Finite Element Analysis of Composite Layered Structures
Finite Element Analysis of Composite Layered Structures
___________________________________
ABSTRACT
A complete formulation of three-dimensional finite element analysis for multi-layered
structures was examined using MATLAB. Throughout the investigation, standard weak
form expressions, model discretization, local node-numbering, global matrix
partitioning, and solution procedures were followed in modeling a uniaxially-loaded,
symmetric laminate. Modeling each discretized element as a tri-linear element, the
effect of mesh refinement was observed to be significant, and agreed well with the
previously hypothesized possibility of a stress singularity. Furthermore, the results
obtained from the three-dimensional analysis were compared with that of Classical
Laminated Plate Theory, as well as ANSYS. For code validation purposes, a forcereaction balance was performed a posteriori to verify that it was implemented correctly.
___________________________________
AUTHORS
Connor Kaufmann
Neola Putnam
Ethan Seo
Ju Hwan (Jay) Shin
___________________________________
Sibley School of Mechanical & Aerospace Engineering
Cornell University, Ithaca, NY, 14853
Submitted on May 1, 2014 to Prof. N. Zabaras
Shin et al.
1. Introduction
more detail in the following paragraphs, the nodal
displacements, strain field, and the stress field were outputted.
Composite materials are known to be more favorable for
optimizing weight of the structure than monolithic materials.
This is due to the anisotropic nature of the fiber-reinforced
laminate, which allows engineers to utilize the composite
materials without overdesigning in certain orientations. While
these multidirectional laminates were shown to be effective at
reducing the overall payload of the structure, they introduced a
new level of complexity in the proper understanding of their
mechanics and led to investigative research in this field.
In the pre-processing stage, the model was discretized
into finite elements. In doing so, bias-factor was considered to
allow for a greater mesh density (Fig. 2) near the free-edge.
This optional step is helpful for obtaining more accurate results
without having to increase the number of elements.
A tri-linear element was employed throughout the project.
A first-order element was considered the easiest to implement
among the general p-order Lagrangian elements. The element
used was an eight-node hexahedron element (Fig. 3) with the
local node-numbering scheme as given, and each node
contained three translational degrees-of-freedom: ?, ?, and ?.
The appropriateness of the node-numbering convention was
confirmed by checking that the determinants of the elemental
Jacobian matrices were positive. This ensured that the mapping
between physical and natural coordinates was correct.
One particular area of such research is devoted to the
study of failure by delamination (Fig. 1). Of the many
mechanisms by which a layered structure fails due to
delamination, one notable cause of this is the development of
interlaminar stresses. Interlaminar stresses are out-of-plane
stresses, such as ??? , ??? , and ??? , that are induced at the ply
interface near the free-edges of a laminated structure. Though
completely neglected in the framework of 2-D CLPT, or Classical
Laminated Plate Theory, these through-thickness stresses can
be quite severe in some cases, as there can exist a state of stress
singularity from the abrupt mismatch of the Poisson¡¯s effects
along the layers. The present study sought to confirm this
behavior numerically by performing a complete threedimensional finite element analysis, as the Kirchhoff-Love¡¯s
assumptions used in CLPT was limited to estimating the
membrane stresses only, or in-plane stresses. It is noted,
however, that to model the physical mechanics with even
greater accuracy, one should take into account the material
nonlinearity in the analysis. Material nonlinearity plays an
important role in failure by delamination because failure is
often not governed only by the magnitude of the interlaminar
stress (which is infinite in linear elastic theory). Nonlinearity of
material properties causes the crack tip, formed at the onset of
progressive fracture to experience a blunting effect at the
material¡¯s yield point. Nevertheless, it is worth acknowledging
that this singular stress is important for understanding the
failure mechanism of a laminated structure.
Moreover, the elasticity, or the stiffness matrix, which
relates the strain to stress, was also defined for each layer of the
? ]{?}, is also
laminate. This constitutive relationship, {?} = [?
referred to as the generalized Hooke¡¯s Law (App. A-1).
