CN108953443B - Concave octagonal cubic lattice sandwich plate structure - Google Patents
Concave octagonal cubic lattice sandwich plate structure Download PDFInfo
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- CN108953443B CN108953443B CN201810781376.9A CN201810781376A CN108953443B CN 108953443 B CN108953443 B CN 108953443B CN 201810781376 A CN201810781376 A CN 201810781376A CN 108953443 B CN108953443 B CN 108953443B
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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
- F16F1/00—Springs
- F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
- F16F1/373—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers characterised by having a particular shape
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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
- F16F1/00—Springs
- F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
- F16F1/373—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers characterised by having a particular shape
- F16F1/3732—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers characterised by having a particular shape having an annular or the like shape, e.g. grommet-type resilient mountings
Abstract
the invention belongs to the field of pressure-bearing sandwich plates, and particularly relates to a concave octagonal cubic lattice sandwich plate structure. Compared with the most common stiffened plate in the field, the lattice sandwich plate structure has the advantages that under the action of the same static load, the deformation mode of the lattice sandwich plate structure is the same as that of the stiffened plate, but the deformation and the stress of an upper panel and a lower panel of the lattice sandwich plate structure are smaller than those of the stiffened plate, and the rigidity of the lattice sandwich plate structure is superior to that of the stiffened plate with the same quality; under the action of equivalent dynamic load, the displacement of the upper panel and the lower panel of the lattice sandwich plate structure is far smaller than that of the stiffened plate, and meanwhile, the displacement of the lower panel of the lattice sandwich plate structure is also smaller than that of the upper panel; under the initial speed load that the stiffened plate enters plastic deformation, the deformation of the lattice sandwich plate structure is still kept in an elastic range, and the shock resistance mechanical property of the lattice sandwich plate structure is far superior to that of the stiffened plate with the same quality.
Description
Technical Field
The invention belongs to the field of pressure-bearing sandwich plates, and particularly relates to a concave octagonal cubic lattice sandwich plate structure.
background
In the field of engineering technology, people have been constantly searching for a structure with high strength, high rigidity and light weight. With the development of modern high and new technologies, people have higher requirements on structures for executing special tasks, and the structures are required to be light and high in strength, and also are expected to have certain other special functions, such as anti-explosion and energy absorption, heat absorption and dissipation, sound absorption and vibration reduction, wave absorption and invisibility, deformation actuation and the like, namely the structures are expected to integrate excellent mechanical properties and special functions. For the naval vessels, along with diversification of warship weapon attack forms and improvement of attack force, the warship is more and more greatly threatened and damaged, and higher requirements are provided for the anti-explosion protection performance of the naval vessel structure. It is in this context that lightweight cellular lattice structures are entering the field of view of researchers.
The lattice structure belongs to one of porous structures, which are ubiquitous in nature, such as wood, bones, and corals, and the like, and is a result of the long-term evolution of organisms. The biological load-bearing agent plays a special biological function in a living body, can bear large static load and dynamic load for a long time, and plays an important role in living of organisms in complex and variable environments.
disclosure of Invention
the invention aims to provide a concave octagonal cubic lattice sandwich plate structure which has a negative Poisson ratio characteristic, generates less deformation and stress under a static load and has stronger shock resistance under a dynamic load, and the structure can effectively improve the capacity of resisting explosion impact deformation of a ship structure.
In order to achieve the purpose, the invention adopts the following technical scheme.
The invention provides an inwards concave octagonal cubic lattice sandwich plate structure which is formed by laminating a plurality of lattice groups, wherein each lattice group comprises a plurality of single structures distributed in an array manner;
the single body structure consists of two square frames which have the same side length and are arranged oppositely in parallel up and down, and a telescopic frame which is arranged between the two frames and is formed by connecting eight telescopic connecting rods end to end;
the eight connecting rods on the telescopic frame comprise four positioning rods which are arranged at intervals and are respectively parallel to four edges of the frame and four middle rods for connecting the positioning rods;
Between each positioning rod and the parallel frames, two end points of the positioning rods are connected with the top points of the frames on the same side through inclined rods;
The length of the diagonal rods positioned on the upper side of the telescopic frame is the same, and the length of the diagonal rods positioned on the lower side of the telescopic frame is the same.
Specifically, in the dot array group, a plurality of cell structures are distributed along two vertical edge arrays of a square frame thereof.
In a preferred embodiment based on the basic structure, in the single structure, four positioning rods are respectively located on four side surfaces of a rectangular parallelepiped surrounded by vertices of the frame.
