Inertia amplification superstructure vibration isolator and design method thereof

Abstract

According to the inertia amplification superstructure vibration isolator and the design method thereof, a vibration reduction superstructure is composed of an elastic body and an inertia amplification assembly, a low-frequency band gap can be generated with small mass through the inertia amplification effect, and high stability is achieved; the contradiction between low-frequency broadband vibration reduction and structural bearing, stability and light weight in the design of an existing superstructure (photonic crystal) vibration isolator can be effectively solved, the defect that broadband resonance cannot be restrained in the design of the existing vibration isolator is overcome through the band gap characteristic of the superstructure, and the high engineering application value is achieved.

Description

Technical Field

[0001] The invention relates to the technical field of vibration reduction and noise reduction, in particular to an inertial amplification superstructure vibration isolator and a design method thereof. Background Art

[0002] Ship vibration can cause the hull structure to be in a fatigue state, resulting in cracks or fatigue damage, affecting the safety and reliability of the structure. The radiated noise caused by vibration can also damage the stealth performance of military ships. Vibration isolators are the most commonly used method to reduce vibration transmission. Various engineering applications require vibration isolators to have not only good low-frequency vibration isolation performance, but also the ability to suppress broadband resonance and good stability.

[0003] The lowest natural frequency of the rubber vibration isolation system can be designed to be around 5Hz. Based on the vibration isolation principle alone, the vibration isolation effect can be achieved after crossing the resonance zone. However, it is inevitable to use a variety of elastic components in the vibration isolator. Under medium and high frequency vibration conditions, the massless assumption is no longer met. The vibration propagates in the form of elastic waves, forming a standing wave effect to produce broadband resonance (generally concentrated in the 50-2500Hz frequency band), which seriously reduces the vibration isolation performance of the vibration isolator. Limited by the vibration reduction mechanism, the attenuation of broadband resonance by traditional rubber vibration isolators is relatively limited. Summary of the invention

[0004] In view of the shortcomings of the above-mentioned existing production technology, the applicant provides a rationally structured inertial amplification superstructure vibration isolator and a design method thereof, which utilizes the bandgap characteristics of the superstructure to suppress the propagation of elastic waves within the bandgap frequency range; utilizes the inertial amplification structure to reduce the natural frequency of the structure itself; thereby overcoming the defect that the broadband resonance caused by the standing wave effect in the existing vibration isolator design cannot be suppressed.

[0005] The technical solution adopted by the present invention is as follows:

[0006] An inertia amplification superstructure vibration isolator includes a connection base as an installation reference, an elastic body is superimposed on the connection base, a connection top plate is added on the top of the elastic body, and the connection top plate bears a vibration reduction component.

[0007] Adjacent elastic bodies are limitedly connected with metal clamps, and adjacent metal clamps are movably connected with inertia amplification components.

[0008] Each set of inertial amplification components includes:

[0009] Connecting rod assembly, both ends of the connecting rod assembly are respectively installed on two adjacent metal clamping plates.

[0010] The weight block is installed at the middle hinge point of the connecting rod assembly.

[0011] The angle of the connecting rod assembly changes with the deformation of the elastic body, and the weight block is displaced along with the connecting rod assembly.

[0012] As a further improvement of the above technical solution:

[0013] The metal clamping plate, the connecting top plate and the connecting base are all formed with limiting recesses facing the elastic body, and the limiting recesses limit the displacement of the elastic body in the shear direction.

[0014] The connecting rod assembly comprises two hinged arms which are hinged to each other. The ends of the two hinged arms which are away from each other are respectively rotatably connected to two adjacent metal clamping plates. The weight block is rotatably connected to the middle hinge point of the two hinged arms.

[0015] The shoulder of the weight block is coaxial with the connection point of the same set of hinge arms.

[0016] The inertial amplification components are arranged symmetrically or in an array on the side wall of the vibration isolator.

[0017] The elastic body adopts linear elastic material or nonlinear elastic material.

[0018] The density of the metal splint is less than the density of the weight block.

