Skip to content
GitLab
Projects
Groups
Snippets
Help
Loading...
Help
Help
Support
Community forum
Keyboard shortcuts
?
Submit feedback
Contribute to GitLab
Sign in / Register
Toggle navigation
C
cometfenics
Project overview
Project overview
Details
Activity
Releases
Repository
Repository
Files
Commits
Branches
Tags
Contributors
Graph
Compare
Issues
0
Issues
0
List
Boards
Labels
Service Desk
Milestones
Merge Requests
0
Merge Requests
0
CI / CD
CI / CD
Pipelines
Jobs
Schedules
Operations
Operations
Incidents
Environments
Analytics
Analytics
CI / CD
Repository
Value Stream
Wiki
Wiki
Members
Members
Collapse sidebar
Close sidebar
Activity
Graph
Create a new issue
Jobs
Commits
Issue Boards
Open sidebar
Francisco Ramírez
cometfenics
Commits
91a2eec4
Commit
91a2eec4
authored
Apr 17, 2018
by
Jeremy BLEYER
Browse files
Options
Browse Files
Download
Email Patches
Plain Diff
2D elasticity example
parent
77250941
Changes
3
Show whitespace changes
Inline
Sidebyside
Showing
3 changed files
with
165 additions
and
1 deletion
+165
1
doc/index.rst
doc/index.rst
+1
1
examples/elasticity/2D_elasticity.py.rst
examples/elasticity/2D_elasticity.py.rst
+164
0
examples/elasticity/cantilever_deformed.png
examples/elasticity/cantilever_deformed.png
+0
0
No files found.
doc/index.rst
View file @
91a2eec4
...
...
@@ 12,7 +12,7 @@ Contents:
:maxdepth: 2
intro
2D_elasticity
demo/elasticity/2D_elasticity.py.rst
demo/modal_analysis_dynamics/cantilever_modal.py.rst
demo/reissner_mindlin/reissner_mindlin.rst
...
...
examples/elasticity/2D_elasticity.py.rst
0 → 100644
View file @
91a2eec4
..
#
gedit
:
set
fileencoding
=
utf8
:
..
_LinearElasticity2D
::
=========================
2
D
linear
elasticity
=========================
Introduction

In
this
first
numerical
tour
,
we
will
show
how
to
compute
a
small
strain
solution
for
a
2
D
isotropic
linear
elastic
medium
,
either
in
plane
stress
or
in
plane
strain
,
in
a
tradtional
displacement

based
finite
element
formulation
.
Extension
to
3
D
is
straightforward
and
an
example
can
be
found
in
the
:
ref
:`
ModalAnalysis
`
example
.
We
consider
here
the
case
of
a
cantilever
beam
modeled
as
a
2
D
medium
of
dimensions
:
math
:`
L
\
times
H
`.
Geometrical
parameters
and
mesh
density
are
first
defined
and
the
rectangular
domain
is
generated
using
the
``
RectangleMesh
``
function
.
We
also
choose
a
criss

crossed
structured
mesh
::
from
__future__
import
print_function
from
fenics
import
*
L
=
25.
H
=
1.
Nx
=
250
Ny
=
10
mesh
=
RectangleMesh
(
Point
(
0.
,
0.
),
Point
(
L
,
H
),
Nx
,
Ny
,
"crossed"
)
Constitutive
relation

