Analysis of complex composite beam by using timoshenko beam theory

International Journal of Design and Manufacturing Technology (IJDMT), ISSN 0976 –
INTERNATIONAL JOURNAL OF DESIGN AND MANUFACTURING
6995(Print), ISSN 0976 – 7002(Online) Volume 4, Issue 1, January- April (2013), © IAEME
TECHNOLOGY (IJDMT)

ISSN 0976 – 6995 (Print)
ISSN 0976 – 7002 (Online) IJDMT
Volume 4, Issue 1, January- April (2013), pp. 43-50
© IAEME: www.iaeme.com/ijdmt.html
Journal Impact Factor (2013): 4.2823 (Calculated by GISI)
©IAEME
www.jifactor.com

ANALYSIS OF COMPLEX COMPOSITE BEAM BY USING
TIMOSHENKO BEAM THEORY & FINITE ELEMENT METHOD

Prabhat Kumar Sinha1, Rohit1
1
Mechanical Engineering Department
Sam Higginbottom Institute of Agriculture, Technology & Sciences
(Deemed-to-be-University) Allahabad, 211007, U.P.India
(Formerly Allahabad Agriculture Institute)

ABSTRACT

Fiber-reinforced composites, due to their high specific strength, and stiffness,
which can be tailored depending on the design requirement, are fast replacing the
traditional metallic structures in the weight sensitive aerospace and aircraft industries. An
analysis Timoshenko beam theory for complex composite beams is presented. Composite
materials have considerable potential for wide use in aircraft structures in the future,
especially because of their advantages of improved toughness, reduction in structural
weight, reduction in fatigue and corrosion problems. The theory consists of a combination
of three key components: average displacement and rotation variables that provide the
kinematic description of the beam, stress and strain moments used to represent the
average stress and strain state in the beam, and the use of exact axially-invariant plane
stress solutions to calibrate the relationships between all these quantities. The
Euler‐Bernoulli beam theory neglects Shear deformations by assuming that plane sections
remain plane and perpendicular to the neutral axis during bending. As a result, shear
strains and stresses are removed from the theory. Two essential aspects of Timoshenko’s
beam theory are the treatment of shear deformation by the introduction of a mid-plane
rotation variable, and the use of a shear correction factor [36].

Keywords: Timoshenko Beam Theory, Finite Element Analysis.

43


INTRODUCTION

Composite materials in this era have considerable potential for wide use in aircraft
structures in the future, especially because of their advantages of improved toughness,
reduction in structural weight, reduction in fatigue and corrosion problems [2]. Most of the
structures experiences severe dynamic environment during their service life; thus the excited
motions are likely to have large amplitudes. The analysis of complex composite structures is
far more complex due to anisotropy, material couplings, and transverse shear flexibility
effects compared to their isotropic counterparts [5]. The use of composite materials requires
complex analytical methods in order to predict accurately their response to external loading,
especially in severe environments, which may induce geometrically non-linear behavior and
material nonlinearity. This requires appropriate design criteria and accurate estimation of the
fatigue life. In addition to the usual difficulties encountered generally in the non-linear
analysis of structures, related to the fact that the theorem of superposition does not hold,
existence and uniqueness of the solutions are generally not guaranteed [1].
The main objective of this work is to analyze the complex composite beams. The
geometrically non-linear analysis of composite beam exhibits specific difficulties due to the
anisotropic material behavior, and to the higher non-linearity induced by a higher stiffness,
inducing tensile mid-plane forces in beam higher, than that observed with conventional
homogeneous materials [1]. These structures with complex boundary conditions, loadings
and shapes are not easily amenable to analytical solutions and hence one has to resort to
numerical methods such as finite elements [11]. A considerable amount of effort has gone
into the development of simple beam bending elements based on the Timoshenko Beam
Theory for homogeneous isotropic beam. The advantages of this approach are (i) it accounts
for transverse shear deformation, (ii) it requires only C0 continuity of the field variables, (iii)
it requires refined equivalent single-layer theory, and (iv) it is possible to develop finite
elements based on 6 engineering degrees of freedom viz. 3 translations and 3 rotations [14].
However, the low-order elements, i.e. the 3-node triangular, 4-node and 8-node quadrilateral
elements, locked and exhibited violent stress oscillations [10]. Unfortunately, this element
which is having the shear strain becomes very stiff when used to model thin structures,
resulting inexact solutions. This effect is termed as shear-locking which makes this otherwise
successful element unsuitable. Many techniques have been tried to overcome this, with
varying degrees of success. The most prevalent technique to avoid shear locking for such
elements is a reduced or selective integration scheme [8]. In all these studies shear stresses at
nodes are inaccurate and need to be sampled at certain optimal points derived from
considerations based on the employed integration order .The use of the same interpolation
functions for transverse displacement and section rotations in these elements results in a
mismatch of the order of polynomial for the transverse shear strain field. This mismatch in
the order of polynomials is responsible for shear locking [7].
The Euler-Bernoulli beam theory neglects shear deformations by assuming that plane
sections remain plane and perpendicular to the neutral axis during bending. As a result, shear
strains and stresses are removed from the theory. Shear forces are only recovered later by
equilibrium: V=dM/dx [5]. In reality, the beam cross-section deforms somewhat like what is
shown in Figure 1a. This is particularly the case for deep beam, i.e., those with relatively high
cross-sections compared with the beam length, when they are subjected to significant shear
forces. Usually the shear stresses are highest around the neutral axis, which is where;
consequently, the largest shear deformation takes place. Hence, the actual cross-section

