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Abstract

The free transverse vibrations of two-dimensional functionally graded double Euler–Bernoulli beam system connected through a variable Winkler elastic layer are presented. The Modulus of elasticity and the density of the material of the beams are assumed to vary along the thickness and the length of the beams according to power-law and exponential functions, respectively. The governing differential equations of motion are established by the means of Hamilton’s principle. The Chebyshev Spectral Collocation Method (CSCM) is used to calculate the natural frequencies of the two-dimensional functionally graded (2D-FG) double beams. The effects of several parameters such as the height ratio of the beams, the stiffness of the coupling layer, the axial and transverse functionally graded indexes, and the boundary conditions on the natural frequencies of the 2D-FG double beams have been investigated. The frequencies obtained from the CSCM have been validated by comparing them with those available in previous literature.

Keywords

Free vibration analysis bi-directional functionally graded material spectral collocation eigenvalue problem

Introduction

Due to the rapid progress in the fields of mechanical, marine, civil, and aerospace engineering, innovative and unique structures have been aroused, and among these structures are the double-beam systems. Double-beam systems are used to model several applications and structures such as composite and sandwich beams, double-walled carbon nanotubes, vibration absorbers, double-beam cranes, pipelines, and railway tracks lying on elastic/viscoelastic foundations.¹ Double-beam systems usually consist of two parallel beams continuously connected through elastic linear/nonlinear springs. In order to create such structures with high performance and efficiency, and to further extend limits of applicability and reliability of the suggested structures, it is crucial to manufacture them from special materials with superior properties. It is known that functionally graded materials (FGMs) are special class of advanced materials that are characterized by their unique properties such as lower density, higher toughness, designability, greater thermal resistance, lower stress concentration, smaller interface problems, and higher corrosion resistance.² FGMs’ powerful features are due to the existence of two or more materials that are blended to get continuously changed properties along the length, thickness, or the width of the structure. Several works were devoted to examine the behavior of FG structures. For example, Shariati et al.³ studied the stability of moving axially functionally graded (AFG) viscoelastic nanobeams. The Laplace transform and Galerkin approach were used to determine the natural frequencies and the flutter instability boundaries. The nonlocal elasticity theory was utilized to take into account the small-scale effect. In another research, Shariati et al.⁴ presented the stability behavior of AFG moving Rayleigh and Euler–Bernoulli beams. Closed form solutions were obtained for the critical velocities, and the stability characteristics for beams with different material distributions were discussed. Hieu et al.⁵ utilized the nonlocal strain gradient theory in conjunction with the Galerkin and Hamiltonian approaches to carry out the nonlinear vibrations of an electrostatically actuated FG microbeam subjected to an axial magnetic field. It was observed that the FG index, the non-local and length scale parameters, the applied voltage, and the magnetic force have a noticeable influence on the nonlinear frequencies of the microbeam. Ton-That 6 carried out the nonlinear vibrations of stiffened functionally graded plates. By the means of Hamilton’s principle, the C0 third-order shear deformation and the Von Karman theories were used to derive the governing equations of motion. The finite element and the Newton–Raphson methods were applied to compute the natural frequencies.

In some advanced and smart engineering applications and structures, the distributions of the stress, temperature, electric, and magnetic fields can alter in different directions; thus, the 1D FGMs are not adequate. Hence, there is a necessity to consider the multi-directional FGMs whose properties are customized and varied in two or three directions to obtain materials with optimized properties.⁷

Mirzabeigy el al.⁸ investigated the natural vibrations of double Euler–Bernoulli beam system joined through variable Winkler elastic translational springs. The edges were assumed to be elastically restrained against translation and rotation, and the differential transform method was used to obtain the natural frequencies and the mode shapes of the double beam system. The effects of the height ratio of the beams, the boundary conditions, and the variation type of the stiffness of the connecting layer on the behavior of the system were examined. Li et al.⁹ presented a state-space approach to calculate the dynamic response, mode shapes, and the frequencies of double Euler–Bernoulli beams with an elastic/viscoelastic interlayer between them. In another article, Kim et al.¹⁰ carried out the natural vibration behavior of functionally graded double beam-system (FGDBS) joined by a uniform layer. Hamilton’s principle was used to obtain the coupled governing equations of motion, and the Haar wavelet series and their integral were utilized to calculate the dimensionless frequencies of the FGDBS with arbitrary boundary conditions. Zhao et al.¹¹ obtained the steady-state forced transverse vibrations of double Timoshenko beams subjected to compressive axial loads. The Laplace transform and the steady-state Green’s functions were adopted with the help of the superposition principle to obtain closed-form solutions and to discuss the dynamic buckling phenomena induced by the axial loads. The impacts of the external frequency, shearing effect, and the height-to-length ratio were examined.

