# User:Egm6936.s09/Curling of paper sheet using shell theory

## Contents

- 1 Small transverse deflections of thin plates
- 2 Large transverse deflections of thin plates
- 3 Classical laminate theory
- 4 Large deformation of paper under thermal loading
- 5 Nonlinear buckling analysis in ANSYS
- 6 References

# Small transverse deflections of thin plates[edit]

Consider a load-free plate in which the plane coincides with plate's midplane and the coordinate is perpendicular to it and is directed downwards. The fundamental assumptions of the linear, elastic, small deflection theory of bending for thin plates may be stated as follows ^{[1]}^{[2]}^{[3]}:

(i) The material of the plate is elastic, homogeneous, and isotropic.

(ii) The plate is initially flat.

(iii) The deflection (the normal component of the displacement vector) of the midplane is small compared with the thickness of the plate. The slope of the deflected surface is therefore very small and the square of the slope is a negligible quantity in comparison with unity.

(iv) The straight lines, initially normal to the middle plane before bending, remain straight and normal to the middle surface during the deformation, and the length of such elements is not altered. This means that the vertical shear strain and are negligible and the normal strain may also be omitted. This assumption is referred to as the "hypothesis of straight normals."

(v) The stress normal to the middle plane, is small compared with the other stress components and may be neglected in the stress-strain relations

(vi) Since the displacements of a plate are small, it is assumed that the middle surface remains unstrained after bending.

## Strain-curvature relations (Kinematic equations)[edit]

Let , and be components of the displacement vector of points in the middle surface of the plate occuring in the , and directions, respectively. As it follows from the assumption (iv) above

(1.1)

Integrating the expressions (1.1) and taking into account assumptions (vi) we have the following form in the context of Kirchhoff's theory ^{[3]}:

(1.2)

From the definitions, strains are given by

(1.3)

where curvatures are

(1.4)

## Stresses, stress resultants, and stress couples[edit]

Stress-strain relations are related by the Hooke's law ^{[3]}:

(1.5)

where

The resultant forces and moments are

(1.6)

(1.7)

Substituting eqs (1.5) into eqs (1.7) one gets

(1.8)

where *D* is the flexural rigidity of the plate as below

(1.9)

## Governing equation for deflection of plates in cartesian coordinates[edit]

To get the governing equation for deflection of plates, we imagine to cut out an infinite element and consider its conditions of equilibrium. The force summation in the *z* axis gives

(1.10)

The moment summation about the *x* and *y* axises lead to

(1.11)

Substituting eqs (1.11) into (1.10), one finds the following:

(1.12)

Finally, introduction of the expressions from eqs (1.8) into eqs (1.12) yields

(1.13)

This is the governing differential equation for the deflections for thin plate bending analysis based on Kirchhoff's assumptions. Equation (1.13) can be rewritten as follows^{[3]}:

(1.14)

where

(1.15)

Expressions for the vertical forces easily obtain by substituting eqs (1.8) into eqs (1.11)

(1.16)

Note that the bending moments and twist depend only on , not on the in-plane displacements.

## Boundary conditions[edit]

Considering boundary condition at one edge, for example, edge . We have three common boundary conditions ^{[3]}:

(A) Plates are simple supported at the edge:

The deflection and bending moment are both zero:

(1.17)

(B) Plates are clamped or built in, or fixed at this edge

The deflection and slope are zero:

(1.18)

(C) Plates are free at this edge

All forces and moments are zero:

(1.19)

However, three boundary conditions are too many for the governing differential equation. Kirchhoff suggested that the three boundary conditions at the free edge be combined into two by equating to zero the bending moment and the so-called effective shear force.

(1.20)

# Large transverse deflections of thin plates[edit]

## Large deformation theory[edit]

To calculate deformations of a elastic body, we consider a chance in length of an infinitesimal line PQ before and after deformation.
The square of length PQ in the original configuration is given by^{[4]}:

(2.1)

Due to deformation, the square of length pq in the deformed configuration is:

(2.2)

The differentials can be transformed into coordinate systems

(2.3)

Hence

By defitinion, Green's strain tensor is obtained as following:

(2.4)

or

(2.5)

From the defition of displacements:

(2.6)

we have:

Substituting above equation into (2.5):

or

(2.7)

In unabridged notations, in-plane strains, for example, are given by:

## Strain-displacement relations[edit]

The linear theory of thin plate ignores strains of middle surface of the plate and the corresponding in-plane stresses are neglected. However, if the magnitude of the lateral deflections are large compared to the thickness of plate, these deflections are accompanied by stretching of the middle surface. As a result, the membrane forces are included. The large deflection plate bending theory uses two assumptions:

- The hypothesis of the straight normals: the straight lines, initially normal to the middle plane before deformation remain straight and normal to the middle surface during the deformation therefore

- The stress normal to the middle surface, , is small compared with the other stress components and may be neglected in the stress-strain relations.