44


curves. Instead of modeling this curved shape of the cross-section, the Timoshenko beam
theory retains the assumption that the cross-section remains plane during bending [7].
However, the assumption that it must remain perpendicular to the neutral axis is relaxed. In
other words, the Timoshenko beam theory is based on the shear deformation mode in Figure
1b. Various boundary conditions have been considered. The effect of variations in some
material and/or geometric properties of the beam have also been studied.

γv

-dwv

V

1. (a) (b)

Actual shear deformation Average shear deformation

LITERATURE REVIEW

A rigorous mathematical model widely used for describing the vibrations of beams is
based on the Thick beam theory (Timoshenko, 1974) developed by Timoshenko in the 1920s.
This partial differential equation based model is chosen because it is more accurate in
predicting the beam’s response than the Euler‐Bernoulli beam theory [14].
Historically, the first important beam model was the one based on the Euler‐Bernoulli
Theory or classical beam theory as a result of the works of the Bernoulli's and Euler. This
model, established in 1744, includes the strain energy due to the bending and the kinetic
energy due to the lateral displacement of the beam [16]. In 1877, Lord Rayleigh improved it
by including the effect of rotary inertia in the equations describing the flexural and
longitudinal vibrations of beams by showing the importance of this correction especially at
high frequency frequencies [15]. In 1921 and 1922, Timoshenko proposed another
improvement by adding the effect of shear deformation. He showed, through the example of a
simply-supported beam, that the correction due to shear is four times more important than
that due to rotary inertia and that the Euler‐Bernoulli and Rayleigh beam equations are
special cases of his new result [18]. As a summary, four beam models can be pointed out in
Table 1, the Euler‐Bernoulli beam and Timoshenko Beam models being the most widely
used.
Table 1.
Effect Lateral Bending Rotary Shear
Beam Model displacement moment inertia deformation
Euler – Bernoulli + + - -
Rayleigh + + + -
Shear + + - +
Timoshenko + + + +

45


METHODOLOGY USED
As we have seen, the Timoshenko Beam Theory accounts for both the effect of rotary
inertia and shear deformation, which are neglected when applied to Euler‐Bernoulli Beam
Theory [22]. The external and internal loading of the beam depends on its geometrical and
material properties as well as the external applied torque. The geometrical properties refer
mainly to its length, size and shape of its cross-section such as its area A , moment of inertia I
with respect to the central axis of bending, and Timoshenko’s shear coefficient k which is a
modifying factor ( k < 1 ) to account for the distribution of shearing stress such that effective
shear area is equal to kA . The material properties refer to its density in mass per unit volume
ρ, Young’s modulus or modulus of elasticity E and shear modulus or modulus of rigidity G
[23].
1. Mathematical Formulation
A Timoshenko beam takes into account shear deformation and rotational inertia effects,
making it suitable for describing the behavior of short beams, sandwich composite beams or
beams subject to high-frequency excitation when the wavelength approaches the thickness of
the beam.
The resulting equation is of 4th order, but unlike ordinary beam theory - i.e. Bernoulli-Euler
theory - there is also a second order spatial derivative present [16].