Deng et al.¹² used the dynamic stiffness method to find the frequencies and the buckling loads of double FG Timoshenko beams on Winkler–Pasternak foundation. Hamilton’s principle was utilized to obtain the governing equations of motion, and the Wittrick-William algorithm was applied to solve for the frequencies and the buckling loads. The effects of the gradient parameter, foundation modulus, axial load, stiffness of the elastic layer, and the damping factor on the performance of the double FG beams were investigated. Fourier transformation was used to find the displacements of the double FG beams under moving loads. Gul and Aydogdu¹³ reported the natural vibrations and buckling of double-walled carbon nanotubes embedded in an elastic medium. Euler–Bernoulli beam theory was used to model the double-walled carbon nanotubes, and the Doublet Mechanics was considered to relate the micro and macro stresses. The governing equations were obtained by the means of Hamilton’s principle, and the Taylor series expansion was utilized to define the increment of several parameters that were considered in the elastic deformation of the double beams. It was observed that in some cases, the double beams move noncoaxially, which will affect the physical properties of the carbon nanotubes. Su et al.¹⁴ analyzed the axial-bending free and forced vibrations of a double-Timoshenko beam system joined by discrete elastic connections. It was assumed that the lower beam is mass eccentric, and the spectral element method was incorporated to get the coupled mode shapes, the axial/transverse responses of the system under longitudinal and flexural excitations, and the influence of the variation in the axial and transverse stiffness on the dynamical characteristics of the double beam system.

On the other hand, Li et al.¹⁵ carried out the nonlinear bending characteristics of two-dimensionally functionally graded (2D-FG) Euler–Bernoulli beam where the mid-plane stretching was taken into consideration. It was assumed that the modulus of elasticity varies along the axial direction via an exponential function, whereas it is graded along the beam’s thickness according to a power-law function. The force and the material compositions were considered and the generalized differential quadrature method (GDQM) was applied to determine the linearized and nonlinearized displacements of the 2D-FG beams.

Shafiei et al.¹⁶ presented the free vibrations of 2D-FG micro and nano Timoshenko beams made of porous materials with properties that alter via a power-law along the length and thickness of the beam. Eringen’s nonlocal elasticity and the modified couple stress theories were utilized, and the GDQM was used to calculate the frequencies of the beams with different boundary conditions. A parametric study was carried out to demonstrate the effects of the nonlocal parameter, small-scale factor, length-to-thickness ratio, the FG power indexes, the boundary conditions, and the porosity volume fraction on the behavior of the micro and nano beams. Nejad and Hadi¹⁷ studied the natural vibration behavior of 2D-FG nano Euler–Bernoulli beams. Hamilton’s principle and Eringen’s nonlocal elasticity theory were adopted to derive the governing equations of motion, and the GDQM was applied to obtain the natural frequencies of the 2D-FG nano-beams. Moreover, the effects of the scale parameter and the inhomogeneity constant on the dynamical response of the nano-beams were discussed.

Mohammadian¹⁸ proposed a cubic-quintic model to carry out the nonlinear vibrations of damped and undamped 2D-FG Euler–Bernoulli beams. The material properties were assumed to vary along the longitudinal and lateral directions according to exponential and power-law functions, respectively. The variational iteration method and the Hamiltonian approach were used to find analytical solutions for the nonlinear frequencies and the beam deflection. It was shown that factors such as the initial amplitude, elastic and mass density ratios, and the FG indices have noticeable influence on the frequencies and the damping behavior of the beams. Shanab and Attia⁷ carried out the bending, buckling, and vibration behaviors of 2D-FG tapered micro and nano Euler–Bernoulli beams with simply supported conditions. The modified couple stress and the Gurtin–Murdoch surface elasticity theories are both employed to take into account the small scale and surface energy effects, and the GDQM is used to calculate the static bending deflections, critical buckling loads, and the fundamental frequencies of 2D-FG nonuniform beams at the micro/nano scales.

