Figure 3–1 shows the element families most commonly used in a stress analysis. One of the major distinctions between different element families is the geometry type that each family assumes.

The element families that you will use in this guide—continuum, shell, beam, truss, and rigid elements—are discussed in detail in other chapters. The other element families are not covered in this guide; if you are interested in using them in your models, read about them in the ABAQUS Analysis User's Manual.

The first letter or letters of an element's name indicate to which family the element belongs. For example, the S in S4R indicates this is a shell element, while the C in C3D8I indicates this is a continuum element.

The degrees of freedom (dof) are the fundamental variables calculated during the analysis. For a stress/displacement simulation the degrees of freedom are the translations as well as, for shell and beam elements, the rotations at each node. For a heat transfer simulation the degrees of freedom are the temperatures at each node; a heat transfer analysis, therefore, requires the use of different elements than a stress analysis, since the degrees of freedom are not the same.

The following numbering convention is used for the degrees of freedom in ABAQUS:

Axisymmetric elements are the exception, with the displacement and rotation degrees of freedom referred to as follows:

See Chapter 5, “Using Shell Elements,” for a discussion of defining a local coordinate system at the nodes.

In this guide our attention is restricted to structural applications. Therefore, only elements with translational and rotational degrees of freedom are discussed. For information on other types of elements (for example, heat transfer elements) consult the ABAQUS Analysis User's Manual.

Displacements, rotations, temperatures, and the other degrees of freedom mentioned in the previous section are calculated only at the nodes of the element. At any other point in the element, the displacements are obtained by interpolating from the nodal displacements. Usually the interpolation order is determined by the number of nodes used in the element. Elements that have nodes only at their corners, such as the 8-node brick shown in Figure 3–2(a), use linear interpolation in each direction and are often called linear elements or first-order elements. Elements with midside nodes, such as the 20-node brick shown in Figure 3–2(b), use quadratic interpolation and are often called quadratic elements or second-order elements.

Typically, the number of nodes in an element is clearly identified in its name. The 8-node brick element, as you have seen, is called C3D8; and the 8-node general shell element is called S8R. The beam element family uses a slightly different convention: the order of interpolation is identified in the name. Thus, a first-order, three-dimensional beam element is called B31, whereas a second-order, three-dimensional beam element is called B32.

An element's formulation refers to the mathematical theory used to define the element's behavior. All of the stress/displacement elements in ABAQUS are based on the Lagrangian or material description of behavior: the material associated with an element remains associated with the element throughout the analysis, and material cannot flow across element boundaries. In the alternative, Eulerian or spatial description, elements are fixed in space as the material flows through them. Eulerian methods are used commonly in fluid mechanics simulations. ABAQUS uses Eulerian elements to model convective heat transfer, a topic not discussed in this guide.

To accommodate different types of behavior, some element families in ABAQUS include elements with several different formulations. For example, the shell element family has three classes: one with a general-purpose formulation, another with a thin-only formulation, and yet another with a thick-only formulation. (These shell element formulations are explained in Chapter 5, “Using Shell Elements.”)

Some element families have a standard formulation as well as some alternative formulations. Elements with alternative formulations are identified by an additional character at the end of the element name. For example, the continuum, beam, and truss element families include members with a hybrid formulation in which the pressure (continuum elements) or axial force (beam and truss elements) is treated as an additional unknown; these elements are identified by the letter “H” at the end of the name (C3D8H or B31H).

Some element formulations allow coupled field problems to be solved. For example, elements whose names begin with the letter C and end with the letter T (such as C3D8T) possess both mechanical and thermal degrees of freedom and are intended for coupled thermal-mechanical simulations.

Several of the most commonly used element formulations are discussed later in this guide.

ABAQUS uses numerical techniques to integrate various quantities over the volume of each element. Using Gaussian quadrature for most elements, ABAQUS evaluates the material response at each integration point in each element. When using continuum elements, you must choose between full or reduced integration, a choice that can have a significant effect on the accuracy of the element for a given problem, as discussed in detail in “Element formulation and integration,” Section 4.1.

ABAQUS uses the letter “R” at the end of the element name to distinguish reduced-integration elements (unless they are also hybrid elements, in which case the element name ends with the letters “RH”). For example, CAX4 is the fully integrated, linear, axisymmetric solid element; and CAX4R is the reduced-integration version of the same element.

Three-dimensional continuum elements can be hexahedra (bricks), wedges, or tetrahedra. The full inventory of three-dimensional continuum elements and the nodal connectivity for each type can be found in “Three-dimensional solid element library,” Section 22.1.4 of the ABAQUS Analysis User's Manual.

ABAQUS has several classes of two-dimensional continuum elements that differ from each other in their out-of-plane behavior. Two-dimensional elements can be quadrilateral or triangular. Figure 3–3 shows the three classes that are used most commonly.