ϴx
డ௪
డ௫

(Fig. 1: Deformation in Timoshenko Beam element)

In static Timoshenko beam theory without axial effects, the displacements of the beam are
assumed to be given by
ux (x, y, z) = -zφ(x); uy = 0; uz = w(x)
Where (x,y,z) are the coordinates of a point in the beam , ux, uy, uz are the components of the
displacement vector in the three coordinate directions, φ is the angle of rotation of the normal
to the mid-surface of the beam, and ω is the displacement of the mid-surface in z-direction
[25]. The governing equations are the following uncoupled system of ordinary differential
equations is:

ௗ௪ ଵ ௗ ௗఝ
=φ- (EI )
ௗ௫ ௞஺ீ ௗ௫ ௗ௫

46


Stiffness Matrix
In the finite element method and in analysis of spring systems, a stiffness matrix, K, is a
symmetric positive semi index matrix that generalizes the stiffness of Hook’s law to a matrix,
describing the stiffness of between all of the degrees of freedom so that
F = - kx
Where F and x are the force and the displacement vectors, and
ଵ
U= ଶ
* xT kx
Is the system's total potential energy [30].

Mass Matrix
A mass matrix is a generalization of the concept of mass to generalized bodies. For static
condition mass matrix does not exist, but in case of dynamic case mass matrix is used to
study the behavior of the beam element. When load is suddenly applied or loads are variable
nature, mass & acceleration comes into the picture [29].

2. FINITE ELEMENT FORMULATION

FEM is a numerical method of finding approximate solutions of partial differential
equation as well as integral equation. The method essentially consists of assuming the
piecewise continuous function for the solution and obtaining the parameters of the functions
in a manner that reduces the error in the solution .By this method we divide a beam in to
number of small elements and calculate the response for each small elements and finally
added all the response to get global value. Stiffness matrix and mass matrix is calculate for
each of the discretized element and at last all have to combine to get the global stiffness
matrix and mass matrix [30]. The shape function gives the shape of the beam element at any
point along longitudinal direction. This shape function also calculated by finite element
method. Both potential and kinetic energy of beam depends upon the shape function. To
obtain stiffness matrix potential energy due to deflection and to obtain mass matrix kinetic
energy due to application of sudden load are use. So it can be say that potential and kinetic
energy of the beam depends upon shape function of beam obtain by FEM method [32].

Formulation of Hermite shape function

Beam is divided in to element. Each node has two degrees of Freedom.
Degrees of freedom of node j are Q2j-1 and Q2j Q2j-1 is transverse displacement and Q2j is
slope or rotation.

Q1 Q3 Q5 Q7 Q9
e1 e2 e3 e4
Q2 Q4 Q6 Q8 Q10

Q= [Q1 Q2Q3...Q10] T Q is the global displacement vector.

47


Local coordinates

q1 q3
e

q2 q4

q= [q1 , q2 , q3 , q4]T
= [v1 , v2’ , v3 , v4’]

Hermite shape function for an element of length le [32].

RESULT AND DISCUSSION

In the present analysis the mathematical formulation and finite element formulation
for loaded complex composite beam have been done. The beam is modeled by Timoshenko
beam theory. This essentially consists of assuming the piecewise continuous function for the
solution and obtaining the parameters of the functions in a manner that reduces the error in
the solution. By this method we divide a beam in to number of small elements and calculate
the response for each small elements and finally added all the response to get global value.
By taking Timoshenko beam theory we have taken shear deformation into consideration
which other theories neglect to make the beam analysis simplified. Due to this we can be able
to formulate a composite beam that would be much more reliable for fabrication of structures
that are under continuous loading.

