Multipurpose multifunctional three-way vibration isolation damper

Abstract

The invention discloses a multipurpose multifunctional three-way vibration isolation damper which comprises a vibration isolator shell, a vibration isolator inner shaft, an additional support, a lattice structure and a fastening bolt. The lattice structure is fixed between the vibration isolator shell and the vibration isolator inner shaft through a bonding or interference fit method, and the additional support is connected to the bottom of the vibration isolator shell. The vibration isolation damper is divided into two types of connection modes of a vibration source and a vibration isolation object: a vibration isolator shell and a vibration isolator inner shaft are respectively fixed on the vibration source part or the isolated object through fastening bolts; the additional bracket and the vibration isolator inner shaft are respectively fixed on a vibration source part or a separated object through fastening bolts; due to the mechanical property of the lattice structure, the vibration isolation damper can bear shearing, pulling and pressing at the same time, so that the vibration isolation damper has the vibration isolation and reduction capacity in three directions, namely the axial direction, the normal direction and the circumferential direction; the invention further provides a design method and a parameter selection basis of the lattice structure, and the vibration isolation performance, the damping performance, the heat insulation performance and the like with good robustness can be achieved.

Description

TECHNICAL FIELD

[0001] The application belongs to the technical field of three-dimensional vibration isolators, and particularly relates to a multipurpose and multifunctional three-dimensional vibration isolator based on a ring-shaped TPMS dot matrix structure. BACKGROUND

[0002] In the fields of aerospace, precision instrument engineering, etc., harmful vibration can cause equipment damage and affect the precision index of the equipment, especially for low-frequency vibration, and conventional vibration control means is difficult to achieve effective control. Vibration isolation is generally divided into active vibration isolation, passive vibration isolation, semi-active vibration isolation and active-passive integrated vibration isolation. Among them, passive vibration isolation has high reliability and is simple to implement, and has been widely applied. High-end equipment is often in a complex and harsh environment, in order to achieve good vibration isolation effect, the vibration isolator needs to have three-dimensional vibration isolation capability and strong environmental adaptability.

[0003] The currently widely used traditional vibration isolator is a metal rubber vibration isolator. It has strong environmental adaptability, uses metal wire as raw material, has rubber elasticity and porosity without ordinary rubber, can work stably in harsh environments such as high and low temperature, large temperature difference, high pressure, high vacuum, strong radiation, severe vibration and corrosion, and is suitable for special scenes such as aerospace. However, it has technical shortcomings, and the cost is higher than that of traditional rubber vibration isolators due to the influence of metal wire raw materials and processing technology; as a strong nonlinear material, it is difficult to accurately design a vibration isolator to meet specific needs, and it requires strict technical and experience requirements; although it has excellent damping characteristics, it may have the risk of transmitting vibration along the metal wire under extreme high-frequency working conditions. Patent No. 202011331683.0 proposes a three-dimensional stiffness damping decoupling high-load metal rubber combined vibration isolator, which has three-dimensional vibration isolation capability through structural design, but still has deficiencies in addition to the problems of metal rubber itself. It uses six pieces of metal rubber to achieve three-dimensional vibration isolation, and the structure is complex and the volume is large, which is difficult to meet the needs of high-end equipment inside the aerospace, ship, etc. field for compact vibration isolators.

[0004] There are also many active isolation mechanisms for three-dimensional vibration isolation. Three-dimensional active isolation mechanism has obvious advantages. The combination of active and passive isolation technology can achieve synchronous active feedback control in vertical and horizontal directions, breaking through the limitations of traditional passive isolation. With high-sensitivity sensors, actuators, and advanced control algorithms, it can accurately identify vibrations and generate counteracting forces, effectively suppressing multi-degree-of-freedom vibrations, solving low-frequency resonance problems, and significantly improving isolation precision and stability, creating a near-zero vibration environment for precision instruments, high-end equipment, and other devices. However, its structure and control system are complex, involving high-precision sensors, actuators, and complex algorithms, increasing design and debugging difficulty and cost; the dynamic range is limited, and strong vibrations can easily exceed the threshold, causing positive feedback and noise, affecting isolation; calibration requirements are strict, requiring professional personnel and equipment, time-consuming and labor-intensive, and dependent on power and control systems, so once a fault occurs, the isolation function is easily lost. Patent No. 202510124669.X proposes a kind of vibration absorber based on magneto-rheological, which uses blade to stir magnetic fluid, and suppresses vibration transmission through energy dissipation to achieve active vibration reduction control. However, such devices are easily affected by environmental factors such as temperature and magnetic field stability. In extreme temperature (such as high and low temperature alternation in aerospace field) and strong electromagnetic interference environment, the physical properties of magnetic fluid may change, making the vibration reduction effect unstable, difficult to meet the compact demand of high-end equipment for "small size, low weight, high integration", and limited in engineering application scenarios.

