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## Stress (physics)
Stress is often broken down into its shear and normal components as these have unique physical significance. In short, stress is to force as strain is to deformation.
The term Solids, liquids and gases have stress fields. Static fluids support normal stress (hydrostatic pressure) but will flow under shear stress. Moving viscous fluids can support shear stress (dynamic pressure). Solids can support both shear and normal stress, with ductile materials failing under shear and brittle materials failing under normal stress. All materials have temperature dependent variations in stress related properties, and non-newtonian materials have rate-dependent variations. ## Additional recommended knowledge
## Stress tensorStress is a second-order tensor with nine components, but can be fully described with six components due to symmetry in the absence of body moments. In where the
The components of the stress tensor depend on the orientation of the plane that passes through the point under consideration, i.e on the viewpoint of the observer. This would lead to the incorrect conclusion that the stress on a structure, and hence its proximity to failure, depends on the viewpoint of the observer. However, every tensor, including stress, has invariants that do not depend on the choice of viewpoint. The length of a first-order tensor, i.e a vector, is a simple example. The existence of invariants means that the components seen by one observer are related, via the tensor transformation relations, to those seen by any other observer. The transformation relations for a second-order tensor like stress are different from those of a first-order tensor, which is why it is misleading to speak of the stress 'vector'. Mohr's circle method is a graphical method for performing stress (or strain) transformations. When the stress tensor is needed to fully describe the state of stress in a body, it is useful to break the concept up into smaller parts that have physical significance. In a 1-dimensional system, such as a uniaxially loaded bar, stress is simply equal to the applied force divided by the cross-sectional area of the bar (see also pressure). The 2-D or 3-D cases are more complex. In three dimensions, the internal force acting on a small area ## Stress in one-dimensional bodiesAll real objects occupy three-dimensional space. However, if two dimensions are very large or very small compared to the others, the object may be modelled as one-dimensional. This simplifies the mathematical modelling of the object. One-dimensional objects include a piece of wire loaded at the ends and viewed from the side, and a metal sheet loaded on the face and viewed up close and through the cross section. For one-dimensional objects, the stress tensor has only one component and is indistinguishable from a scalar. The simplest definition of stress, σ =
In one dimension, conversion between true stress and nominal (engineering) stress is given by - σ
_{true}= (1 + ε_{e})(σ_{e}),
where ε - ε
_{true}= ln(1 + ε_{e}).
In uniaxial tension, true stress is then greater than nominal stress. The converse holds in compression. Example: A steel bolt of diameter 5 mm has a cross-sectional area of 19.6 mm The ultimate tensile strength is a property of a material and is usually determined experimentally from a uniaxial tensile test. It allows the calculation of the load that would cause fracture. The compressive strength is a similar property for compressive loads. The yield strength is the value of stress causing plastic deformation. ## Stress in two-dimensional bodies
All real objects occupy 3-dimensional space. However, if one dimension is very large or very small compared to the others, the object may be modelled as two-dimensional. This simplifies the mathematical modelling of the object. Two-dimensional objects include a piece of wire Notice that the same physical, three-dimensional object can be modelled as one-dimensional, two-dimensional or even three-dimensional, depending on the loading and viewpoint of the observer. ## Plane stressPlane stress is a two-dimensional state of stress (Figure 2). This 2-D state models well the state of stresses in a flat, thin plate loaded in the plane of the plate. Figure 2 shows the stresses on the See also plane strain. ## Principal stresses in 2-DAugustin Louis Cauchy was the first to demonstrate that at a given point, it is always possible to locate two orthogonal planes in which the shear stress vanishes. These planes in which the normal forces are acting are called the The two dimensional Cauchy stress tensor is defined as: Then principal stresses σ Those formulas have geometrical interpretation in the form of Mohr Circle presented in section below. ## Mohr's circleMohr's circle is a graphical representation of any 2-D stress state. It was named for Christian Otto Mohr. Mohr's circle may also be applied to three-dimensional stress. In this case, the diagram has three circles, two within a third. Mohr's circle is used to find the principal stresses, maximum shear stresses, and principal planes. For example, if the material is brittle, the engineer might use Mohr's circle to find the maximum component of normal stress (tension or compression); and for ductile materials, the engineer might look for the maximum shear stress. ## Stress in three dimensional bodies## Cauchy's principleCauchy enunciated the principle that, within a body, the forces that an enclosed volume imposes on the remainder of the material must be in equilibrium with the forces upon it from the remainder of the body. This intuition provides a route to characterizing and calculating complicated patterns of stress. To be exact, the stress at a point may be determined by considering a small element of the body that has an area Δ Being a tensor, the stress has