REFERENCES

[1] Abir, Humayun R.H. “On free vibration response and mode shapes of arbitrarily
laminated rectangular plates” Composite Structures 65 (2004) 13–27.
[2] Ahmed, S., Irons, B. M., and Zienkiewicz, O. C. “Analysis of thick and thin structures by
curved finite elements” Comput. Methods Appl. Mech. Eng.(2005) 501970:121-145.
[3] Allahverdizadeh, A., Naei, M. H., and Nikkhah, B. M. “Vibration amplitude and thermal
effects on the nonlinear behavior of thin circular functionally graded plates” International
Journal of Mechanical Sciences 50 (2008) 445–454.
[4] Amabili, M. “Nonlinear vibrations of rectangular plates with different boundary
conditions theory and experiments” Computers and Structures 82 (2004) 2587–2605.
[5] Amabili, M. “Theory and experiments for large-amplitude vibrations of rectangular plates
with geometric imperfections” Journal of Sound and Vibration 291 (2006) 539–565.
[6] Barik, M. and Mukhopadhyay, M. “Finite element free flexural vibration analysis of
arbitrary plates” Finite element in Analysis and Design 29(1998)137-151.
[7] Barik, M. and Mukhopadhyay, M. “A new stiffened plate element for the analysis of
arbitrary plates” Thin-Walled Structures 40 (2002) 625–639.
[8] Bhavikatti, S. S. “finite element analysis”.
[9] Bhimaraddi, A. and Chandrasekhara, K.” Nonlinear vibrations of heated asymmetric
angle ply laminated plates” Int. J. Solids Structures Vol. 30, No. 9, pp.1255-1268, (1993).

48


[10] Bikri, K. El., Benamar, R., and Bennouna, M. “Geometrically non-linear free vibrations
of clamped simply supported rectangular plates. Part I: the effects of large vibration
amplitudes on the fundamental mode shape” Computers and Structures 81 (2003) 2029–2043.
[11] Chandrashekhara, K. and Tenneti, R. “Non-linear static and dynamic analysis of heated
laminated plates: a finite element approach” Composites Science and Technology 51 (1994)
85-94.
[12] Chandrasekhar et al. “Nonlinear vibration analysis of composite laminated and sandwich
plates with random material properties” International Journal of Mechanical Sciences, 8
march 2010.
[13] Das, D., Sahoo, P., and Saha, K. “Large-amplitude dynamic analysis of simply
supported skew plates by a variational method” Journal of Sound and Vibration 313 (2008)
246–267.
[14] Dolph, C. (1954). On the Timoshenko theory of transverse beam vibrations. Quarterly of
Applied Mathematics, Vol. 12, No. 2, (July 1954) 175-187, ISSN: 0033-569X.
[15] Ekwaro-Osire, S.; Maithripala, D. H. S. & Berg, J. M. (2001). A Series expansion
approach to interpreting the spectra of the Timoshenko beam. Journal of Sound and
Vibration, Vol. 240, No. 4, (March 2001) 667-678, ISSN: 0022-460X.
[16] Dadfarnia, M.; Jalili, N. & Esmailzadeh, E. (2005). A Comparative study of the Galerkin
approximation utilized in the Timoshenko beam theory. Journal of Sound and Vibration, Vol.
280, No. 3-5, (February 2005) 1132-1142, ISSN: 0022-460X.
[17] Ferreira, A.J.M. “MATLAB codes for finite element analysis”.
[18] Fiber Model Based on Timoshenko Beam Theory and Its Application (May 2011)
Zhang, Lingxin; Xu, Guolin; Bai, Yashuang.
[19] Geist, B. & McLaughlin, J. R. (2001). Asymptotic formulas for the eigen values of the
Timoshenko beam. Journal of Mathematical Analysis and Applications, Vol. 253, (January
2001) 341-380, ISSN: 0022-247X.
[20] Gürgöze, M.; Doğruoğlu, A. N. & Zeren, S (2007). On the Eigen characteristics of a
cantilevered visco-elastic beam carrying a tip mass and its representation by a spring-damper-
mass system. Journal of Sound and Vibrations, Vol. 1-2, No. 301, (March 2007) 420-426,
ISSN: 0022-460X.
[21] Han, S. M.; Benaroya, H.; & Wei T. (1999). Dynamics of transversely vibrating beams
using four engineering theories. Journal of Sound and Vibration, Vol. 225, No. 5, (September
1999) 935-988, ISSN: 0022-460X.
[22] Hoa, S. V. (1979). Vibration of a rotating beam with tip mass. Journal of Sound and
Vibration, Vol. 67, No. 3, (December 1979) 369-381, ISSN: 0022-460X.
[23] Kapur, K. K. (1966). Vibrations of a Timoshenko beam, using a finite element approach.
Journal of the Acoustical Society of America, Vol. 40, No. 5, (November 1966) 1058– 1063,
ISSN: 0001-4966.
[24] N. Ganesan and r. C. Engels, 1992, timoshenko beam elements using the assumed
Modes method, journal of sound and vibration 156(l), 109-123
[25] P jafarali, s mukherje, 2007, analysis of one dimensional finite elements using the
Function space approach.
[26] Oguamanam, D. C. D. & Heppler, G. R. (1996). The effect of rotating speed on the
flexural vibration of a Timoshenko beam, Proceedings of the IEEE International Conference
on Robotics and Automation, pp. 2438-2443, ISBN: 0-7803-2988-0, Minneapolis, April
1996, MN, USA.