Simsek¹⁹ examined the free and forced vibrations of BDFG Timoshenko beam subjected to a moving load. The Lagrange equations were applied to obtain the governing equations of motion, and trial functions were used to express the displacements in polynomial forms. The implicit time integration Newmark-β method was utilized to solve the equations of motion, and the natural frequencies were calculated. The effects of the material gradation, the boundary conditions, aspect ratio, and the moving load velocity on the dynamic behavior of the BDFG beams were discussed. Tang et al.²⁰ presented the nonlinear vibrations of BDFG of Euler–Bernoulli beams. The equations of motion and the boundary conditions were derived by the means of Hamilton's principle, and the GDQM was applied to calculate the vibration modes. The homotopy analysis was utilized to determine the analytical solutions of the time-domain responses. A parametric study was conducted to study the effects of the axial and thickness FG indexes, the length–thickness ratio, and the value of the initial amplitude on the natural vibrations of the BDFG beams. Pavlović et al.²¹ examined the stability of a double nanobeam subjected to stochastic compressive axial forces. The moment Lyapunov exponent and perturbation methods were applied to analyze the stability of the double nanobeam. Other researchers studied several BDFG structures^22-32 and double-beam systems.^33-36

Based on the above discussion, it is noted that no efforts have been dedicated to carry out the free vibrations of bi-directional functionally graded (BDFG) double Euler–Bernoulli beams connected by a variable Winkler elastic layer, as they can represent applications as double-beam cranes, double-beam spectrometers, and double-beam interferometers. Therefore, the aim of this study is to fill this gap in the literature and propose a new approach to investigate the natural vibration analysis of BDFG double and uniform beams joined by linear elastic springs. Hence, the original contributions of this research include the application of the spectral collocation method to study the vibration behavior of double bi-directionally functionally graded (DBDFG) uniform beams, and to propose a convenient method for the vibration analysis of DBDFG beams. The presented approach is comprehensive and can be used to study other uniform and tapered functionally graded structures.

Theory problem formulation

Mathematical model

Figure 1 shows a 2D FG double beam connected by a variable elastic foundation. In the present study, it is assumed that the modulus of elasticity and the density of the material vary along the axial and lateral directions as follows¹⁸

E (x, z) = e^{p x / L} ((E_{c} - E_{m}) {(\frac{2 (z + d) + h}{2 h})}^{n} + E_{m}) = f (x) E (z)

(1)

ρ (x, z) = e^{p x / L} ((ρ_{c} - ρ_{m}) {(\frac{2 (z + d) + h}{2 h})}^{n} + ρ_{m}) = f (x) ρ (z)

(2)where x is the axial direction of the beam, z is the transverse axis taken from the mid-plane of the beam along its thickness, E(x, z) is the modulus of elasticity,

ρ (x, z)

is the density of the material, the subscripts m and c represent the metallic and ceramic rich surfaces, respectively,

n

is the lateral FG index, p is the axial FG index, and d is the distance between the physical and geometric neutral surfaces of each beam and is given as¹⁸

d = \frac{(E_{r} - 1) n h}{2 (2 + n) (E_{r} + n)}, E_{r} = \frac{E_{c}}{E_{m}}

(3)

Figure 1.

The double bi-directional functionally graded Euler–Bernoulli beams connected by a variable Winkler elastic layer.

