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<div class="Section1">
<p><b><span style="font-size: 18pt;" lang="EN-GB">4.18
PLATE NO.18 WITH 6 NODES</span></b><span style="" lang="EN-GB"><o:p></o:p></span></p>
<p><span style="" lang="EN-GB">This is a curvilinear
Serendipity <i>Reissner- Mindlin</i> plate element with square shape
functions.
The transformation is isoparametric. The integration is carried out
numerically
in both axises according to Gauss- Legendre. Consequently, the
integration
order can be selected in Z88I1.TXT in the material information lines.
The order
3 (= 3 points) is mostly sufficient (reduced integration). This element
calculates both displacements and stresses quite good. The integration
order
can be chosen again for the stress calculation. The stresses are
calculated in
the corner nodes (good for an overview) or calculated in the Gauss
points
(substantially more exactly). Area loads are defined in the appropriate
material lines, file </span><a href="e88i1.htm"><span style=""
lang="EN-GB">Z88I1.TXT</span></a><span style="" lang="EN-GB">, instead
of Second moment of inertia RIYY. For
this element you need to set the plate flag IPFLAG to 1. Attention: In
contrary
to the usual rules of the classic mechanics Z88 defines ThetaX the
rotation
around the X- axis and ThetaY the rotation around the Y- axis. <o:p></o:p></span></p>
<p><i><span style="" lang="EN-GB">This element type is
implemented for use with automeshers e.g. Pro/MECHANICA <span style=""> </span>for
the 3D CAD system Pro/ENGINEER by
Parametric Technology. Thus, a mesh generation with Z88N is not
possible,
because this will make no sense. Use plates </span><a href="e88e20.htm"><span
style="" lang="EN-GB">No.20</span></a></i><i><span style=""
lang="EN-GB"> for the mesher Z88N.</span></i><span style=""
lang="EN-GB"><o:p></o:p></span></p>
<p><i><span style="" lang="EN-GB">Because plates No.20
compute both the deflections and the stresses more exactly than the
curvilinear
triangle plates No.18, you should prefer always plates No.20.<br>
<br>
</span><img id="_x0000_i1025" src="pla1.gif" border="0" height="160"
width="337"></i><i><span style="" lang="EN-GB"><br>
<br>
</span><img id="_x0000_i1026" src="g88e18.gif" border="0" height="233"
width="356"></i><span style="" lang="EN-GB"><o:p></o:p></span></p>
<p><a name="OLE_LINK1"><b><span style="" lang="EN-GB">Input:</span></b></a><span
style=""></span><span style="" lang="EN-GB"><o:p></o:p></span></p>
<p><a href="e88x.htm"><b><span style="" lang="EN-GB">CAD</span></b></a><b><span
style="" lang="EN-GB"> :</span></b><i><span style="" lang="EN-GB">
1-4-2-5-3-6-1 ,</span></i><b><span style="" lang="EN-GB"> </span></b><span
style="" lang="EN-GB">ref. chap. 2.7.2<o:p></o:p></span></p>
<p><a href="e88i1.htm"><b><span style="" lang="EN-GB">Z88I1.TXT</span></b></a><span
style="" lang="EN-GB"><o:p></o:p></span></p>
<p><i style=""><span style="" lang="EN-GB">> KFLAG for cartesian (0)
or cylindrical coordinates (1) <br>
> set plate flag IPFLAG to 1 (or 2, if you want to reduce the shear
influence) <br>
> set surface and pressure loads flag IQFLAG to 0 for your
convenience. Then
the entry of the pressure is done via the "Second moment of inertia
RIYY", see below. If IQFLAG is set to 1, then the entry of the pressure
is
done via the surface and pressure loads file Z88I5.TXT<br>
<span style="">> 3 degrees of freedom for each
node (w, ThetaX, ThetaY )</span></span></i><span style="" lang="EN-GB">
<br>
<i>> Element type is 18</i> <br>
<i>> 6 nodes per element</i> <br>
<i>> Cross-section parameter QPARA is the element thickness</i> <br>
> "<i>Second moment of inertia RIYY" is the area load</i> <br>
<i>> Integration order INTORD per each mat info line. 3 is usually
good.