two directional components: one for force and one for plane orientation; in three dimensions these can be two forces within the plane of the area The considerations above can be generalized to three dimensions. However, this is very complicated, since each shear loading produces shear stresses in one orientation and normal stresses in other orientations, and vice versa. Often, only certain components of stress will be important, depending on the material in question. The von Mises stress is derived from the ## The stress tensor in 3-D(see also viscosity and Hooke's law for development of the stress tensor in viscous and elastic materials respectively) Because the behavior of a body does not depend on the coordinate systems used to measure it, stress can be described by a tensor. In the absence of body moments, the stress tensor is symmetric and can always be resolved into the sum of two symmetric tensors: - a
**mean**or**hydrostatic stress**tensor, involving only pure tension and compression; and - a
**shear**or**deviatoric stress**tensor, involving only shear stress.
In the case of a fluid, Pascal's law shows that the hydrostatic stress is the same in all directions, at least to a first approximation, so can be captured by the scalar quantity pressure. Thus, in the case of a solid, the hydrostatic (or isostatic) pressure is defined as one third of the trace of the tensor, i.e., the mean of the diagonal terms. For viscous fluids the Cauchy stress tensor σ is defined as:
If the fluid is incompressible it follows that: If the fluid is compressible the assumption above is true, if the viscosity of compression vanishes: ## Principal stresses in 3-DThe three dimensional Cauchy stress tensor is defined as: In equilibrium, τ To calculate the principal stresses σ Then the characteristic equation of 3-D principal stresses is expressed as: The three roots of this equation are principal stresses σ ## Generalized notationIn the generalized stress tensor notation, the tensor components are written σ (caution: subscript notation in this section is different from the rest of the article - the order of subscripts is reversed) The first step is to number the sides of the cube. When the lines are parallel to a vector base , then: - the sides perpendicular to are called
*j*and -*j*; and - from the center of the cube, points toward the
*j*side, while the -*j*side is at the opposite.
σ
This generalized notation allows an easy writing of equations of the continuum mechanics, such as the generalized Hooke's law: The correspondence with the former notation is thus:
## Why is Newtonian stress a symmetric tensor?The fact that the Newtonian stress is a symmetric tensor follows from some simple considerations. The force on a small volume element will be the sum of all the stress forces over the surface area of that element. Suppose we have a volume element in the form of a long bar with a triangular cross section, where the triangle is a right triangle. We can neglect the forces on the ends of the bar, because they are small compared to the faces of the bar. Let be the vector area of one face of the bar, be the area of the other, and be the area of the "hypotenuse face" of the bar. It can be seen that Let's say is the force on area and likewise for the other faces. Since the stress is by definition the force per unit area, it is clear that The total force on the volume element will be: Let's suppose that the volume element contains mass, at a constant density. The important point is that if we make the volume smaller, say by halving all lengths, the area will decrease by a factor of four, while the volume will decrease by a factor of eight. As the size of the volume element goes to zero, the ratio of area to volume will become infinite. The total stress force on the element is proportional to its area, and so as the volume of the element goes to zero, the force/mass (i.e. acceleration) will also become infinite, unless the total force is zero. In other words: This, along with the second equation above, proves that the σ function is a linear vector operator (i.e. a tensor). By an entirely analogous argument, we can show that the total torque on the volume element (due to stress forces) must be zero, and that it follows from this restriction that the stress tensor must be symmetric. However, there are two fundamental ways in which this mode of thinking can be misleading. First, when applying this argument in tandem with the underlying assumption from continuum mechanics that the Knudsen number is strictly less than one, then in the limit , the symmetry assumptions in the stress tensor may break down. This is the case of Non-Newtonian fluid, and can lead to rotationally non-invariant fluids, such as polymers. The other case is when the system is operating on a purely finite scale, such as is the case in mechanics where Finite deformation tensors are used. ## Equilibrium conditionsThe state of stress as defined by the stress tensor is an equilibrium state if the following conditions are satisfied: σ These equations can be compactly written using Einstein notation in which repeated indices are summed. Defining as the equilibrium conditions are written: The equilibrium conditions may be derived from the condition that the net force on an infinitesimal volume element must be zero. Consider an infinitesimal cube aligned with the A similar calculation can be carried out for the other pairs of faces. The sum of all the stress forces on the infinitesimal cube will then be Since the net force on the cube must be zero, it follows that this stress force must be balanced by the force per unit volume Equilibrium also requires that the resultant moment on the cube of material must be zero. Taking the moment of the forces above about any suitable point, it follows that, for equilibrium in the absence of body moments - .
