FORMULATION OF FINITE ELEMENT EQUATIONS 9 1 2 3 0 L 2L x b R Figure 1.3: Tension of the one dimensional bar subjected to a distributed load and a concentrated load. Properties of the shape functions: 1. 1. u … Integrate by parts using the Neumann and Robin boundary conditions 3. In the finite element approach, the nodal values of the field variable are treated as unknown constants that are to be determined. The interpolation functions are most often polynomial forms of the independent variables, Kronecker delta property 3. Completeness y y x x i i = = = ∑ ∑ ∑ = = = 4 i 1 i 4 i 1 i 4 i 1 i N N N 1 2. Task is to find the function ‘w’ that minimizes the potential energy of the system From the Principle of Minimum Potential Energy, that function ‘w’ is the exact solution. In the finite element method, or for that matter,in any approximate method, we are trying to replace an unknown function Ø(x), which is the exact solution to a boundary value problem over a domain enclosed by a boundary by an approximate function Ø(x) which is constituted from a set of shape or basis functions. The shape functions are also first order, just as the original polynomial was. We will use D’Alembert’s principle and introduce an effective body force Xe as. The shape functions N1, N2, N3 and N4 are bilinear functions of x and y ⎩ ⎨ ⎧ = at other nodes at node i x y 0 1 ' ' Ni ( , ) 3. the minus sign indicates that the acceleration produces D’Alembert’s body forces opposite in the direction as the acceleration. Finite element formulation, takes as its starting point, not the strong formulation, but the Principle of Minimum Potential Energy. For scalar elds the location of the nodal unknowns in d is most obviously as follows d I = d(I); (6) An IsoparametricRectangular Lagrange Element (Cont.) of the consistent mass matrix where use the shape function to model the mass along the bar. Derivation of shape function and stiffness matrix for a 1 dimensional bar element Consider a bar element with nodes 1 and 2 as shown with displacements of u 1 and u 2 at the respective nodes The displacement u can be given as u=a 0 +a 1 x -----(1) where a 0 and a1 are generalised coordinates. Generalization of FEM Using Node-Based Shape Functions Kanok-Nukulchai, W.1*, Wong, F.T.2, and Sommanawat, W.3 Abstract: In standard FEM, the stiffness of an element is exclusively influenced by nodes associated with the element via its element-based shape functions. Multiply the residual of the PDE by a weighting function wvanishing on the Dirichlet boundary Γ0 and set the integral over Ω equal to zero 2. 1.3. The shape functions, which are used to interpolate global coordinates and displacement components and weighting function components between their respective nodal values, must be linear along an element side. 2011 Alex Grishin MAE 323 Lecture 3 Shape Functions and Meshing 13 •The shape functions are obtained by using the shape functions from before for a rectangular domain, setting a and b to 1, and replace x and y with r and s Lagrange Interpolation and Natural Coordinates (Cont.) In the two-dimensional plane these functions are functions of the isoparametric coordinates ξ1 and ξ2. Finite Element Discretization The problem domain is partitioned into a collection of pre-selected finite elements (either triangular or quadrilateral) On each element displacements and test functions are interpolated using shape functions and the corresponding nodal values Shape functions Nodal values I(x) are the nite element shape functions, d I are the nodal un-knowns for the node Iwhich may be scalar or vector quantities (if uh(x) is a scalar or vector) and nnis the number of nodes in the discretization. The sum of the shape functions sums to one. In this paper, the authors present a method that can be viewed 3 are the interpolation functions, also known as shape functions or blending functions. From inspection of Eqn.26 we can deduce that each shape function has a value of 1 at its own node and a value of zero at the other nodes.
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