In the current study, it is assumed that the beams have the same length L and width b (in the out of plane direction), while the heights of the beams may be different. Based on Euler–Bernoulli’s theorem, the normal strain $ϵ_{x x}$ is given as³⁷

ε_{x x} = - z \frac{\partial^{2} \hat{w} (x, \hat{t})}{\partial x^{2}}

(4)where

\hat{w}

is the transverse displacement and

\hat{t}

is the time. The kinetic energy T for the two parallel beams is given as³⁷

T = \frac{1}{2} \int_{0}^{L} (ρ_{1} (x, z) A_{1} {(\frac{\partial^{2} {\hat{w}}_{1}}{\partial t^{2}})}^{2} + ρ_{2} (x, z) A_{2} {(\frac{\partial^{2} {\hat{w}}_{2}}{\partial t^{2}})}^{2}) d x

(5)where A is the cross-sectional area of the beam. The potential energy is given as³⁷

U = \frac{1}{2} \int_{0}^{L} (σ_{1 x x} ε_{1 x x} A_{1} + σ_{2 x x} ε_{2 x x} A_{2} + k (x) {({\hat{w}}_{2} - {\hat{w}}_{1})}^{2}) d x

(6)where k(x) is the Winkler stiffness of the elastic foundation connecting the upper and lower beams. Hamilton’s principle is applied to formulate the governing equation of motion as^37-40

\int_{t_{1}}^{t_{2}} (δ T - δ U) d t = 0

(7)where

δ

is the variation operator. In light of equation (5), the variation of the kinetic energy is expressed as³³

δ T = \int_{0}^{L} (ρ_{1} (x, z) A_{1} \frac{\partial {\hat{w}}_{1}}{\partial t} \frac{\partial δ {\hat{w}}_{1}}{\partial t} + ρ_{2} (x, z) A_{2} \frac{\partial {\hat{w}}_{2}}{\partial t} \frac{\partial δ {\hat{w}}_{2}}{\partial t}) d x

(8)

Similarly, the variation of the potential energy is given as³⁷

δ U = \int_{0}^{L} (σ_{1 x x} δ ε_{1 x x} A_{1} + σ_{2 x x} δ ε_{2 x x} A_{2} + k (x) ({\hat{w}}_{2} - {\hat{w}}_{1}) (δ {\hat{w}}_{2} - δ {\hat{w}}_{1})) d x

(9)

Using equations (7–9), and after some manipulation and simplification, one obtains

\int_{t_{1}}^{t_{2}} \int_{0}^{L} (ρ_{1} (x, z) A_{1} \frac{\partial {\hat{w}}_{1}}{\partial t} \frac{\partial δ {\hat{w}}_{1}}{\partial t} + ρ_{2} (x, z) A_{2} \frac{\partial {\hat{w}}_{2}}{\partial t} \frac{\partial δ {\hat{w}}_{2}}{\partial t} - M_{1} (x, \hat{t}) δ \frac{\partial^{2} {\hat{w}}_{1}}{\partial x^{2}} - M_{2} (x, \hat{t}) δ \frac{\partial^{2} {\hat{w}}_{2}}{\partial x^{2}} + k (x) ({\hat{w}}_{2} - {\hat{w}}_{1}) (δ {\hat{w}}_{2} - δ {\hat{w}}_{1})) d x d t = 0

(10)

The bending moment $M (x, \hat{t})$ is expressed as³⁷

M (x, \hat{t}) = \int_{A} σ_{x x} z d A = - f (x) D_{x x} \frac{\partial^{2} \hat{w}}{\partial x^{2}}

(11)where

D_{x x} = b \int_{\frac{h}{2} - d}^{- \frac{h}{2} - d} z^{2} E (z) d z

(12)

Then, integrating equation (10) by parts and since δw_i is arbitrary, we get the following governing equations of motion as

\frac{\partial^{2} M_{i} (x, \hat{t})}{\partial x^{2}} = k (x) (- 1^{i}) ({\hat{w}}_{2} - {\hat{w}}_{1}) + f (x) ρ A_{i} \frac{\partial^{2} {\hat{w}}_{i}}{\partial {\hat{t}}^{2}}

(13)

Substituting equation (13) in equation (10) yields

D_{x x 1} f^{″} (x) \frac{\partial^{2} {\hat{w}}_{1} (x, \hat{t})}{\partial x^{2}} + 2 D_{x x 1} f^{'} (x) \frac{\partial^{3} {\hat{w}}_{1} (x, \hat{t})}{\partial x^{3}} + D_{x x 1} f (x) \frac{\partial^{4} {\hat{w}}_{1} (x, \hat{t})}{\partial x^{4}} + k (x) ({\hat{w}}_{1} - {\hat{w}}_{2}) + ρ A_{1} f (x) \frac{\partial^{2} {\hat{w}}_{1} (x, \hat{t})}{\partial t^{2}} = 0

