CN116201837B - Three-dimensional vibration reduction structure with nonlinear rigidity and vibration reduction device - Google Patents
Three-dimensional vibration reduction structure with nonlinear rigidity and vibration reduction deviceInfo
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- CN116201837B CN116201837B CN202310152626.3A CN202310152626A CN116201837B CN 116201837 B CN116201837 B CN 116201837B CN 202310152626 A CN202310152626 A CN 202310152626A CN 116201837 B CN116201837 B CN 116201837B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F7/00—Vibration-dampers; Shock-absorbers
- F16F7/12—Vibration-dampers; Shock-absorbers using plastic deformation of members
- F16F7/123—Deformation involving a bending action, e.g. strap moving through multiple rollers, folding of members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/08—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with rubber springs ; with springs made of rubber and metal
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2224/00—Materials; Material properties
- F16F2224/02—Materials; Material properties solids
- F16F2224/025—Elastomers
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- Aviation & Aerospace Engineering (AREA)
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Abstract
本发明公开了一种具有非线性刚度的三维减振结构及减振装置，其中的三维减振结构包括上端面、下端面和减振结构；所述上端面和所述下端面同轴设置；所述减振结构包括多根弹性弯杆，多根弹性弯杆沿着所述上端面和所述下端面的轴心的连线呈圆周排列；所述弹性弯杆的横截面为月牙形截面；当三维减振结构压缩时，产生非线性几何刚度；非线性刚度可以通过杆件的多种结构参数灵活调整，从而根据减振要求设计三维减振结构，得益于刚度非线性特性，结构的减振性能有效提高。本发明还公开一种减振装置，所述减振装置弥补了现有非线性刚度减振装置的不足，为非线性刚度减振装置的设计、分析和应用开辟了全新的方向。
This invention discloses a three-dimensional vibration damping structure and device with nonlinear stiffness. The three-dimensional vibration damping structure includes an upper end face, a lower end face, and a damping structure. The upper end face and the lower end face are coaxially arranged. The damping structure includes multiple elastic bending rods arranged circumferentially along the line connecting the axes of the upper end face and the lower end face. The cross-section of each elastic bending rod is crescent-shaped. When the three-dimensional vibration damping structure is compressed, nonlinear geometric stiffness is generated. The nonlinear stiffness can be flexibly adjusted through various structural parameters of the rods, thereby allowing for the design of the three-dimensional vibration damping structure according to vibration requirements. Benefiting from the nonlinear stiffness characteristics, the vibration damping performance of the structure is effectively improved. This invention also discloses a damping device that overcomes the shortcomings of existing nonlinear stiffness damping devices, opening up a new direction for the design, analysis, and application of nonlinear stiffness damping devices.
Description
Technical Field
The invention relates to the technical field of passive vibration control, in particular to a three-dimensional vibration reduction structure with nonlinear rigidity and a vibration reduction device.
Background
Vibration is a problem in many engineering and manufacturing fields, and in general, vibration is considered as a detrimental factor, which affects the working performance of mechanical equipment, accelerates local harmful wear, and shortens the service life of the equipment. Therefore, it is particularly important to reduce the damage caused by vibration, and vibration control has been a key problem not negligible in the engineering field.
Vibration control generally refers to the dynamic response or dynamic instability of the control system, thereby limiting the amplitude to an allowable range. Methods of controlling vibration are largely classified into active control and passive control. The active control method has the characteristic of being capable of being adjusted in real time through an algorithm according to the actual condition of excitation, and is applied to many engineering practices at present. However, the active control system is complex in technical structure, high in manufacturing cost, difficult to maintain and requires external energy support. In contrast, passive vibration control avoids the above drawbacks, with certain advantages.
