CN113027989A - Zero-rigidity vibration isolator based on mechanism metamaterial - Google Patents
Zero-rigidity vibration isolator based on mechanism metamaterial Download PDFInfo
- Publication number
- CN113027989A CN113027989A CN202110322324.7A CN202110322324A CN113027989A CN 113027989 A CN113027989 A CN 113027989A CN 202110322324 A CN202110322324 A CN 202110322324A CN 113027989 A CN113027989 A CN 113027989A
- Authority
- CN
- China
- Prior art keywords
- zero
- face
- spring
- vibration isolator
- stiffness
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- 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
- F16F15/06—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 metal springs
- F16F15/067—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 metal springs using only wound springs
-
- 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
- F16F3/00—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic
- F16F3/02—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic with springs made of steel or of other material having low internal friction
- F16F3/026—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic with springs made of steel or of other material having low internal friction to give a zero-spring rate characteristic
-
- 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
- F16F3/00—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic
- F16F3/02—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic with springs made of steel or of other material having low internal friction
- F16F3/04—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic with springs made of steel or of other material having low internal friction composed only of wound springs
-
- 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
- F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
- F16F2228/06—Stiffness
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The invention discloses a zero-stiffness vibration isolator based on a mechanism metamaterial, which comprises an upper end face and a lower end face, wherein the upper end face is connected with a load, the lower end face is contacted with external vibration excitation input, the upper end face and the lower end face are connected through a vertical spring, four side rods are arranged between the upper end face and the lower end face at intervals, the four side rods are arranged in a pairwise correspondence mode to form two groups, two side rods of one group are connected through a transverse spring, and two ends of each side rod are movably connected with the upper end face and the lower end face respectively. The vibration isolation device has low manufacturing cost, the positive and negative rigidity in the whole vibration isolation system is easy to adjust, different loads can be adapted by simply adjusting the relative position of the I-shaped sliding block in the sliding groove, meanwhile, the minimum unit is in modular design, multi-direction vibration isolation is realized by combining a plurality of minimum units, and the engineering requirements are met.
Description
Technical Field
The invention belongs to the technical field of zero-rigidity vibration isolation, and particularly relates to a zero-rigidity vibration isolator based on mechanism metamaterial.
Background
The vibration problem is a key problem influencing the service life and reliability of special equipment such as ships, rockets, satellites and the like, and the low-frequency vibration problem in actual life is still a problem to be solved urgently at home and abroad. The quasi-zero stiffness vibration isolation system has the characteristics of high static stiffness and low dynamic stiffness, and the basic principle is that a negative stiffness mechanism and a positive stiffness mechanism are connected in parallel to achieve the purpose of isolating vibration, so that the problem caused by low-frequency vibration can be effectively solved.
In general, the vibration problem is mainly divided into active vibration isolation and passive vibration isolation. Most of the passive vibration isolation in actual production is passive vibration isolation, and the traditional passive vibration isolation is very difficult to implement due to the limitation of self characteristics and cannot give consideration to both bearing capacity and stability. The quasi-zero stiffness vibration isolator can enable the vibration isolation system to have lower stiffness and good low-frequency vibration isolation performance under the condition of ensuring the bearing capacity, so that the research of the quasi-zero stiffness system becomes a hot spot. The quasi-zero stiffness vibration isolator is characterized in that positive and negative stiffness elastic elements are connected in parallel at a static balance position, so that quasi-zero stiffness is obtained, but the general quasi-zero stiffness vibration isolator is formed by combining an Euler beam and a spring or connecting the spring and the spring in parallel, the existing quasi-zero stiffness vibration isolator is usually adapted to a certain specific load, and the biggest problem brought by the quasi-zero stiffness vibration isolator is that once the load changes, the vibration isolator can easily work outside a quasi-zero stiffness vibration isolation interval, so that the vibration isolation effect cannot be achieved, or certain parameters of the quasi-zero stiffness vibration isolator can be adjusted, but the adjustment process is extremely complex, and the practicability is poor. In addition, the existing quasi-zero stiffness vibration isolator is not complete zero stiffness, and the quasi-zero stiffness is difficult to realize in large-range deformation.
