Products: ABAQUS/Standard ABAQUS/Explicit ABAQUS/CAE
The shell section behavior:
may or may not require numerical integration over the section;
can be linear or nonlinear; and
can be homogeneous or composed of layers of different material.
Two methods are provided to define the cross-sectional behavior of a shell.
Linear moment-bending and force-membrane strain relationships can be defined by using a general shell section (see “Using a general shell section to define the section behavior,” Section 23.6.6). In this case all calculations are done in terms of section forces and moments.
In ABAQUS/Standard when section properties are given directly (i.e., the section is not associated with one or more material definitions), strains and stresses are not available for output. However, when section properties are specified by one or more elastic material layers, strains and stresses are available when requested for output. In ABAQUS/Explicit stresses and strains are not available for output at the section points whenever a general shell section is used; only section forces, section moments, and section strains are available for output.
In ABAQUS/Standard nonlinear behavior of the shell section, formulated in terms of forces and moments, can be defined by using a general shell section in conjunction with user subroutine UGENS.
Alternatively, a shell section integrated during the analysis (see “Using a shell section integrated during the analysis to define the section behavior,” Section 23.6.5) allows the cross-sectional behavior to be calculated by numerical integration through the shell thickness, thus providing complete generality in material modeling. With this type of section any number of material points can be defined through the thickness and the material response can vary from point to point.
For conventional shell elements you can specify an offset of the reference surface from the shell's midsurface when the section properties are specified by one or more material layers. When the section properties are given directly, you cannot directly specify an offset; however, an offset can be included implicitly in the section properties. Offsets are ignored for continuum shell elements, since these elements do not have a reference surface or midsurface. You can define offsets for homogeneous conventional shells on an element-by-element basis with an element property assignment. See “Assigning element properties on an element-by-element basis,” Section 21.1.5, for details.
When a shell section integrated during the analysis (see “Using a shell section integrated during the analysis to define the section behavior,” Section 23.6.5) is used, ABAQUS uses numerical integration through the thickness of the shell to calculate the section properties. This type of shell section is generally used with nonlinear material behavior in the section. It must be used with shells that provide for heat transfer, since general shell sections do not allow the definition of heat transfer properties.
Use a general shell section (see “Using a general shell section to define the section behavior,” Section 23.6.6) if the response of the shell is linear elastic and its behavior is not dependent on changes in temperature or predefined field variables or, in ABAQUS/Standard, if nonlinear behavior in terms of forces and moments is to be defined in user subroutine UGENS.
For all shell elements in ABAQUS/Standard that use transverse shear stiffness and for the finite-strain shell elements in ABAQUS/Explicit, the transverse shear stiffness is computed by matching the shear response for the shell to that of a three-dimensional solid for the case of bending about one axis. For the small-strain shell elements in ABAQUS/Explicit the transverse shear stiffness is based on the effective shear modulus.
In all shell elements in ABAQUS/Standard that are valid for thick shell problems or that enforce the Kirchhoff constraint numerically (i.e., all shell elements except STRI3) and in the finite-strain shell elements in ABAQUS/Explicit (S3R, S4R, SAX1, SC6R, and SC8R), ABAQUS computes the transverse shear stiffness by matching the shear response for the case of the shell bending about one axis, using a parabolic variation of transverse shear stress in each layer. The approach is described in “Transverse shear stiffness in composite shells and offsets from the midsurface,” Section 3.6.8 of the ABAQUS Theory Manual, and generally provides a reasonable estimate of the shear flexibility of the shell. It also provides estimates of interlaminar shear stresses in composite shells. In calculating the transverse shear stiffness, ABAQUS assumes that the shell section directions are the principal bending directions (bending about one principal direction does not require a restraining moment about the other direction). For composite shells with orthotropic layers that are not symmetric about the shell midsurface, the shell section directions may not be the principal bending directions. In such cases the transverse shear stiffness is a less accurate approximation and will change if different shell section directions are used. ABAQUS computes the transverse shear stiffness only once at the begining of the analysis based on initial elastic properties given in the model data. Any changes to the transverse shear stiffness that occur due to changes in the material stiffness during the analysis are ignored.
Axisymmetric shell elements SAX1 and SAX2; three-dimensional shell elements S3/S3R, S4, S4R, S8R, and S8RT; and continuum shell elements SC6R and SC8R are based on a first-order shear deformation theory. Other shell elements—such as S4R5, S8R5, S9R5, STRI65, and SAXAmn—use the transverse shear stiffness to enforce the Kirchhoff constraints numerically in the thin shell limit. The transverse shear stiffness is not relevant for shells without displacement degrees of freedom nor is it relevant for element type STRI3. Although element type S4 has four integration points, the transverse shear calculation is assumed constant over the element. Higher resolution of the transverse shear may be obtained by stacking continuum shell elements.