Classical passive vibration control employs a linear vibration damping system, however, linear systems have significant limitations in practical applications. In order to solve the problem, a nonlinear vibration reduction system is developed in recent years, wherein the nonlinear rigidity system is an important research content of vibration control direction, and the nonlinear vibration reduction system is mainly characterized in that the rigidity of the system shows nonlinear change along with displacement change, and excellent vibration reduction effect is realized by utilizing the beneficial nonlinear rigidity change. The nonlinear vibration damping structure has wide application prospect in various key fields such as precision instrument manufacturing, aerospace, automobile manufacturing and the like.
Although the existing nonlinear stiffness vibration damper can reduce the natural frequency of a system, improve the vibration damping performance and inhibit resonance, some unresolved problems exist. Firstly, the force transmission of the vibration damper needs a complex transmission mechanism, so that the size and the weight of the vibration damper are large, and the vibration damper cannot be applied to vibration damper occasions with high requirements on size and weight, such as precision instruments, aerospace and the like. In addition, most parts of the vibration damping device are usually connected by bolts or hinges, and small gaps exist between the parts, so that the vibration damping device cannot effectively damp vibration with small amplitude.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide the three-dimensional vibration reduction structure with nonlinear rigidity, and the three-dimensional vibration reduction structure can be flexibly combined and has wide application range.
The second object of the present invention is to provide a vibration damper with a three-dimensional vibration damper structure with nonlinear stiffness, which overcomes the shortcomings of the existing nonlinear stiffness vibration damper, and opens up a new direction for the design, analysis and application of the nonlinear stiffness vibration damper.
The technical scheme for solving the problems in the prior art is as follows:
the three-dimensional vibration reduction structure with the nonlinear rigidity comprises an upper end face, a lower end face and a vibration reduction structure arranged between the upper end face and the lower end face, wherein the upper end face and the lower end face are coaxially arranged, the vibration reduction structure comprises a plurality of elastic bending rods which are circumferentially arranged along a connecting line of axes of the upper end face and the lower end face, the cross section of each elastic bending rod is a crescent section, and when the upper end face or the lower end face is loaded, the vibration reduction structure is compressed and deformed to generate the nonlinear rigidity.
Preferably, the concave direction of the elastic bending rod is towards the connecting line of the axle centers of the upper end face and the lower end face.
Preferably, the concave of the elastic bending rod is opposite to the connecting line of the axle centers of the upper end face and the lower end face.
Preferably, a major circle and a minor circle in the cross section of the elastic bent rod are intersected to form a minor arc and a major arc, wherein two end points of the minor arc and the major arc are connected and concave to be consistent, so that the crescent-shaped cross section is formed.
Preferably, the guide line of the elastic bent rod in the length direction is a two-dimensional curve, and is represented by a hyperbolic function or a trigonometric function.
Preferably, the upper end face, the lower end face and the vibration reduction structure are all manufactured through integral molding by a 3D printing technology, wherein a thermoplastic polyurethane elastomer is adopted as a material in the 3D printing technology.
The vibration damper comprises m vibration damper modules and m+1 connecting plates, wherein m is a positive integer, the m+1 connecting plates are coaxially and equidistantly arranged, each vibration damper module is respectively arranged between two adjacent connecting plates, and each vibration damper module is formed by connecting a plurality of three-dimensional vibration damper structures with nonlinear rigidity in parallel.
Preferably, the plurality of three-dimensional vibration reduction structures are arranged in a matrix or in a circumference between two adjacent groups of connecting plates.
Preferably, two adjacent groups of connecting plates respectively form an upper end face and a lower end face in the three-dimensional vibration reduction structure.
Preferably, the connecting plate is flat, circular or cylindrical.
Compared with the prior art, the invention has the following beneficial effects:
1. The invention produces the three-dimensional vibration damping structure with nonlinear rigidity, and the vibration damping device with nonlinear rigidity makes up the defect of the existing nonlinear rigidity. The vibration damping element made of the material has the advantages of small volume, light weight, no hinge clearance, no need of lubrication, high motion precision and the like, can meet the requirements of small size, low weight and high reliability in vibration damping scenes, and provides an innovative scheme for the design of nonlinear rigidity.
