4.10
HEXAHEDRON NO.10 WITH 20 NODES
This is a curvilinear
Serendipity volume element with square shape functions. The
transformation is
isoparametric. The integration is carried out numerically in all axises
according to Gauss- Legendre. Thus, the integration order can be
selected in Z88I1.TXT in the material information lines. The
order 3 is good. This element calculates both displacements and
stresses very
exactly. The quality of the displacement and stress calculations are
far better
than the results of the hexahedron element No.1.
Hexahedron No.1 also
applies well for thick plate elements, if the plate's thickness is not
too
small compared to the other dimensions.
The element causes an enormous
computing load and needs an extreme amount of memory because the
element
stiffness matrix has the order 60*60. Pay attention to surface and
pressure
loads when using forces, cf. chapter 3.4. It
is easier
to enter these loads via the surface and pressure loads file Z88I5.TXT.
The nodal numbering of
the element No.10 must be done carefully and must exactly match the
sketch
below. Pay attention to the location of the axis system ! The possible
error
message " Jacobi determinant zero or negative " is a hint for
incorrect node numbering.
Hexahedron No.10 can be generated
by the mesh
generator Z88N from super
elements Hexahedron No.10. Thus, the Hexahedron No.10 is
well suited as super element. Hexahedron No.10 can also generate 8-node
Hexahedrons No.1,
see chapter 4.1.
Hexahedron No.10 is
recommended for all sort of deflection and stress computation in space. Though its need for memory and
computing power is enormous, this element gives precise results for
displacements and stresses. Or use it as superelements for meshing
Hexahedrons
No.1 with 8 nodes.
Input:
CAD (see chapter 2.7.2):
Upper plane: 1 - 9 - 2 - 10 - 3 - 11 - 4 -12 - 1, quit LINE function
Lower plane: 5 - 13 - 6 - 14 - 7 - 15 - 8 - 16 - 5, quit LINE function
1 - 17 - 5, quit LINE function
2 - 18 - 6, quit LINE function
3 - 19 - 7, quit LINE function
4 - 20 - 8, quit LINE function
Z88I1.TXT
> KFLAG for cartesian (0) or
cylindrical coordinates (1)
> IQFLAG=1 if surface and pressure loads for this element are filed
in
Z88I5.TXT
> 3 degrees of freedom for each node
> Element type is 10
> 20 nodes per element
> Cross-section parameter QPARA is 0 or any value, has no
influence
> Integration order INTORD for each mat info line. 3 is usually
good.
Z88I3.TXT
> Integration order INTORD for stress calculation: Can be
different
from INTORD in Z88I1.TXT.
0 = Calculation of stresses in the corner nodes
1,2,3,4 = Calculation of stresses in the Gauss points
> KFLAG , any, has no influence
> Reduced stress flag
ISFLAG:
0 = no calculation of reduced
stresses
1 = von Mises stresses in the Gauss points ( INTORD not 0 !)
2 = principal stresses in the Gauss points (INTORD not 0!)
3 = Tresca stresses in the Gauss
points (INTORD not 0!)
This file is
optional and only used if in
addition to nodal forces surface and pressure loads applied onto
element no.10:
>
Element number with surface and pressure
load [Long]
>
Pressure, positive if poiting towards the
surface [Double]
>
Tangential shear, positive in local r
direction [Double]
>
Tangential shear, positive in local s
direction [Double]
> 4
nodes of the loaded surface [4 x Long]
The local r direction is defined by
the nodes 1-2, the local s direction is defined by the nodes 1-4. The
local
nodes 1, 2, 3 , 4 may differ from the local nodes 1, 2, 3, 4 used for
the
coincidence.
Results:
Displacements in X, Y and Z
Stresses: SIGXX, SIGYY, SIGZZ, TAUXY, TAUYZ, TAUZX, respectively
for
corner nodes or Gauss points. Optional von Mises stresses.
Nodal forces in X, Y and Z for each element and each node.