The above figure shows a section of the plate normal to the *y*-axis before and after deformation. The *x-y* plane is equidistant from the top and bottom surfaces of the plate and is called the midplane of reference plane.

The reference plane displacements and in the *x* and *y* directions and the out of plane displacment *w* in the *z* direction are functions of *x* and *y* only:

(2.8)

The in-plane displacements components of a point of coordinate *z* are:

(2.9)

where *z* is the through-thickness coordinate of a general point of the cross section.

Due to large deformations, strain-displacement relations (2.7) must be used. However, we assume that displacements *u* and *v* are small, one can neglect

Thus strain-displacement relations for large deformation of thin plate are:

(2.10)

Substituting (2.9) into (2.10) we get

(2.11)

where

(2.12)

or in matrix form

(2.13)

From Hooke's Law, one obtains:

(2.14)

Relation (2.14), however, is valid for isotropic materials except for anisotropic materials.

## Force resultants and moment resultants[edit]

Similar to the small transverse deflection of thin plates ^{[3]}, shear forces and moments are the same in (1.6) (1.7):

(1.6)

(1.7)

The linear theory ignores straining of the middle surface of the plate and the corresponding in-plane stresses are neglected. However, in case of large deflection of thin plates, we have additional in-plane forces as below:

(2.15)

Using (2.14), Eqs (1.7) and (2.15) are rewritten as followings:

(2.16)

Or

(1.8)

And

(2.17)

Or

(2.18)

where

## The equilibrium of thin plate with large deflections[edit]

From six equilibrium equations:

One gets:

(2.19)

(2.20)

(2.21)

Substituting (2.20) into (2.19) to obtain the following:

(2.22)

Or

(2.23)

Thus we have 4 unknown functions and with three equations (2.21) and (2.23). The rest equation obtained by eliminating the tangential components of displacements and from Eqs (2.11) to get the following equation of the compatibility of deformations in the middle surface of the plate:

(2.24)

The strain-membrane force equations, according to Hooke's law (2.18) are of the form:

(2.25)

Upon substitution of Eqs (2.25) into Eqs (2.24), we derive the following:

(2.26)

Introducing a stress function for in-plane stress components, as follows:

(2.27)

Where

It is easy to find that by doing so, Eqs (2.21) are identically satisfied. Substituting for from (2.27) into Eqs (2.23) we obtain:

(2.28)

These are the governing differential equations for large deflections of thin plates. Equations (2.28) are coupled, nonlinear, partial differential equations, each of fourth order. The first equation can be interpreted as a compatibility equation in terms of the stress function, while the second one is an equilibrium equation. They are often called **VON KARMAN** the system of equations.

For small deflection, the above P.D.Es become uncoupled and we can use displacement- based method to find solutions as following. And strain-displacement relations of middle surface obtained from (2.12) when ignoring :

(2.29)

Substituting Eqs (2.29) into (2.18) yields:

(2.30)

Substituting Eqs (2.30) into Eqs (2.21):

(2.31)

The above Eqs can be reduced to:

(2.32)

## The boundary conditions[edit]

# Classical laminate theory[edit]

The strain-displacement (geometry) relations remain those of equations (2.9), (2.13), the membrane forces, bending moments and twists and vertical shear forces remain those of equations (1.6), (1.7), (2.15). The P.D.E's equations (2.19), (2.21) involving the vertical and membrane forces, respectively, remain valid. The relationship between transverse shear forces and the moments or also accounting for the effect of membrane forces as expressed by equation (2.20) are valid irrespective of whether the response is isotropic or anisotropic.
For general orthotropy^{[6]}:

Thus, the in the orthotropic ply or lamina of a stacked laminate is (assuming )

(3.1)

Where are general orthotropic coordinates, are the transformed reduced stiffness of the ply which can be related to and of this ply and the angle between the 1-direction (fiber direction) of this lamina and the -axis Since the strains in the ply are given by equation (2.13):

(3.2)

(3.3)

(3.4)

(3.5)

Where

(3.6)

Also

(3.7)

(3.8)

(3.9)