2. The cross section of the elastic bent rod is crescent, and compared with the rectangular cross section bent rod and the round cross section bent rod, the force-displacement curve of the crescent cross section bent rod has stronger nonlinearity, namely, the crescent cross section bent rod has higher rigidity in the early stage of compression and has lower rigidity in the later stage of compression. The stronger nonlinear stiffness enables the structure to provide greater load carrying capacity and more excellent vibration damping performance over an operating range.
3. Compared with the traditional vibration damping element, the vibration damping element with nonlinear rigidity is adopted, so that lower natural frequency and excellent broadband vibration damping effect can be realized, and resonance can be effectively restrained.
4. The invention has wide application range, and can be applied to the fields of development and design of vibration damping elements of precise instruments with special requirements on size, weight and reliability, such as precise instruments, aerospace, and the like, such as unmanned aerial vehicle holder, optical vibration damping table, photoetching machine vibration damping, and the like. In addition, the invention has the advantages of simple structure, small volume, light weight, no hinge gap, no need of lubrication, high motion precision, simple installation and use, low running cost and the like, and can realize excellent (optimal) broadband vibration reduction and resonance suppression effects in a narrow space.
5. The three-dimensional vibration reduction structure provided by the invention can be prepared by preparation processes such as a 3D printing technology, so that batch production is realized, the production cost can be effectively reduced, the production efficiency is improved, the material waste is greatly reduced, and obvious economic and social benefits are realized.
6. The three-dimensional vibration reduction structures can be combined into modules with specific rigidity coefficients and shapes in parallel, series and the like, and the modules can be mutually combined again to form the vibration reduction device so as to adapt to different engineering application scenes.
7. The three-dimensional vibration damping structure with nonlinear stiffness can be manufactured into vibration damping devices with different shapes (gaskets, bushings, suspensions, supports, etc.) from a plurality of different base materials (metals, rubbers, etc.).
Drawings
Fig. 1 is a perspective view of a three-dimensional vibration damping structure with nonlinear stiffness of the present invention in embodiment 1.
Fig. 2 is a front view of the three-dimensional vibration damping structure with nonlinear stiffness of the present invention in embodiment 1.
FIG. 3 is a schematic view of an elastic flexure of the vibration damping structure of FIG. 1.
Fig. 4 is an enlarged view at a in fig. 3.
Fig. 5 is a front view of the crescent-shaped cross-section of fig. 4.
Fig. 6 is a schematic diagram of the compression deformation of the three-dimensional vibration damping structure with nonlinear stiffness of the present invention in embodiment 1.
Fig. 7 is a perspective view of a three-dimensional vibration damping structure with nonlinear stiffness according to the present invention in embodiment 2.
Fig. 8 is a perspective view of a three-dimensional vibration damping structure with nonlinear stiffness of the present invention in embodiment 3.
Fig. 9 is a schematic structural view of a vibration damping device of the present invention in embodiment 4.
Fig. 10 is a schematic structural view of a vibration damping device of the present invention in embodiment 5.
Fig. 11 is a schematic structural view of a vibration damping device of the present invention in embodiment 6.
Fig. 12 is a schematic structural view of a vibration damping device of the present invention in embodiment 7.
Fig. 13 is a schematic structural view of a vibration damping device of the present invention in embodiment 8.
Fig. 14 is a schematic structural view of a vibration damping device of the present invention in embodiment 9.
Fig. 15 is a perspective view of the gasket in embodiment 10.
Fig. 16 is a perspective view of the bushing in example 11.
Fig. 17 is a schematic structural view of a vibration damping element having nonlinear stiffness.
FIG. 18 is a graph of a kinetic model of a vibration damping element having nonlinear stiffness.
Fig. 19 is a graph of theoretical and calculated displacement transmissibility values for a vibration damping element.