[0019] A method for designing an inertial amplification superstructure vibration isolator comprises the following steps:

[0020] Step 1: Calculate the dynamic stiffness and static stiffness required for the superstructure vibration isolator based on the weight of the vibration isolation system and the requirements for the natural frequency;

[0021] Step 2: Select the elastic material and plan the main dimensions of the superstructure;

[0022] Step 3: According to the theoretical model of inertial amplification structure, the band gap boundary parameter expression is obtained;

[0023] Step 4: Predict the suppressed broadband resonance frequency based on the band gap boundary expression and structural parameters;

[0024] Step 5: Construct a three-dimensional multi-body dynamics simulation model of the superstructure vibration isolator with hinge joints;

[0025] Step 6: Calculate the vibration transmission characteristics of the superstructure isolator and verify the band gap range and vibration attenuation capability.

[0026] In step 3, the specific process of calculating the dynamic stiffness and static stiffness required by the superstructure isolator is as follows:

[0027] Vertical dynamic stiffness of the entire vibration isolation system:

[0028] K d =(2πf n ) 2 M a , where M a is the total weight of the isolator, fn is the natural frequency,

[0029] Vertical static stiffness of the entire vibration isolation system:

[0030] K s =K d / 1.3.

[0031] In step 3, the band gap boundary parameter expression is:

[0032] The motion equation of the unit cell of the inertial amplification structure is:

[0033] The starting frequency of the periodic structure band gap composed of the inertial amplification structure unit cell is: The band gap range is (f 0 , +∞),

[0034] Where M represents the amplified mass, m represents the mass connected by the spring, γ=cot(θ) represents the cotangent value of the angle θ, k represents the spring stiffness, and u represents the displacement of mass m. represents the acceleration of mass m.

[0035] The beneficial effects of the present invention are as follows:

[0036] The invention has a compact and reasonable structure and is easy to operate. It breaks through the constraint relationship between the low-frequency band gap and the mass of the superstructure based on the inertial amplification mechanism and overcomes the defect that the broadband resonance caused by the standing wave effect in the existing vibration isolator design cannot be suppressed through the band gap characteristics of the superstructure.

[0037] Compared with the prior art, the inertial amplification superstructure vibration isolator disclosed in the present invention uses a hinge structure, a weight block and an elastic body to form a superstructure, which has better stability. The introduction of the inertial amplification structure can produce medium and low frequency band gaps with a small mass, overcoming the defect that the broadband resonance cannot be suppressed in the existing vibration isolator design. The above-mentioned vibration isolator disclosed in the present invention has a simple elastic bearing part structure, and the band gap frequency range can be adjusted by replacing the additional inertial amplification component to effectively meet different vibration reduction and isolation requirements. BRIEF DESCRIPTION OF THE DRAWINGS

[0038] Figure 1 It is a three-dimensional schematic diagram of the inertial amplification superstructure vibration isolator in the preferred embodiment of the present invention.

[0039] Figure 2 It is a cross-sectional view of the load-bearing body part passing through the center of the vibration isolator.

[0040] Figure 3 This is an exploded assembly view of the inertia amplification component.

[0041] Figure 4(a) is a rotational partial cross-sectional view of the articulated joint assembly.

[0042] FIG4( b ) is a rotated partial cross-sectional view of the articulated joint assembly from another perspective.

[0043] Figure 5 Schematic diagram of the theoretical model of inertia-amplifying superstructure vibration isolator.

[0044] FIG6( a ) is a three-dimensional multi-body dynamics simulation model of the inertial amplification superstructure vibration isolator.

[0045] FIG6( b ) is a schematic diagram of the articulated joint setting, taking an upper hinge arm as an example.

[0046] Figure 7(a) is a curve showing the change of band gap starting frequency with angle.

[0047] Figure 7(b) is a comparison of the transmission characteristic curves of the inertial amplification superstructure isolator at different angles.

[0048] Figure 8(a) is a nephogram of the vibration response of the inertial amplified superstructure isolator at 475 Hz.

[0049] Figure 8(b) is a nephogram of the vibration response of the inertial amplified superstructure isolator at 1686 Hz.

[0050] Figure 9(a) is a comparison of the vibration isolation curves of the inertial amplification superstructure isolator and the equal stiffness rubber block under no load.

[0051] Figure 9(b) is a comparison of the vibration isolation curves of the inertia amplification superstructure isolator and the equal stiffness rubber block under rated load.