Therefore, how to design the vibration isolation effect which is easy to operate, realizes complete zero stiffness, can realize zero stiffness in large-range deformation, and can be convenient for artificially adjusting the parameters of the zero-stiffness vibration isolator according to different loads so as to achieve the adaptive load becomes a problem which needs to be solved urgently.
Disclosure of Invention
The technical problem to be solved by the invention is to provide a zero-stiffness vibration isolator based on a mechanism metamaterial, aiming at the defects in the prior art, so that the complete zero-stiffness vibration isolator can achieve the vibration isolation performance of full frequency bands, and can achieve the zero-stiffness in large-range deformation.
The invention adopts the following technical scheme:
the utility model provides a zero rigidity isolator based on mechanism metamaterial, including a plurality of spring hinge mechanisms, a plurality of spring hinge mechanisms dot matrix are arranged and are formed three-dimensional space structure, every spring hinge mechanism includes up end and lower terminal surface, the up end is connected with the load, lower terminal surface and external vibration excitation input contact, pass through vertical spring coupling between up end and the lower terminal surface, the interval is provided with four side levers between up end and the lower terminal surface, four side levers two liang correspond the setting and constitute two sets ofly, pass through horizontal spring coupling between two side levers of one set of wherein, the both ends of every side lever respectively with up end and lower terminal surface swing joint.
Specifically, the side bars are of an L-shaped structure and comprise an upper part and a lower part, and the upper part and the lower part are hinged and connected.
Further, the upper portion is a fork-shaped structure, the lower portion is an H-shaped structure, one end of the fork-shaped structure is connected with the sliding block arranged on the upper end face, the other end of the fork-shaped structure is connected with one end of the H-shaped structure through a hinge, and the other end of the H-shaped structure is connected with the sliding block correspondingly arranged on the lower end face.
Furthermore, the upper end face and the lower end face are respectively provided with a slide way in an embedded mode, and the slide blocks are respectively arranged in the corresponding slide ways.
And furthermore, the sliding block is in an I-shaped structure and is fixedly connected with the upper end surface and the lower end surface through bolts.
Still further, four sliders are arranged on the upper end face and the lower end face at intervals.
Furthermore, the joint of the side rod and the sliding block adopts an additional boss design.
Specifically, the two ends of the transverse spring are respectively connected with the hinged parts of the upper part and the lower part of the side rod.
Furthermore, one transverse spring is selected, and two vertical springs are selected.
Specifically, the structural parameters of the spring hinge mechanism satisfy the following relationship:
wherein, K1For the stiffness of the transverse spring, K2Is the stiffness of the vertical spring, b is the side length of the upper end face, L10Is the original length of the transverse spring;
the load mass and the structural parameters satisfy the following formula:
mg＝K1(L20-2c)
wherein m is the load mass, c is the height of the upper end face, L20Is the original length of the vertical spring.
Compared with the prior art, the invention has at least the following beneficial effects:
according to the zero-stiffness vibration isolator based on the mechanism metamaterial, the mechanism and the spring are combined, complete zero stiffness can be achieved, manual adjustment can be conducted according to different loads, the transverse spring is positive in stiffness, the vertical spring is negative in stiffness, the overall structure is finally zero in stiffness, vibration from any direction can be isolated through the modularized design of the spring hinge mechanism, and the practicability is higher.
Further, L type side lever design for overall structure shows for protruding type outward, and hinged joint sets up that the aim at makes coupling part can the free rotation and the friction is less, shows for positive rigidity with the horizontal spring of hope, and vertical spring shows for negative rigidity, finally makes overall structure be zero rigidity.
Furthermore, the design of the fork-shaped structure and the H-shaped structure ensures the strength of the vibration isolator, reduces the weight of the vibration isolator as much as possible, is hinged with the H-shaped structure, ensures smooth connection to the maximum extent and reduces friction.