Possible is: 3 for 3 Gauss points, 7 for 7 Gauss points and 13 for 13
Gausspoints. For easy use with plate element No.20 (e.g. with
Pro/ENGINEER),
function SPLA88 of Z88 uses internally these values:</i> <br>
<i>integration order 1 or 2 in Z88I1.TXT: 3 Gauss points<br>
integration order 4 in Z88I1.TXT: 7 Gauss points<br>
Example: Z88I1.TXT uses an entry of 2 for INTORD: Thus, plate elements
No.20
use 2*2 = 4 Gauss points and plate elements No.18 use 3 Gauss points
for
integration.</i><o:p></o:p></span></p>
<p><a href="e88i3.htm"><b><span style="" lang="EN-GB">Z88I3.TXT</span></b></a><span
style="" lang="EN-GB"><br>
<i>> Integration order INTORD</i>: Basically, it is a good idea to
use the
same value as chosen in Z88I1.TXT , but different values are permitted<br>
0 = Calculation of the stresses in the corner nodes <br>
1, 7, 13 = Calculation of the stresses in the Gauss points (e.g. 7
Gauss
points) See note for Z88I1.TXT. <o:p></o:p></span></p>
<p><i><span style="" lang="EN-GB">> KFLAG</span></i><span style=""
lang="EN-GB"> has no meaning<o:p></o:p></span></p>
<p><i><span style="" lang="EN-GB">> Reduced stress flag
ISFLAG:</span></i><span style="" lang="EN-GB"> <br>
</span><span style="" lang="EN-GB">0 = no calculation of reduced
stresses <br>
1 = von Mises stresses in the Gauss points ( INTORD not 0 !)<br>
2 = principal stresses in the Gauss points (INTORD not 0!)<br>
3 = Tresca </span><span style="" lang="EN-GB">stresses in the Gauss
points (INTORD not 0!)</span></p>
<p class="MsoNormal" style=""><b style=""><span style="" lang="EN-GB"><a
href="e88e18.htm">Z88I5.TXT</a><o:p></o:p></span></b></p>
<p class="MsoNormal" style="text-align: justify;"><span style=""
lang="EN-GB">This file is optional and normally
not used here because it is much more convenient to enter the pressure
data for
the plate elements into <a href="e88i1.htm">Z88I1.TXT</a> in the
section
material information. However, the possibility for entering the
pressure loads
by the surface and pressure loads file Z88I5.TXT, too, is implemented
for
universal use of this file. Then set IQFLAG to 1 and proceed as follows:<o:p></o:p></span></p>
<p class="MsoNormal" style=""><span style="" lang="EN-GB"><o:p> </o:p></span></p>
<p class="MsoNormal"><i style=""><span style="" lang="EN-GB">>
Element number with pressure load <o:p></o:p></span></i></p>
<p class="MsoNormal"><i style=""><span style="" lang="EN-GB">>
Pressure, positive if poiting towards the
edge <o:p></o:p></span></i></p>
<p><b><span style="font-size: 13.5pt;" lang="EN-GB">Results:</span></b><span
style="" lang="EN-GB"><o:p></o:p></span></p>
<p><b><span style="" lang="EN-GB">Displacements</span></b><span style=""
lang="EN-GB"> in Z (i.e. w) and rotations ThetaX
around X- axis and ThetaY around the Y- axis. <br>
<b>Stresses:</b> The stresses are calculated in the corner nodes or
Gauss
points and printed along with their locations. The following results
will be
presented: <o:p></o:p></span></p>
<ul type="disc">
<li class="MsoNormal" style=""><span style="" lang="EN-GB">plate
bending moments M<sub>xx</sub> and M<sub>yy</sub> (unit: force x lenght
/ length) <o:p></o:p></span></li>
<li class="MsoNormal" style=""><span style="" lang="EN-GB">plate
torsion moments M<sub>xy</sub> = M<sub>yx</sub> (unit: force x length /
length) <o:p></o:p></span></li>
<li class="MsoNormal" style=""><span style="" lang="EN-GB">the shear
forces Q<sub>yz</sub> and Q<sub>zx</sub> (unit: force / length) <o:p></o:p></span></li>
<li class="MsoNormal" style=""><span style="" lang="EN-GB">the true
stresses resulting from plate bending moments and plate torsion moments
<o:p></o:p></span></li>
</ul>
<p><span style="" lang="EN-GB">Optional <i>von Mises</i>
stresses <br>
<b>Nodal forces</b> in X and Y for each element and each node. <o:p></o:p></span></p>
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