For most shell sections, including layered composite or sandwich shell sections, ABAQUS will calculate the transverse shear stiffness values required in the element formulation. You can override these default values. The default shear stiffness values are not calculated in some cases if estimates of shear moduli are unavailable during the preprocessing stage of input; for example, when the material behavior is defined by user subroutine UMAT, UHYPEL, UHYPER, or VUMAT or, in ABAQUS/Standard, when the section behavior is defined in UGENS. You must define the transverse shear stiffnesses in such cases.
The transverse shear stiffness of the section of a shear flexible shell element is defined in ABAQUS as
are the components of the section shear stiffness (
refer to the default surface directions on the shell, as defined in “Conventions,” Section 1.2.2, or to the local directions associated with the shell section definition);
is a dimensionless factor that is used to prevent the shear stiffness from becoming too large in thin shells; and
is the actual shear stiffness of the section (calculated by ABAQUS or user-defined).
, 
, and 
); otherwise, they will take the default values defined below. The dimensionless factor is always included in the calculation of transverse shear stiffness, regardless of the way is obtained. For shell elements of type S4R5, S8R5, S9R5, STRI65, or SAXAn the average of and is used and 
is ignored. The have units of force per length.The dimensionless factor is defined as
If you do not specify the , they are calculated as follows. For laminated plates and sandwich constructions the are estimated by matching the elastic strain energy associated with shear deformation of the shell section with that based on piecewise quadratic variation of the transverse shear stress across the section, under conditions of bending about one axis. For unsymmetric lay-ups the coupling term can be nonzero.
When a general shell section is used and the section stiffness is given directly, the are defined as
is the section stiffness matrix.When a user subroutine (for example, UMAT, UHYPEL, UHYPER, or VUMAT) is used to define a shell element's material response, you must define the transverse shear stiffness. The definition of an appropriate stiffness depends on the shell's material composition and its lay-up; that is, how material is distributed through the thickness of the cross-section.
The transverse shear stiffness should be specified as the initial, linear elastic stiffness of the shell in response to pure transverse shear strains. For a homogeneous shell made of a linear, orthotropic elastic material, where the strong material direction aligns with the element's local 1-direction, the transverse shear stiffness should be
and 
are the material's shear moduli in the out-of-plane direction. The number 5/6 is the shear correction coefficient that results from matching the transverse shear energy to that for a three-dimensional structure in pure bending. For composite shells the shear correction coefficient will be different from the value for homogeneous ones; see “Transverse shear stiffness in composite shells and offsets from the midsurface,” Section 3.6.8 of the ABAQUS Theory Manual, for a discussion of how the effective shear stiffness for elastic materials is obtained in ABAQUS.For linear elastic materials the slenderness ratio, 
, where 
=1 or 2 (no sum on ) and l is a characteristic length on the surface of the shell, can be used as a guideline to decide if the assumption that plane sections must remain plane is satisfied and, hence, shell theory is adequate. Generally, if
.To obtain the 
and 
, you must run a data check analysis using a composite general shell section definition. The will be printed under the title “TRANSVERSE SHEAR STIFFNESS FOR THE SECTION” in the data (.dat) file if you request model definition data (see “Controlling the amount of analysis input file processor information written to the data file” in “Output,” Section 4.1.1). The 
will be printed out under the title “SECTION STIFFNESS MATRIX.”
When a shell section integrated during the analysis is used, the transverse shear stresses for the small-strain shells in ABAQUS/Explicit are assumed to have a piecewise constant distribution in each layer. The transverse shear force will converge to the correct solution for single or multilayer isotropic sections and single-layer orthotropic sections. The transverse shear stiffness is approximate for multilayer orthotropic sections where convergence to the proper transverse shear behavior may not be obtained as shells become thick and principal material directions deviate from the principal section directions. The finite-strain S4R element should be used with a shell section integrated during the analysis if accurate through-thickness transverse shear stress distributions are required for the analysis of composite shells.
The same transverse shear stiffness described for the finite-strain shells is used to calculate the transverse shear force for the small-strain shells in ABAQUS/Explicit when a general shell section is used. Thus, for this case the transverse shear force for multilayer composite shells will converge to the correct value for both thin and thick sections.
All three-dimensional shell elements in ABAQUS use bending strain measures that are approximations to those of Koiter-Sanders shell theory (see “Shell element overview,” Section 3.6.1 of the ABAQUS Theory Manual). As per the Koiter-Sanders theory the displacement field normal to the shell surface does not produce any bending moments. For example, a purely radial expansion of a cylinder will result in only membrane stress and strains—there are no variations through the thickness and, hence, no bending. This applies to both the incremental strain measures for linear elastic materials and the deformation gradient for hyperelastic materials.
For composite shell sections ABAQUS computes the nodal masses based on an average density through the section, weighted with respect to the layer thicknesses. This average density is used to compute an average rotary inertia as if the section were homogeneous. As a consequence, ABAQUS does not account for an unsymmetric distribution of mass: the center of mass is assumed to be at the reference surface of the shell. For continuum shells the mass is equally distributed to the top and bottom surface nodes.