Based on the basic structure, a preferable scheme is that the plane where the telescopic frame is located is the middle plane of the plane where the two side frames are located.
in a preferred embodiment based on the basic structure, the frame is formed by square bars, and the connecting rods and the diagonal rods are formed by round bars.
one preferred solution based on the above basic structure is that the length of the diagonal is half of the side length of the square frame.
In a preferred embodiment based on the basic structure, the square frame is formed by square bars with a length of 30mm, the cross section of each square bar is a square with a side length of 3mm, the connecting rods and the inclined rods are round rods with a diameter of 3mm, and the length of each inclined rod is 15 mm.
The beneficial effects are that:
Through statistical analysis, the lattice sandwich plate structure of the invention has the following characteristics compared with the most common stiffened plate in the field:
Under the action of the same static load, the deformation mode of the lattice sandwich plate structure is the same as that of the stiffened plate, but the deformation and the stress of the upper panel and the lower panel of the lattice sandwich plate structure are smaller than those of the stiffened plate, and the rigidity of the lattice sandwich plate structure is superior to that of the stiffened plate with the same mass; under the action of equivalent dynamic load, the displacement of the upper panel and the lower panel of the lattice sandwich plate structure is far smaller than that of the stiffened plate, and meanwhile, the displacement of the lower panel of the lattice sandwich plate structure is also smaller than that of the upper panel; under the initial speed load that the stiffened plate enters plastic deformation, the deformation of the lattice sandwich plate structure is still kept in an elastic range, and the shock resistance mechanical property of the lattice sandwich plate structure is far superior to that of the stiffened plate with the same quality.
The invention has good physical properties and wide application prospect, including:
The elastic material can be used for manufacturing the pressure bearing structure for supporting based on the structure, so that the integral pressure bearing capacity is improved;
The boundary-constrained pressure-bearing structure can be made of elastic or plastic materials based on the structure, so that the thinning of the section thickness of the pressure-bearing structure can be resisted, and the pressure-bearing capacity of the pressure-bearing structure is improved.
Can use plastic material preparation reinforcing protection and buffer structure based on this structure, have the characteristics that the quality is light but intensity is high, can produce a certain amount of deformation in the twinkling of an eye in order to cushion impact force in the twinkling of an eye in the contact of strikeing, the structural deformation in-process, make buffer structure draw in after the inner structure extrudes each other, the relative density at high stress position constantly increases, buffer structure intensity improves gradually, realize dynamic buffering, offset the effect of impact force step by step, can effectively avoid the follow-up bearing capacity decline scheduling problem of impact failure and buffer structure in the twinkling of an eye.
Drawings
FIG. 1 is a perspective view of a single structure in the embodiment;
FIG. 2 is a front view of a single structure in the embodiment;
FIG. 3 is a top view of a unitary structure according to an embodiment;
FIG. 4 is a partial view of a finite element mesh of a monolithic structure in an embodiment;
FIG. 5 is a displacement cloud of the monolithic structure under static load in the examples;
FIG. 6 is a stress cloud for the monolithic structure under static load in the examples;
FIG. 7 is a front view of a structure of a sandwich panel of the lattice in the example;
FIG. 8 is a top view of a sandwich plate structure of the lattice in the example;
FIG. 9 is a cloud view of displacement of the upper panel of the lattice sandwich plate structure under static load in the embodiment;
FIG. 10 is a cloud view of displacement of a lower panel of the lattice sandwich plate structure under a static load in the embodiment;
FIG. 11 is a stress cloud under static load of the upper panel of the lattice sandwich plate structure in the embodiment;
FIG. 12 is a stress cloud under static load of the lower panel of the lattice sandwich plate structure in the embodiment;
FIG. 13 is a cloud view of the displacement of the stiffened panel under static load in the example;
FIG. 14 is a stress cloud under static load for a stiffened panel in an example embodiment;
FIG. 15 is a graph of displacement-time curves of the central node of the lower plate under the loading action with initial speeds of 10m/s for the lattice sandwich plate structure and the stiffened plate respectively;
FIG. 16 is a graph showing displacement-time curves of the central node of the lower plate under the loading action at initial speeds of 20m/s for the lattice sandwich plate structure and the stiffened plate respectively;
FIG. 17 is a graph of displacement-time curves of the central node of the lower plate under the loading action with the initial speed of 30m/s for the lattice sandwich plate structure and the stiffened plate.