We
now
define
the
material
parameters
which
are
here
given
in
terms
of
a
Young
's
modulus :math:`E` and a Poisson coefficient :math:`\nu`. In the following, we will
need to define the constitutive relation between the stress tensor :math:`\boldsymbol{\sigma}`
and the strain tensor :math:`\boldsymbol{\varepsilon}`. Let us recall
that the general expression of the linear elastic isotropic constitutive relation
for a 3D medium is given by:
.. math::
\boldsymbol{\sigma} = \lambda \text{tr}(\boldsymbol{\varepsilon})\mathbf{1} + 2\mu\boldsymbol{\varepsilon}
:label: constitutive_3D
for a natural (no prestress) initial state where the Lamé coefficients are given by:
.. math::
\lambda = \dfrac{E\nu}{(1+\nu)(12\nu)}, \quad \mu = \dfrac{E}{2(1+\nu)}
:label: Lame_coeff
In this demo, we consider a 2D model either in plane strain or in plane stress conditions.
Irrespective of this choice, we will work only with a 2D displacement vector :math:`\boldsymbol{u}=(u_x,u_y)`
and will subsequently define the strain operator ``eps`` as follows::
def eps(v):
return sym(grad(v))
which computes the 2x2 plane components of the symmetrized gradient tensor of
any 2D vectorial field. In the plane strain case, the full 3D strain tensor is defined as follows:
.. math::
\boldsymbol{\varepsilon} = \begin{bmatrix} \varepsilon_{xx} & \varepsilon_{xy} & 0\\
\varepsilon_{xy} & \varepsilon_{yy} & 0 \\ 0 & 0 & 0\end{bmatrix}
so that the 2x2 plane part of the stress tensor is defined in the same way as for the 3D case
(the outofplane stress component being given by :math:`\sigma_{zz}=\lambda(\varepsilon_{xx}+\varepsilon_{yy})`.
In the plane stress case, an outofplane strain component :math:`\varepsilon_{zz}`
must be considered so that :math:`\sigma_{zz}=0`. Using this condition in the
3D constitutive relation, one has :math:`\varepsilon_{zz}=\dfrac{\lambda}{\lambda+2\mu}(\varepsilon_{xx}+\varepsilon_{yy})`.
Injecting into :eq:`constitutive_3D`, we have for the 2D plane stress relation:
.. math::
\boldsymbol{\sigma} = \lambda^* \text{tr}(\boldsymbol{\varepsilon})\mathbf{1} + 2\mu\boldsymbol{\varepsilon}
where :math:`\boldsymbol{\sigma}, \boldsymbol{\varepsilon}, \mathbf{1}` are 2D tensors and with
:math:`\lambda^* = \dfrac{\lambda^2}{\lambda+\mu}`. Hence, the 2D constitutive relation
is identical to the plane strain case by changing only the value of the Lamé coefficient :math:`\lambda`
(equivalently, this corresponds to using a pseudoPoisson coefficient :math:`\nu^*=\dfrac{\nu}{1\nu}`
instead of :math:`\nu` when defining :math:`\lambda` in :eq:`Lame_coeff`). We can then have::
E = Constant(1e5)
nu = Constant(0.3)
model = "plane_stress"
mu = E/2/(1+nu)
lmbda = E*nu/(1+nu)/(12*nu)
if model == "plane_stress":
lmbda = lmbda**2/(lmbda+mu)
def sigma(v):
return lmbda*tr(eps(v))*Identity(2) + 2.0*mu*eps(v)
.. note::
Note that we used the variable name ``lmbda`` to avoid any confusion with the
lambda functions of Python
We also used an intrinsic formulation of the constitutive relation. Example of
constitutive relation implemented with a matrix/vector engineering notation
will be provided in the :ref:`OrthotropicElasticity` example.
Variational formulation

For this example, we consider a continuous polynomial interpolation of degree 2
and a uniformly distributed loading :math:`\boldsymbol{f}=(0,f)` corresponding
to the beam selfweight. The continuum mechanics variational formulation (obtained
from the virtual work principle) is given by:
.. math::
\text{Find } \boldsymbol{u}\in V \text{ s.t. } \int_{\Omega}
\boldsymbol{\sigma}(\boldsymbol{u}):\boldsymbol{\varepsilon}(\boldsymbol{v}) d\Omega
= \int_{\Omega} \boldsymbol{f}\cdot\boldsymbol{v} d\Omega \quad \forall\boldsymbol{v} \in V
which translates into the following FEniCS code::
rho_g = 1e3
f = Constant((0,rho_g))
V = VectorFunctionSpace(mesh, '
Lagrange
', degree=2)
du = TrialFunction(V)
u_ = TestFunction(V)
a = inner(sigma(du), eps(u_))*dx
l = inner(f, u_)*dx
Resolution

Fixed displacements are imposed on the left part of the beam, the ``solve``
function is then called and solution is plotted by deforming the mesh::
def left(x, on_boundary):
return near(x[0],0.)
bc = DirichletBC(V, Constant((0.,0.)), left)
u = Function(V, name="Displacement")
solve(a == l, u, bc)
plot(1e3*u, mode="displacement")
The (amplified) solution should look like this:
.. image:: cantilever_deformed.png
:scale: 15%
Validation and postprocessing

The maximal deflection is compared against the analytical solution from
EulerBernoulli beam theory which is here :math:`w_{beam} = \dfrac{qL^4}{8EI}`::
print("Maximal deflection:", u(L,H/2.)[1])
print("Beam theory deflection:", float(3*rho_g*L**4/2/E/H**3))
One finds :math:`w_{FE} = 5.8172\text{e3}` against :math:`w_{beam} = 5.8594\text{e3}`
that is a 0.72% difference.
\ No newline at end of file
examples/elasticity/cantilever_deformed.png
0 → 100644
View file @
91a2eec4
127 KB
Write
Preview
Markdown
is supported
0%
Try again
or
attach a new file
.
Attach a file
Cancel
You are about to add
0
people
to the discussion. Proceed with caution.
Finish editing this message first!
Cancel
Please
register
or
sign in
to comment