Furthermore, the upper end face and the lower end face are respectively provided with a sliding groove, so that the I-shaped sliding block can move in the sliding groove, when the load changes, the relative position of the sliding block in the sliding groove is adjusted manually by screwing the bolt, and further zero rigidity of the whole structure is realized.
Further, the design of the drum block is designed to accommodate different loads, and this adjustment is achieved by movement of the drum block.
Furthermore, the upper end face and the lower end face are respectively provided with four sliding blocks, so that the upper end face and the lower end face are prevented from generating non-parallel deformation, the symmetry of the whole structure is ensured, and the stress is uniform.
Furthermore, the Y-shaped structure and the H-shaped structure are provided with bosses at the connecting parts of the H-shaped structure and the H-shaped slide blocks, so that the side rods are prevented from sinking inwards in the compression process of the vibration isolator.
Further, one transverse spring is selected for use, and two vertical springs are selected for use, so that the interference intersection of the vertical spring set and the transverse spring set can be avoided, the symmetry of the structure can be guaranteed, and the stress is uniform.
In conclusion, the vibration isolation system is low in manufacturing cost, positive and negative rigidity in the whole vibration isolation system is easy to adjust, different loads can be adapted by simply adjusting the relative position of the I-shaped sliding block in the sliding groove, meanwhile, the minimum units are in modular design, multi-direction vibration isolation is realized by combining a plurality of minimum units, and engineering requirements are met.
The technical solution of the present invention is further described in detail by the accompanying drawings and embodiments.
Drawings
FIG. 1 is a view of the spring hinge structure of the present invention in its smallest unit;
FIG. 2 is a simplified model diagram of a finite element model of the present invention;
FIG. 3 is a diagram of finite element simulation results according to the present invention;
FIG. 4 is a layout diagram of a minimum cell structure lattice according to the present invention.
Wherein: 1. the spring comprises an upper end face, 2 sliding blocks, 3 side rods, 4 hexagon bolts, 5 lower end faces, 6 transverse springs and 7 vertical springs.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some, not all, embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "one side", "one end", "one side", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed in a particular orientation, and be operated, and thus, are not to be construed as limiting the present invention. In addition, in the description of the present invention, "a plurality" means two or more unless otherwise specified.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
It is also to be understood that the terminology used in the description of the invention herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used in the specification of the present invention and the appended claims, the singular forms "a," "an," and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise.
It should be further understood that the term "and/or" as used in this specification and the appended claims refers to and includes any and all possible combinations of one or more of the associated listed items.
Various structural schematics according to the disclosed embodiments of the invention are shown in the drawings. The figures are not drawn to scale, wherein certain details are exaggerated and possibly omitted for clarity of presentation. The shapes of various regions, layers and their relative sizes and positional relationships shown in the drawings are merely exemplary, and deviations may occur in practice due to manufacturing tolerances or technical limitations, and a person skilled in the art may additionally design regions/layers having different shapes, sizes, relative positions, according to actual needs.
The metamaterial has the advantage of realizing singular mechanical properties, so the invention provides the spring hinge mechanism metamaterial which is obtained by designing the minimum structural unit by using the spring and the hinge and modularizing the designed minimum structural unit. Compared with the common metamaterial, the metamaterial of the mechanism has the characteristics of the mechanism, such as large deformation, large-range adjustable mechanical property, large zero-stiffness deformation interval and the like, has the advantages of simple structure and the like, and has certain bearing capacity compared with the mechanism. The invention provides a zero-stiffness vibration isolator based on a mechanism metamaterial, when the stiffness of a positive stiffness spring and the stiffness of a negative stiffness spring of a designed structure are equal, the whole vibration isolator structure shows zero stiffness, the vibration isolation frequency band is expanded to the lowest frequency, and the full-band vibration isolation effect is realized. In addition, if a plurality of minimum units are arranged in a lattice mode to form a three-dimensional space structure, the spring stiffness can be reasonably designed, the length of a side rod of an L-shaped structure and the relative position of a sliding block of an I-shaped structure in a sliding groove achieve vibration isolation effects on different loads, connection and combination modes among cell elements can be reasonably designed, and isolation of vibration from the x direction, the y direction and the z direction and even vibration from any direction can be achieved.