[0052] Among them: 1. Connecting base; 2. Elastic body; 3. Inertial amplification component; 4. Metal clamping plate; 5. Connecting top plate;

[0053] 101, seat plate through hole; 102, upper surface limiting groove;

[0054] 301, weight block; 302, lower hinge arm; 303, upper hinge arm; 304, nut; 305, plug bolt; 306, outer hinge base; 307, inner hinge base;

[0055] 3011, shaft shoulder; 3012, threaded shaft;

[0056] 3021, lower hinge external threaded hole; 3022, lower hinge internal threaded hole; 3023, lower hinge through hole;

[0057] 3031, upper hinge outer through hole; 3032, upper hinge inner through hole; 3033, upper hinge bottom through hole;

[0058] 3051, plug bolt rod body; 3052, plug bolt thread section;

[0059] 3061, threaded hole of external hinge base;

[0060] 3071, inner hinge base through hole;

[0061] 401, limit slot;

[0062] 501, mounting hole; 502, positioning groove. DETAILED DESCRIPTION

[0063] The specific implementation of the present invention is described below in conjunction with the accompanying drawings.

[0064] like Figure 1 As shown, the inertia amplification superstructure vibration isolator of this embodiment includes a connection base 1 as a mounting base, an elastic body 2 is superimposed on the connection base 1, a connection top plate 5 is added on the top of the elastic body 2, and the connection top plate 5 receives the vibration damping member.

[0065] Metal clamping plates 4 are connected between adjacent elastic bodies 2, and inertia amplification components 3 are movably connected between adjacent metal clamping plates 4.

[0066] Each set of inertial amplification components 3 includes:

[0067] The connecting rod assembly, both ends of which are respectively mounted on two adjacent metal clamping plates 4,

[0068] The weight block 301 is installed at the middle hinge point of the connecting rod assembly.

[0069] The angle of the connecting rod assembly changes with the deformation of the elastic body 2, and the weight block 301 is displaced along with the connecting rod assembly.

[0070] The metal clamping plate 4 , the connecting top plate 5 , and the connecting base 1 are all formed with limiting recesses facing the elastic body 2 , and the limiting recesses limit the displacement of the elastic body 2 in the shear direction.

[0071] The connecting rod assembly includes two hinged arms hinged to each other, and the ends of the two hinged arms that are away from each other are rotatably connected to two adjacent metal clamping plates 4 respectively; the weight block 301 is rotatably connected to the middle hinge point of the two hinged arms.

[0072] The shoulder 3011 of the weight block 301 is coaxial with the connection point of the same set of hinge arms.

[0073] The inertial amplification components 3 are arranged symmetrically or in an array on the side wall of the vibration isolator.

[0074] The elastic body 2 is made of linear elastic material or nonlinear elastic material.

[0075] The density of the metal clamping plate 4 is lower than the density of the weight block 301 .

[0076] The method for designing an inertia amplification superstructure vibration isolator of this embodiment includes the following steps:

[0077] Step 1: Calculate the dynamic stiffness and static stiffness required for the superstructure vibration isolator based on the weight of the vibration isolation system and the requirements for the natural frequency;

[0078] Step 2: Select the material of the elastic body 2 and plan the main dimensions of the superstructure;

[0079] Step 3: According to the theoretical model of inertial amplification structure, the band gap boundary parameter expression is obtained;

[0080] Step 4: Predict the suppressed broadband resonance frequency based on the band gap boundary expression and structural parameters;

[0081] Step 5: Construct a three-dimensional multi-body dynamics simulation model of the superstructure vibration isolator with hinge joints;

[0082] Step 6: Calculate the vibration transmission characteristics of the superstructure isolator and verify the band gap range and vibration attenuation capability.

[0083] The specific structure and working principle of the present invention are as follows:

[0084] like Figure 1 , Figure 2 and Figure 3 Shown are a stereoscopic view, a cross-sectional view and an exploded view of the elastic structure of the inertia amplification superstructure vibration isolator of the present invention.

[0085] like Figure 1 and Figure 2 As shown, the connection base 1 is used as the installation reference surface, and a seat plate through hole 101 is opened on the connection base 1. The seat plate through hole 101 provides an installation point for installing the vibration isolator at a specified position; a limit groove 102 is opened on the upper surface of the connection base 1, and the limit groove 102 is a sunken groove, and the elastic body 2 falls into the limit groove 102. If multiple elastic bodies 2 are to be installed, they can be stacked and installed upward, and a metal clamping plate 4 is set between adjacent elastic bodies 2. The top and bottom surfaces of the metal clamping plate 4 are both concavely set to form a limit groove 401 for adapting to the upper and lower layers of elastic bodies 2. The limit grooves 401 on both sides are alternately arranged and bonded with the elastic bodies 2 to form a periodic structure.