The rest of the components required to formulate the
elemental stiffness equation were calculated in the preprocessing stage. These included the [?? ], [?? ], [?? ], and [?? ]
matrices evaluated at the Gauss integration points. Here it is
noted that [?? ] is the shape function matrix, [?? ] = [?s ?? ] is
the symmetric gradient of [?? ], and [?? ] and [?? ] are referred
to as the Jacobian matrix and the connectivity matrix,
respectively (App. A-2).
The last step of the pre-processing stage involved
specifying the boundary conditions. In the case of uniaxiallyloaded laminate, three symmetry planes within the model were
observed, such that only one octant of the model was analyzed.
The essential boundary conditions were that the appropriate
degrees-of-freedom on each symmetry plane were set to zero
directional displacements. In addition, the applied pressure
load boundary condition was specified as follows.
Ply interface
?(? = 0, ?, ?) = 0
?(?, ? = 0, ?) = 0
?(?, ?, ? = 0) = 0
??(? = ?, ?, ?) = ?0
Fig. 1: Failure due to delamination
2. FEM Formulation
In developing the FEM code, the analysis was divided into
three main stages: pre-processing, processing, and postprocessing. Using MATLAB, any necessary inputs, including the
anisotropic material properties, the applied load, the laminate
configuration, and the laminate dimensions, were specified.
Following the standard solution procedures to be discussed in
Fig. 2: Mesh profile of a laminated structure
-2-
Shin et al.
?
Similarly, the stress field was calculated by applying
Hooke¡¯s Law using the [?? ] matrices that were previously
computed.
?
{?} = [?? ]{?}
While there are other ways of displaying the strain/stress
fields, such as an interpolated field that would result in a smooth
variation over the model, as opposed to a discontinuous set of
elemental results, the latter was chosen for its slightly greater
efficiency. Furthermore, a number of useful features were built
into the code, including the options to show the deformed
model, display the elemental boundaries, and generate a
comprehensive solution file.
?
Fig. 3: 8-node hexahedron element with 3 degrees-of-freedom per node
Once the pre-processing stage was completed, the
elemental stiffness equations were assembled to construct the
global stiffness equation. Recalling that the weak form of the
governing equation is as shown below, the stiffness matrix, [?? ],
and the load vector, {? ? }, were simply summed for all elements.
3. Numerical Results
Several salient path-wise and contour plots (App. B) are
illustrated in this section. A number of observations with
emphasis on the free-edge effects are also briefly mentioned.
nel
+1 +1 +1
¡Æ (?? ?
??=1
¡Ò ¡Ò ¡Ò ?? ? ?? ?? |?? | d? d? d? ?? ) ?
?1 ?1 ?1
?
nel
= ¡Æ (?? ? ¡Ò ?? ? ?? ? d¦£)
?
¦£?t
?=1
?
To solve for the unknown components of the global
degrees-of-freedom, {?? } , the global stiffness equation was
rearranged and partitioned by applying the appropriate
transformation, as shown below.
???
?? = ?
??
[ ?
???
(Free-edge)
??? ??
?
] [ ] = [ ?]
??
?? ??
Fig. 4: Path-wise distribution of ??? along y
?
?? = ??1
? ?? , ? ?? = 0
It is noted that the method of Gaussian elimination
implemented in MATLAB was used to solve the above set of
equations; this is done by setting d_F = K_F \ f_F for greater
efficiency than direct matrix inversion. The known components
of the degrees-of-freedom, {?? } were appended to the solved
solutions, or {?? }, in order to construct the full set of solutions.
Possibility
of stress
singularity
Finally, the strain field and the stress field were calculated
in the post-processing stage. Using the kinematic relationship,
the element-averaged strain was calculated, as follows.
{?} = [?? ]{?},
where [?? ] was computed as the weighted average of the
values obtained at each Gauss integration point.
(Ply interface)
???
Fig. 5: Path-wise distribution of ??? along z
-3-
Shin et al.
???
Fig. 9: ??? distribution along ? for various mesh profiles
Fig. 6: ??? distribution along ? for various mesh profiles
???
Fig. 7: ??? distribution along ? for various mesh profiles
Fig. 10: ??? distribution along ? for various mesh profiles
???