(14)

D_{x x 2} f^{″} (x) \frac{\partial^{2} {\hat{w}}_{2} (x, \hat{t})}{\partial x^{2}} + 2 D_{x x 2} f^{'} (x) \frac{\partial^{3} {\hat{w}}_{2} (x, \hat{t})}{\partial x^{3}} + D_{x x 2} f (x) \frac{\partial^{4} {\hat{w}}_{2} (x, \hat{t})}{\partial x^{4}} + k (x) ({\hat{w}}_{2} - {\hat{w}}_{1}) + ρ A_{2} f (x) \frac{\partial^{2} {\hat{w}}_{2} (x, \hat{t})}{\partial t^{2}} = 0

(15)where

ρ A = b \int_{\frac{h}{2} - d}^{- \frac{h}{2} - d} ρ (z) d z

(16)

The boundary conditions are given as:

Simply Supported (SS)

M (x, t) = 0 \Rightarrow - D_{x x} f (x) \frac{\partial^{2} \hat{w} (x, \hat{t})}{\partial x^{2}} = 0 \Rightarrow \frac{\partial^{2} \hat{w} (x, \hat{t})}{\partial x^{2}} = 0

(17a)

\hat{w} (x, t) = 0

(17b)

Clamped (C)

\hat{w} (x, t) = 0

(18a)

\frac{\partial \hat{w} (x, \hat{t})}{\partial x} = 0

(18b)Free (F)

\begin{array}{l} M (x, t) = 0 \Rightarrow - D_{x x} f (x) \frac{\partial^{2} \hat{w} (x, \hat{t})}{\partial x^{2}} = 0 \Rightarrow \frac{\partial^{2} \hat{w} (x, \hat{t})}{\partial x^{2}} = 0 \\ V (x, t) = 0 \Rightarrow \frac{\partial}{\partial x} (- D_{x x} f (x) \frac{\partial^{2} \hat{w} (x, \hat{t})}{\partial x^{2}}) = 0 \Rightarrow - D_{x x} f^{'} (x) \frac{\partial^{2} \hat{w} (x, \hat{t})}{\partial x^{2}} - D_{x x} f (x) \frac{\partial^{3} \hat{w} (x, \hat{t})}{\partial x^{3}} = 0 \end{array}

(19a)

\Rightarrow p \frac{\partial^{2} \hat{w} (x, \hat{t})}{\partial x^{2}} + \frac{\partial^{3} \hat{w} (x, \hat{t})}{\partial x^{3}} = 0

(19b)

In the present study, the variable stiffness of the elastic layer joining the beams is expressed as ⁸

k (x) = k (1 + α x + β x^{2})

(20)where k, α, and β are constants.

For harmonic natural vibration, the transverse displacements are expressed as

{\hat{w}}_{j} (x, t) = w_{j} (x) e^{i ω t}, j = 1,2

(21)where

ω

is the natural frequency in rad/s. For convenience, the following dimensionless parameters are introduced as

X = \frac{x}{L}, W_{n} = \frac{w_{n}}{L}, α^{*} = α L, β^{*} = β L^{2},

(22)

Substituting equations (21) and (22) into equations (14) and (15), and recalling that $f (x) = e^{p x / L}$ , one obtains

\frac{\partial^{4} W_{1}}{\partial X^{4}} + 2 p \frac{\partial^{3} W_{1}}{\partial X^{3}} + p^{2} \frac{\partial^{2} W_{1}}{\partial X^{2}} + \frac{k L^{4}}{D_{x x 1}} (1 + α^{*} X + β^{*} X^{2}) (W_{1} - W_{2}) = \frac{ρ A_{1} L^{4}}{D_{x x 1}} ω^{2} W_{1}

(23)

\frac{\partial^{4} W_{2}}{\partial X^{4}} + 2 p \frac{\partial^{3} W_{2}}{\partial X^{3}} + p^{2} \frac{\partial^{2} W_{2}}{\partial X^{2}} + \frac{k L^{4}}{D_{x x 2}} (1 + α^{*} X + β^{*} X^{2}) (W_{2} - W_{1}) = \frac{ρ A_{2} L^{4}}{D_{x x 2}} ω^{2} W_{2}

(24)

Equations (23) and (24) can be tackled by several methods such as the finite element method,⁶ the GDQM,^15,16 Li-He’s modified homotopy perturbation method,^41,42 and CSCM that will be applied in this article.