Detailed Description
The invention is described in detail below with reference to specific embodiments.
As shown in fig. 1, the single structure, which is a basic unit of the concave octagonal cubic lattice sandwich plate structure, of the present invention, is composed of two square frames with equal side length and arranged in parallel up and down in a right-to-right manner, and a telescopic frame arranged between the two frames and formed by connecting eight telescopic connecting rods end to end, wherein the eight connecting rods on the telescopic frame include four positioning rods (2a, 2b, 2c, 2d) arranged at intervals and respectively parallel to four sides (1a, 1b, 1c, 1d) of the frame, and four intermediate rods (3a, 3b, 3c, 3d) for connecting the positioning rods; between each positioning rod and the side parallel to the positioning rod, the end point of the positioning rod and the end point at the same side of the side are connected through a telescopic oblique rod 4; the length of the diagonal rods positioned on the upper side of the telescopic frame is the same, and the length of the diagonal rods positioned on the lower side of the telescopic frame is the same.
in this embodiment, the monolithic structure comprises square pole and round bar, wherein constitute the square by length 30mm, the cross-section of upper and lower frame, square side length 3 mm's square pole constitutes, connecting rod and down tube are long 15mm, diameter 3 mm's round bar constitutes, and the plane that flexible frame place is two planar intermediate planes in frame place, and four locating levers are located four sides of the cuboid that two frames enclose respectively, consequently, in this embodiment, the down tube length of flexible frame top and below is unanimous.
In order to facilitate comparison, physical characteristic data of the negative Poisson ratio lattice sandwich plate structure is obtained at the same time, the monomer structure and the lattice sandwich plate structure are analyzed and calculated by using MSC.Patran, MSC.Nastran and MSC.Dytran, and the specific content mainly comprises the steps of establishing a model of the monomer structure and the lattice sandwich plate structure, and performing simulation calculation on physical characteristics of the model, including deformation and stress, and comparing the model with the existing stiffened plate to determine the actual performance of the model.
Firstly, modeling is performed based on the monomer structure in the embodiment to obtain the monomer structure model in fig. 1, fig. 2, and fig. 3, the monomer structure model is imported into msc.patran software, finite element meshing is performed on the monomer structure entity to obtain a mesh division diagram as shown in fig. 4, in the embodiment, a 4-node tetrahedral unit (Tet4) is used for dividing the monomer structure into meshes, the mesh size is 3mm, the total number of nodes is 5129, and the total number of units is 19309.
based on corresponding materials used in the actual application process, calculating by adopting related physical data of Q235 steel; specific material parameters for Q235 are shown in table 1:
TABLE 1 Material parameters
Patran software is used for post-processing to obtain a displacement cloud picture and a stress cloud picture of the monomer structure under the action of static load, and the simulation data/results in figures 5 and 6 show that the maximum position of the monomer structure is shifted to the central position of the upper end square rod, and the maximum stress of the monomer structure is at the connecting position of the rod pieces. The material attribute of Q235 is still used, an Elasplas ideal elastic-plastic model is adopted to simulate the dynamic mechanical property of the monomer structure, MSC.Patran software is used for post-processing to obtain displacement cloud charts of the monomer structure at different time points under the action of dynamic load, and the maximum displacements of the time nodes of 1ms, 4ms, 7ms and 10ms are respectively 19.2 μm, 16.2 μm, 12.8 μm and 7.65 μm; the maximum stress values of the monomer structure at various time points under the action of dynamic load are 184MPa, 152MPa, 153MPa and 112MPa respectively.
through the calculation and analysis of the quasi-static mechanical property and the dynamic mechanical property of the single structure, when the single structure is subjected to static load, the maximum position is shifted out of the center of the upper square rod, and the maximum stress is generated at the connecting part of the inclined rod and the elastic ring.
In the practical application process, the lattice sandwich plate structure is used after the single structure arrays are combined and stacked, so that on the basis of the calculation result, the single structure arrays and the stacked single structure arrays form the lattice sandwich plate structure; in the stacked cell structures, the cell structures adjacent in the vertical direction share the side of the upper or lower frame.
for convenience of analysis and calculation, in the embodiment, a simulation test is performed on the basis of a lattice sandwich plate model formed by laminating three layers after 30 × 30 single structure arrays along the length direction, and simultaneously, reinforcing plates with the same mass are used for comparison; the stiffened plate is the same with dot matrix sandwich plate structure quality, and length and width is 0.9m, and length direction has 5T shaped steel, interval 150mm, and width direction has 4T shaped steel, interval 180mm, T shaped steel web height 50mm, thickness 6mm, panel width 60mm, thickness 8 mm.