Referring to fig. 4, the zero-stiffness vibration isolator based on the mechanism metamaterial of the present invention includes a plurality of spring hinge mechanisms, the plurality of spring hinge mechanisms are arranged in a lattice manner to form a three-dimensional structure, and the spring hinge mechanisms are designed to isolate vibration around the vibration isolator. The plurality of spring hinge mechanisms are reasonably arranged in an array mode to obtain the mechanism metamaterial based on the structure, the excellent performance of adapting to different loads and isolating vibration in multiple directions can be achieved, and the size and the shape of the metamaterial are easy to adjust.
Referring to fig. 1, the spring hinge mechanism includes an upper end surface 1, a slider 2, a side lever 3, a hexagon bolt 4, a lower end surface 5, a transverse spring 6 and a vertical spring 7.
The upper end face 1 is connected with a load and plays a role in bearing the load, the lower end face 5 is in contact with external vibration excitation input, side rods 3 are arranged between the upper end face 1 and the lower end face 5 at intervals, each side rod 3 comprises two parts, the two parts are connected through hinge joint, a transverse spring 6 for providing negative stiffness is arranged between the two side rods 3, and two ends of the transverse spring 6 correspond to the hinge joint of the connecting side rod 3; a vertical spring 7 for providing positive stiffness is arranged between the upper end face 1 and the lower end face 5.
Lower terminal surface 5 is unanimous with the whole shape of up end 1, and the symmetry is placed, and the slide is all embedded to up end 1 and lower terminal surface 5, corresponds in the slide and is provided with slider 2, all is provided with four sliders 2 on lower terminal surface 5 and the up end 1, and slider 2 is "worker" style of calligraphy structure, and every slider 2 is fixed through two hex bolts 4, and here bolt supports slider 2 with its axial helical force and fixes in order to realize.
The upper end surface 1, the lower end surface 5 and the side rods 3 are made of lubricating materials (pa66) with high hardness and light weight; this ensures that the rods undergo little bending shear deformation when the system is under compression or tension, the rotational friction is low and the dead weight of the structure is negligible in relation to the load.
The upper part of the side rod 3 is of a fork-shaped structure, and one end of the fork-shaped structure is hinged with a sliding block 2 correspondingly arranged on the upper end surface 1; the lower part is an H-shaped structure, one end of the H-shaped structure is hinged and fixedly connected with a fork-shaped structure, the other end of the H-shaped structure is hinged with a corresponding sliding block 2 on the lower end face 5, the H-shaped structure and the fork-shaped structure form a side rod 3 of an L-shaped structure together, and the hinged connection is an internal thread straight-through pipe connection and is fixed through a bolt.
The joint of the side rod 3 and the sliding block 2 adopts an additional boss design, and the purpose is to increase the interference of the side rod and the sliding block so as to prevent the condition that the side rod 3 is inwards sunken when the structure is pressed.
Vertical spring 7 is a set of for two spring constitution, and horizontal spring 6 chooses for use one, can avoid vertical spring group 7 and horizontal spring group 6 to interfere alternately like this, can guarantee the symmetry of structure again, and the atress is even.
Referring to fig. 2, the structural dimensions and physical parameters of the spring hinge mechanism include:
the length b of the upper end surface 1, the height c of the upper end surface 1, the length a of the side lever 3 and the rigidity K of the transverse spring 61Vertical spring 7 single spring rate K2The length of the transverse spring 6 is L1Original length is L10The length of the vertical spring 7 is L2Original length is L20。
When the structural parameters satisfy the relation (1), the mechanical characteristics are represented by zero stiffness.
When the formula (1) is satisfied, the load mass and the structural parameter satisfy the following formula:
mg＝K1(L20-2c) (2)
wherein m is the load mass.
At the moment, the structure works in a zero-rigidity interval, and plays a role in vibration isolation on loads.