FIG. 20 is a stress cloud before and after deformation of an elastic bent rod.
FIG. 21 is a stress cloud before and after deformation of a crescent section at the midpoint of an elastic bent rod.
Fig. 22 is a force versus displacement curve comparison for different cross-sectional shapes.
The damping device comprises a 1-upper end face, a 2-lower end face, a 3-elastic bent rod, a 4-vibration damping structure, a 5-outer convex face of the elastic bent rod, a 6-inner concave face of the elastic bent rod, a 7-crescent section, an 8-small circular arc, a 9-large circular arc, a 10-three-dimensional vibration damping structure before compression, a 11-three-dimensional vibration damping structure after compression, a 12-middle end face, a 13-outer end face, a 14-inner end face, a 15-load mass, a 16-base, a 17-nonlinear elastic force and a 18-hysteresis damping force.
Detailed Description
The present invention will be described in further detail with reference to examples and drawings, but embodiments of the present invention are not limited thereto.
Example 1
Referring to fig. 1-6, the three-dimensional vibration damping structure with nonlinear rigidity provided in this embodiment includes an upper end surface 1, a lower end surface 2 and a vibration damping structure 4, wherein the vibration damping structure 4 is disposed between the upper end surface 1 and the lower end surface 2 in a length direction (i.e., an up-down direction in fig. 2), the vibration damping structure 4 is composed of four elastic bending rods 3, a connecting line of each elastic bending rod 3 facing to an axis of the upper end surface 1 and the lower end surface 2 in a concave direction, and the connecting lines of the upper end surface 1 and the axis of the lower end surface 2 of the plurality of elastic bending rods 3 are uniformly distributed circumferentially.
Referring to fig. 1 to 6, the guide line of the bending bar 3 in the length direction is a two-dimensional curve, which is represented by a trigonometric function.
The cross section of the bent rod 3 is in a crescent shape, wherein a big circle and a small circle in the cross section are intersected to form a small circular arc 8 and a big circular arc 9, two end points of the small circular arc 8 and the big circular arc 9 are connected and concave to be consistent, so that a crescent cross section 7 is formed, the length of the two end points of the small circular arc 8 or the big circular arc 9 is the width of the crescent cross section 7, and the length of the bottommost end of the small circular arc 8 and the bottommost end of the big circular arc 9 is the thickness of the crescent cross section 7.
Referring to fig. 1 to 6, the upper end surface 1, the lower end surface 2 and the vibration damping structure 4 are all integrally formed by a 3D printing technology, wherein a thermoplastic polyurethane elastomer is adopted as a material for the 3D printing technology.
Referring to fig. 6 and 20, when the upper end surface 1 is compressed by a load, a relative displacement occurs between the upper end surface 1 and the lower end surface 2, and an external force is transmitted to the vibration damping structure 4, so that the elastic bending rod 3 is bent and deformed. In the deformation process, as the guide line of the elastic bending rod 3 is a trigonometric function and the cross section shape of the guide line is a crescent shape, the curvature of the middle part of the elastic bending rod 3 is obviously reduced, the stress is larger, the curvature change at the two ends of the elastic bending rod is not obvious, the stress is smaller, the elastic force generated by the compression of the elastic bending rod is mainly derived from the bending deformation of the middle part of the bending rod, the outer convex surface 5 of the elastic bending rod 3 is in a tensile state to generate tensile stress during compression, and the inner concave surface 6 of the elastic bending rod 3 is in an extrusion state to generate compressive stress. In order to restore the original state of the elastic bending rod 3, the material of the elastic bending rod 3 generates nonlinear elastic force against tensile stress and compressive stress.
As shown in fig. 21, the stress at the time of deformation is concentrated in the middle portions of the upper and lower arcs of the cross section, and the stress at the middle level is small. The cross section shape before and after deformation can be seen that after the elastic bending rod 3 is bent and deformed, the upper end circular arc and the lower end circular arc are stretched to increase the curvature, and the change of the crescent cross section shape enables the elastic bending rod 3 to be compressed more easily relative to the initial state.