Modeling is directly carried out in MSC.Patran according to the basic arrangement to obtain a model of a lattice sandwich plate structure. Firstly, a beam unit model of a single structure is created, a bottom 4 vertex is established by an XYZ method, a middle vertex is established by an Offset method, a lower half straight line is established by a Point method, and then the upper half model is established by a mirror image method. The finite element mesh division needs to be carried out on the monomer structure model firstly, the monomer structure rod pieces are divided by 2-node rod units (Bar2), the unit size is 3mm, then the copying operation is carried out in the X, Z direction, the mirror image operation is carried out in the Y direction to obtain the rest meshes of the sandwich structure in the sandwich plate, then the Equisalence operation is carried out on all the nodes to avoid the occurrence of repeated nodes, and the total number of the obtained beam units is 518400. When the outer plate model is established, a Point method is used for selecting the top and bottom vertexes of the internal sandwich structure to respectively make two straight lines, a current method is used for creating top and bottom planes, the size of each plane is 0.9m by 0.9m, then finite element mesh division is carried out on the planes, seeds are scattered on the edges of the planes according to the distance of 90mm, 4-node quadrilateral units (Quad4) are used for carrying out mesh division, and the total number of shell units is 200. Finally, Equisalness operation is performed on all the nodes, the number of the nodes is 225604, and the model which is built is completed is shown in FIG. 7 and FIG. 8.
And then entering a Load/BCs interface to add Load and boundary conditions to the test piece, selecting Displacement in an Object option, and adding the boundary conditions. For the bottom plate of the surface ship, each plate can be considered to be closely connected with other plates, so the boundary condition is set as a fixed support, namely displacement and a corner are set as 0, then a load is set, an Object (Object) is selected as Pressure, the type of a target node is selected as 2D, and the size of the load is input to be 0.2 Mpa.
And after the post-processing is carried out by MSC. As shown in fig. 9 and 10, the displacements of the upper and lower panels are almost uniform, the maximum displacement of the upper panel is 0.58mm, the maximum displacement of the lower panel is 0.56mm, and the difference is 3.4%, and the maximum displacements are both present in the middle of the panel. The reason why the displacements of the upper and lower panels are almost uniform is that the load acting on the upper panel is a static pressure, so that the deformation mode of the lattice sandwich panel structure can be considered as integral deformation.
FIGS. 11 and 12 are stress distributions of the upper and lower panels of the lattice structure, respectively, with the upper panel having a maximum stress of 20.5MPa and the lower panel having a maximum stress of 19.9 MPa. It can be seen that the midpoint of the clamped edge is a stress concentration point, the center of the panel also has a certain degree of stress concentration, the central stress of the upper panel is 12.9Mpa, the central stress of the lower panel is 12.3Mpa, and a square low-stress area is arranged between the clamped edge and the two stress concentration positions in the center.
Also, stiffened plates were directly modeled in msc. Firstly establishing 4 vertexes by using an XYZ method, establishing a straight line by using a 2Point method, establishing a plane as a stiffened plate panel by using a Curve method, and then establishing a transverse rib vertex and a longitudinal rib vertex at corresponding positions by using the XYZ method, and establishing a straight line to complete the establishment of a stiffened plate model. The transverse and longitudinal bars are divided into grids by adopting 2-node rod units (Bar2), the unit size is 30mm, and the total number of beam units is 270. Then, finite element meshing is carried out on the plane, seeds are scattered on the edges of the plane according to the distance of 30mm, meshing is carried out by 4-node quadrilateral units (Quad4), and the total number of shell units is 900. And performing Equisalness operation on all the nodes to avoid repeated node calculation, wherein the number of the nodes is 961. And (3) adopting a 1DBeam type to endow the beam unit with properties, wherein the beam unit direction is the vertical direction, using a T-shaped section, selecting a 2DShell type to endow the shell unit with properties, wherein the thickness is 8mm, and entering a Load/BCs interface to add Load and boundary conditions to the test piece. For surface vessel bottom plates, each plate can be considered to be in close connection with the other plates, so the boundary conditions are set as clamped. Selecting Displacement in the Object (Object), adding a clamped boundary condition, wherein the Displacement and the corner are both 0, and then selecting all nodes on the side face in a frame to finish the addition of the boundary condition. And then setting a load, selecting an Object as Pressure, selecting a target node type as 2D, inputting the load size to 0.2Mpa, and processing by using MSC.Patran software to obtain the displacement of the stiffened plate. As shown in fig. 13, the maximum displacement is 0.8mm, the maximum displacement occurring in the middle of the plate.
fig. 14 is a stress distribution of the reinforced plate, and the maximum stress is 41.7Mpa, which appears at the midpoint of the side of the reinforcing bar, because the difference in the number of the transverse and longitudinal ribs causes the difference in the stress distribution of the adjacent sides. The stress concentration phenomenon occurs in the center of the panel, and is mainly concentrated at the part without transverse and longitudinal ribs below the panel.