[0005] Lattice structures have the characteristics of lightweight and high strength, are formed by periodic array of cell structures, are easy to design and process, and have isotropic performance, which are expected to replace metal rubber as vibration isolation elements. However, their damping effect is poor (damping ratio is about 0.02). Patent No. 202310000470.7 proposes a high-damping variable-stiffness BCC lattice composite structure vibration absorber, which fills the lattice structure with viscoelastic material based on epoxy resin / polyurethane matrix to achieve the effect of increasing damping. However, the mass of the lattice structure filled with viscoelastic material increases significantly and can only achieve vibration isolation effect in one direction, which cannot meet the three-dimensional vibration isolation demand of high-end equipment in aerospace, shipbuilding and other fields; Patent No. CN118030729A designs a passive three-dimensional isolator based on BCC-B type lattice, which covers high-damping material through composite lattice structure to improve three-dimensional vibration isolation capacity. Its stress concentration effect at the node is significant, making it difficult to balance the performance requirements of lightweight, compact, low stiffness and large bearing; the porosity is influenced by the combination of beam length and beam diameter, and the minimum hole diameter is difficult to define, increasing the difficulty of stiffness design and restricting the application in harsh environments such as aerospace. Therefore, it is urgent to propose a three-dimensional lattice structure vibration isolator that integrates lightweight, high strength, heat insulation, and vibration isolation to meet the research needs of high-end equipment. SUMMARY

[0006] In order to overcome the above-mentioned deficiencies of the prior art, the purpose of the present application is to achieve specific bearing, vibration isolation and heat insulation effects by designing a TPMS lattice structure with specific parameters; a multi-purpose and multi-functional three-way vibration isolation damper based on the TPMS lattice structure is provided; the damper overcomes the defect that the traditional lattice structure is prone to stress concentration and damage, can realize similar vibration isolation frequency bands in different directions, has the characteristics of strong designability, adjustable stiffness, compact structure and wide application range, and is intended for vibration isolation of machinery / structure.

[0007] In order to achieve the above-mentioned purpose, the present application adopts the following technical solutions:

[0008] A multi-purpose and multi-functional three-way vibration isolation damper, comprising a vibration isolator shell 1, a vibration isolator inner shaft 2, an additional support 3, a lattice structure 4 and fastening bolts 5; the lattice structure 4 is fixed between the vibration isolator shell 1 and the vibration isolator inner shaft 2 by bonding or interference fit, and the additional support 3 is connected to the bottom of the vibration isolator shell 1; the vibration isolation damper is divided into two categories in terms of the connection mode of the vibration source and the isolated object: the vibration isolator shell 1 and the vibration isolator inner shaft 2 are respectively fixed on the vibration source part or the isolated object by the fastening bolts 5; the additional support 3 and the vibration isolator inner shaft 2 are respectively fixed on the vibration source part or the isolated object by the fastening bolts 5; the mechanical properties of the lattice structure 4 enable it to simultaneously withstand shear and tension and compression, so that the vibration isolation damper has three-way vibration isolation and damping capacity in the axial, normal and circumferential directions.

[0009] The lattice structure 4 is composed of an array structure 6, an outer thin wall 7 and an inner thin wall 8, the array structure 6 is located between the outer thin wall 7 and the inner thin wall 8, and the lattice structure is manufactured by an integrated molding method; the outer thin wall 7 and the inner thin wall 8 respectively increase the contact area of the lattice structure 4 with the vibration isolator shell 1 and the vibration isolator inner shaft 2, so that the connection is more firm; the array structure 6 is composed of a plurality of three-period minimal surface TPMS unit cells, is arranged around the vibration isolator inner shaft 2 as a whole, is distributed in a ring array in the horizontal plane, and extends in the vertical direction perpendicular to the horizontal plane to form a three-dimensional configuration; the lattice structure is regularly arranged in the circumferential space with the center of the vibration isolator inner shaft 2 as the symmetry reference, and constitutes the main structure with vibration isolation and damping effects.

