Free longitudinal vibrations of functionally graded tapered axial bars by pseudospectral method
Sri Harikrishna Pillutla^{1} , Sudheer Gopinathan^{2} , Vasudeva Rao Yerikalapudy^{3}
^{1}GITAM (Deemed to be University), Visakhapatnam, India
^{2}GVP College of Engineering for Women, Visakhapatnam, India
^{3}IIT Bhubaneswar, Bhubaneswar, India
^{2}Corresponding author
Journal of Vibroengineering, Vol. 20, Issue 5, 2018, p. 21372150.
https://doi.org/10.21595/jve.2018.19373
Received 9 November 2017; received in revised form 13 March 2018; accepted 20 April 2018; published 15 August 2018
In this work, the problem of free longitudinal vibration of rods with variable crosssectional area and material properties is investigated using the pseudospectral method. With the gradation of material properties like modulus of elasticity and mass density in the axial direction, the results corresponding to a functionally graded axial bar are obtained using the proposed pseudospectral formulation. The pseudospectral formulation used is relatively easy to implement and powerful in analyzing vibration problems. With the help of several numerical examples, the nondimensional natural frequencies of rods obtained using the pseudospectral method are compared with those obtained by the analytical solution, generalized finite element method, the discrete singular convolution method and differential transformation method. The numerical results obtained show that the proposed technique allows boundary conditions to be incorporated easily and yields results with good accuracy and faster convergence rates than other methods.
Keywords: vibrations, inhomogeneous rod, graded axial bar, numerical, pseudospectral.
1. Introduction
Functionally graded (FG) material structures find extensive use in modern engineering as their material properties can be tailored to meet the requirements of different applications [1]. The FG axial bars are a class of inhomogeneous rods/bars with material properties varying continuously in desired spatial directions. The inhomogeneous rods are known to provide a suitable distribution of strength and weight for engineering structures [2]. A study of the vibration characteristics of these rods is a subject of considerable scientific interest that has wide applications in aerospace, civil and mechanical engineering [35].
The governing differential equations of motion for longitudinal vibration of nonuniform rods have variable coefficients introduced by variable crosssectional area. In addition, for functionally graded tapered axial bars, the varying material properties add up to the previous variable coefficients in the governing equation increasing the complexity in vibration analysis of these bars/rods. In general, methods of vibration analysis are classified as analytical and numerical methods while some are semianalytical that use a combination of both the approaches. It is generally agreed that obtaining analytical/closedform solutions of this vibration problem is possible only for some specific geometric and material functions and are often cumbersome. Application of numerical methods becomes essential to obtain the solution of the problem for general cases. There are many different methods for the numerical solution of differential equations which include Finite Element Method (FEM), Differential Quadrature Method (DQM), Differential Transformation Method (DTM), Discrete Singular Convolution (DSC) method and Spectral/Pseudo Spectral methods. Several studies have been dedicated to the problem of exact/analytic solutions for longitudinal vibrations of nonuniform rods [613] while some researchers [3, 1417] have developed numerical methods.
Eisenberger [6] obtained the exact longitudinal vibration of a rod with polynomial variation in the crosssectional area and mass distribution along the member employing an exact element method. Bapat [7] introduced an efficient approach to solve the vibration problem of a rod composed of $N$ uniformly tapered sections and studied the vibrations of a rod composed of uniform, conical, exponential and catenoidal tapers. Abrate [8] has shown that there is a class of nonuniform rods for which the equations of motion can be transformed into the wave equation and considered area of variation of the form ${A}_{0}{\left(1+\alpha x/L\right)}^{2}$. Kumar and Sujith [9] obtained exact analytical solutions for the longitudinal vibration of rods with polynomial and sinusoidal area variations of form ${\left(ax+b\right)}^{n}$, ${A}_{0}{\mathrm{s}\mathrm{i}\mathrm{n}}^{2}\left(ax+b\right).$ Li [10] carried out a functional transformation of the governing differential equation and presented the exact solutions for certain functional forms of an involved parameter. The differential transformation method was used in [11] to obtain exact solutions of the free axial vibration of a tapered bar with linearly varying mass and area. Raj and Sujith [12] derived a general analytical technique that helps in obtaining crosssectional area variations which give specific, closedform solutions for the longitudinal vibration of rods and have presented numerical solution for area variation of the form ${x}^{n}\mathrm{exp}\left(b{x}^{n}\right)$, ${x}^{n}\mathrm{exp}\left(bx\right)$. Yardimoglu and Aydin [13] obtained the exact longitudinal vibration characteristics of rods with sinusoidal area crosssections of the form ${\mathrm{s}\mathrm{i}\mathrm{n}}^{n}\left(ax+b\right)$, in terms of associated Legendre functions. In [14], a domain partition power series method for the vibration analysis of variable crosssection rods is presented and the longitudinal vibrations of a rod with linearly varying area is studied. The differential quadrature method was used in [15] to analyze the free vibrations of a general nonuniform rod. In [16], the free vibration analysis of elastic rods was investigated using a novel global collocation method. An adaptive generalized finite element (GFEM) method was proposed in [17] to study the free longitudinal vibration analysis of straight bars and trusses. The results obtained using GFEM for sinusoidal and polynomial area variations of rod were compared with those obtained using finite element and composite elements methods. Several closed form solutions have been derived by the semiinverse method for the problem of determining eigenvalues of inhomogeneous structures in [18]. It is also shown in [19] than an inhomogeneous rod can possess an exponential mode shape and derived closedform solutions that can be utilized as model solutions for verification purposes. Recently, [3] investigated the longitudinal free vibrations of nonuniform rods by using the Discrete Singular Convolution (DSC) approach. The nondimensional natural frequencies, obtained were compared with those obtained using exact methods and the differential quadrature method.
In most of the aforementioned works, the focus was on vibration of rods having variable area crosssections. Recently, the longitudinal vibration of a functionally graded tapered axial bar was considered in [20] wherein, the material gradation was accounted for by varying the modulus of elasticity and mass density. Two new approaches based on Differential Transformation Method (DTM), namely Differential Transform Element Method (DTEM) and Differential Quadrature Element method of Lowest order (DQEL) were introduced by them to numerically study the free longitudinal vibration of tapered functionally graded (FG) rods. Further, in [21], the longitudinal vibrations of a $FG$ linearly tapered axial bar with exponential variation in mass density and modulus of elasticity was investigated using Finite Element Method (FEM) by proposing a new element that could be derived by using the basic principles of structural mechanics.
The purpose of this paper is to implement the pseudospectral method for the longitudinal vibration analysis of tapered $FG$ axial bars. Pseudospectral methods (PSM) are powerful tools for solving differential equations with high accuracy in a simple domain. The method has been successfully applied to the free vibration analysis of curved Timoshenko beams [22], Timoshenko beams and axisymmetric Mindlin plates [23], linear and nonlinear beams [24], cylindrical helical springs [25] and Functionally graded Timoshenko beams [26]. There have been different approaches in implementing the pseudospectral formulations based on their treatment of boundary conditions. In this work, an efficient formulation of the PSM involving a change of independent variable that greatly simplifies computer programs for solving differential equations is used to transform the governing differential equation together with the boundary conditions into an eigenvalue problem, in which the eigenvalue represents the physical property of the vibration problem, namely the natural frequency. The problem is then solved using standard eigensolvers. The remainder of the paper is organized as follows. In Section 2, we introduce the pseudospectral method. In Section 3, we outline the problem and the solution methodology. In Section 4, the method is applied to examples that outline the convergence behavior, perform validations and demonstrate the advantages of the method.
2. Pseudospectral method
The spectral methods arise from the fundamental problem of approximation of a function by interpolation on an interval and are very much successful for the numerical solution of differential equations [27]. The PS method can be considered as a spectral method that performs a collocation process and delivers exponential (spectral) accuracy under the condition of smoothness. The starting point for the Pseudospectral method is the representation of the approximate solution $\left({u}_{N}\left(x\right)\right)$ of the solution $\left(u\left(x\right)\right)$ of the given differential equation by a linear combination of basis functions $\left({\varphi}_{n}\left(x\right)\right),(n=\mathrm{0,1},2,\dots .,N)$:
The best choice for ${\varphi}_{n}\left(x\right)$ are the eigenfunctions of a singular SturmLiouville problem such as the Chebyshev polynomials. Although the Legendre, Hermite and Laguerre polynomials are eigenfunctions of SturmLiouville problem, Chebyshev polynomials are more effective in handling the boundaries [28]. The Chebyshev polynomials are recursive orthogonal polynomials that can be defined as:
where $k$ is an integer [29]. Although defined for all $x$, Chebyshev polynomials are a stable representation only on $\left(1,1\right)$.
In PS method, one is usually content with obtaining an approximation to the solution on a discrete set of grid points. The PS method, demands that the differential equation be exactly satisfied at these set of points known as collocation points [30]. The accuracy, stability and rate of convergence of the numerical solutions depend on the choice of the collocation point [31] and the best choice for the collocation points is to use nodes that are clustered near the edges of the interval with an asymptotic density proportional to ${\left(1{x}^{2}\right)}^{1/2}$ as $n\to \infty $ [32]. The Chebyshev polynomial extreme points that are the ChebyshevGaussLobatto sampling grid points on $\left[1,1\right]$ are known to have such density properties [33]. Therefore, these points are chosen as collocation points in this work. The internal points which are the extrema of ${T}_{N}\left(x\right)$ are given by:
with $i=0,N$ denoting the end points and $i=$ 1, 2, …, $N1$ the internal points. These points correspond to:
The pseudospectral method associates the grid of collocation points with the basis set and the coefficients ${a}_{n}$ in the expansion (1) are found by requiring the residual function $L{u}_{N}f$ where $L$ is the operator of the differential equation $Lu=f\left(x\right)$ to vanish at the collocation points. There are several ways of implementing the PS method of which the differentiation based formulation [34, 35], integration based formulation [36, 37] and straight forward implementation [22, 23] are normally used. The differentiation based formulation is widely used in which one can construct the differentiation matrices using the recurrence finitedifferences formulae on arbitrarily spaced grids [34, 38] or utilizing the approach followed in [35, 39]. However, incorporation of boundary conditions when using differentiation matrices is complicated. The present work utilizes the straight forward implementation utilizing the Chebyshev polynomialtocosine change of variable together with a proper selection of internal collocation points based on the boundary conditions.
3. Mathematical formulation and solution methodology
The differential equation that governs the free longitudinal vibration of a axially graded bar reads as [40]:
Here $l$ denotes the axial coordinate, $u(l,t)$ denotes longitudinal displacement at any position $l$ and time $t$. $E\left(l\right)$, $A\left(l\right)$ and $\rho \left(l\right)$ are the modulus of elasticity, crosssectional area and mass density respectively, which are assumed to vary along the axial coordinate $l$ with ${l}_{1}$ and ${l}_{2}$ being the end coordinates of the rod. The classical boundary conditions considered are:
The longitudinal displacement is assumed to be separable in space and time where the time dependence is harmonic with angular frequency $\omega $ i.e., $u\left(l,t\right)=W\left(l\right){e}^{i\omega t}$ where $W\left(l\right)$ represents the mode shape. Denote $E\left(l\right)A\left(l\right)=S\left(l\right)$ where $S\left(l\right)$ is the axial rigidity that varies along the axial coordinate $l$.
Eq. (5) becomes $\frac{d}{dl}\left[S\left(l\right)\frac{dW}{dl}\right]={\omega}^{2}\rho \left(l\right)A\left(l\right)$:
where:
The governing equation becomes:
We now outline the solution methodology for Eq. (8) using PSM. The natural interval $x\in \left[\mathrm{1,1}\right]$ in which the collocation points are located may be adapted to the interval of interest $l\in \left[{l}_{1},{l}_{1}\right]$ by the transformation:
where $h={l}_{2}{l}_{1}$.
Due to change of variable:
Applying the transformation, the solution function $W\left(l\right)$ is now a function of $x$ and is assumed to be of the form:
Here:
$\frac{dW\left(x\right)}{dx}={W}^{\text{'}}\left(x\right)=\frac{dW}{d\theta}.\frac{d\theta}{dx}=\frac{{a}_{1}\mathrm{s}\mathrm{i}\mathrm{n}\theta +2{a}_{2}\mathrm{s}\mathrm{i}\mathrm{n}2\theta +........+N{a}_{N}\mathrm{s}\mathrm{i}\mathrm{n}N\theta}{\mathrm{s}\mathrm{i}\mathrm{n}\theta},$
$\frac{{d}^{2}W\left(x\right)}{d{x}^{2}}={W}^{\mathrm{\text{'}}\mathrm{\text{'}}}\left(x\right)=\frac{d}{d\theta}\left(\frac{dW}{dx}\right)\frac{d\theta}{dx},$
It is to be noticed that the trigonometric form of the Chebyshev polynomial which is a change of coordinate is used for the representation of the approximate solution. This is coupled with analytic differentiation and collocation at internal points followed by enforcement of boundary conditions at end points.
The transformed governing differential equation is:
If we collocate Eq. (17) at the points given by Eq. (4) and enforce the boundary conditions at $\theta =$ 0, $\theta =\pi $ which are given by:
Then we get a system of equations that is expressed as a matrix eigen value equation. The resulting equation is then solved using a standard eigensolver.
4. Numerical results and discussion
In this section we examine the convergence behavior of the PS method, validate the accuracy by comparing the results obtained with other analytical/numerical methods. Finally, we apply the method to obtain the nondimensional frequencies of vibration of a functionally graded axial bar. In all the examples considered, the rods are of unit length. The details of the work carried out in this section are presented in Table 1. A diagrammatic view of typical rods considered herein is given in Fig. 1.
Table 1. A layout of the numerical work carried out in Section 4
Purpose

Section

Variable characteristics of rod

End conditions

Previous literature (used for comparison)


${l}_{1}$, ${l}_{2}$

Method

Reference
number


Convergence behaviour study

4.1

1. $A\left(x\right)={A}_{0}{\left(1+2x\right)}^{2}$

FixedFree

Analytical

[8]

2. $A\left(x\right)=2{A}_{0}x$;
$m\left(x\right)=\rho \left(x\right)A\left(x\right)=2{m}_{0}x$

FreeFixed

Differential transform

[11]


3. $A\left(x\right)={x}^{0.5}\mathrm{e}\mathrm{x}\mathrm{p}(0.5{x}^{2})$

FixedFixed and
FixedFree

Discrete singular convolution

[3]


Validation of accuracy

4.2

$A\left(x\right)={A}_{0}{\mathrm{s}\mathrm{i}\mathrm{n}}^{2}\left(x+1\right)$
and
$A\left(x\right)={A}_{0}{\left(x+1\right)}^{4}$

FixedFixed

Analytical and generalized FEM

[9, 17]

4.3

$A\left(x\right)={A}_{0}{\mathrm{s}\mathrm{i}\mathrm{n}}^{n}\left(ax+b\right)$

FixedFixed
and
FixedFree

Analytical

[13]


4.4

$A\left(x\right)=K{x}^{n}\mathrm{e}\mathrm{x}\mathrm{p}\left(b{x}^{2}\right)$
and
$A\left(x\right)=K{x}^{n}\mathrm{e}\mathrm{x}\mathrm{p}\left(bx\right)$

FixedFixed,
FixedFree
and
FixedFixed

Analytical

[12]


4.5

1. $A\left(x\right)={A}_{0}\left(1{c}_{h}x\right)(1{c}_{b}x)$
$E\left(x\right)={E}_{0}\left(1+x\right)$
$\rho \left(x\right)={\rho}_{0}(1+x+{x}^{2})$

FixedFree
and
FixedFixed

DQEL/
DTEM

[20]


2. $A\left(x\right)={A}_{0}\left(1x\right),$
$E\left(x\right)={E}_{0}{e}^{x}$ and
$\rho \left(x\right)={\rho}_{0}{e}^{x}$

FixedFree
and
FixedFixed

FEM with a new element

[21]

4.1. Convergence behaviour of PS method
To study the convergence behaviour of the PS method in obtaining the frequency values of the vibration of nonuniform rods, some examples have been examined. As a first example, we consider the longitudinal free vibration of a fixedfree nonuniform bar with polynomial variation of crosssection area, constant elasticity modulus $E$ and constant density $\rho $ and unit length. The crosssection area varies as $A\left(x\right)={A}_{0}{\left(1+2x\right)}^{2}$ where ${A}_{0}$ is a reference crosssection area. Abrate [8] has presented exact analytical solution for longitudinal free vibration of bars with polynomial area variations. The exact nondimensional frequency parameters of rods given [8] are set as basis values and the relative error of the PS method with $N$ values varying from 10 to 16 is analyzed. The relative errors of the numerical values of the first six nondimensional natural frequencies given by $\mathrm{\Omega}=\omega \sqrt{\rho /E}$; computed using the PS method are presented in Table 2. It is observed that the proposed method requires less number of grid points to obtain a relative error of the order of 10^{5} in the computation of the first six nondimensional frequency values of a nonuniform rod with polynomial variation of cross section area.
As a second example we examine the convergence of the PS method by considering the free axial vibration of a tapered fixedfree bar. The area of crosssection $A\left(x\right)$ and mass density are assumed to vary linearly i.e. $A\left(x\right)=2{A}_{0}x$ and $m\left(x\right)=\rho \left(x\right)A\left(x\right)=2{m}_{0}x$ where ${A}_{0}$ is the characteristic area and ${m}_{0}$ the characteristic mass. The computations are carried out for a unit length rod. The exact first two nondimensional frequency values given in [11] are taken as basis values and the relative error of the PS method with $N$ varying from 6 to 9 are presented in Table 3. It is observed that the present method achieves a relative error of order 10^{6} with fewer grid points.
Fig. 1. A Schematic view of typical inhomogeneous rods
a) FixedFixed nonuniform exponential rod
b) FixedFree nonuniform exponential rod
c) FixedFree nonuniform sinusoidal rod
d) Side view of axially graded fixedfree bar
Table 2. Convergence study of nonuniform fixed free rods with $A\left(x\right)={A}_{0}{\left(1+2x\right)}^{2}$
Mode

Non dimensional frequency values
Abrate [8]

Relative errors


$N=$ 10

$N=$ 12

$N=$ 14

$N=$ 16


1

0.967403

3.976E05

3.7 E06

6.512 E07

4.031 E07

2

4.567452

3.027 E06

1.860 E07

4.816 E08

3.721 E08

3

7.768373

1.888 E05

4.003 E07

5.535 E08

4.427 E08

4

10.934682

6.278 E04

3.47 E05

1.415 E06

9.145 E09

5

14.089887

2.545 E03

2.346 E05

1.675 E05

8.928 E07

6

17.240109

1.525E02

3.22 E04

3.22 E04

2.700 E05

Table 3. Convergence study of tapered fixed free rod with $A\left(x\right)={2A}_{0}x$ and $m\left(x\right)=2{m}_{0}x$
Mode

Non dimensional frequency values
Zang and Bert [11]

Relative errors


$N=$ 6

$N=$ 7

$N=$ 8

$N=$ 9


1

2.4048

8.316E05

8.316E06

8.316E06

8.316E06

2

5.5201

1.105E04

3.623 E06

3.623 E06

3.623 E06

We further study the convergence of the frequency values obtained for fixedfixed and fixedfree nonuniform rods with crosssection area given by$A\left(x\right)={x}^{0.5}\mathrm{e}\mathrm{x}\mathrm{p}(0.5{x}^{2})$. We examine our results with the nondimensional frequency values presented in [3] as basis values. Using the four digit DSC results that were computed in [3] with 500 grid points for a unit length rod, the relative error of the PS method for fixedfixed and fixedfree rods with $N$ taking values $N=$ 20, 22, 25 and 28 is presented in Table 4. The relative errors of the nondimensional frequency parameter given by $\mathrm{\Omega}=\omega \sqrt{\rho /E}$ for the first 13 modes are given in the table. It is observed that precision of the order of 10^{5} is obtained for all the 13 modes with $N=$ 28 (29 collocation points).
4.2. Comparison with GFEM
In this example, the longitudinal free vibration of a fixedfixed nonuniform rod with area variation given by $A\left(x\right)={A}_{0}{\left(x+1\right)}^{4}$ where ${A}_{0}$ is a reference crosssection area is analyzed and the nondimensional frequencies obtained using PS method are compared with the corresponding results obtained using GFEM method.
Table 4. Convergence study of nonuniform rod with $A\left(x\right)={x}^{0.5}\mathrm{e}\mathrm{x}\mathrm{p}(0.5{x}^{2})$
Boundary condition

Mode

Shokrollahi and
Nejad DSC [3]
$N=$ 500

Relative errors


$N=$ 25

$N=$ 20

$N=$ 22

$N=$ 28


FixedFixed

1

3.4662

2.452 E05

4.298 E05

3.346 E05

1.875 E05

2

6.6399

1.506 E05

3.991 E05

2.725 E05

7.379 E06


3

9.7930

2.460 E05

5.483 E05

3.941 E05

1.552 E05


4

12.9405

3.013 E05

6.460 E05

4.706 E05

1.962 E05


5

16.0857

3.577 E05

7.397 E05

5.427 E05

2.374 E05


6

19.2297

3.879 E05

8.066 E05

5.938 E05

2.605 E05


7

22.3730

4.116 E05

8.671 E05

6.351 E05

2.748 E05


8

25.5158

4.115 E05

8.900 E05

6.454 E05

2.621 E05


9

28.6584

4.428 E05

1.433 E04

7.048 E05

2.875 E05


10

31.8008

4.767 E05

4.683 E04

5.330 E05

3.116 E05


11

34.9430

4.538 E05

4.991 E03

4.781 E04

3.196 E05


12

38.0851

1.016 E04

1.619 E02

2.423 E03

3.313 E05


13

41.2272

3.379 E04

2.320 E02

1.234 E02

4.334 E05


FixedFree

1

2.1954

3.006 E05

2.960 E05

2.505 E05

1.776 E05

2

5.2032

2.229 E05

5.169 E05

3.939 E05

2.037 E05


3

8.3081

2.864 E05

5.067 E05

3.755 E05

1.709 E05


4

11.4328

2.212 E05

5.886 E05

4.163 E05

1.495 E05


5

14.5648

3.199 E05

6.495 E05

4.689 E05

1.881 E05


6

17.7002

3.581 E05

7.926 E05

5.819 E05

2.547 E05


7

20.8374

3.978 E05

7.976 E05

5.907 E05

2.495 E05


8

23.9757

3.870 E05

7.741 E05

6.460 E05

2.594 E05


9

27.1148

4.329 E05

1.339 E04

5.934 E05

2.714 E05


10

30.2544

4.657 E05

5.397 E04

1.979 E05

3.001 E05


11

33.3944

6.444 E05

4.309 E04

1.366 E04

3.129 E05


12

36.5346

1.083 E05

1.925 E03

1.518 E03

2.923 E05


13

39.6750

1.698 E04

7.268 E03

6.095 E04

4.398 E05

Table 5. Comparison of nondimensional frequencies of fixedfixed nonuniform rods
Variation in area

Mode

Kumar and Sujith [9]

Adaptive GFEM Arndt et al. [17]

PS method $N=$ 16

Polynomial
$A\left(x\right)={A}_{0}{\left(x+1\right)}^{4}$

1

3.286007

3.286007

3.286007

2

6.360678

6.360678

6.360678


3

9.477196

9.477196

9.477196


4

12.605890

12.605890

12.605890

The GFEM method is an iterative approach whose main goal is to increase the accuracy of eigenvalues related to a chosen vibration mode. In the method [17] each tangent frequency was obtained by different iterative analysis. The results presented in [17] brought out the narrow precision of GFEM than the cversion of composite element method and the $h$version of FEM in free longitudinal vibration analysis of uniform and nonuniform straight bars for the same degree of freedom. For the considered example, the results of the PS method have been obtained using $N=$ 16 (17 collocation points). Table 5 presents the first four nondimensional eigenvalues $\left({\omega}_{i}\sqrt{\rho /E}\right)$ obtained by these methods. The results show that the PS method which is easier and simple to implement achieves the same accuracy as that of the adaptive GFEM with relatively few grid points.
4.3. Rods with sinusoidal variation of crosssection area
A numerical study of the longitudinal vibrations of nonuniform rods with area variations of the form $A\left(x\right)={A}_{0}{\mathrm{s}\mathrm{i}\mathrm{n}}^{n}\left(x+1\right)$ is carried out. The nondimensional eigenvalues are computed with$N=$ 29 (i.e. 30 collocation points) for various parameter ($n$, $a$, $b$) values under different boundary conditions and the lowest six eigenvalues for each end conditions are listed in the tables. The nondimensional frequencies of fixedfixed and fixedfree nonuniform rods with variation in area given by $A\left(x\right)={A}_{0}{\mathrm{s}\mathrm{i}\mathrm{n}}^{n}\left(ax+b\right)$, $a=\pi 2b$, $b=$ 1 for $n=$ 1, 2, 3, 4 is computed. The computations have been carried out with $N=$ 29 (30 collocation points) to obtain a precision of 6 digits. The results obtained are given in Tables 6 and 7 and are found to be in good agreement with the exact results obtained by [13].
Table 6. Nondimensional natural frequencies of fixedfixed rods with $A\left(x\right)={A}_{0}{\mathrm{s}\mathrm{i}\mathrm{n}}^{n}\left(ax+b\right)$, $a=\pi 2b$, $b=$ 1
$n=$ 1

$n=$ 2

$n=$ 3

$n=$ 4


Mode

Yardimoglu
and Aydin [13]

PS method

Yardimoglu
and Aydin [13]

PS method

Yardimoglu
and Aydin [13]

PS method

Yardimoglu
and Aydin [13]

PS method

1

3.033658

3.0336576

2.926836

2.9268362

2.821246

2.8212460

2.717003

2.7170029

2

6.228475

6.2284746

6.178607

6.1786069

6.133696

6.1336963

6.093840

6.0938397

3

9.388171

9.3881713

9.355384

9.3553837

9.326456

9.3264558

9.301424

9.3014242

4

12.538877

12.5388771

12.514409

12.5144091

12.492985

12.4929848

12.474621

12.4746212

5

15.685954

15.6859536

15.666425

15.6664251

15.649387

15.6493872

15.634849

15.6348492

6

18.831208

18.8312077

18.814955

18.8149548

18.800803

18.8008028

18.788757

18.7887572

Table 7. Nondimensional natural frequencies of clampedfree (fixedfree) rods with
$A\left(x\right)={A}_{0}{\mathrm{s}\mathrm{i}\mathrm{n}}^{n}\left(ax+b\right)$, $a=\pi 2b$, $b=$ 1


$n=$ 1

$n=$ 2

$n=$ 3

$n=$ 4


Mode

Yardimoglu and Aydin
[13]

PS method

Yardimoglu and Aydin [13]

PS method

Yardimoglu and Aydin [13]

PS method

Yardimoglu and Aydin [13]

PS method

1

1.568123

1.5681231301

1.560155

1.5601546708

1.547041

1.5470412314

1.529023

1.5290233495

2

4.715830

4.7158295684

4.726102

4.7261023944

4.743064

4.7430637298

4.766484

4.7664838791

3

7.856372

7.8563718913

7.863537

7.8635367860

7.875459

7.8754586693

7.892108

7.8921080766

4

10.997350

10.9973504866

11.002678

11.0026777710

11.011552

11.0115521944

11.023967

11.0239671552

5

14.138571

14.1385710137

14.142783

14.1427828065

14.149801

14.1498010423

14.159624

14.1596235881

6

17.279918

17.2799178393

17.283392

17.2833923984

17.289183

17.2891827469

17.297288

17.2972880091

4.4. Rods with exponential variation of crosssection area
In this section, the variation in the natural frequencies of rod with exponential area variation of the forms $A\left(x\right)=K{x}^{n}\mathrm{e}\mathrm{x}\mathrm{p}\left(b{x}^{2}\right)$ and $A\left(x\right)=K{x}^{n}\mathrm{e}\mathrm{x}\mathrm{p}\left(bx\right)$ are analyzed. The length of the rod is considered to be one unit with ${l}_{1}=$ 0.1 units and ${l}_{2}=$ 1.1 units as in [12]. The fundamental frequencies for fixedfixed and fixedfree rods are computed using PS method for $n=$ –2.5, –2.0, –1.5, –0.5, 0.5, 1.0, 1.5, 2.0, 2.5 and $b=$ –3, –1, 1 and 3 in the first area variation. A comparison of the values obtained is carried out with the corresponding the exact values in [12]. The frequency values with 6 significant digits for the three end conditions are given in Tables 8, 9 and have been obtained using $N=$ 29. The results bring out the accuracy of the method. Now, consider a fixedfixed nonuniform rod with area variation given by $A\left(x\right)=K{x}^{n}\mathrm{e}\mathrm{x}\mathrm{p}\left(bx\right)$ The natural frequencies $\left(\mathrm{\Omega}\right)$ for different values of the parameters are given in Table 10. The fundamental, first overtone and second overtone frequency values obtained using the PS method are presented in the tables for $n=$ –2.5, –1.5, –0.5, 0.5, 1.5, 2.5 and $b=$ –3, –1, 1 and 3. These values are presented along with the corresponding exact values given in [12]. Though exact values are available for 3 significant digits, the approximate values are given for 6 significant digits for future comparison. It is observed from the results that the proposed PS formulation achieves good accuracy/convergence with less computational effort.
Table 8. Fundamental frequency values for fixedfixed rods with $A\left(x\right)=K{x}^{n}\mathrm{e}\mathrm{x}\mathrm{p}\left(b{x}^{2}\right)$
$n$

$b$


–3

–1

1

3


Raj and
Sujith [12]

PS method

Raj and
Sujith [12]

PS method

Raj and
Sujith [12]

PS method

Raj and
Sujith [12]

PS method


–2.5

5.286

5.286487

4.608

4.607728

4.270

4.269796

4.353

4.352809

–2.0

4.885

4.884997

4.280

4.278711

4.038

4.038238

4.226

4.226488

–1.5

4.471

4.471088

3.949

3.948826

3.820

3.820109

4.122

4.121969

–0.5

3.622

3.622149

3.317

3.316916

3.464

3.464380

4.015

4.014968

0.0

3.206

3.205804

3.043

3.043136

3.356

3.355694

4.034

4.034498

0.5

2.817

2.816767

2.825

2.825281

3.314

3.313942

4.115

4.115115

1.0

2.479

2.479202

2.686

2.686375

3.349

3.349120

4.260

4.259864

1.5

2.221

2.221301

2.642

2.642387

3.462

3.461533

4.465

4.464770

2.0

2.068

2.068134

2.695

2.694565

3.642

3.641521

4.720

4.719870

2.5

2.030

2.029770

2.829

2.828769

3.873

3.873233

5.012

5.011982

3.0

2.094

2.094091

3.023

3.022737

4.140

4.139679

5.328

5.327778

Table 9. Fundamental frequency values for fixedfree rods with $A\left(x\right)=K{x}^{n}\mathrm{e}\mathrm{x}\mathrm{p}\left(b{x}^{2}\right)$
$n$

$\mathrm{b}$


–3

–1

1

3


Raj and Sujith [12]

PS method

Raj and Sujith [12]

PS method

Raj and Sujith [12]

PS method

Raj and Sujith [12]

PS method


–2.5

4.884

4.883958

3.738

3.737838

2.638

2.637833

1.674

1.674235

–2.0

4.494

4.494413

3.399

3.398900

2.350

2.350311

1.447

1.446866

–1.5

4.089

4.088940

3.051

3.050617

2.061

2.060792

1.226

1.225409

–0.5

3.233

3.233094

2.330

2.330227

1.485

1.484599

0.812

0.812405

0.0

2.791

2.790891

1.966

1.966070

1.207

1.207392

0.630

0.629796

0.5

2.350

2.350355

1.610

1.609937

0.948

0.947727

0.470

0.470061

1.0

1.924

1.923852

1.274

1.273623

0.715

0.715118

0.338

0.337307

1.5

1.525

1.525415

0.970

0.970008

0.518

0.517865

0.233

0.233024

2.0

1.169

1.168590

0.710

0.710121

0.359

0.360406

0.156

0.155565

2.5

0.864

0.863907

0.500

0.500186

0.242

0.242026

0.101

0.100883

3.0

0.617

0.616690

0.341

0.340130

0.158

0.157712

0.064

0.063935

4.5. Functionally graded tapered axial bar
In the first example, we consider a tapered bar with a rectangular crosssection whose breath taper ratio is ${c}_{b}\text{,}$ height taper ratio is ${c}_{h}$ and whose crosssection is given by $A\left(x\right)={A}_{0}\left(1{c}_{h}x\right)(1{c}_{b}x)\text{.}$ The modulus of elasticity and mass density vary as $E\left(x\right)={E}_{0}\left(1+x\right)$ and $\rho \left(x\right)={\rho}_{0}(1+x+{x}^{2})$ respectively. For such an FG axial bar, Shahba and Rajasekharan [20] computed the nondimensional frequencies using DQEL and DTEM methods. Both the methods are known to considerably improve the convergence rate of conventional Differential Transform Method (DTM). PSM is used in the present work to compute the nondimensional longitudinal frequencies given by ${\mu}_{i}=\omega \sqrt{{\rho}_{0}/{E}_{0}}$, ($i=\mathrm{1,2},3$) with $N=$ 10 (11 collocation point) under FixedFree and FixedFixed boundary conditions. The first three frequency values computed using the PSM method are compared with those obtained using DQEL/DTEM methods in Tables 11, 12. It is observed that the frequencies are significantly dependent on the crosssection area which is in turn dependent on both the height and breadth taper ratios. The accuracy of the proposed method is evident from the results presented in the Tables 11, 12. The ease of implementation is the added advantage.
Table 10. Fundamental, first and second overtone frequency values for fixedfixed rods with $A\left(x\right)=K{x}^{n}\mathrm{e}\mathrm{x}\mathrm{p}\left(bx\right)$
Frequency

$\mathrm{n}$

$\mathrm{b}$


–3

–1

1

3


Raj and Sujith
[12]

PS
method

Raj and Sujith
[12]

PS
method

Raj and Sujith
[12]

PS
method

Raj and Sujith
[12]

PS
method


Fundamental

–2.5

5.238

5.238527

4.637

4.637222

4.181

4.181430

3.921

3.920829

–1.5

4.551

4.551209

4.023

4.023155

3.690

3.689657

3.605

3.604571


–0.5

3.835

3.835153

3.436

3.435609

3.300

3.300225

3.460

3.460119


0.5

3.149

3.149215

2.979

2.978935

3.134

3.134029

3.572

3.572401


1.5

2.645

2.644851

2.814

2.813816

3.280

3.280556

3.941

3.941452


2.5

2.509

2.509226

3.008

3.007659

3.689

3.688720

4.473

4.472545


First
overtone

–2.5

8.014

8.013470

7.570

7.569653

7.234

7.234170

7.023

7.022754

–1.5

7.335

7.335764

6.980

6.980137

6.754

6.753894

6.670

6.670355


–0.5

6.720

6.719940

6.488

6.488146

6.406

6.405740

6.478

6.478436


0.5

6.245

6.244882

6.170

6.170228

6.256

6.256576

6.498

6.497498


1.5

5.982

5.981634

6.083

6.082643

6.342

6.341725

6.740

6.740350


2.5

5.965

5.964897

6.237

6.237472

6.650

6.649665

7.176

7.176343


Second overtone

–2.5

10.858

10.859154

10.511

10.510870

10.248

10.247762

10.077

10.076690

–1.5

10.249

10.248726

9.985

9.984917

9.816

9.816274

9.748

9.747800


–0.5

9.743

9.742691

9.581

9.581170

9.523

9.522504

9.568

9.568586


0.5

9.386

9.385647

9.339

9.338701

9.398

9.398571

9.563

9.563248


1.5

9.205

9.205052

9.278

9.278490

9.458

9.458103

9.738

9.737949


2.5

9.211

9.211393

9.404

9.404156

9.697

9.697506

10.080

10.082356

Table 11. Nondimensional frequencies of a fixedfree axially FG bar
${C}_{h}$

${C}_{b}$

Shahba and
Rajasekaran [20]
${\mu}_{1}$ DQEL/DTEM

PS method

Shahba and
Rajasekaran [20]
${\mu}_{2}$ DQEL/DTEM

PS method

Shahba and
Rajasekaran [20]
${\mu}_{3}$ DQEL/DTEM

PS method

0.2

0.2

1.3119

1.311936

4.2841

4.284133

7.1821

7.181803

0.4

1.3928

1.392789

4.3090

4.309044

7.1970

7.196715


0.6

1.5059

1.505925

4.3559

4.355943

7.2260

7.225773


0.8

1.6818

1.681840

4.4726

4.472646

7.3068

7.306703


0.4

0.4

1.4759

1.475871

4.3377

4.337722

7.2143

7.214022

0.6

1.5917

1.591695

4.3897

4.389690

7.2466

7.246450


0.8

1.7706

1.770668

4.5138

4.513827

7.3329

7.332918


0.6

0.6

1.7104

1.710443

4.4487

4.448671

7.2839

7.283791

0.8

1.8918

1.891820

4.5832

4.583282

7.3787

7.378728


0.8

0.8

2.0723

2.072303

4.7328

4.732920

7.4888

7.488952

In the second example we consider a functionally graded tapered axial bar with $A\left(x\right)={A}_{0}\left(1x\right)$; $E\left(x\right)={E}_{0}{e}^{x}$ and $\rho \left(x\right)={\rho}_{0}{e}^{x}$ where $c$ is the taper ratio. For such an FG axial bar Shahba et al [21] computed the nondimensional frequencies ${\mu}_{i}=\omega \sqrt{{\rho}_{0}/{E}_{0}}$, ($i=\mathrm{1,2},3$) using Finite element method by introducing the concept of basic displacement functions. The pseudospectral method is used in the present work to compute the first three nondimensional frequencies of the axial bar with $N=$ 16 under fixedfixed, fixedfree boundary conditions. The results obtained using the present method are compared with those presented in [21] in Table 13. It is observed from the table that the results obtained using PSM is slightly lower than that of [21]. The results presented in [21] were calculated utilizing 20 elements to model the bar for a taper ratio of $c=$ 0.1 and higher number of elements for other taper ratios. Moreover, it is observed from literature [21], that the stiffness method generally provides results that are higher than the exact ones. We therefore, feel that the results obtained here are of high precision with fewer collocation points.
Table 12. Nondimensional frequencies of a fixedfixed axially FG bar
${C}_{h}$

${C}_{b}$

Shahba and
Rajasekaran [20]
${\mu}_{1}$ DQEL/DTEM

PS method

Shahba and
Rajasekaran [20]
${\mu}_{2}$ DQEL/DTEM

PS method

Shahba and
Rajasekaran [20]
${\mu}_{3}$ DQEL/DTEM

PS method

0.2

0.2

2.8539

2.853926

5.7515

5.751501

8.6378

8.637841

0.4

2.8369

2.836936

5.7430

5.742966

8.6321

8.632147


0.6

2.8042

2.804223

5.7260

5.726023

8.6207

8.620747


0.8

2.7311

2.731119

5.6829

5.682900

8.5903

8.590337


0.4

0.4

2.8260

2.825973

5.7375

5.737498

8.6284

8.628504

0.6

2.8016

2.801561

5.7249

5.724929

8.6200

8.620056


0.8

2.7415

2.741519

5.6892

5.689170

8.5947

8.594748


0.6

0.6

2.7886

2.788644

5.7188

5.718775

8.6160

8.615999

0.8

2.7468

2.746813

5.6942

5.694204

8.5986

8.598631


0.8

0.8

2.7340

2.734041

5.6901

5.690056

8.5965

8.596521

Table 13. Nondimensional frequencies of a FG tapered axial bar
Taper ratio ($c$)

FixedFixed

FixedFree


Shahba et al.
[21] ${\mu}_{i}$

PS Method
($N=$ 16)

Shahba et al.
[21] ${\mu}_{i}$

PS method
($N=$ 16)


0.1

3.17567

3.172409

1.2988

1.2985

6.3247

6.298648

4.6478

4.637424


9.5228

9.435093

7.8592

7.809505


0.3

3.1514

3.148153

1.3722

1.371958

6.3123

6.286365

4.6656

4.655118


9.5144

9.426885

7.8698

7.819942


0.5

3.1120

3.108831

1.4710

1.470676

6.2916

6.265918

4.6983

4.687528


9.5005

9.413135

7.8899

7.839570


0.7

2.9780

2.975221

1.7168

1.716251

6.2113

6.186568

4.8486

4.836778


9.4427

9.357079

7.9958

7.9433464

5. Conclusions
The main contribution of the present study consists in applying a pseudospectral formulation for solving the governing differential equation of motion for tapered functionally graded axial bars. The method utilizes a Chebyshev polynomialtocosine change of variable that simplifies the computer implementation and achieves good precision. Numerical experiments that include variation in geometrical properties (area of crosssection) and/or material properties (mass density, modulus of elasticity) have been considered and the results obtained with less computational effort exhibits good accuracy and flexibility for longitudinal vibration analysis of tapered axial bars.
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