Referring to fig. 2 and 3, finite element simulations were performed based on theoretical derivation. FIG. 2 is a finite element model with the finite element parameters set as:
a＝b＝0.08m
c＝0.03m
K1＝2×K2＝450N/m
L10＝0.08m
L20＝39.22/K1+0.06m
according to the theoretical derivation formula (1), the force-displacement curve of the structure should be represented as: with the increase of the displacement, the force on the upper end face 1 is constant force F with the magnitude of K1×(L20-2c) ═ 39.22N. The force-displacement curve in fig. 3 sets finite element simulation results for the parameters, consistent with theory, presenting a completely zero stiffnessMechanical property, and excellent vibration isolation performance.
The working process of the zero-rigidity vibration isolator based on the mechanism metamaterial comprises the following steps:
in consideration of engineering manufacturing, if the load is known, the manufacturing that the spring stiffness, the original length and the length of the side bar 3 all satisfy the conditions has certain difficulty. Therefore, the slider 2 structure designed by the invention can well solve the problems, and has the advantages that when the load is known, the spring stiffness, the original length and the length of the side rods 3 are determined, then the spring is adapted to the spring by adjusting the size of c to meet the constraint condition formula (2), and once the load is changed, the vibration isolator is generally required to be replaced again to match the load, but the value of c is only adjusted by screwing the hexagon bolts outwards, the slider 2 slides relatively in the sliding groove, generally, when the load is greater than the set value of the initial value, the I-shaped slider 2 is required to move towards each other to reduce the value of c, otherwise, the I-shaped slider 2 moves inwards, and the hexagon bolts are screwed again after the adjustment is finished to fix the position of the slider 2 in the sliding groove, so that the aim of vibration isolation is finally achieved.
In conclusion, the zero-stiffness vibration isolator based on the mechanism metamaterial combines the mechanism and the spring, not only can realize complete zero stiffness, but also can be easily adjusted manually according to different loads, the modularized design of the spring hinge mechanism can isolate vibration from any direction, and meanwhile, each vibration isolator can change the position of the sliding block in the sliding groove, so that the practicability of the vibration isolator is improved.
The above-mentioned contents are only for illustrating the technical idea of the present invention, and the protection scope of the present invention is not limited thereby, and any modification made on the basis of the technical idea of the present invention falls within the protection scope of the claims of the present invention.
Claims (10)
1. The utility model provides a zero rigidity isolator based on mechanism metamaterial, a serial communication port, including a plurality of spring hinge mechanisms, a plurality of spring hinge mechanisms dot matrix are arranged and are formed three-dimensional space structure, every spring hinge mechanism includes up end (1) and lower terminal surface (5), up end (1) is connected with the load, lower terminal surface (5) and external vibration excitation input contact, connect through vertical spring (7) between up end (1) and the lower terminal surface (5), the interval is provided with four side lever (3) between up end (1) and the lower terminal surface (5), two liang of settings that correspond of four side lever (3) constitute two sets ofly, connect through horizontal spring (6) between two side lever (3) of one set of them, the both ends of every side lever (3) respectively with up end (1) and lower terminal surface (5) swing joint.
2. The zero stiffness vibration isolator based on mechanism metamaterial according to claim 1, wherein the side bars (3) are of L-shaped structure and comprise an upper part and a lower part, and the upper part and the lower part are hinged.
3. The zero-stiffness vibration isolator based on the mechanism metamaterial according to claim 2, wherein the upper portion is of a fork-shaped structure, the lower portion is of an H-shaped structure, one end of the fork-shaped structure is connected with a sliding block (2) arranged on the upper end face (1), the other end of the fork-shaped structure is connected with one end of the H-shaped structure through a hinge, and the other end of the H-shaped structure is connected with a sliding block (2) correspondingly arranged on the lower end face.
4. The zero-stiffness vibration isolator based on mechanism metamaterial according to claim 3, wherein slide ways are embedded in the upper end surface (1) and the lower end surface (5), and the slide blocks (2) are respectively arranged in the corresponding slide ways.