[0010] The porosity and material damping ratio of the three-period minimal surface unit cell in the array structure 6 are variable; increasing the porosity of the three-period minimal surface TPMS unit cell in the array structure 6 to 40%-80% can reduce the shear modulus of the lattice structure, thereby widening the frequency interval of vibration isolation, and the increased porosity increases the volume ratio of air in the lattice structure, weakens the heat transfer capacity of the lattice structure, reduces the thermal conductivity of the lattice structure, and realizes good heat insulation function; increasing the material damping ratio of the TPMS unit cell in the array structure 6 to 0.1-0.4 can enhance the damping capacity of the vibration isolation damper in the three directions, i.e. the axial, normal and circumferential directions.

[0011] The dot matrix structure 4 adopted by the vibration isolation damper has the following characteristics in terms of vibration isolation frequency band and damping ratio: when the vibration source amplitude increases, the dynamic stiffness of the vibration isolation damper decreases, the resonance peak frequency decreases, the vibration isolation frequency band widens, and the structural damping ratio of the vibration isolation damper increases, and the resonance peak value decreases; this characteristic improves the vibration isolation and damping effect of the vibration isolator.

[0012] The vibration isolator shell 1, the vibration isolator inner shaft 2 and the additional support 3 all adopt high-strength metal materials to provide sufficient support capacity; and the dot matrix structure 4 adopts high-temperature-resistant rubber material to enhance the vibration isolation and damping effect of the vibration isolator.

[0013] The vibration isolator shell 1 is in the form of a regular cylindrical cavity structure, extends in the vertical direction, forms a hollow containing space, and is provided with a plurality of through holes for facilitating connection with the outside through bolts.

[0014] The additional support 3 is in the form of an integral rigid structure and is in the form of a rectangular frame, has a plurality of mutually perpendicular wall surfaces, and forms a hollow chamber extending in the length direction; a circular through hole is formed in the center of the bottom surface of the additional support, and the inner diameter of the through hole is matched with the outer diameter of the vibration isolator inner shaft 2, so as to limit the displacement of the vibration isolator inner shaft; the additional support 3 is uniformly provided with four auxiliary mounting holes around the circular through hole, which are mainly used for connection function.

[0015] The design method of the array structure 6 is as follows:

[0016] Step 1: Establish the design equation of the three-period minimal surface TPMS unit cell: the three-period minimal surface TPMS unit cell in the array structure 6 is composed of a series of curved surfaces, and its design equation is as follows:

[0017]

[0018] In the formula: ω is the circular frequency, C is a real number for controlling the shape of the unit cell, x, y and z are the coordinates in the three perpendicular coordinate axis directions;

[0019] Step 2: According to the known target relative thermal conductivity λ, i.e. the ratio of the thermal conductivity of the unit cell to the same equivalent volume structure steel, the parameter C of the three-period minimal surface TPMS unit cell is determined; ω=2 is used by default in the unit cell design to control the size of the unit cell, and the shape of the three-period minimal surface TPMS unit cell is controlled by the unique parameter C; in the case of the known target relative thermal conductivity λ, the parameter C is calculated by the following formula

[0020]

[0021] In the formula: λ material is the thermal conductivity of the material of the three-period minimal surface TPMS unit cell, and λsteel The thermal conductivity of the structural steel is a known parameter;

[0022] Step 3: Establish a three-period minimal surface TPMS unit cell model according to the value of parameter C, calculate the relative thermal conductivity of the three-period minimal surface TPMS unit cell, and perform verification;

[0023] Substitute the value of parameter C into the design equation of the three-period minimal surface TPMS unit cell to generate a unit cell model, simulate the heat conduction process by using the finite element method FEM, calculate the relative thermal conductivity of the unit cell by using the Fourier heat conduction law, and verify whether the calculated relative thermal conductivity is less than the target relative thermal conductivity λ. If not, reduce the value of parameter C and repeat step 3 until it is satisfied.