Plane strain elements assume that the out-of-plane strain, , is zero; they can be used to model thick structures.

Plane stress elements assume that the out-of-plane stress, , is zero; they are suitable for modeling thin structures.

Axisymmetric elements without twist, the “CAX” class of elements, model a 360° ring; they are suitable for analyzing structures with axisymmetric geometry subjected to axisymmetric loading.

ABAQUS also provides generalized plane strain elements, axisymmetric elements with twist, and axisymmetric elements with asymmetric deformation.

Generalized plane strain elements include the additional generalization that the out-of-plane strain may vary linearly with position in the plane of the model. This formulation is particularly suited to the thermal-stress analysis of thick sections.

Axisymmetric elements with twist model an initially axisymmetric geometry that can twist about the axis of symmetry. These elements are useful for modeling the torsion of cylindrical structures, such as axisymmetric rubber bushings.

Axisymmetric elements with asymmetric deformation model an initially axisymmetric geometry that can deform asymmetrically (typically as a result of bending). They are useful for simulating problems such as an axisymmetric rubber mount that is subjected to shear loads.

The latter three classes of two-dimensional continuum elements are not discussed in this guide.

Two-dimensional solid elements must be defined in the 1–2 plane so that the node order is counterclockwise around the element perimeter, as shown in Figure 3–4.

All of the stress/displacement continuum elements have translational degrees of freedom at each node. Correspondingly, degrees of freedom 1, 2, and 3 are active in three-dimensional elements, while only degrees of freedom 1 and 2 are active in plane strain elements, plane stress elements, and axisymmetric elements without twist. Consult “Two-dimensional solid element library,” Section 22.1.3 of the ABAQUS Analysis User's Manual, to find the active degrees of freedom in the other classes of two-dimensional solid elements.

The *SOLID SECTION option defines the material and any additional geometric data associated with a set of continuum elements. For three-dimensional and axisymmetric elements no additional geometric information is required: the nodal coordinates completely define the element geometry. For plane stress and plane strain elements the thickness of the elements must be specified on the data line. For example, if the elements are 0.2 m thick, the element property definition would be the following:

*SOLID SECTION, ELSET=<element set name>, MATERIAL=<material name>
0.2,

Alternative formulations available for the continuum family of elements include an incompatible mode formulation (the last or second-to-last letter in the element name is I) and a hybrid element formulation (the last letter in the element name is H), both of which are discussed in detail later in this guide. The solid elements can use full or reduced integration. Both the formulation and type of integration can have a significant effect on the accuracy of solid elements, as discussed in “Element formulation and integration,” Section 4.1.

By default, element output variables such as stress and strain refer to the global Cartesian coordinate system. Thus, the -component of stress at the integration point shown in Figure 3–5(a) acts in the global 1-direction. Even if the element rotates during a large-displacement simulation, as shown in Figure 3–5(b), the default is still to use the global Cartesian system as the basis for defining the element variables. However, ABAQUS allows you to define a local coordinate system for element variables, using the *ORIENTATION option (see “Example: skew plate,” Section 5.5). This local coordinate system rotates with the motion of the element in large-displacement simulations. A local coordinate system can be very useful if the object being modeled has some natural material orientation, such as the fiber directions in a composite material.

General three-dimensional shell elements are available with three different formulations: general-purpose, thin-only, and thick-only. Triangular and quadrilateral elements with linear and quadratic interpolation are available. Both linear and quadratic axisymmetric shell elements are available. Table 3–1 summarizes the available shell elements.

Three-dimensional elements whose names end in the number “5” (e.g., S4R5, STRI65) have 5 degrees of freedom at each node: three translations and two in-plane rotations (i.e., no rotations about the shell normal). However, all six degrees of freedom are activated at a node if required; for example, if rotational boundary conditions are applied or the node is on a fold line of the shell.

The remaining three-dimensional shell elements (e.g., S4R and S8R) have six degrees of freedom at each node (three translations and three rotations).

The axisymmetric shells have three degrees of freedom associated with each node:

Use either the *SHELL GENERAL SECTION or the *SHELL SECTION option to define the thickness and material properties for a set of shell elements. These two options have similar formats:

*SHELL SECTION, ELSET=<element set name>, MATERIAL=<material name>
<thickness>,<number of section points>

*SHELL GENERAL SECTION, ELSET=<element set name>,
MATERIAL=<material name>
<thickness>

If you specify the *SHELL SECTION option, ABAQUS uses numerical integration to calculate the behavior at selected points through the thickness of the shell. These points are called section points, as shown in Figure 3–6. The MATERIAL parameter refers to a material property definition, which may be linear or nonlinear. You can specify any odd number of section points through the shell thickness.

