Strain (mechanics)

Depending on the amount of strain, or local deformation, the analysis of deformation is subdivided into three deformation theories: • Finite strain theory, also called large strain theory, large deformation theory, deals with deformations in which both rotations and strains are arbitrarily large. In this case, the undeformed and deformed configurations of the continuum are significantly different and a clear distinction has to be made between them. This is commonly the case with elastomers, plastically-deforming materials and other fluids and biological soft tissue. • Infinitesimal strain theory, also called small strain theory, small deformation theory, small displacement theory, or small displacement-gradient theory where strains and rotations are both small. In this case, the undeformed and deformed configurations of the body can be assumed identical. The infinitesimal strain theory is used in the analysis of deformations of materials exhibiting elastic behavior, such as materials found in mechanical and civil engineering applications, e.g. concrete and steel. • Large-displacement or large-rotation theory, which assumes small strains but large rotations and displacements. ==Strain measures==

In each of these theories the strain is then defined differently. The engineering strain is the most common definition applied to materials used in mechanical and structural engineering, which are subjected to very small deformations. On the other hand, for some materials, e.g., elastomers and polymers, subjected to large deformations, the engineering definition of strain is not applicable, e.g. typical engineering strains greater than 1%; thus other more complex definitions of strain are required, such as stretch, logarithmic strain, Green strain, and Almansi strain. Engineering strain Engineering strain, also known as Cauchy strain, is expressed as the ratio of total deformation to the initial dimension of the material body on which forces are applied. In the case of a material line element or fiber axially loaded, its elongation gives rise to an engineering normal strain or engineering extensional strain , which equals the relative elongation or the change in length per unit of the original length of the line element or fibers (in meters per meter). The normal strain is positive if the material fibers are stretched and negative if they are compressed. Thus, we have e=\frac{\Delta L}{L} = \frac{l -L}{L}, where is the engineering normal strain, is the original length of the fiber and is the final length of the fiber. The true shear strain is defined as the change in the angle (in radians) between two material line elements initially perpendicular to each other in the undeformed or initial configuration. The engineering shear strain is defined as the tangent of that angle, and is equal to the length of deformation at its maximum divided by the perpendicular length in the plane of force application, which sometimes makes it easier to calculate. Stretch ratio The stretch ratio or extension ratio (symbol λ) is an alternative measure related to the extensional or normal strain of an axially loaded differential line element. It is defined as the ratio between the final length and the initial length of the material line. \lambda = \frac{l}{L} The extension ratio λ is related to the engineering strain e by e = \lambda - 1 This equation implies that when the normal strain is zero, so that there is no deformation, the stretch ratio is equal to unity. The stretch ratio is used in the analysis of materials that exhibit large deformations, such as elastomers, which can sustain stretch ratios of 3 or 4 before they fail. On the other hand, traditional engineering materials, such as concrete or steel, fail at much lower stretch ratios. Logarithmic strain The logarithmic strain , also called, true strain or Hencky strain. Considering an incremental strain (Ludwik) \delta \varepsilon = \frac{\delta l}{l} the logarithmic strain is obtained by integrating this incremental strain: \begin{align} \int\delta \varepsilon &= \int_L^l \frac{\delta l}{l} \\ \varepsilon &= \ln\left(\frac{l}{L}\right) = \ln (\lambda) \\ &= \ln(1+e) \\ &= e - \frac{e^2}{2} + \frac{e^3}{3} - \cdots \end{align} where is the engineering strain. The logarithmic strain provides the correct measure of the final strain when deformation takes place in a series of increments, taking into account the influence of the strain path. Green strain The Green strain is defined as: \varepsilon_G = \tfrac{1}{2} \left(\frac{l^2-L^2}{L^2}\right) = \tfrac{1}{2} (\lambda^2-1) Almansi strain The Euler-Almansi strain is defined as \varepsilon_E = \tfrac{1}{2} \left(\frac{l^2-L^2}{l^2}\right) = \tfrac{1}{2} \left(1-\frac{1}{\lambda^2}\right) ==Strain tensor==