[0024] Step 4: Calculate the equivalent mechanical parameters of the three-period minimal surface TPMS unit cell, and design the main parameters of the array structure 6:

[0025] Substitute the value of parameter C that meets the heat conduction requirement in step 3 into the design equation of the three-period minimal surface TPMS unit cell to obtain a unit cell model, and calculate the equivalent mechanical parameters of the three-period minimal surface TPMS unit cell, including the equivalent elastic modulus E, Poisson's ratio v, and shear modulus G, by using the representative volume element method RVE. Given the mass M of the vibration isolation object and the target natural frequency f, the main design parameters are the inner diameter r1, the outer diameter r2, and the lattice structure height h of the array structure 6, which satisfy the following formula:

[0026]

[0027] Step 5: Establish a three-dimensional model of the array structure 6 according to the parameters calculated in step 4, calculate the natural frequency of the array structure, and complete the verification;

[0028] Based on parameter C, the inner diameter r1, the outer diameter r2, and the array structure height h of the array structure 6, a three-dimensional model of the array structure 6 is established to verify whether the natural frequency of the vibration isolation damper is less than the target natural frequency f by modal analysis. If it is satisfied, the parameters are available. If it is not satisfied, adjust the size of the lattice structure height h and repeat step 5 until the requirements are met.

[0029] Compared with the prior art, the present application has the following advantages:

[0030] The lattice structure of the present application has the characteristics of lightweight, heat insulation, high damping, and vibration reduction, and can be flexibly designed to achieve multiple functions according to requirements. The special mechanical properties of the annular lattice structure enable it to simultaneously withstand shear and tension and compression, i.e., simultaneously isolate vibration in multiple directions.

[0031] The application utilizes the lattice structure characteristics to design a multipurpose vibration isolator, overcomes the shortcomings of single vibration isolation direction, single use and single function of the traditional vibration isolator, and realizes flexible design, multipurpose and three-way damping effect.

[0032] The application also provides a design method and parameter selection basis of the lattice structure, and can realize good robustness, vibration isolation performance, damping performance and heat insulation performance. BRIEF DESCRIPTION OF DRAWINGS

[0033] Figure 1 Fig. 1 is a structural schematic diagram of the application.

[0034] Figure 2 Fig. 2 is a structural longitudinal section view of the application.

[0035] Figure 3 Fig. 3 is a three-dimensional schematic diagram of the vibration isolator shell.

[0036] Figure 4 Fig. 4 is a three-dimensional schematic diagram of the inner shaft of the vibration isolator.

[0037] Figure 5 Fig. 5 is a three-dimensional schematic diagram of the additional support.

[0038] Figure 6 Fig. 6 is a three-dimensional schematic diagram of the lattice structure.

[0039] Figure 7 Fig. 7 is a top view of the lattice structure.

[0040] Figure 8 Fig. 8 is a vibration transmissibility curve diagram of the vibration isolator in three directions, wherein (a), (b) and (c) are respectively axial, normal and circumferential vibration transmissibility curves with frequency change. DETAILED DESCRIPTION

[0041] In order to make the purpose, technical scheme and advantages of the application more clear, the application will be further described in detail below with reference to the drawings, such as Figure 1 As shown in the drawings, the application utilizes the three-period minimal surface TPMS lattice structure, utilizes the multi-direction deformation characteristics of the three-period minimal surface TPMS lattice structure, and realizes vibration isolation in multiple directions. Meanwhile, the application provides a design method of the array structure applied to the vibration damper, which is used to realize vibration isolation and heat insulation functions.

[0042] As Figure 1As shown, the present application is a multi-purpose and multi-functional three-way vibration isolation damper, comprising a vibration isolator shell 1, a vibration isolator inner shaft 2, an additional support 3, a dot matrix structure 4 and fasteners; the dot matrix structure 4 is fixed between the vibration isolator shell 1 and the vibration isolator inner shaft 2 by bonding or interference fit, and the additional support 3 is connected to the bottom of the vibration isolator shell 1 by fastening bolts 5; the mechanical properties of the dot matrix structure 4 enable it to simultaneously withstand shear and tension and compression, so that the vibration isolation damper has three-way vibration isolation and damping capability in the axial, normal and circumferential directions. The vibration isolation damper of the present application is divided into two categories in terms of the connection mode of the vibration source and the isolated object: the vibration isolator shell 1 and the vibration isolator inner shaft 2 are respectively fixed on the vibration source part or the isolated object by fastening bolts 5; the additional support 3 and the vibration isolator inner shaft 2 are respectively fixed on the vibration source part or the isolated object by fastening bolts 5.