49


[27] Ortner, N. & Wagner, P. (1996). Solution of the initial-boundary value problem for the
simply supported semi-finite Timoshenko beam. Journal of Elasticity, Vol. 42, No. 3, (March
1996) 217-241, ISSN: 0374-3535.
[28] R. Davis. R. D. Henshell and g. B. Warburton, 1972, A Timoshenko beam element,
Journal of Sound and Vibration 22 (4), 475-487
[29] Salarieh, H. & Ghorashi, M. (2006). Free vibration of Timoshenko beam with finite
mass rigid tip load and flexural–torsional coupling. International Journal of Mechanical
Sciences, Vol. 48, No. 7, (July 2006) 763–779, ISSN: 0020-7403.
[30] S. P. Timoshenko, D. H. Young, 2008, Elements of strength of materials: Stresses in
beam, An East West Publication, 5th Edition, p. (95-120),New Delhi
[31] S. S. Bhavikatti, 2005, Finite Element Analysis, New Age International Limited, P. (25-
28) & P.(56-58), New Delhi.
[32] Tafeuvoukeng, I. G., 2007. A unified theory for laminated plates. Ph.D. thesis,
University of Toronto.
[33] Thiago G. Ritto, Rubens Sampaio, Edson Cataldo, 2008, Timoshenko Beam with
Uncertainty on the Boundary Conditions, Journal of the Brazilian Society of Mechanical
Sciences andEngineering,Vol-4 / 295.
[34] Timoshenko, S. P., 1921. On the correction for shear of the differential equation for
transverse vibrations of prismatic bars. Philosophical Magazine 41, 744–746.
[35] Timoshenko, S. P., 1922. On the transverse vibrations of bars of uniform cross-section.
Philosophical Magazine 43, 125 – 131.
[36] Timoshenko beam theory with pressure corrections for layered orthotropic beams. (Nov
2011) Graeme J. Kennedya,Jorn S. Hansena,2, Joaquim R.R.A. Martinsb,3 University of
Toronto Institute for Aerospace Studies, 4925 Dufferin Street, Toronto, M3H 5T6, Canada .
Department of Aerospace Engineering, University of Michigan, Ann Arbor, MI 48109, USA
[37] Umasree P. and Bhaskar K., 2006: Analytical solutions for flexure of clamped
rectangular cross ply plates using an accurate zig-zag type higher-order theory. Composite
Structures, Vol. 74, pp. 426-439.
[38] I.M.Jamadar, S.M.Patil, S.S.Chavan, G.B.Pawar and G.N.Rakate, “Thickness
Optimization of Inclined Pressure Vessel using Non Linear Finite Element Analysis using
Design by Analysis Approach” International Journal of Mechanical Engineering &
Technology (IJMET), Volume 3, Issue 3, 2012, pp. 682 - 689, ISSN Print: 0976 – 6340,
ISSN Online: 0976 – 6359, Published by IAEME.
[39] T.Vishnuvardhan and Dr. B.Durga Prasad, “Finite Element Analysis And Experimental
Investigations On Small Size Wind Turbine Blades” International Journal of Mechanical
Engineering & Technology (IJMET), Volume 3, Issue 3, 2012, pp. 493 - 503, ISSN Print:
0976 – 6340, ISSN Online: 0976 – 6359, Published by IAEME.

50

Analysis of complex composite beam by using timoshenko beam theory

More Related Content

What's hot (17)

Viewers also liked (7)

Similar to Analysis of complex composite beam by using timoshenko beam theory (20)

More from IAEME Publication (20)

Analysis of complex composite beam by using timoshenko beam theory