[0086] Combined with reference Figure 3 An inertia amplification component 3 is arranged around the elastic body 2, and the inertia amplification component 3 is periodically connected between adjacent metal clamping plates 4.

[0087] Each inertia amplification assembly 3 includes an outer hinge base 306 and an inner hinge base 307 mounted on the metal clamping plate 4. The outer hinge base 306 and the inner hinge base 307 are connected by a plug bolt 305 to form a mounting point. An upper hinge arm 303 is rotatably connected to each mounting point. The end of the upper hinge arm 303 away from the mounting point is rotatably connected to the lower hinge arm 302. The lower end of the lower hinge arm 302 is rotatably connected to the mounting point on the adjacent metal sandwich 4.

[0088] The specific structure is:

[0089] A mounting point is set at each end of the same side wall of the same metal clamping plate 4. Figure 1 In the direction of the top metal clamp plate 4, for example, two mounting points are set on each of the four side walls of the metal clamp plate 4, for a total of eight mounting points. An upper hinge arm 303 is hinged between each mounting point, and eight mounting points are also set on the second layer of metal clamp plate 4 from top to bottom, and an upper hinge arm 303 and a lower hinge arm 302 are installed on each mounting point; the lower hinge arm 302 on the second layer of metal clamp plate 4 is rotatably connected to the upper hinge arm 303 on the first layer of metal clamp plate 4, and the threaded shaft 3012 at both ends of the weight block 301 passes through the connection point.

[0090] The weight block 301 is a cylinder, and the two ends are coaxially formed with threaded shafts 3012. The threaded shaft 3012 is threadedly matched with the lower hinge internal threaded hole 3022 and the lower hinge external threaded hole 3021 of the lower hinge arm 302 to limit the position.

[0091] The upper hinge bottom through hole 3033 of the upper hinge arm 303 is penetrated on the threaded shaft 3012 and rotates relative to the threaded shaft 3012. The shaft shoulders 3011 at both ends of the weight block 301 are limited by the hinge arms on both sides.

[0092] The upper hinge arm 303 is provided with an upper hinge inner through hole 3032 and an upper hinge outer through hole 3031 , and a driving bolt 305 penetrates the upper hinge inner through hole 3032 , the upper hinge outer through hole 3031 , the outer hinge base 306 , and the inner hinge base 307 , so that the upper hinge arm 303 can rotate around the driving bolt 305 .

[0093] The lower hinge arm 302 has a lower hinge through hole 3023 , and the lower hinge through hole 3023 is limited by the corresponding plug bolt 305 and the hinge base, so that the lower hinge arm 302 can rotate around the corresponding plug bolt 305 .

[0094] At this point, a complete inertia amplification assembly 3 is obtained, that is, it includes a set of two hinge arms set at an angle in the same plane, and a follower weight block 301 located at the hinge point between the two hinge arms. When subjected to external force and the elastic body 2 is deformed, the elastic body 2 itself provides elastic support and a certain vibration isolation and damping effect, and the angle between the two hinge arms changes accordingly, and the weight block 301 moves with the displacement of the hinge point.

[0095] The weight block 301 is fastened to the lower hinge external threaded hole 3021 and the nut 304 through the threaded shaft 3012, and there is no relative rotation between the weight block 301 and the lower hinge arm 302. The shaft shoulder 3011 of the weight block 301 and the upper hinge bottom through hole 3033 of the upper hinge arm 303 form a clearance fit to ensure flexible rotation between the weight block 301 and the upper hinge arm 303.

[0096] The connection between the shoulder 3011 of the weight block 301 and the upper hinge arm 303 and the lower hinge arm 302 must be on the same axis to ensure that no additional degrees of freedom are introduced into the additional inertia amplification component 3. In addition, in order to avoid friction caused by interference between the moving parts during vibration, the width of the hinge arm is slightly smaller than the distance between the inner and outer hinge bases 307 and the outer hinge base 306, and the length of the shoulder 3011 of the weight block 301 is slightly larger than the width of the hinge arm.

[0097] In one embodiment of the present invention, the height of the elastic body 2 is greater than twice the depth of the limiting groove 401 .

[0098] In order to facilitate the reception of vibration-damping parts, a connecting top plate 5 is added to the top elastomer 2. The connecting top plate also has a mounting hole 501 for connecting to an external vibration-isolated object, and the side of the connecting top plate 5 facing the elastomer 2 is concave to form a positioning groove 502 for limiting connection with the elastomer 2.