[0043] As shown in Figure 2 and Figure 6 , the dot matrix structure 4 is composed of an array structure 6, an outer thin wall 7 and an inner thin wall 8, the array structure 6 is located between the outer thin wall 7 and the inner thin wall 8, and the dot matrix structure is manufactured by integrated molding; the outer thin wall 7 of the array structure 6 is connected with the vibration isolator shell 1, and the inner thin wall 8 is connected with the vibration isolator inner shaft 2, the outer thin wall 7 and the inner thin wall 8 increase the contact area of the dot matrix structure 4 with the vibration isolator shell 1 and the vibration isolator inner shaft 2 respectively, so that the connection is more firm.

[0044] The array structure 6 is composed of a plurality of three-period minimal surface TPMS cells, which are arranged around the vibration isolator inner shaft 2, distributed in a ring array in the horizontal plane, and extended in the vertical direction perpendicular to the horizontal plane to form a three-dimensional configuration; the dot matrix structure is regularly arranged in the ring space with the center of the vibration isolator inner shaft 2 as the symmetry reference, forming the main structure with vibration isolation and damping effect.

[0045] As shown in Figure 3 , the vibration isolator shell 1 is a regular cylindrical cavity structure as a whole, extending in the vertical direction to form a hollow containing space, and is provided with a plurality of through holes for facilitating connection with the outside world by bolts.

[0046] As shown in Figure 4 , the vibration isolator inner shaft 2 is a hollow cylindrical structure as a whole, the top end is a circular platform, and the platform is provided with four through holes for connecting external objects; the cylindrical surface is provided with symmetrical through holes for connecting tubular objects.

[0047] As shown in Figure 5As shown, the additional support 3 is a one-piece rigid structure in the shape of a cuboid frame, has multiple walls perpendicular to each other, and forms a hollow chamber extending in the length direction; a circular through hole is formed in the center of the bottom surface of the additional support, the inner diameter of the through hole is matched with the outer diameter of the vibration isolator inner shaft 2, so as to limit the displacement of the vibration isolator inner shaft; the additional support 3 is uniformly distributed with four auxiliary mounting holes in the circumferential direction of the circular through hole, which are mainly used to realize the connection function.

[0048] Figure 7 The lattice structure 4 is a top view, the array structure 6 in the lattice structure 4 is composed of a plurality of three-period minimal surface TPMS unit cells, and is arranged around the vibration isolator inner shaft 2, is distributed in a ring array in a horizontal plane, and extends in a vertical direction perpendicular to the horizontal plane to form a three-dimensional configuration. With the center of the vibration isolator inner shaft 2 as a symmetric reference, regularly arranged in the circumferential space, to form a main structure with vibration isolation and vibration reduction effects.

[0049] The design method of the array structure 6 in the multipurpose multifunctional three-way vibration damper of the application is as follows:

[0050] Step 1: Establish the design equation of the three-period minimal surface TPMS unit cell: the three-period minimal surface TPMS unit cell in the array structure 6 is composed of a series of curved surfaces, and its design equation is as follows:

[0051]

[0052] In the formula, ω is the circular frequency, C is a real number for controlling the shape of the unit cell, and x, y and z are the coordinates in the directions of the three perpendicular coordinate axes, respectively;

[0053] Step 2: According to the known target relative thermal conductivity λ, i.e. the ratio of the thermal conductivity of the unit cell to the thermal conductivity of the same equivalent volume of structural steel, the parameter C of the three-period minimal surface TPMS unit cell is determined; ω is set to 2 by default in the unit cell design, which is used to control the size of the unit cell, and the shape of the three-period minimal surface TPMS unit cell is controlled by the unique parameter C. In the case of the known target relative thermal conductivity λ, the parameter C is calculated by the following formula

[0054]

[0055] In the formula, λ material is the thermal conductivity of the material of the three-period minimal surface TPMS unit cell, and λ steel is the thermal conductivity of the structural steel, both of which are known parameters.