The *SHELL GENERAL SECTION option allows you to define the cross-section behavior in a number of general ways to model linear or nonlinear behavior. Since ABAQUS models the shell's cross-section behavior directly in terms of section engineering quantities (area, moments of inertia, etc.) with this option, there is no need for ABAQUS to integrate any quantities over the element cross-section. Therefore, *SHELL GENERAL SECTION is less expensive computationally than *SHELL SECTION. The response is calculated in terms of force and moment resultants; the stresses and strains are calculated only when they are requested for output.

ABAQUS has three classes of shell elements distinguishable by their element formulations: general-purpose, thin-only, and thick-only. The shell formulations are discussed in detail in Chapter 5, “Using Shell Elements.” The S4, S4R, S3/S3R, and the SAX axisymmetric shell elements account for finite membrane strains and allow the shell thickness to change with the element deformation. All of the other shell elements assume small strains and no change in shell thickness, even though the element's nodes may undergo finite rotations.

All of the quadrilateral shell elements (except for S4) and the triangular shell element, S3/S3R, use reduced integration. The S4 element and the other triangular shell elements use full integration.

The element output variables for shells are defined in terms of local material directions that lie on the surface of each shell element. In large-displacement simulations these axes rotate with the element's deformation.

You can also define a local material coordinate system that rotates with the element's deformation in a large-displacement analysis.

Linear, quadratic, and cubic beams are available in two and three dimensions.

Three-dimensional beams have six degrees of freedom at each node: three translational degrees of freedom (1–3) and three rotational degrees of freedom (4–6). “Open-section”-type beams (such as B31OS) have an additional degree of freedom (7) that represents the warping of the beam cross-section.

Two-dimensional beams have three degrees of freedom at each node: two translational degrees of freedom (1 and 2) and one rotational degree of freedom (6) about the normal to the plane of the model.

Use either the *BEAM SECTION or the *BEAM GENERAL SECTION option to define the geometry of the beam cross-section; the nodal coordinates define only the length.

If you specify the *BEAM SECTION option, the beam cross-section is defined geometrically, and the MATERIAL parameter refers to a material property definition. ABAQUS calculates the cross-section behavior of the beam by numerical integration over the cross-section, allowing both linear and nonlinear material behavior.

The *BEAM GENERAL SECTION option allows you to define the cross-section behavior in a number of general ways to model linear or nonlinear behavior. Since ABAQUS models the beam's cross-section behavior directly in terms of section engineering quantities (area, moments of inertia, etc.) with this option, there is no need for ABAQUS to integrate any quantities over the element cross-section. Therefore, *BEAM GENERAL SECTION is less expensive computationally than *BEAM SECTION. The response is calculated in terms of the force and moment resultants; the stresses and strains are calculated only when they are requested for output.

The linear beams (B21 and B31) and the quadratic beams (B22 and B32) are shear deformable and account for finite axial strains; therefore, they are suitable for modeling both slender and nonslender beams. The cubic beam elements (B23 and B33) do not account for shear flexibility and assume small axial strain, although large displacements and rotations of the beams are valid. They are, therefore, suitable for modeling slender beams. ABAQUS provides variants of linear and quadratic beam elements that are suitable for modeling thin-walled, open-section beams (B31OS and B32OS). These elements correctly model the effects of torsion and warping in open cross-sections, such as I-beams or U-section channels. Open-section beams are not covered in this guide.

ABAQUS also has hybrid beam elements that are used for modeling very slender members, such as flexible risers on offshore oil installations, or for modeling very stiff links. Hybrid beams are not covered in this guide.

The stress components in three-dimensional, shear-deformable beam elements are the axial stress () and the shear stress due to torsion (). The shear stress acts about the section wall in a thin-walled section. Corresponding strain measures are also available. The shear deformable beams also provide estimates of transverse shear forces on the section. The slender (cubic) beams have only the axial variables as output. Open-section beams in space also have only the axial variables as output, since the torsional shear stresses are negligible in this case.

All two-dimensional beams use only axial stress and strain.

The axial force, bending moments, and curvatures about the local beam axes can also be requested for output. For details of what components are available with which elements, refer to “Beam modeling: overview,” Section 23.3.1 of the ABAQUS Analysis User's Manual. Details of how the local beam axes are defined are given in Chapter 6, “Using Beam Elements.”

Linear and quadratic trusses are available in two and three dimensions.

Truss elements have only translational degrees of freedom at each node. Three-dimensional truss elements have degrees of freedom 1, 2, and 3, while two-dimensional truss elements have degrees of freedom 1 and 2.

The *SOLID SECTION option is used to specify the name of the material property definition associated with the given set of truss elements. The cross-sectional area is given on the data line:

*SOLID SECTION, ELSET=<element set name>, MATERIAL=<material>
<cross-sectional area>

In addition to the standard formulation a hybrid truss element formulation is available. It is useful for modeling very stiff links whose stiffness is much greater than that of the overall structure.

Axial stress and strain are available as output.