As shown in fig. 22, the crescent-shaped cross-section elastic bent rod 3 can generate stronger nonlinear elastic force, which is shown to have greater rigidity in the early stage of compression and smaller rigidity in the later stage of compression, than the rectangular cross-section bent rod and the circular cross-section bent rod. The stronger nonlinear rigidity can enable the vibration reduction structure to have larger bearing capacity and lower resonance frequency in the working range, and the vibration reduction performance can be effectively improved. The three-dimensional vibration damping structure utilizes the elastic deformation of the elastic bent rod 3 to realize the transmission and conversion of motion, force and energy, thereby realizing vibration damping. After the external load is removed, the vibration reduction structure 4, the upper end face 1 and the lower end face 2 can be reset.
Example 2
Referring to fig. 7, the three-dimensional vibration damping structure with nonlinear rigidity provided in this embodiment is different from embodiment 1 in that the vibration damping structure 4 in this embodiment is composed of six elastic bending rods 3, each elastic bending rod 3 is concave towards the connecting line of the axes of the upper end face 1 and the lower end face 2, and the connecting lines of the axes of the upper end face 1 and the lower end face 2 of the plurality of elastic bending rods 3 are uniformly distributed circumferentially.
When the upper end face 1 is compressed by load, relative displacement occurs between the upper end face 1 and the lower end face 2, and external force is transmitted to the vibration reduction structure 4, so that the elastic bent rod 3 is bent and deformed to generate nonlinear rigidity, a certain bearing capacity of the structure can be provided, the smaller resonance frequency of the structure is ensured, and the vibration reduction performance is effectively improved. The three-dimensional vibration damping structure utilizes the elastic deformation of the elastic bent rod 3 to realize the transmission and conversion of motion, force and energy, thereby realizing vibration damping. After the external load is removed, the vibration reduction structure 4, the upper end face 1 and the lower end face 2 can be reset.
Example 3
Referring to fig. 8, the three-dimensional vibration damping structure with nonlinear stiffness provided in this embodiment is different from embodiment 1 in that the vibration damping structure 4 in this embodiment is composed of four elastic bending rods 3, each elastic bending rod 3 is concave towards the line connecting the axes of the upper end face 1 and the lower end face 2, and the plurality of elastic bending rods 3 are uniformly distributed circumferentially along the line connecting the axes of the upper end face 1 and the lower end face 2.
When the upper end face 1 is compressed by load, relative displacement occurs between the upper end face 1 and the lower end face 2, and external force is transmitted to the vibration reduction structure 4, so that the elastic bent rod 3 is bent and deformed to generate nonlinear rigidity, a certain bearing capacity of the structure can be provided, the smaller resonance frequency of the structure is ensured, and the vibration reduction performance is effectively improved. The three-dimensional vibration damping structure utilizes the elastic deformation of the elastic bent rod 3 to realize the transmission and conversion of motion, force and energy, thereby realizing vibration damping. After the external load is removed, the vibration reduction structure 4, the upper end face 1 and the lower end face 2 can be reset.
Example 4
Referring to fig. 9, the vibration damping device with nonlinear rigidity provided in this embodiment is only schematically configured as a module, the area of which is determined according to the product requirement, and the vibration damping device connects a plurality of three-dimensional vibration damping structures of embodiment 1 in parallel to form a vibration damping module, where the vibration damping device in this embodiment includes two vibration damping modules, an upper end surface 1, a lower end surface 2 and a middle end surface 12, and in the length direction, the end surfaces are connected by the vibration damping module.
Wherein the upper end face 1, the lower end face 2 and the middle end face 12 are in a flat plate shape, and in the vibration damping module, a plurality of three-dimensional vibration damping structures are arranged in a rectangular array on a plane vertical to the length direction, and the arrangement form is 2 multiplied by 2 in the figure.