[0056] Step 3: Establish the three-period minimal surface TPMS unit cell model according to the value of the parameter C, calculate the relative thermal conductivity of the three-period minimal surface TPMS unit cell, and check it;

[0057] The value of parameter C is substituted into the design equation of the three-period minimal surface TPMS unit cell to generate a unit cell model, the finite element method FEM is used to simulate the heat conduction process, the relative thermal conductivity of the unit cell is calculated by using the Fourier heat conduction law, and whether the calculated relative thermal conductivity is less than the target relative thermal conductivity λ is checked. If not, the value of parameter C is reduced and step 3 is repeated until it is satisfied.

[0058] Step 4: Calculate the equivalent mechanical parameters of the three-period minimal surface TPMS unit cell, and design the main parameters of the array structure 6:

[0059] The value of parameter C that meets the heat conduction requirement in step 3 is substituted into the design equation of the three-period minimal surface TPMS unit cell to obtain a unit cell model. The representative volume element method RVE is used to calculate the equivalent mechanical parameters of the three-period minimal surface TPMS unit cell: equivalent elastic modulus E, Poisson's ratio v, and shear modulus G. Given the mass M of the vibration isolation object and the target natural frequency f, the main design parameters are the inner diameter r1, the outer diameter r2, and the lattice structure height h of the array structure 6, which satisfy the following formula:

[0060]

[0061] Step 5: Establish a three-dimensional model of the array structure 6 according to the parameters calculated in step 4, calculate the natural frequency of the array structure, and complete the verification.

[0062] Based on parameter C, the inner diameter r1, the outer diameter r2, and the array structure height h of the array structure 6 are used to establish a three-dimensional model of the array structure 6. The modal analysis is used to verify whether the natural frequency of the vibration isolation damper is less than the target natural frequency f. If it is satisfied, the parameters are available. If it is not satisfied, adjust the size of the lattice structure height h and repeat step 5 until the requirements are met.

[0063] Embodiment

[0064] The design method of the array structure 6 will be described below through a specific embodiment.

[0065] First, considering the target relative thermal conductivity λ = 0.2, the parameter C is calculated according to the formula

[0066]

[0067] The value of parameter C is calculated to be 0.53, i.e. the porosity is about 70%. The relative thermal conductivity obtained by heat conduction simulation is 0.19, which meets the requirements. Therefore, the value of the unit cell parameter C is determined to be 0.53.

[0068] The finite element method is used to analyze the statics of the unit cell with periodic boundary conditions, and the equivalent elastic modulus E=0.1 MPa and G=0.061 MPa are calculated. According to the pipe specifications and the space occupied by the equipment, the inner diameter r1 of the array structure 6 is determined to be 20 mm, and the outer diameter r2 is 40 mm. Substituting the formula can obtain the height h=6 mm. According to the parameters C, the inner diameter r1, the outer diameter r2 and the height h of the unit cell, the finite element model of the array structure is established, and the modal analysis is carried out to verify that the natural frequency of the vibration isolation damper is less than the target natural frequency, which meets the condition. In order to facilitate installation, 1 mm thick inner and outer thin walls are added to the array structure, and thus the design parameters of the point array structure have been determined.

[0069] According to the parameters of the point array structure and the pipe size, the inner diameter of the inner shaft of the vibration isolation damper is designed to be 16 mm, and the outer diameter is 19 mm. The inner diameter of the vibration isolation damper shell is 41 mm, which ensures that the vibration isolation damper shell has sufficient stiffness and pressure capacity. After assembly, a finite element model is established, and modal analysis shows that when vibration occurs, three different directions of vibration may occur: the first type is the axial movement of the inner shaft of the vibration isolator, at this time the point array structure is sheared; the second type is the normal direction movement along the inner shaft of the vibration isolator, at this time the point array structure mainly occurs tensile deformation; the third type is the circumferential direction movement along the inner shaft of the vibration isolator, at this time the point array structure occurs shear deformation. The specific simulation transmissibility curve is shown in (a), (b) and (c) of Figure 8 The stiffness in the axial, normal and circumferential directions is 5.52 kN / m, 11.12 kN / m and 29.19 Nm / dec, respectively, and the natural frequency is 21.37 Hz, 18.1 Hz and 24.51 Hz, respectively.