Note that unlike the isotropic case, both the in-plane forces and moments depend on membrane displacements and transverse flexure , i.e. there is coupling between in-plane and out-of-plane activity. The coupling vanishes if and only if

By determining and from the equilibrium equations:

(3.10)

and boundary conditions at or from (for small deflections)

(3.11)

One obtains:

(3.12)

Expressions for membrane forces and moments can be written in a matrix form as follows:

(3.13)

Governing equation of the classic laminate theory and general solution procedures Solving the problem of the classical laminate theory, one is aiming at finding or and or by solving equation (2.19) and (2.21). Using the generalized stress-strain relationship (3.13), all the generalized stresses and strains can be determined. The strains in a lamina at any a given coordinate can be found using Eqs (3.2). The strains found are in the laminate loading coordinate system. The stresses in the loading coordinate system can obtained using (3.1) and can be both transformed to the material principal coordinate system of the lamina, using the coordinate transformation matrix.

There are two typical ways of obtaining the governing equations.

## Displacement-based method[edit]

If the generalized strains on the right hand side of the generalized stress-strain relationship (3.13) are replaced by displacement derivatives according to their definition in (2.12), all the generalised stresses have been expressed in terms of displacements and . Substituting them into equilibrium equations (2.19) and (2.21), one obtains three partial differentical equations as the governing equations for three displacements and .

(3.14)

Solving these governing equations, one obtains displacements and . Generalised strains can then be obtained using (2.29). The procedure as described in the previous paragraph then prevails. Finite element method is a special case following this approach. It uses the energy minimization to satisfy equilibrium instead of solving the partial differential governing equations directly.

## Stress function-based method[edit]

This approach is mostly used for analytical study. The generalized stress-strain relationship can be reorganized into the following form:

(3.15)

Where

(3.16)

Introducing the Airy stress function as (2.27) one finds the in-plane equilibrium equations (2.21) are satisfied identically. From the membrane strains as defined in (2.29) (for small deflections), a compatibility equation for these strains can be obtained as (a compatibility equation (2.24) is for large deformation):

(3.17)

This should be satisfied by the membrane strains corresponding to the membrane forces derived from the Airy stress function. Replacing and by the expression of and in the right hand side of (3.15), and have been expressed in terms of and . Then substituting such and into equation (3.17) and (1.12), two fourth order partial differential equations are obtained as the governing equations for and :

(3.18)

Where

(3.19)

# Large deformation of paper under thermal loading[edit]

Remember that if a plate is bent by lateral load only and deflections are so small, the plate middle surface was assumed to be unstrained, hence it is considered as a neutral surface. Occasionally, however, direct forces (acting in the plane of the middle surface of the plate) are applied directly at the boundaries or they arise due to temperature (or moisture) changes. The latter will be considered below in detail.

It was assumed in the foregoing discussions that the temperature of an elastic plate remains constant and has the same value at all points of the plate; whence, temperature effects were not taken into consideration. If the temperature of the plate is raised or lowered it expands or contracts, respectively. Within a certain change, such expansion or contraction, for most structural materials, is directly proportional to the change in temperature. When a free plate made of homogenous isotropic material is heated uniformly, there appear normal strains but no thermal stresses. The thermal stresses will occur in the following cases: first, if the plate experiences a nonuniform temperature field; secondly, if the displacements are prevented from occurring freely because of the restrictions placed on the boundary even with a uniform temperature; and thirdly, if the material displays anisotropy even with uniform heating-for example, if a heated plate consists of several layers of different materials.

Curl is defined as the departure form an ideal flat form of a paper caused by ambient humidity or temperature changes. The deformation of an unconstrained sheet may be expressed by three basic curl curvatures where represent bending curvatures while is the twist curvature. Classical laminate theory based on linear kinematics has been used to analyze curl of papers. Such analysis generally predicts a double curvature shape of the sheets. Observations of curled papers and asymmetric composite laminates, however, indicate a single curvature, i.e a cylindrical shape^{[7]}.
The reason for this phenomenon was examined by Hyer [??] who showed that laminate theory modeling of curvatures of unsymmetric carbon/epoxy laminates requires incorporation of nonlinear kinematics. The analysis of Hyer showed that, at a certain critical temperature, the cylindrical shape becomes the most energetically favorable.