[0099] The limiting groove 401 and the positioning groove 502 are both used to limit the shearing movement of the elastic body 2 .

[0100] See FIG4 for a partial cross-sectional view of the rotation of the two articulated joint assemblies between the hinge arm and the hinge base and between the hinge arm and the weight block.

[0101] The plug bolt threaded section 3052 of the plug bolt 305 passes through the inner hinge base through hole 3071 and the outer hinge base threaded hole 3061, and is fastened with the nut 304. The outer hinge base 306 is provided with the threaded hole 3061 to make the connection tight and not easy to loosen.

[0102] The rod body 3051 of the plug bolt forms a clearance fit with the lower hinge through hole 3023 of the lower hinge arm 302 or the upper hinge outer through hole 3031 and the lower hinge outer threaded hole 3021 of the upper hinge arm 303 to ensure flexible movement of the joint.

[0103] The elastic body 2 can be made of linear or nonlinear elastic materials such as springs with elastic restoring force, folded elastic sheets, polymer rubber, foam materials, polyurethane or metal rubber.

[0104] When the elastomer 2 is made of linear elastic material, the superstructure isolator is linear; when it is made of nonlinear material, the superstructure isolator is nonlinear. The linear isolator has a low natural frequency of vibration isolation, and can achieve a vibration isolation effect after crossing the resonance zone; on this basis, the stiffness of the nonlinear isolator increases with the increase in compression, and can maintain a small deformation under large dynamic loads. Preferably, for linear isolators, the elastomer 2 can be made of polymer rubber, foam material or spring; for nonlinear isolators, the elastomer can be made of metal rubber material.

[0105] See also Figure 1 Preferably, the connecting base 1, the metal clamping plate 4, the elastic body 2 and the bearing platform 5 are all square structures, which are convenient for connection with the inertial amplification component 3, and the weight block 301 is a rotating body, which is convenient for processing; in this embodiment, the weight block 301 is a cylinder.

[0106] Two adjacent metal clamps 4, an elastic body 2 located between the two metal clamps 4, and four groups of inertia amplification components 3 arranged around the metal clamps 4 form a set of superstructure cells. Preferably, the number of superstructure cells in a shock absorber is greater than or equal to 3.

[0107] The metal clamping plate 4, the connecting base 1, the connecting top plate 5, the upper hinge arm 303 and the lower hinge arm 302 are made of light metals such as aluminum alloy or titanium alloy, and the weight block 301 is made of a material with a higher density such as stainless steel or copper.

[0108] In addition, the present invention provides a method for designing an inertial amplification superstructure vibration isolator, which will be described below in conjunction with a specific preferred embodiment.

[0109] Select rated load 200kg, total weight of vibration isolation system M a is 203.62kg, and the natural frequency is f n is 16Hz. Therefore, the vertical dynamic stiffness K of the entire vibration isolation system is d =(2πf n ) 2 M a =2058N / mm.

[0110] Rubber is a widely used vibration reduction and isolation material in engineering. Preferably, the elastomer in the embodiment is chloroprene rubber with good elasticity, Young's elastic modulus of 2MPa at small deformation, and density of 1000kg / m 3, Poisson's ratio is 0.47, and loss factor is 0.04. Rubber elastic body has viscoelasticity and shows viscoelastic hysteresis to dynamic load. Therefore, the dynamic-static stiffness ratio of the vibration isolator using rubber as the elastic body is greater than 1.

[0111] According to experience, under alternating loads, the dynamic-static stiffness ratio of rubber is in the range of 1.2-1.5. The closer the dynamic-static ratio is to 1, the better the vibration transmission performance is. Here, the dynamic-static stiffness ratio is selected as 1.3. Therefore, the vertical static stiffness of the entire vibration isolation system is K s =K d / 1.3=1583N / mm. If the height of the vibration isolator is too high, the shear stiffness of the structure will be reduced, and bending instability will easily occur under the action of large loads. Considering the stability of the structure, as a preferred solution, the lateral dimension of the vibration isolator should not be less than the effective height of the rubber vibration isolator.

[0112] See also Figure 5 The theoretical model of the inertia amplification superstructure vibration isolator consists of three inertia amplification structure units, and the motion equation of the inertia amplification structure unit cell is: Where M represents the amplified mass, m represents the mass connected by the spring, γ=cot(θ) represents the cotangent value of the angle θ, k represents the spring stiffness, and u represents the displacement of mass m. represents the acceleration of mass m.