5. The zero-stiffness vibration isolator based on the mechanism metamaterial according to claim 4, wherein the sliding block (2) is of an I-shaped structure and is fixedly connected with the upper end surface (1) and the lower end surface (5) through bolts.
6. The zero-stiffness vibration isolator based on the mechanism metamaterial according to claim 4, wherein four sliders (2) are arranged on the upper end surface (1) and the lower end surface (5) at intervals.
7. The zero-stiffness vibration isolator based on the mechanism metamaterial according to claim 4, wherein the joints of the side rods (3) and the sliding block (2) are designed by using additional bosses.
8. The zero stiffness vibration isolator based on mechanism metamaterial according to claim 1, wherein both ends of the transverse spring (6) are respectively connected with the hinged parts of the upper part and the lower part of the side rod (3).
9. The zero-stiffness vibration isolator based on the mechanism metamaterial according to claim 8, wherein one transverse spring (6) is selected, and two vertical springs (7) are selected.
10. The zero stiffness vibration isolator based on mechanism metamaterial according to any one of claims 1 to 9, wherein the structural parameters of the spring hinge mechanism satisfy the following relationship:
wherein, K1For the stiffness of the transverse spring, K2Is the stiffness of the vertical spring, b is the side length of the upper end face, L10Is the original length of the transverse spring;
the load mass and the structural parameters satisfy the following formula:
mg＝K1(L20-2c)
wherein m is the load mass, c is the height of the upper end face, L20Is the original length of the vertical spring.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110322324.7A CN113027989B (en) | 2021-03-25 | 2021-03-25 | Zero-rigidity vibration isolator based on mechanism metamaterial |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110322324.7A CN113027989B (en) | 2021-03-25 | 2021-03-25 | Zero-rigidity vibration isolator based on mechanism metamaterial |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113027989A true CN113027989A (en) | 2021-06-25 |
| CN113027989B CN113027989B (en) | 2022-05-20 |
Family
ID=76474025
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110322324.7A Active CN113027989B (en) | 2021-03-25 | 2021-03-25 | Zero-rigidity vibration isolator based on mechanism metamaterial |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113027989B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114001137A (en) * | 2021-07-20 | 2022-02-01 | 北京航空航天大学 | Movable force limiter |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU1257320A1 (en) * | 1984-07-04 | 1986-09-15 | Производственное Объединение "Ново-Краматорский Машиностроительный Завод" | Shock-absorber |
| JPH06272735A (en) * | 1993-03-19 | 1994-09-27 | Mitsubishi Electric Corp | Damping mechanism |
| CN205154998U (en) * | 2015-10-23 | 2016-04-13 | 上海理工大学 | Passive vibration isolation platform of multi freedom |
| CN105889385A (en) * | 2016-06-14 | 2016-08-24 | 西安交通大学 | Compression spring type six-degree-of-freedom quasi-zero stiffness vibration isolator and design method thereof |
| CN106402229A (en) * | 2016-06-20 | 2017-02-15 | 南京航空航天大学 | Shear type quasi zero rigidity vibration isolator and work method thereof |
| CN106402267A (en) * | 2016-05-23 | 2017-02-15 | 福州大学 | Extension type quasi-zero stiffness vibration isolator and implementation method thereof |
| CN109139787A (en) * | 2018-09-10 | 2019-01-04 | 中国人民解放军陆军装甲兵学院 | Extension spring formula quasi-zero stiffness vibration isolators |
| CN109737168A (en) * | 2019-02-28 | 2019-05-10 | 安徽工程大学 | A kind of quasi-zero stiffness vibration isolators |
| CN112211952A (en) * | 2020-10-12 | 2021-01-12 | 哈尔滨工程大学 | Low-frequency large-stroke quasi-zero rigidity vibration isolation device |
-
2021