Fig. 8: ??? distribution along ? for various mesh profiles
Fig. 11: ??? distribution along ? for various mesh profiles
-4-
(Free-edge)
(Free-edge)
???
(Free-edge)
(Free-edge)
???
(Free-edge)
(Free-edge)
???
Shin et al.
It is observed (Fig. 4-11) that the magnitude of ???
begins to decay rapidly near the free-edge, which is consistent
with the behavior for a traction-free surface. Similarly, ??? ,
which is assumed to be zero for a cross-ply laminate under the
framework of CLPT, displayed a gradual decay toward the freeedge. On the other hand, ??? exhibited a possible state of stress
singularity. It is noted that this observation was consistent with
findings from prior research.
orthogonal to the direction of the applied load. The table above
summarizes a sample computation. Since the applied load is
equal and opposite to the corresponding reaction traction, their
sum is zero and the force balance is satisfied.
A simple error analysis is shown in the following
paragraph. Due to the difficulty in solving for the exact solution
for a layered structure, the theoretical L2 and energy norm
errors were computed to demonstrate the error convergence
rate with mesh refinement.
Furthermore, the validity of CLPT for various laminates
was investigated. The table below indicated that CLPT was an
accurate assumption only for a laminate with small mismatch in
Poisson effect between the neighboring plies. Moreover, it was
noted that the mesh refinement had a significant effect on the
axial stress results, especially for a laminate with a large
mismatch in fiber orientation.
2
||?||L = (¡Æ ¡Ò (?(?) ? ?(? )) d¦¸)
2
||?||en
(%)
nel
¦¸?
1?
2
¡Ü ???+1
1
= (¡Æ ¡Ò ? ? (?(?) ? ? ? (?)) d¦¸)
2 ¦¸?
1?
2
¡Ü ???
nel
Here, it is noted that ? is a constant that is dependent on
the interpolation function used for the FE solution, ? refers to
the order of the element (? = 1 for a linear element), and ? ¡Ô
¡Ì??2 + ??2 + ??2 is the largest diameter (Fig. 13) that can
inscribed in each element.
4. Further Verification
Fig. 13: Schematic illustrating element size, ?
After the model was implemented in MATLAB, a forcereaction balance test was conducted as a sanity check to confirm
that the code had solved the mathematical model correctly. The
configuration being modeled was in static equilibrium, and as
such, summation of forces in each coordinate direction should
be equal to zero. The following figure (Fig. 12) shows how the
reaction forces at nodes with essential boundary conditions
specified should equal the externally applied traction forces.
fr
Thus by reducing the element parameter, ?, by a factor of
2, the L2 and energy errors are expected to be reduced to ? and
? the original values, respectively. As successively refined
meshes were tested with the developed code, mesh
convergence was observed, and it could be reasonably be
assumed that the FE solution approached the exact solution.
Lastly, the effect of varying the aspect ratio of an element
was also investigated in the present study. Here, the aspect
ratio, ? ¡Ô ?max /?min , is defined as the ratio of the largest
dimension that can be inscribed in the element to the smallest
dimension. While the reasoning behind how the aspect ratio
has an effect on the solution will not be explained in detail, it is
noted that this is due to the shear locking phenomena. The firstorder element¡¯s inability to capture the effect of large shear
deformation leads to an inaccurate result as the stiffness will be
too high. Thus it is recommended that the element be
discretized appropriately so as to attain a moderate aspect ratio.
fext
Fig. 12: Free-body-diagram of the force-reaction balance
Laminate width, ?
Laminate thickness, ?
Applied load, ?0
Total reaction force
Normalized traction
10 m
3.6 m
5 ¡Á 107 Pa
-1.8 ¡Á 109 N
-5 ¡Á 107 Pa
¡Æ ?? = ?ext + ??
0
5. Concluding Remarks
This paper discusses the formulation methodology for
implementing a 3-D finite element analysis of a layered
structure using MATLAB. Following the standard procedures of
FEM for an eight-node tri-linear element, several path-wise and
contour plots were examined. The results exhibited our
expected behavior for a uniaxially-loaded, symmetric laminate.
The reaction traction was computed by dividing the
external force by the cross-sectional area of the plane
-5-
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