The test data are arranged to obtain a comparison result data table 2, and the table shows that under the same static load, the deformation mode of the lattice sandwich plate structure is the same as that of the stiffened plate, but the deformation and the stress of the upper panel and the lower panel of the lattice sandwich plate structure are smaller than those of the stiffened plate, so that the rigidity of the lattice sandwich plate structure is superior to that of the stiffened plate with the same mass.
table 2 displacement and stress data of dot matrix sandwich plate structure and stiffened panel under quasi-static load
under the same setting condition, data of an upper panel and a lower panel of the lattice sandwich plate structure under the loading action with the initial speed of 10m/s are obtained after the data are processed by MSC.Patran software, the maximum displacements corresponding to the upper panel are respectively 3.64mm, 2.13mm, 2.07mm and 2.66mm at four time points of 1ms, 4ms, 7ms and 10ms, and the maximum displacements corresponding to the lower panel are respectively 2.5mm, 0.85mm, 0.89mm and 1.42mm and are all shown in the center of the panel; the maximum stresses corresponding to the upper panel are 171Mpa, 120Mpa, 93.9Mpa and 92Mpa, respectively, and the maximum stresses corresponding to the lower panel are 137Mpa, 130Mpa,107Mpa and 100Mpa, respectively.
under the loading action with the initial speed of 20m/s, the maximum displacements corresponding to the upper panel are respectively 7.24mm, 6.17mm, 7.47mm and 7.92mm, the maximum displacements corresponding to the lower panel are respectively 4.71mm, 3.79mm, 4.79mm and 5.28mm, the maximum stresses corresponding to the upper panel are respectively 118Mpa, 97.5Mpa, 73.4Mpa and 90.5Mpa, and the maximum stresses corresponding to the lower panel are respectively 152Mpa,106Mpa and 110Mpa at four time points of 1ms, 4ms, 7ms and 10 ms.
Under the loading action with the initial speed of 30m/s, the maximum displacements corresponding to the upper panel are 10.3mm, 9.75mm, 11.5mm and 10.5mm respectively, and the maximum displacements corresponding to the lower panel are 6.83mm, 6.77mm, 8.39mm and 8.24mm respectively at four time points of 1ms, 4ms, 7ms and 10 ms. The maximum stresses corresponding to the upper panel are 126Mpa, 105Mpa and 89.3Mpa, respectively, and the maximum stresses corresponding to the lower panel are 184Mpa, 179Mpa,111Mpa and 113Mpa, respectively.
Establishing a stiffened plate model based on the same steps, simulating deformation and stress change states of the stiffened plate model, and processing the stiffened plate model by MSC.Patran software to obtain displacement and stress data of a stiffened plate panel at different time points under the loading action of an initial speed of 10 m/s; at four time points, 1ms, 4ms, 7ms and 10ms, the maximum displacements corresponding to the upper panel were 10.1mm, 5.33mm, 5.64mm and 5.73mm, respectively, and the maximum stresses corresponding to the upper panel were 234Mpa, 133Mpa, 107Mpa and 110Mpa, respectively.
Under the loading action with the initial speed of 20m/s, the maximum displacements of the upper panel are respectively 18.6mm, 16.6mm, 18.5mm and 18.6mm at four time points of 1ms, 4ms, 7ms and 10ms, and the maximum stresses of the upper panel are respectively 235MPa, 234MPa, 166MPa and 172 MPa.
Under the loading action with the initial speed of 30m/s, the maximum displacements of the upper panel are respectively 26.9mm, 38.5mm, 40.8mm and 39.8mm at four time points of 1ms, 4ms, 7ms and 10ms, and the maximum stresses of the upper panel are respectively 235Mpa, 217Mpa, 213Mpa and 207 Mpa.