The damping principle of the damping device with nonlinear stiffness of the invention is as follows:
Referring to fig. 17-18, a single degree of freedom vibration damping element is illustrated that is composed of a harmonic excited, vibration damping device having a nonlinear stiffness and a mass. Based on nonlinear dynamics principle, the vibration reduction element is simplified into a dynamic model of nonlinear elastic force and hysteresis damping force. Wherein x and y are respectively harmonic excitation and displacement of load mass 15, M is mass, F k(xr), Respectively as a function of the nonlinear elastic force 17 and as a function of the hysteresis damping force 18, where x r is the displacement difference between the harmonic excitation and the displacement of the load mass 15, i.e. x r =y-x.Is the first derivative of x r with time t,Is the second derivative of x r with respect to time t.
The lagrangian method is used for listing the motion differential equation of the system as follows:
where d is the sign of the differential operation, Is a partial differential operation symbol, t is time, D is a non-conservative generalized force,Is the first derivative of y over time T, T and V are the total kinetic energy of the system and the total potential energy of the system, respectively.
Solving the motion differential equation of the system can be obtained:
wherein, the Is the second derivative of y with respect to time t, and based on the functional model, the displacement transmissibility of the damping element can be calculated by the ratio of response to excitation. Taking a module formed by a three-dimensional vibration damping structure as an example, the transmissibility was tested and compared with the calculated value, and the result is shown in fig. 19.
The result shows that the vibration damper with nonlinear rigidity has good vibration damping performance and can effectively inhibit the resonance peak value of the system.
Example 5
Referring to fig. 10, the vibration damping device with nonlinear rigidity provided in this embodiment is only schematically configured as a module, the area of which will be determined according to the product requirement, and the vibration damping device connects a plurality of three-dimensional vibration damping structures of embodiment 1 in parallel to form a vibration damping module, and the vibration damping device includes three vibration damping modules and four end faces (an upper end face 1, a lower end face 2, and two middle end faces 12), and in the length direction, the end faces are connected by the vibration damping modules.
Wherein the upper end face 1, the lower end face 2 and the two middle end faces 12 are all in a flat plate shape.
In the vibration damping module, a plurality of three-dimensional vibration damping structures are arranged in a rectangular array on a plane perpendicular to the length direction, and the arrangement form is 3×3 in the figure.
Example 6
Referring to fig. 11, the vibration damping device with nonlinear rigidity provided in this embodiment is only schematically configured as a module, the area of which is determined according to the product requirement, and the vibration damping device connects a plurality of three-dimensional vibration damping structures of embodiment 1 in parallel to form a vibration damping module, wherein the vibration damping device comprises four vibration damping modules and five end faces (an upper end face 1, a lower end face 2 and three middle end faces 12), and the end faces are connected by the vibration damping modules in the length direction.
Wherein the upper end face 1, the lower end face 2 and the three middle end faces 12 are in a flat plate shape.
In the vibration damping module, a plurality of three-dimensional vibration damping structures are arranged in a rectangular array on a plane perpendicular to the length direction, and are arranged in a 4×4 mode in the figure.
Example 7
Referring to fig. 12, the vibration damping device with nonlinear rigidity provided in this embodiment is only schematically configured as a module, the area of which will be determined according to the product requirement, and the vibration damping device connects a plurality of three-dimensional vibration damping structures of embodiment 1 in parallel to form a vibration damping module, wherein the vibration damping device includes three vibration damping modules and four end faces (an upper end face 1, a lower end face 2, and two intermediate end faces 12), and the end faces are connected by the vibration damping modules in the length direction.
Wherein the upper end face 1, the lower end face 2 and the two middle end faces 12 are in a flat plate shape, in particular in a circular ring shape.
In the vibration damping module, a plurality of three-dimensional vibration damping structures are arranged in a circumferential array on a plane perpendicular to the length direction, and six three-dimensional vibration damping structures are arranged in a circle in the figure.