[0113] The starting frequency of the band gap of the periodic structure composed of the above-mentioned inertial amplification structure unit cell is: The band gap range is (f 0 , +∞).

[0114] From the equation of motion and the band gap boundary parameter expression, it can be seen that the mass M in the inertial term can be magnified by γ 2 times, increasing the mass M is more beneficial to reducing the natural frequency of the structure and reducing the band gap range.

[0115] Preferably, the mass block in the embodiment is made of 304 stainless steel with a high density, a Young's modulus of elasticity of 200 MPa, and a density of 8000 kg / m 3 , Poisson's ratio is 0.33; the metal plate should be made of materials with greater rigidity as much as possible to avoid bending deformation in the mid-frequency band that affects the effect of the vibration isolator. At the same time, considering the lightweight of the vibration isolator, the metal plate and hinge arm are made of titanium alloy, with a Young's elastic modulus of 120MPa and a density of 4500kg / m 3 , Poisson's ratio 0.33.

[0116] Referring to Figure 6(a), the finite element model of the superstructure vibration isolator was established using finite element software. In order to divide the high-quality grid, the components and details such as the plug bolt 305, nut 304, thread and screw hole were removed. Figure 6(b) shows the hinge joint setting between an upper hinge arm and a hinge base in the simulation model. Through the multi-body dynamics physics field, the inner surface of the through hole of the hinge base is set as connector one, and the inner surface of the through hole of the upper hinge arm is set as connector two. A hinge joint is set between connector one and connector two, and the hinge axis points to the axial direction of the hole. Based on the multi-body dynamics simulation model constructed above, the vibration transmission characteristics of the superstructure vibration isolator are calculated. In the simulation, a vertical load is applied to the metal plate at the lower end of the vibration isolator, and the displacement output of the metal plate at the upper end of the vibration isolator is picked up. From this, the vibration transmission rate of the vibration isolator can be calculated as η=20log 10 |U 2 / U 1 |,U 1 represents the average displacement of the probe on the lower metal plate surface, U 2 Represents the average displacement of the probe on the upper metal plate surface.

[0117] The design parameters make the mass of a single metal plate m 1 =0.4kg, mass of a single weight block m 2 =0.144kg. Finite element calculation shows that the overall stiffness of the superstructure isolator in the embodiment is 1661N / mm, so the stiffness of a single rubber elastic body is 4983N / mm. Therefore, in the theoretical model, k = 4983N / mm, m = m 1 , M = 2m 2 . According to the band gap starting frequency estimation formula proposed above, Figure 7(a) shows the curve of the band gap starting frequency changing with γ. Among them, when the angle θ in the inertial amplification component is 30° (γ=1.73), 20° (γ=2.75) and 15° (γ=3.73), the band gap starting frequencies are 345Hz, 231Hz and 173Hz respectively. It can be seen that the angle θ determines the effect of the inertial amplification mechanism. The smaller the angle θ, the more obvious the inertial amplification effect.

[0118] The vibration transmission characteristics of the superstructure isolator at the above three angles are shown in Figure 7(b). The band gap starting frequency is basically consistent with Figure 7(a), but there is an obvious vibration peak at around 1650Hz, which makes it difficult to further show the vibration reduction effect. In addition, when the band gap starting frequency appears in a lower frequency range, the band gap width becomes narrower and the vibration attenuation ability is reduced. The displacement response cloud diagram corresponding to 475Hz and 1686Hz in the transmission characteristic curve of the inertial amplification superstructure isolator when θ=30° is shown in Figure 8, which are the frequencies with the largest vibration attenuation amplitude within the band gap range and the resonance peak frequency near 1650Hz mentioned above.

[0119] The displacement response of the superstructure isolator in Figure 8(a) has obvious inertial amplification structural motion characteristics. The vertical movement of the metal clamp plate 4 causes a larger displacement of the weight block 301 through the hinge. Figure 8(b) shows that the resonance peak at 1686Hz is caused by the bending mode of the metal clamp plate 4, resulting in a decrease in the vibration reduction effect. The vibration suppression range can be further widened by selecting a material with a larger Young's model.