[0070] As a preferred embodiment of the present application, all the fastening bolts, the vibration isolator shell, the vibration isolator inner shaft and the additional support part are made of steel material, and the point array structure part is made of high-temperature-resistant and high-wear-resistant rubber material.

[0071] The above description is only a preferred embodiment of the present application and is not intended to limit the present application. Obviously, those skilled in the art can make various modifications and changes to the present application without departing from the spirit and scope of the present application. Thus, if these modifications and changes of the present application fall within the scope of the claims of the present application and their equivalent technologies, the present application also intends to include these modifications and changes.

Claims

1. A multi-purpose, multifunctional three-way vibration isolation damper, characterized by: The invention comprises a vibration isolator shell (1), a vibration isolator inner shaft (2), an additional bracket (3), a lattice structure (4) and a fastening bolt (5); the lattice structure (4) is fixed between the vibration isolator shell (1) and the vibration isolator inner shaft (2) by bonding or interference fit, and the additional bracket (3) is connected to the bottom of the vibration isolator shell (1); the vibration isolation damper is divided into two categories in terms of the connection method between the vibration source and the vibration isolation object: the vibration isolator shell (1) and the vibration isolator inner shaft (2) are respectively fixed to the vibration source part or the isolated object by fastening bolts (5); the additional bracket (3) and the vibration isolator inner shaft (2) are respectively fixed to the vibration source part or the isolated object by fastening bolts (5); the mechanical properties of the lattice structure (4) enable it to withstand shear and tension and compression at the same time, so that the vibration isolation damper has vibration isolation and vibration reduction capabilities in three directions, namely, axial, normal and circumferential directions.

2. The multi-purpose, multifunctional three-way vibration isolation damper according to claim 1 is characterized in that: The lattice structure (4) is composed of an array structure (6), an outer thin wall (7) and an inner thin wall (8), the array structure (6) is located between the outer thin wall (7) and the inner thin wall (8), and the lattice structure (4) is manufactured by an integrated molding method; the outer thin wall (7) and the inner thin wall (8) respectively increase the contact area between the lattice structure (4) and the isolator shell (1) and the isolator inner shaft (2), so as to make the connection more secure; the array structure (6) is composed of a plurality of three-periodic minimal surface TPMS unit cells, which are arranged around the isolator inner shaft (2) as a whole, distributed in a circular array in a horizontal plane, and extended in a vertical direction perpendicular to the horizontal plane to form a three-dimensional configuration; the lattice structure is symmetrically based on the center of the isolator inner shaft (2), and is regularly arranged in the annular space, forming a main structure with vibration isolation and vibration reduction effects.

3. The multi-purpose, multifunctional three-way vibration isolation damper according to claim 2 is characterized in that: The porosity and material damping ratio of the three-periodic minimal surface unit cell in the array structure (6) are variable. Increasing the porosity of the three-periodic minimal surface TPMS unit cell in the array structure (6) to 40%-80% can reduce the shear modulus of the lattice structure, thereby widening the frequency range of vibration isolation. The increased porosity increases the volume proportion of air in the lattice structure, weakens the heat transfer capacity of the lattice structure, reduces the thermal conductivity coefficient of the lattice structure, and achieves a good heat insulation function. Increasing the material damping ratio of the TPMS unit cell in the array structure (6) to 0.1-0.4 can enhance the vibration reduction capacity of the vibration isolation damper in three directions, namely, axial, normal and circumferential directions.