For simulation of curl in paper incorporating effects of nonlinear kinematics, the finite element code ANSYS was used. A two-layer papers of various stacking sequence,i.e, [0/15], [0/30], [0/45] and [0/90] consisting of orthotropic linear elastic plies were considered in the numerical analyses. The paper has properties:

- Dimension: and thickness per layer is

- Elastic modulus:

- Thermal coefficients (unit is in/in per temperature change):

- Moisture coefficients (unit is in/in per %RH change):

- Density:

A gird 16x16 was used to discretize a plate.

Two different cases are considering here: the first is to increase the moisture and the second is to increase the temperature.

## Curling of paper fixed at the top line due to moisture changes^{[3]}[edit]

The paper was moisturized from 50% RH to 90% RH after 12 hours. So the increasing of moisture is 40%. These are the results between experiments (done by **J. T. Decker**, an undergraduate student from University of Wisconsin,Madison) and ANSYS (done by **Tuan Hoang**, UW Madison)

### Curling of [0-15] laminate[edit]

### Curling of [0-30] laminate[edit]

### Curling of [0-45] laminate[edit]

### Curling of [0-90] laminate[edit]

## Curling of paper fixed at the center due to temperature changes^{[3]}[edit]

The reference temperature is and then paper was heated up to At the critical temperature, the stiffness matrix is zero and the Ansys program crashes, hence we can obtain the value of .To find the possible stable cylindrical solution, a three-step solution procedure was performed:

- Firstly, four concentrated loads F=0.01N, but no temperature changes, were applied at four corners of the paper to achieve a slight curvature

- Then the temperature was increased incrementally. When the temperature , the concentrated loads were released.

- Finally, the temperature was increased until without concentrated loads, the shape of the panel will then remain approximately cylindrical.

### Curling of [0-90] (cross-ply) laminate[edit]

- Step 1: apply four small loads

- Step 2: increase the temperature from T=0 to T=170 while keeping forces

- Step 3: continue increasing the temperature but remove the forces

- Step 4: keep on increasing temperature until T=300

The final shape for layer [0-90] after heating up to 300 Celsius is shown as below:

### Curling of [0/45] laminate[edit]

- Step 1: apply four small loads

- Step 2: increase the temperature from T=0 to T=170 while keeping forces

- Step 3: continue increasing the temperature but remove the forces

- Step 4: keep on increasing temperature until T=300

The final shape for layer [0-45] after heating up to 300 Celsius is shown as below:

# Nonlinear buckling analysis in ANSYS[edit]

- Eccentric loading or geometry/imperfection is required
- Is more accurate then linear buckling solutions
- Requires gradual loading to find the point of instability
- can model "post-buckling" response of a structure

## ANSYS nonlinear buckling procedure[edit]

- (OPTIONAL) CLEAR the Options of previous analyses on the same model, see Solution > Reset Options
- Solve the linear, static analysis of a structure
- Include large deformation effects NLGEOM,ON from Solution > Analysis Options
- Use Output Controls to insure data other than the Last Step is available for postprocessing (use ALL SUBSTEPS, if possible)
- Use gradual (ramped) loading and automatic time stepping from Solution > Time/Frequenc > Time and Substeps
- Control convergence behavior for number of equilibrium iteration, convergence criteria, etc. under Solution > Nonlinear
- Difficult problems (or analysis of post-buckling) may require use of the "Arc Length" convergence enhancement tool for a successful run

## What to do when it will not converge[edit]

- check the solution output and error log file for messages
- apply the load in more, smaller substeps
- allow more equilibrium iterations
- try alternative material models (bilinear vs. multilinear, different hardening rules, etc.)
- inspect the mesh in high stress regions for poor element shapes
- re-evaluate you choice of loads (get rid of point loads, overconstrained edges)
- look at the last good solution for any irregularities
- re-check element options (and material properties, and real constants, and load values, and dimensions)
- experiment with convergence enhancement tools in the code
- deactivate one or more of the nonlinear conditions to find the problem
- (rarely) loosen the convergence criteria - to find the problem - then tighten it up again