From the above experimental results, the displacement-time curves of the central node of the panel under the loading action with the initial speeds of 10m/s, 20m/s and 30m/s are obtained for the lattice sandwich plate structure and the stiffened plate, as shown in fig. 15, 16 and 17; similarly, the data of displacement, stress, and the like of the upper panel and the upper panel can be obtained, see tables 3, 4, and 5, where the data in the tables are the data of displacement, stress, and the like corresponding to the time nodes at the initial velocity of 1ms, 4ms, 7ms, and 10 ms:
TABLE 3 displacement and stress data at different time points under the loading action with initial velocity of 10m/s
TABLE 4 displacement and stress data at different time points under the loading action with initial velocity of 20m/s
TABLE 5 Displacement and stress data at different time points under a loading action with an initial velocity of 30m/s
compared with the traditional stiffened plate, the dot matrix sandwich plate structure disclosed by the invention has the following advantages that:
(1) the maximum displacement of the panel of the lattice sandwich plate structure and the traditional stiffened plate under the action of dynamic load is in the center of the plate, the deformation characteristics are similar, but under the same load, the deformation/displacement of the upper panel and the lower panel of the lattice sandwich plate structure is far smaller than that of the stiffened plate, and the maximum stress of the upper panel and the lower panel of the lattice sandwich plate structure is far smaller than that of the stiffened plate.
(2) When the stiffened plate bears initial speed loads of 20m/s and 30m/s, the stress of the plate exceeds the yield limit of the material, the stiffened plate enters plastic deformation, but the deformation of the lattice sandwich plate structure is kept in an elastic range. Therefore, in the aspect of impact resistance mechanical property, the performance of the lattice sandwich plate structure is far superior to that of a stiffened plate with the same quality.
Finally, it should be noted that the above embodiments are only used for illustrating the technical solutions of the present invention, and not for limiting the protection scope of the present invention, although the present invention has been described in detail with reference to the preferred embodiments, it should be understood by those skilled in the art that modifications or equivalent substitutions can be made on the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention.
Claims (7)
1. The concave octagonal cubic lattice sandwich plate structure is characterized in that the lattice structure sandwich plate is formed by laminating a plurality of lattice groups, and each lattice group comprises a plurality of single structures distributed in an array manner;
The single body structure consists of two square frames which have the same side length and are arranged oppositely in parallel up and down, and a telescopic frame which is arranged between the two frames and is formed by connecting eight telescopic connecting rods end to end;
the eight connecting rods on the telescopic frame comprise four positioning rods which are arranged at intervals and are respectively parallel to four edges of the square frame and four middle rods for connecting the positioning rods;
Between each positioning rod and the frame parallel to the positioning rod, two end points of the positioning rod and the top point of the frame on the same side are connected through an inclined rod;
the length of the diagonal rods positioned on the upper side of the telescopic frame is the same, and the length of the diagonal rods positioned on the lower side of the telescopic frame is the same.
2. the sandwich panel structure of claim 1, wherein the plurality of cell structures are arranged in an array along two vertical edges of a square frame of the cell structure in the array group.
3. The sandwich panel structure of claim 1, wherein in the single structure, four positioning rods are respectively located on four sides of a rectangular parallelepiped formed by two side frames.
4. The sandwich panel structure of claim 1, wherein the plane of the expansion frame is the middle plane of the planes of the two side frames.
5. The sandwich panel structure of claim 1, wherein said frame is made of square rods, and said connecting rods and diagonal rods are made of round rods.
6. The sandwich panel structure of claim 1, wherein the length of the diagonal member is half of the side length of the square frame.
7. The sandwich plate structure of claim 1, wherein the square frame is formed by square rods with a length of 30mm, the cross section of each square rod is a square with a side length of 3mm, the connecting rods and the inclined rods are round rods with a diameter of 3mm, and the length of each inclined rod is 15 mm.
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| CN109878443B (en) * | 2019-03-12 | 2022-04-19 | 南京理工大学 | Energy absorption box based on inner core with concave polyhedron negative Poisson ratio three-dimensional structure |
| CN110744873A (en) * | 2019-11-22 | 2020-02-04 | 南京工业大学 | 3D printing structure composite material sandwich board with negative Poisson ratio effect and processing method |
| CN112012983B (en) * | 2020-09-12 | 2022-08-30 | 长沙理工大学 | Negative Poisson ratio flexible buffering hydraulic cylinder |
| CN112861252B (en) * | 2020-12-24 | 2022-07-12 | 中国航空工业集团公司成都飞机设计研究所 | Lattice standard unit and lattice structure for aircraft structure design and modeling |
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