4. The multi-purpose, multifunctional three-way vibration isolation damper according to claim 2, characterized in that: The design method of the array structure (6) is as follows: Step 1: Establish the design equation of the three-periodic minimal surface TPMS unit cell: The three-periodic minimal surface TPMS unit cell in the array structure (6) is composed of a solid body surrounded by a series of surfaces. Its design equation is as follows: Where: ω is the circular frequency, C is the real number that controls the shape of the unit cell, and x, y, and z are the coordinates in the directions of the three perpendicular coordinate axes respectively; Step 2: Determine the parameter C of the three-periodic minimal surface TPMS unit cell based on the known target relative thermal conductivity λ, which is the ratio of the thermal conductivity of the unit cell to the thermal conductivity of the structural steel of the same equivalent volume. The default value ω = 2 in the unit cell design is used to control the unit cell size. The shape of the three-periodic minimal surface TPMS unit cell is controlled by the only parameter C. When the target relative thermal conductivity λ is known, the parameter C is calculated using the following formula: Where: material is the thermal conductivity of the material used in the three-periodic minimal surface TPMS unit cell, λ steel is the thermal conductivity of structural steel, both of which are known parameters; Step 3: Establish a three-periodic minimal surface TPMS unit cell model based on the value of parameter C, calculate the relative thermal conductivity of the three-periodic minimal surface TPMS unit cell, and perform verification; Substitute the value of parameter C into the design equation of the three-periodic minimal surface TPMS unit cell to generate a unit cell model. Use the finite element method (FEM) to simulate the heat conduction process. Calculate the relative thermal conductivity of the unit cell using Fourier's law of heat conduction. Verify that the calculated relative thermal conductivity is less than the target relative thermal conductivity λ. If not, reduce the value of parameter C and repeat step 3 until it is satisfied. Step 4: Calculate the equivalent mechanical parameters of the three-periodic minimal surface TPMS unit cell and design the main parameters of the array structure (6): Substitute the value of the parameter C that meets the heat conduction requirements in step 3 into the design equation of the three-periodic minimal surface TPMS unit cell to obtain the unit cell model. Use the representative volume element method RVE to calculate the equivalent mechanical parameters of the three-periodic minimal surface TPMS unit cell: equivalent elastic modulus E, Poisson's ratio v and shear modulus G. Given the mass M of the vibration isolation object and the target natural frequency f, the main design parameters are the inner diameter r1, outer diameter r2 and lattice structure height h of the array structure (6). These three parameters satisfy the following formula: Step 5: Establish a three-dimensional model of the array structure (6) based on the parameters calculated in step 4, calculate the natural frequency of the array structure, and complete the verification; Based on the parameter C, the inner diameter r1, outer diameter r2 and array structure height h of the array structure (6), a three-dimensional model of the array structure (6) is established, and modal analysis is used to check whether the natural frequency of the vibration isolation damper is less than the target natural frequency f. If it is satisfied, the parameters are usable. If not, the size of the lattice structure height h is adjusted and step 5 is repeated until it meets the requirements.

5. The multi-purpose, multifunctional three-way vibration isolation damper according to claim 2 is characterized in that: The lattice structure (4) adopted by the vibration isolation damper has the following characteristics in terms of vibration isolation frequency band and damping ratio: when the vibration source amplitude increases, the dynamic stiffness of the vibration isolation damper decreases, the resonance peak frequency decreases, and the vibration isolation frequency band becomes wider. At the same time, the structural damping ratio of the vibration isolation damper increases, and the resonance peak value decreases; this characteristic improves the vibration isolation and vibration reduction effect of the vibration isolation damper.

6. The multi-purpose, multifunctional three-way vibration isolation damper according to claim 1, characterized in that: The vibration isolator housing (1), the vibration isolator inner shaft (2) and the additional bracket (3) are all made of high-strength metal materials to provide sufficient supporting capacity; while the lattice structure (4) is made of high-temperature resistant rubber material to enhance the vibration isolation and vibration reduction effects of the vibration isolator.

7. The multi-purpose, multifunctional three-way vibration isolation damper according to claim 1, characterized in that: The vibration isolator housing (1) is in a regular columnar cavity structure as a whole, extending in a vertical direction to form a hollow accommodation space, and is provided with multiple groups of through holes for easy connection with the outside world via bolts.

8. The multi-purpose, multifunctional three-way vibration isolation damper according to claim 1, characterized in that: The additional bracket (3) is an integrated rigid structure in the shape of a rectangular parallelepiped frame, and has a plurality of mutually perpendicular walls, forming a hollow chamber extending in the length direction; a circular through hole is provided at the center of the bottom surface of the additional bracket, the inner diameter of the through hole being adapted to the outer diameter of the inner shaft (2) of the vibration isolator, thereby limiting the displacement of the inner shaft of the vibration isolator; the additional bracket (3) has four auxiliary mounting holes evenly distributed around the circumference of the circular through hole, mainly used to realize the connection function.

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