The stress tensor is then symmetric and the subscripts can be written in either order. ## Stress in big bending deformationFor - Assumption of flat sections - before and after deformation the considered section of body remains flat (i.e. is not swirled).
- Shear and normal stresses in this section that are perpendicular to the normal vector of cross section have no influence on normal stresses that are parallel to this section.
The - ρ < 10
*h*
With those assumptions the stress in big bending is calculated as: where *F*is the normal force*A*is the section area*M*is the bending moment- ρ is the local bending radius (the radius of bending at the current section)
*I*_{x}' is the area moment of inertia along the**x**axis, at the*y*place (see Steiner's theorem)*y*is the position along**y**axis on the section area in which the stress σ is calculated
When bending radius ρ approaches infinity and - .
## Stress measurementAs with force, stress cannot be measured directly but is usually inferred from measurements of strain and knowledge of elastic properties of the material. Devices capable of measuring stress indirectly in this way are strain gauges and piezoresistors. ## UnitsThe SI unit for stress is the pascal (symbol ## Residual stressResidual stresses are stresses that remain after the original cause of the stresses has been removed. Residual stresses occur for a variety of reasons, including inelastic deformations and heat treatment. Heat from welding may cause localized expansion. When the finished weldment cools, some areas cool and contract more than others, leaving residual stresses. Castings may also have large residual stresses due to uneven cooling. While uncontrolled residual stresses are undesirable, many designs rely on controlled ones. For example, toughened glass and prestressed concrete rely on residual stress to prevent brittle failure. Similarly, a gradient in martensite formation leaves residual stress in some swords with particularly hard edges (notably the katana), which can prevent the opening of edge cracks. In certain types of gun barrels made with two telescoping tubes forced together, the inner tube is compressed while the outer tube stretches, preventing cracks from opening in the rifling when the gun is fired. These tubes are often heated or immersed in liquid nitrogen to aid assembly. In manufacturing, press fits are the most common intentional use of residual stress. Automotive wheel studs, for example, are pressed into holes on the wheel hub. The holes are smaller than the studs, requiring force to drive the studs into place. The residual stresses fasten the parts together. Nails are another example. ## See also- 3-D elasticity
- Linear elasticity
- Piola-Kirchhoff stress tensor
- Shot peening
- Strain
- Strain tensor
- Stress-energy tensor
- Stress-strain curve
- Stress concentration
- Von Mises stress
- Yield stress
- Yield surface
## Books- Dieter, G. E. (3 ed.). (1989).
*Mechanical Metallurgy*. New York: McGraw-Hill.__ISBN 0-07-100406-8__. - Love, A. E. H. (4 ed.). (1944).
*Treatise on the Mathematical Theory of Elasticity*. New York: Dover Publications.__ISBN 0-486-60174-9__. - Marsden, J. E., & Hughes, T. J. R. (1994).
*Mathematical Foundations of Elasticity*. New York: Dover Publications.__ISBN 0-486-67865-2__. - L.D.Landau and E.M.Lifshitz. (1959).
*Theory of Elasticity*.
- ESDU Stress Analysis Methods
- True stress and true strain
- Stress-Strain Curve for Ductile Material
Categories: Continuum mechanics | Materials science |
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This article is licensed under the GNU Free Documentation License. It uses material from the Wikipedia article "Stress_(physics)". A list of authors is available in Wikipedia. |