- 2021-03-25 CN CN202110322324.7A patent/CN113027989B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU1257320A1 (en) * | 1984-07-04 | 1986-09-15 | Производственное Объединение "Ново-Краматорский Машиностроительный Завод" | Shock-absorber |
| JPH06272735A (en) * | 1993-03-19 | 1994-09-27 | Mitsubishi Electric Corp | Damping mechanism |
| CN205154998U (en) * | 2015-10-23 | 2016-04-13 | 上海理工大学 | Passive vibration isolation platform of multi freedom |
| CN106402267A (en) * | 2016-05-23 | 2017-02-15 | 福州大学 | Extension type quasi-zero stiffness vibration isolator and implementation method thereof |
| CN105889385A (en) * | 2016-06-14 | 2016-08-24 | 西安交通大学 | Compression spring type six-degree-of-freedom quasi-zero stiffness vibration isolator and design method thereof |
| CN106402229A (en) * | 2016-06-20 | 2017-02-15 | 南京航空航天大学 | Shear type quasi zero rigidity vibration isolator and work method thereof |
| CN109139787A (en) * | 2018-09-10 | 2019-01-04 | 中国人民解放军陆军装甲兵学院 | Extension spring formula quasi-zero stiffness vibration isolators |
| CN109737168A (en) * | 2019-02-28 | 2019-05-10 | 安徽工程大学 | A kind of quasi-zero stiffness vibration isolators |
| CN112211952A (en) * | 2020-10-12 | 2021-01-12 | 哈尔滨工程大学 | Low-frequency large-stroke quasi-zero rigidity vibration isolation device |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114001137A (en) * | 2021-07-20 | 2022-02-01 | 北京航空航天大学 | Movable force limiter |
| CN114001137B (en) * | 2021-07-20 | 2023-06-16 | 北京航空航天大学 | Movable force limiter |
Also Published As
| Publication number | Publication date |
|---|---|
| CN113027989B (en) | 2022-05-20 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN113027989B (en) | Zero-rigidity vibration isolator based on mechanism metamaterial | |
| CN106812864A (en) | A kind of Industrial Boiler with shock-absorbing function | |
| CN110331660A (en) | A kind of modulus type bridge expanssion joint with flat pendulum support beam | |
| CN103334509A (en) | High-frequency tuning mass damper | |
| CN207110241U (en) | A kind of steel structure pillar construction | |
| CN114741811A (en) | Variable-rigidity three-dimensional concave negative Poisson ratio cell element and design method thereof | |
| CN101929517B (en) | Damping device with disk spring assembly structure | |
| CN101498146A (en) | Disperse barrel construction structure system | |
| CN109881784B (en) | Cambered surface sliding type three-dimensional shock insulation support | |
| CN206470664U (en) | A kind of computer multi-functional antishock device | |
| CN203257971U (en) | Three-way metal rubber vibration isolator and array thereof | |
| CN103276830B (en) | A kind of lead shear damper | |
| CN205978232U (en) | Imitative leg type isolation mounting based on X type structure | |
| CN102433942A (en) | Method for using modular steel hysteresis damper | |
| CN203361392U (en) | High-frequency tuning mass vibration absorber | |
| CN109518814A (en) | Combined isolation method | |
| CN103042522A (en) | 3-5R (revolute) and SS (sphere-sphere) two-degree-of-freedom parallel mechanism with function of posture adjustment and positioning | |
| CN209703743U (en) | A kind of multidimensional vibration reduction damper based on Stewart mechanism | |
| CN207981858U (en) | A kind of flexibility self-balancing closed-loop system spindle carrier | |
| CN109990193A (en) | A kind of multistage concertina honeycomb | |
| CN111969327A (en) | Deformation-designable and non-contact-controllable two-dimensional mechanical metamaterial | |
| CN109518816A (en) | The shock isolation method of comprehensive shock isolating pedestal | |
| CN109401480A (en) | Structural fire protection coating fire proofing material | |
| CN109296103A (en) | Assembly, energy consumption and the self-resetting method of the anti-buckling support of shape memory alloy spring | |
| CN109457830A (en) | The comprehensive shock isolating pedestal of annular shape memory alloy spring |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |