequency positions and widths of the first, second, and third band gaps only change slightly, with characteristic frequency fluctuations of each band gap less than 4%, and total energy absorption variation less than 5%. These results indicate that within the scope of this study, the Young's modulus ratio has a relatively limited impact on the overall structural load-bearing response, absolute band gap distribution, and total energy absorption, and can be used as an auxiliary adjustment parameter for vibration isolation and impact resistance performance.

[0067] Please see Figures 33-34 When the mass ratio of the hollow tubular component to the support rod increases from 2.3 to 4.1, the stress-strain curves of the two-phase three-dimensional non-chiral concave unit cell structure remain basically consistent, with initial peak stress fluctuations below 5%. The frequency positions and bandgap widths of each bandgap order only change slightly, with characteristic frequency fluctuations of each bandgap order less than 4%, and total energy absorption variation less than 5%. These results indicate that within the scope of this study, changes in the mass ratio do not significantly alter the overall compression deformation mode, absolute bandgap distribution, or total energy absorption of the structure, and can be used for auxiliary adjustment of the structural modal mass and bandgap position.

[0068] comprehensive Figures 27-34It is known that for a two-phase three-dimensional non-chiral concave unit cell structure, relative density and strut radius are the main parameters affecting the vibration isolation bandgap, load-bearing capacity, and energy absorption performance. Increasing the relative density can stably widen multiple bandgap orders and increase total energy absorption, while increasing the strut radius can significantly improve the load-bearing capacity and total energy absorption, while simultaneously causing the formation, migration, and width changes of multiple bandgap orders. In contrast, within the scope of this embodiment, the Young's modulus ratio and mass ratio have relatively small effects on the absolute bandgap position, compressive response, and total energy absorption; the characteristic frequency fluctuations of each bandgap order are less than 4%, and the total energy absorption variation is less than 5%. Therefore, in the structural design process, the main vibration isolation and impact resistance performance can be adjusted primarily through relative density and strut radius, and then the bandgap and material configuration can be adjusted auxiliaryly through Young's modulus ratio and mass ratio. Although the two-phase three-dimensional non-chiral concave unit cell structure also has strong broadband design potential, chiral connections should still be preferred for achieving the target overall vibration isolation and energy absorption efficiency.

[0069] In summary, this invention utilizes hollow tubular components to provide the modal mass and local support required for local resonance, uses struts to adjust modal stiffness and control compression buckling and progressive collapse paths, and further adjusts the mass and stiffness of the two types of components separately through dual-phase material partitioning. Parameter analysis shows that relative density and strut radius are the main parameters affecting the vibration isolation bandgap, load-bearing capacity, and energy absorption performance, while Young's modulus ratio and mass ratio are mainly used for auxiliary adjustment, thus providing parameter basis for the coordinated design of vibration isolation performance and impact resistance performance. The specific advantages of this invention include: (1) Outstanding vibration isolation function without the need for additional concentrated mass blocks: The present invention directly distributes the local resonant mass of the vibration isolator in the hollow tubular component, and provides adjustable modal stiffness by slender support rods, so that the tube-rod combination itself forms a subwavelength bandgap, resulting in outstanding vibration isolation function; at the same time, compared with additional weight blocks or spring-mass resonators, it is not necessary to set up independent weight blocks in the unit cell, which can reduce the additional mass and installation space of the vibration isolation base.

[0070] (2) True three-dimensional multi-directional vibration isolation: Unlike traditional 2.5-dimensional structures, the six hollow tubular components of this invention are arranged in pairs along three orthogonal directions. Slender support rods connect adjacent hollow tubular components with different axes in space. Multiple unit cells are directly and periodically extended along three directions. The three main directions of X, Y, and Z all contain local resonant branches and load-bearing branches, which can form a three-dimensional approximately equivalent response. On this basis, controllable orthogonal anisotropy is formed through material and size configuration. In contrast, the specific response of traditional two-dimensional chiral and concave structures after out-of-plane stretching is usually mainly in-plane. It can be seen that this invention can better adapt to the multi-directional vibrations generated by engines, pumps, and precision equipment.

[0071] (3) Compatibility of vibration isolation and impact resistance: Vibration isolation requires the connecting structure to have adjustable flexibility, while impact resistance requires the structure to maintain load-bearing capacity and stably dissipate energy. It is usually difficult to achieve both simultaneously. This invention solves this contradiction through functional division of labor: a second material phase with higher density and higher modulus is arranged in the hollow tubular component to provide modal mass and maintain local support; the first material phase is arranged in the slender support rod to provide modal stiffness and undergo bending, torsion, and progressive buckling during impact. The above arrangement allows the hollow tubular component to mainly provide local resonant modal mass and the slender connecting support rod to mainly provide modal stiffness during the small amplitude vibration stage of normal operation. The two generate local relative vibration to form a band gap, thereby achieving vibration isolation; during the larger compression or impact stage, the slender connecting support rod further undergoes bending, torsion, and buckling, and multiple unit cells gradually enter the plateau deformation and densification stage to dissipate energy.

[0072] (4) The structure is manufacturable and easy to form a vibration isolation base for equipment: the hollow tubular components and the support rods are connected in one unit cell and can be formed in one step by multi-material three-dimensional printing. There is no need to assemble independent springs, mass blocks and buffers later. The structure can be sandwiched between the equipment mounting plate and the foundation support plate to form a modular vibration isolation base, which is suitable for lightweight vibration isolation, energy absorption, anti-collision buffer and impact protection components in aerospace, precision instruments, transportation equipment and impact protection.

[0073] The specific embodiments of the present invention described above do not constitute a limitation on the scope of protection of the present invention. Any other corresponding changes and modifications made in accordance with the technical concept of the present invention should be included within the scope of protection of the claims of the present invention.

Claims

1. A three-dimensional vibration isolation superstructure with impact resistance, characterized in that, The three-dimensional vibration isolation superstructure, which also has impact resistance, is formed by multiple three-dimensional concave unit cells arranged periodically along three mutually orthogonal spatial directions and interconnected; wherein... Each of the three-dimensional concave unit cells includes three sets of hollow tubular component units and eight sets of support units, and the axes of the hollow tubular component units are arranged along three mutually orthogonal spatial directions. Each group of hollow tubular component units includes two coaxially arranged hollow tubular components that are spaced apart from each other. Each set of support rod units includes three support rods. One end of the three support rods is connected as a whole to form a connection node. The other end of the three support rods is respectively connected to three adjacent and mutually orthogonal hollow tubular components. Each support rod does not geometrically intersect with any unconnected hollow tubular component.

2. The three-dimensional vibration isolation superstructure with impact resistance function according to claim 1, characterized in that, The three-dimensional concave unit cell includes a three-dimensional non-chiral concave unit cell and / or a three-dimensional chiral concave unit cell; wherein, A plane perpendicular to the tube axis and passing through the junction of the support rod and the hollow tubular component is taken as the cross-section. In the three-dimensional non-chiral concave unit cell, the extension of the orthographic projection of the support rod's axis onto the cross-section passes through the intersection of the cross-section and the tube axis; and / or, A plane perpendicular to the tube axis and passing through the junction of the support rod and the hollow tubular component is taken as the cross-section. In the three-dimensional chiral concave unit cell, the extension of the orthographic projection of the support rod's axis onto the cross-section does not pass through the intersection of the cross-section and the tube axis, and the direction of the orthographic projection on the cross-section is the same as the tangent direction of the circle centered at the intersection of the cross-section and the tube axis, so that all the support rods constitute a left-handed spatial connection or a right-handed spatial connection; and / or, A plane perpendicular to the tube axis and passing through the junction of the support rod and the hollow tubular component is taken as the cross-section. In the three-dimensional chiral concave unit cell, the orthographic projection of the axis of the support rod on the cross-section is tangent to a median diameter circle of the cross-section, and the orthographic projection and the tangent of the median diameter circle have the same rotation direction, so that all the support rods form a left-handed spatial connection or a right-handed spatial connection; the median diameter circle is located between the inner wall and the outer wall of the hollow tubular component, is concentric with the inner wall and the outer wall, and is equidistant from both of them radially.

3. The three-dimensional vibration isolation superstructure with impact resistance function according to claim 1, characterized in that, The three-dimensional concave unit cell is a single-phase three-dimensional concave unit cell, and both the support rod and the hollow tubular component are made of the first material phase; or, The three-dimensional concave unit cell is a two-phase three-dimensional concave unit cell, and the support rod is made of a first material phase, while the hollow tubular component is made of a second material phase, and the density and Young's modulus of the second material phase are both higher than those of the first material phase.

4. The three-dimensional vibration isolation superstructure with impact resistance function according to claim 3, characterized in that, The density of the first material phase is 0.8~1.2 g / cm³. 3 Young's modulus is 2000~3000 MPa; and / or, The first material phase is a photosensitive resin with a density of 1.03 g / cm³. 3 Young's modulus is 2638.51 MPa; and / or, The density of the second material phase is 1.5~2 g / cm³. 3 Young's modulus is 20,000~40,000 MPa; and / or, The second material phase is a silicone core-shell particle-reinforced photosensitive resin with a density of 1.75 g / cm³. 3 The Young's modulus is 31672.1 MPa.

5. The three-dimensional vibration isolation superstructure with impact resistance function according to claim 1, characterized in that, The radius of the support rod is 0.2~1.8 mm; and / or, The length of the support rod is 5~20 mm.

6. The three-dimensional vibration isolation superstructure with impact resistance function according to claim 1, characterized in that, The effective height of the hollow tubular component is 8~12 mm; and / or, The inner diameter of the hollow tubular component is 2~6 mm; and / or, The outer diameter of the hollow tubular component is 6~10 mm; and / or, The side length of the three-dimensional concave unit cell is 30~40 mm.

7. The three-dimensional vibration isolation superstructure with impact resistance function according to claim 1, characterized in that, The relative density of the three-dimensional concave unit cell is 0.06~0.11; and / or, The Young's modulus ratio of the hollow tubular component to the support rod is 7.2~13.3; and / or, The mass ratio of the hollow tubular component to the support rod is 2.3 to 4.

4.

8. A method for preparing a three-dimensional vibration isolation superstructure with impact resistance as described in any one of claims 1 to 7, characterized in that, Includes the following steps: A three-dimensional concave unit cell model is constructed using 3D modeling software; The three-dimensional concave unit cell model is periodically arrayed in three-dimensional space to construct a three-dimensional overall model of a three-dimensional vibration isolation superstructure with shock resistance function. The three-dimensional overall model of the three-dimensional vibration isolation superstructure with impact resistance is imported into slicing software for layer-by-layer slicing and printing path generation. The 3D printing equipment is then used to form the structure layer by layer according to the printing path to obtain the three-dimensional vibration isolation superstructure with impact resistance.

9. The method for preparing the three-dimensional vibration isolation superstructure with impact resistance function according to claim 8, characterized in that, The 3D printing process employs multi-material photopolymerization 3D printing; and / or, During the 3D printing process, the light source wavelength is 350~360 nm, the single-layer curing time is 10~20 seconds, and the layer thickness is 0.05~0.2 mm.

10. An application of a three-dimensional vibration isolation superstructure with impact resistance as described in any one of claims 1 to 7, characterized in that, The three-dimensional vibration isolation superstructure with impact resistance is applied in the field of vibration reduction.

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