Are there any examples of the new (ANSYS 9.0) SOLSH190 solid-shell element?
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Yes, please see the ANSYS 9.0 example below created with the UP20040915 build. Note: If you encounter problems with data below, please use the attachment instead. ! This SOLSH190 example is intended as a reference to validate the new ! element technology. The input is set up for the user to vary the "n" ! value from -4 to 4 in increments of 4. These settings provide for a ! parabolic thickness distribution with the center of the circular "flat" ! plate almost half as thick as the outer edge for n=-4 and almost twice ! as thick as the outer edge for n=4. The circular plate is completely ! flat (no thickness variation) for n=0. In addition to running these ! linear elastic static analyses with the new SOLSH190 element, the user ! may switch over to the SOLID185 element to compare the results. This ! comparison is summarized at the bottom of this input file. fini /clear /view,,1,1,1 /plopts,info,1 pi=acos(-1.0) /title, SOLSH190/SOLID185 Clamped Circular Flat Plate Example ! Reference: Formulas for Stress and Strain - Fifth Edition, ! by Raymond J. Roark and Warren C. Young. McGraw-Hill ! Book Company, Copyright 1975. ISBN 0-07-053031-9 ! Case 10b: Circular plate with edges fixed (clamped) and thickness ! defined by parabolic relation: t=to*e^(-n*x^2/6) => see Section 10.7, ! "Circular Plates of Variable Thickness", pages 381-383 ... t0 = 0.10 ! thickness at center of plate, inches ! e = 2.71828183 => base for napierian system of logarithms n = -4 ! increase in thickness as radius increases !!! n = 0 ! no change in plate thickness (no taper) !!! n = 4 ! decrease in thickness as radius increases *if,n,eq,-4,then alpha = 0.0653 beta = 0.26 *elseif,n,eq,4 alpha = 0.4375 beta = 2.14 *else n=0 alpha=0.1707 beta=0.75 *endif a = 50.0 ! outer radius of circular plate, inches ! x = radius/a=> where radius = radial location in question q = 0.1 ! uniform pressure, psi sigmamax = (beta*q*a**2)/(t0**2) ! maximum stress, psi maxdefl = (alpha*q*a**4)/(30.0e6*t0**3) ! maximum deflection, inches elemtype = 190 ! new SOLSH190 !!! elemtype = 185 ! existing SOLID185 /prep7 *if,elemtype,eq,185,then et,1,SOLID185 keyopt,1,2,2 ! enhanced strain formulation (for bending) keyopt,1,6,0 ! pure displacement formulation *else elemtype=190 et,1,SOLSH190 ! always has enhanced strain activated keyopt,1,6,0 ! pure displacement formulation *endif r,1 mp,ex,1,30.0e6 mp,nuxy,1,0.30 n,101,0,0,0 n,121,0,a,0 radinc=a/20 ngen,21,1, 101,121,20, 0.0,radinc,0.0 csys,1 ! global cylindrical coordinate system thetadiv=10 ! number of divisions for 90 degrees theta=(90.0/thetadiv) ngen,thetadiv+1,100, 101,121,1, 0.0,theta,0.0 *get,ncount,node,0,count ! nodes in plane = 0 ncurr=0 *do,i,1,ncount,1 ! loop through all of the nodes ncurr=ndnext(ncurr) ! current node number radius=nx(ncurr) ! radius of current node number x=radius/a ! thickness parameter thick=t0*exp(-n/6*x**2) ! thickness, t=to*e^(-n*x^2/6) angle=ny(ncurr) ! theta value of current node n,ncurr+10000,radius,angle,-thick/2 ! corresponding node on top plane n,ncurr+20000,radius,angle,thick/2 ! corresponding node on bottom plane *enddo csys,0 en,10102,10102,10202,10101,10101,20102,20202,20101,20101 engen,100,thetadiv,100,10102 en,10103,10103,10203,10202,10102,20103,20203,20202,20102 engen,1,19,1,10103 engen,100,thetadiv,100,10103,10121,1 nummrg,node !!! /psym,esys,1 !!! /dev,vect,1 eplot fini /solu antype,static time,1.0 nsel,s,loc,x,0 d,all,ux,0.0 ! symmetry boundary condition nsel,s,loc,y,0 d,all,uy,0.0 ! symmetry boundary condition csys,1 nsel,s,loc,x,a csys,0 d,all,all,0.0 ! clamp edges to meet case 10b requirements nsel,s,node,,20000,30000 /psf,pres,norm,2 sf,all,press,q ! apply uniform pressure to top surface, psi nsel,all /pbc,u,,1 eplot /wait,1 nsel,u,node,,1,10000 ! unused nodes on mid-plane ... save solve save fini /post1 set,last /edge,,1 /dscale,,1 /show,png /title, Element Type = %elemtype% - Theoretical Max Deflection is %maxdefl%" for n=%n% plnsol,u,sum,2 ! Z deflection, inches !!! /wait,3 /title, Element Type = %elemtype% - Theoretical Max Stress is %sigmamax% psi for n=%n% rsys,1 plnsol,s,x ! radial bending stress, psi /show,close /eof = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = The following assumes: t0=0.10", a=50.0", and q=0.1 psi Note: The theoretical equations do not account for shear deflection, and the wedges at the center reduce the accuracy of the results. For the stress, the maximum radialstress was used, but the reference was not absolutely clear as to what it meant by the term "maximum stress". Further, a Poisson's ratio of 0.30 is assumed in the calculation of the alpha and beta terms. Other error can be attributed to the pressures being applied to the surface of the elements as opposed to the mid-surface. Also, some stress error is due to the extrapolation of the integration point values to the nodes ... = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = = Theoretical Deflections: ======================== 1.3604" for n = -4 3.5563" for n = 0 9.1146" for n = 4 Deflections for Element Type SOLSH190: ====================================== 1.3570" for n = -4 3.5540" for n = 0 9.1270" for n = 4 Deflections for Element Type SOLID185: ===================================== |
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