## Commands to calculate curl of papers[edit]

```
/BATCH !ANSYS command for batch mode
/NERR,5,1E6 !Increase the default warnings
* SET,L,114.3 !Set the side length of a paper
* SET,t,0.31 !Set the thickness of each layer
* SET,E1,3.8e3 !Set modulus in the machine direction
* SET,E2,1.7e3 !Set modulus in the fiber direction
* SET,Nu12,0.15 !Set poisson coefficient
* SET,G12,1e3 !Set shear modulus
* SET,T0,0 !Set initial or reference temperature
* SET,Tend,200 !Set final temperature
/PREP7 !Enter preprocessing
/TITLE, NONLINEAR ANALYSIS FIXED @ CENTER
ET,1,SHELL99 !Select element type
R,1 !Set the direction and thickness of each layer
RMODIF,1,1,2,0,0,0,0,0
RMODIF,1,13,1,0,t,1,90,t
MP,EX,1,E1 !Assign above properties
MP,EY,1,E2
MP,PRXY,1,Nu12
MP,GXY,1,G12
MP,REFT,1,T0
MP,CTEX,1,4E-6 !Thermal coefficient along machine direction
MP,CTEY,1,1E-5 !Thermal coefficient along fiber direction
K,1,-L/2,-L/2 !Create a plate L x L
K,2,L/2,-L/2
K,3,L/2,L/2
K,4,-L/2,L/2
A,1,2,3,4
LESIZE,ALL,,,16 !Mesh the plate with a grid of 16 x 16
MSHKEY,1
AMESH,ALL
FINISH
/SOLU !Enter processing
ANTYPE,STATIC !Set the analysis type is static
NLGEOM,ON !Use nonlinear geometric
AUTOTS,ON !Turn the automatic time step on
OUTRES,ALL,ALL !Write all steps into output window
NSEL,S,LOC,X,0 !Select origin (0,0) and fixed all d.o.f
NSEL,R,LOC,Y,0
D,ALL,ALL
NSEL,S,LOC,X,L/2 !Select four corners and apply a small load to create an imperfection of plate
NSEL,R,LOC,Y,-L/2
F,ALL,FZ,0.01
NSEL,S,LOC,X,-L/2
NSEL,R,LOC,Y,L/2
F,ALL,FZ,0.01
NSEL,S,LOC,X,-L/2
NSEL,R,LOC,Y,-L/2
F,ALL,FZ,0.01
NSEL,S,LOC,X,L/2
NSEL,R,LOC,Y,L/2
F,ALL,FZ,0.01
SOLVE !Solve the first step
BFA,1,TEMP,70 !In the second step, keep the load and apply temperature changes
SOLVE !Solve the second step
NSEL,S,LOC,X,L/2 !In the final step, delete the load and keep increasing temperature until Tend
NSEL,R,LOC,Y,-L/2
FDEL,ALL,FZ
NSEL,S,LOC,X,-L/2
NSEL,R,LOC,Y,L/2
FDEL,ALL,FZ
NSEL,S,LOC,X,-L/2
NSEL,R,LOC,Y,-L/2
FDEL,ALL,FZ
NSEL,S,LOC,X,L/2
NSEL,R,LOC,Y,L/2
FDEL,ALL,FZ
BFA,1,TEMP,Tend
LNSRCH,ON !Turn the line search on
NSUBST,10,1000,10 !Set the substep 10, the maximum step is 1000 and minimum step is 10
NEQIT,150 !Set the number of equilibrium iteration 150
SOLVE !Solve the final step
FINISH
/POST1 !Enter post processing
SET,LIST
PLDISP,1
FINISH
```

For sets of command in Ansys refer to ^{[8]}

# References[edit]

- ↑ Timoshenko, S.P. and Gere, J.M.,
*Theory of plates and shells*, McGram-Hill, 1959. - ↑ Ugural, A.C.,
*Stresses in plates and shells*, McGraw-Hill, New York 1981. - ↑
^{3.0}^{3.1}^{3.2}^{3.3}^{3.4}^{3.5}^{3.6}^{3.7}Eduard Ventsel, Theodor Krauthammer,*Thin plates and shells, theory, analysis and applications*,CRC Press, 2001. View pp 17-30 for small deflection theory of plate bending, pp 191-220 for large deflection and thermal stresses in plate. - ↑ Sudhakar Nair,
*Theory of plates and shells*, Cambridge, 2009. - ↑ Robert M. Jones,
*Thermal buckling of uniformly heated unidirectional and symmetric cross-ply laminated fiber-reinforced composite uniaxial in-plane restrained simply supported rectangular plates*, Composites: part A, Vol. 36, 2005. - ↑ Hyer, M.W.,
*Stress Analysis of Fiber-Reinforced Composite Materials*, Destech Pubns Inc; 2008. - ↑ A. Nordstrom, P. Gudmundson and L.A. Carlsson,
*Influence of sheet dimensions on curl of paper*, Journal of pulp and paper science: Vol. 24, No. 1, Jan 1996. - ↑ Erdogan Madenci and Ibrahim Guven,
*The Finite Element Method and Applications in Engineering Using ANSYS*, Springer 2005.