Algebraic Structure Of The Honeycomb Hexagonal Topology Structure

After the analysis on the first design brought to light the zero for members, it was decided that these members should be removed. In order to combat the flex of such a simple design the decision was made to double the thickness. This design would have the same outer frame of two triangles with a height of 20 centimeters and a width of 40 centimeters. Instead of being spaced five centimeters apart the wood be bonded directly together using Gorilla Glue. Balsa wood, a very lightweight wood with properties similar to a dense foam, was used for the main supporting member. Basswood, a lightweight yet firm wood, was used for the horizontal member. The final design added a triple layer sheet of balsa wood to rear side of the truss. This balsa sheet was added for the purpose of mounting and supporting the main structure. Additionally, a five centimeter square frame of bass wood was added at the end of the boomilever to place the loading block for testing. Once this design was implemented two key issues were discovered. First, due to the properties of the bass wood and balsa wood it was obvious that the placement needed to be reversed. The bass wood should be used for the hypotenuse and the balsa wood should be used for the

With modern computational methods, most notably finite element analysis, designers are now able to simulate the response of a structure under a multitude of highly complex loading conditions. Another important aspect of these tools are their ability to solve ever increasingly complex problems in a faster time than ever before. These advanced computational tools also allow engineers to optimize designs much faster. These new optimal designs will improve the strength and stiffness of structures and lower their weight. This will not only improve a design's performance, but also help improve efficiency. These abilities are very exciting since they allow for a more fully developed and accurate picture of a structure's performance evident even in the most demanding

Mesh size was selected based on the average size of components and where the mesh became independent of results. Over the course of the following simulations, meshing will be completed automatically based on component size; if done otherwise, it is due to poor element quality or element violations due to the difference in element size required for components. When this occurs, mesh size is selected based on medium between component-mesh-size values.

Each separate truss (of the dimensions 920x5x50mm) consisted of a Pratt truss with nine diagonal members on each side of the centre. The model was tested in sufficiently isolated condition by tutors. It successfully passed the initial weight test, and satisfactorily resisted horizontal forces. Once fitted onto the testing rig, loads were applied and increased incrementally. Slight deformation was observed before failing at 12.5 kg, at which force a collection of members failed in succession, concluding the test.

{N} and {M} are the generalised stresses can can be expressed as membrane strains and curvatures by using the laminar stress-strain relationship and Love Kirchhoff hypothesis.

In Figure 4, Young's modulus is plotted against yield strength. The diagonal line in the figure represents the material index M= σy/E. Materials below the diagonal line are the best candidate materials because they will remain elastic while providing the maximum conformability. All materials that cost more than $2.20 per pound and have a UV rating of "poor" were eliminated. Also, only materials that can be made through the polymer extrusion process were considered. The candidate materials are listed in Table 1 and ranked by the material index. The current material, TPV, is included in the table for

quadrilateral cuboid or ”strip” form and of mass close enough to assure a relatively low

Experiment Two: Stiffness Report from laboratory work performed on 12 May 2011 as a part of the unit of study CIVL2201 Structural Mechanics

\parindent{\ \ \ }Figure~\ref{fig:mdg} shows the average strain at different time instants for various mesh densities. The variation in the results obtained with the finest mesh and the mesh immediately next to the finest one is less than 5\%. Hence, we can reasonably assume that the study reached convergence. The difference in results obtained from the dense mesh (i.e., mesh 6) and coarse mesh (i.e., mesh 3) is less than 8\%.

Abstract— This work illustrates the manufacturing of the honeycomb hexagonal topology structures by the kirigami technical, and the compressive testing of this specimen. The cellular configuration is simulated using a series of finite element models representing fullscale. The models are benchmarked against experimental results from pure compression tests. Finite element models of the honeycomb assemblies under compressive loading have been developed using nonlinear shell elements from an ANSYS code. Good agreement is observed between numerical nonlinear simulations and the experimental results.

Thus, we conclude that in this project we can use the Kawasaki theorem to construct a pelican or a crane using certain folds of origami.

(Numerical)Finite Element Analysis of Buckling and wrinkling of prestressed membranes Kapton, Mylar & Kevlar with different types of shapes and different load conditions

Helical spring is defined as an elastic body, whose function is to distort when loaded and to recover its original shape when the load is removed. The helical springs are made up of a wire coiled in the form of a helix and are primarily intended for compressive or tensile loads. The cross-section of the wire from which the spring is made may be circular, square or rectangular. Helical compression springs have applications to resist applied compression forces or in the push mode, store energy to provide the "push". Different forms of compression springs are produced. The helical springs are said to be closely coiled when the spring wire is coiled so close that the plane containing each

The main load carrying structure of a wing is the torsion box formed by front spar, rear spar, and top spar & bottom skins. In the preliminary design stages an effect is made to arrive at an efficient design of this box –structure. The load carrying capacity of this box structure is largely controlled by the buckling of the compression cover plate. In order to get a minimum weight design of such a box the

The ANSYS is a large scale multi-purpose finite element computer program. This is used for solving several classes of engineering analysis. Different types of analysis can be done here. They can be static and dynamic structural analysis, mode-frequency and buckling, eigen value problems, steady state and transient heat transfer problems, static or time-varying magnetic analyses and various types of field and coupled-field applications. ANSYS consist many special features which allow nonlinearities or secondary effects such as plasticity, hyper elasticity, large strain, creep, large deflections, swelling, stress stiffening, contact, temperature dependency, radiation and material anisotropy, to be included in the solution. Other special capabilities have been developed by ANSYS and added to the program which contribute further to making ANSYS a multi-purpose tool for varied engineering disciplines.