The (infinitesimal) strain tensor (symbol \boldsymbol\varepsilon) is defined in the International System of Quantities (ISQ), more specifically in ISO 80000-4 (Mechanics), as a "tensor quantity representing the deformation of matter caused by stress. Strain tensor is symmetric and has three linear strain and three shear strain (Cartesian) components." ISO 80000-4 further defines linear strain as the "quotient of change in length of an object and its length" and shear strain as the "quotient of parallel displacement of two surfaces of a layer and the thickness of the layer". Thus, strains are classified as either normal or shear. A normal strain is perpendicular to the face of an element, and a shear strain is parallel to it. These definitions are consistent with those of normal stress and shear stress. The strain tensor can then be expressed in terms of normal and shear components as: \underline{\underline{\boldsymbol{\varepsilon}}} = \begin{bmatrix} \varepsilon_{xx} & \varepsilon_{xy} & \varepsilon_{xz} \\ \varepsilon_{yx} & \varepsilon_{yy} & \varepsilon_{yz} \\ \varepsilon_{zx} & \varepsilon_{zy} & \varepsilon_{zz} \\ \end{bmatrix} = \begin{bmatrix} \varepsilon_{xx} & \tfrac 1 2\gamma_{xy} & \tfrac12\gamma_{xz} \\ \tfrac 1 2\gamma_{yx} & \varepsilon_{yy} & \tfrac 1 2\gamma_{yz} \\ \tfrac12\gamma_{zx} & \tfrac 1 2 \gamma_{zy} & \varepsilon_{zz} \\ \end{bmatrix} Geometric setting Consider a two-dimensional, infinitesimal, rectangular material element with dimensions , which, after deformation, takes the form of a rhombus. The deformation is described by the displacement field . From the geometry of the adjacent figure we have \mathrm{length}(AB) = dx and \begin{align} \mathrm{length}(ab) &= \sqrt{\left(dx+\frac{\partial u_x}{\partial x}dx \right)^2 + \left( \frac{\partial u_y}{\partial x}dx \right)^2} \\ &= \sqrt{dx^2\left(1+\frac{\partial u_x}{\partial x} \right)^2 + dx^2\left( \frac{\partial u_y}{\partial x} \right)^2} \\ &= dx~\sqrt{\left(1+\frac{\partial u_x}{\partial x} \right)^2 + \left( \frac{\partial u_y}{\partial x} \right)^2} \end{align} For very small displacement gradients the squares of the derivative of u_y and u_x are negligible and we have \mathrm{length}(ab) \approx dx \left(1+\frac{\partial u_x}{\partial x}\right) = dx + \frac{\partial u_x}{\partial x} dx Normal strain For an isotropic material that obeys Hooke's law, a normal stress will cause a normal strain. Normal strains produce dilations. The normal strain in the -direction of the rectangular element is defined by \varepsilon_x = \frac{\text{extension}}{\text{original length}} = \frac{\mathrm{length}(ab) - \mathrm{length}(AB)}{\mathrm{length}(AB)} = \frac{\partial u_x}{\partial x} Similarly, the normal strain in the - and -directions becomes \varepsilon_y = \frac{\partial u_y}{\partial y} \quad , \qquad \varepsilon_z = \frac{\partial u_z}{\partial z} Shear strain The engineering shear strain () is defined as the change in angle between lines and . Therefore, \gamma_{xy} = \alpha + \beta From the geometry of the figure, we have \begin{align} \tan \alpha & = \frac{\tfrac{\partial u_y}{\partial x} dx}{dx + \tfrac{\partial u_x}{\partial x}dx} = \frac{\tfrac{\partial u_y}{\partial x}}{1 + \tfrac{\partial u_x}{\partial x}} \\ \tan \beta & = \frac{\tfrac{\partial u_x}{\partial y}dy}{dy+\tfrac{\partial u_y}{\partial y}dy}=\frac{\tfrac{\partial u_x}{\partial y}}{1+\tfrac{\partial u_y}{\partial y}} \end{align} For small displacement gradients we have \frac{\partial u_x}{\partial x} \ll 1 ~;~~ \frac{\partial u_y}{\partial y} \ll 1 For small rotations, i.e. and are ≪ 1 we have , . Therefore, \alpha \approx \frac{\partial u_y}{\partial x} ~;~~ \beta \approx \frac{\partial u_x}{\partial y} thus \gamma_{xy} = \alpha + \beta = \frac{\partial u_y}{\partial x} + \frac{\partial u_x}{\partial y} By interchanging and and and , it can be shown that . Similarly, for the - and -planes, we have \gamma_{yz} = \gamma_{zy} = \frac{\partial u_y}{\partial z} + \frac{\partial u_z}{\partial y} \quad , \qquad \gamma_{zx} = \gamma_{xz} = \frac{\partial u_z}{\partial x} + \frac{\partial u_x}{\partial z} Volume strain ==Metric tensor==

A strain field associated with a displacement is defined, at any point, by the change in length of the tangent vectors representing the speeds of arbitrarily parametrized curves passing through that point. A basic geometric result, due to Fréchet, von Neumann and Jordan, states that, if the lengths of the tangent vectors fulfil the axioms of a norm and the parallelogram law, then the length of a vector is the square root of the value of the quadratic form associated, by the polarization formula, with a positive definite bilinear map called the metric tensor. ==See also==