[0120] Figure 9(a) and Figure 9(b) compare and analyze the vibration transmission characteristics of the inertia-amplified superstructure vibration isolator and the equal-stiffness rubber block under no load and rated load, respectively. It can be seen that the superstructure vibration isolator produces a highly efficient vibration suppression effect in the range of 350Hz-1650Hz. The vibration transmissibility of the inertia-amplified superstructure vibration isolator under no load is reduced by an average of 16.5dB compared with the equal-stiffness rubber block, and the vibration transmissibility of the inertia-amplified superstructure vibration isolator under rated load is reduced by an average of 13.2dB compared with the equal-stiffness rubber block, which has the effect of suppressing broadband resonance.

[0121] The above description is an explanation of the present invention, not a limitation of the present invention. The scope of the present invention is defined in the claims. Any form of modification may be made within the scope of protection of the present invention.

Claims

1. An inertial amplification superstructure vibration isolator, characterized in that: The invention comprises a connection base (1) as a mounting base, an elastic body (2) is superimposed on the connection base (1), a connection top plate (5) is installed on the top of the elastic body (2), and the connection top plate (5) receives a vibration damping component. A metal clamping plate (4) is provided between adjacent elastic bodies (2) to limit the connection, and an inertia amplification component (3) is movably connected between adjacent metal clamping plates (4). Each set of inertial amplification components (3) includes: The connecting rod assembly has two ends mounted on two adjacent metal clamping plates (4). The weight block (301) is mounted at the middle hinge point of the connecting rod assembly. The angle of the connecting rod assembly changes with the deformation of the elastic body (2), and the weight block (301) is displaced along with the connecting rod assembly.

2. The inertial amplification superstructure vibration isolator according to claim 1, characterized in that: The metal clamping plate (4), the connecting top plate (5) and the connecting base (1) are all formed with limiting recesses facing the elastic body (2), and the limiting recesses limit the displacement of the elastic body (2) in the shear direction.

3. The inertial amplification superstructure vibration isolator according to claim 1, characterized in that: The connecting rod assembly comprises two hinged arms hinged to each other, and the ends of the two hinged arms which are away from each other are rotatably connected to two adjacent metal clamping plates (4) respectively; the weight block (301) is rotatably connected at the middle hinge point of the two hinged arms.

4. The inertial amplification superstructure isolator according to claim 4, characterized in that: The shoulder (3011) of the weight block (301) is coaxial with the connection point of the same set of hinge arms.

5. The inertial amplification superstructure vibration isolator according to claim 1, characterized in that: The inertia amplification components (3) are arranged symmetrically or in an array on the side wall of the vibration isolator.

6. The inertial amplification superstructure isolator according to claim 1, characterized in that: The elastic body (2) is made of linear elastic material or nonlinear elastic material.

7. The inertial amplification superstructure vibration isolator according to claim 1, characterized in that: The density of the metal clamping plate (4) is less than the density of the weight block (301).

8. A method for designing the inertial amplification superstructure vibration isolator according to claim 1, characterized in that: The steps include: Step 1: Calculate the dynamic stiffness and static stiffness required for the superstructure vibration isolator based on the weight of the vibration isolation system and the requirements for the natural frequency; Step 2: Select the material of the elastic body (2) and plan the main dimensions of the superstructure; Step 3: According to the theoretical model of inertial amplification structure, the band gap boundary parameter expression is obtained; Step 4: Predict the suppressed broadband resonance frequency based on the band gap boundary expression and structural parameters; Step 5: Construct a three-dimensional multi-body dynamics simulation model of the superstructure vibration isolator with hinge joints; Step 6: Calculate the vibration transmission characteristics of the superstructure isolator and verify the band gap range and vibration attenuation capability.

9. The design method according to claim 8, characterized in that: In step 3, the specific process of calculating the dynamic stiffness and static stiffness required by the superstructure isolator is as follows: Vertical dynamic stiffness of the entire vibration isolation system: K d =(2πf n ) 2 M a , where M a is the total weight of the isolator, f n is the natural frequency, Vertical static stiffness of the entire vibration isolation system: K s =K d / 1.3。 10. The design method according to claim 8, characterized in that: In step 3, the band gap boundary parameter expression is: The motion equation of the unit cell of the inertial amplification structure is: The starting frequency of the periodic structure band gap composed of the inertial amplification structure unit cell is: The band gap interval is (f0, +∞), Wherein, M represents the amplified mass, m represents the mass connected by the spring, γ=cot(θ) represents the cotangent value of the angle θ, k represents the spring stiffness, u represents the displacement of mass m, and ü represents the acceleration of mass m.

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