Example 8
Referring to fig. 13, the vibration damping device with nonlinear rigidity provided in this embodiment is only schematically configured as a module, the area of which will be determined according to the product requirement, and the vibration damping device connects a plurality of three-dimensional vibration damping structures of embodiment 2 in parallel to form a vibration damping module, and the vibration damping device includes three vibration damping modules and four end faces (an upper end face 1, a lower end face 2, and two middle end faces 12), and in the length direction, the end faces are connected by the vibration damping modules.
Wherein the upper end face 1, the lower end face 2 and the two middle end faces 12 are in a flat plate shape.
In the vibration damping module, a plurality of three-dimensional vibration damping structures are arranged in a rectangular array on a plane perpendicular to the length direction, and the arrangement form is 3×3 in the figure.
Example 9
Referring to fig. 14, the vibration damping device with nonlinear rigidity provided in this embodiment is only schematically configured as a module, the area of which will be determined according to the product requirement, and the vibration damping device connects a plurality of three-dimensional vibration damping structures of embodiment 3 in parallel to form a vibration damping module, and the vibration damping device includes three vibration damping modules and four end faces (an upper end face 1, a lower end face 2, and two middle end faces 12), and in the length direction, the end faces are connected by the vibration damping modules.
Wherein the upper end face 1, the lower end face 2 and the 2 middle end faces 12 are in a flat plate shape.
In the vibration damping module, a plurality of three-dimensional vibration damping structures are arranged in a rectangular array on a plane perpendicular to the length direction, and the arrangement form is 3×3 in the figure.
Example 10
Referring to fig. 15, the present embodiment provides a vibration damping device with nonlinear stiffness for manufacturing a spacer.
In the vibration damping element, a plurality of three-dimensional vibration damping structures with nonlinear rigidity are connected in parallel to form a vibration damping module by a vibration damping device, the vibration damping device comprises a vibration damping module, an upper end face 1 and a lower end face 2, and the end faces are connected through the vibration damping module in the length direction.
Wherein the upper end face 1 and the lower end face 2 are in a flat plate shape, in particular in a circular ring shape.
In the vibration damping module, a plurality of three-dimensional vibration damping structures are arranged in a circumferential array on a plane perpendicular to the length direction.
Example 11
Referring to fig. 16, the present embodiment provides a vibration damping device with nonlinear stiffness for manufacturing a bushing.
In the vibration damping element, a plurality of three-dimensional vibration damping structures with nonlinear rigidity are connected in parallel to form a vibration damping module, the vibration damping device comprises two vibration damping modules and three end faces (an outer end face 13, an inner end face 14 and a middle end face 12), and the end faces are connected through the vibration damping modules in the length direction.
Wherein the inner end face 14, the middle end face 12 and the outer end face 13 are cylindrical, and are sequentially arranged from inside to outside.
In the vibration damping module, a plurality of three-dimensional vibration damping structures are uniformly distributed on a cylindrical surface, and the length direction is arranged along the radial direction of the cylindrical surface.
In addition to the manner mentioned in the above embodiments, the following transformations may be performed:
in the three-dimensional vibration reduction structure, the number, shape, size and materials of the vibration reduction structure can be flexibly selected according to the needs, and the requirements of engineering on different shapes and specific rigidity can be met.
In the vibration damper, the number, shape, size, material selection and stacking mode of the vibration damper modules and the end faces can be flexibly selected according to the needs, and the requirements of engineering on different shapes and specific rigidities can be met. The vibration damping element with a specific shape is formed through superposition combination of the vibration damping modules and is applied to the actual engineering vibration damping environment.
The foregoing is illustrative of the present invention, and is not to be construed as limiting thereof, but rather as merely providing for the purpose of teaching herein before described various modifications, alternatives, variations and alternatives, as well as variations and alternatives, without departing from the spirit and principles of the invention.
Claims (9)
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