Chebyshev spectral collocation method

The Chebyshev collocation points are defined on the interval [-1, 1] as⁴³

x_{j} = \cos (\frac{j π}{N}), j = 0,1, \dots ., N

(25)

The entries of the Chebyshev differentiation matrix, ${[D]}_{N}$ , which is an $(N + 1) x (N + 1)$ matrix, are given as⁴³

\begin{array}{l} {(D_{N})}_{00} = \frac{2 N^{2} + 1}{6}, {(D_{N})}_{N N} = - \frac{2 N^{2} + 1}{6}, {(D_{N})}_{j j} = \frac{- x_{j}}{2 (1 - x_{j}^{2})}, j = 1, \dots, N - 1 \\ {(D_{N})}_{i j} = \frac{c_{i}}{c_{j}} \frac{{(- 1)}^{i + j}}{(x_{i} - x_{j})}, i \neq j, i, j = 0, \dots, N . c_{i} = {\begin{matrix} 2, & i = 0 o r N, \\ 1, & o t h e r w i s e \end{matrix} \end{array}

(26)

The nth derivative of an unknown function is given as $D_{n} = {(D_{N})}^{n}$ . In the current study, the axial direction of the beam (x-axis) is normalized to be in the range of [0, 1]; thus, the entries of $D_{N}$ will be modified. Due to its accuracy, rapid convergence rate, flexibility, and simplicity in utilization, the CSCM has been successfully utilized to carry out the stability and dynamic behavior in several articles.^44,45

Solution procedure

In this section, the CSCM is applied to discretize the governing equations along with the boundary conditions and convert them into a system of algebraic equations. In the present study, the boundary conditions will be used to modify the entries of the Chebyshev collocation differentiation matrices. For instance, in case beam 1 is clamped at both edges, the boundary conditions are expressed as

W_{1} (0) = \frac{\partial W_{1} (0)}{\partial X} = W_{1} (1) = \frac{\partial W_{1} (1)}{\partial X} = 0

(27)

Using the Chebyshev collocation method, these conditions are discretized as

W_{1,1} = 0

\begin{array}{l} D 1_{1,1}^{1} W_{1,1} + D 1_{1,2}^{1} W_{1,2} + D 1_{1, N}^{1} W_{1, N} + D 1_{1, N + 1}^{1} W_{1, N + 1} = - \sum_{k = 3}^{N - 1} D 1_{1, k}^{1} W_{1, k} \\ W_{1, N + 1} = 0 \\ D 1_{N + 1,1}^{1} W_{1,1} + D 1_{N + 1,2}^{1} W_{1,2} + D 1_{N + 1, N}^{1} W_{1, N} + D 1_{N + 1, N + 1}^{1} W_{1, N + 1} = - \sum_{k = 3}^{N - 1} D 1_{N + 1, k}^{1} W_{1, k} \end{array}

(28)where the first subscript used in the displacements refers to the ith beam (beam 1 or beam 2) and the second subscript refers to the jth Chebyshev point along the beam’s span (j = 1, 2, …, N + 1).

From equation (28), the displacements $W_{1,2}$ and $W_{1, N}$ are given as functions of the displacements at the other points in the domain as

W_{1,2} = \frac{1}{D e t} (- D 1_{N + 1, N}^{1} \sum_{k = 3}^{N - 1} D 1_{1, k}^{1} W_{1, k} + D 1_{1, N}^{1} \sum_{k = 3}^{N - 1} D 1_{N + 1, k}^{1} W_{1, k})

(29)

W_{1, N} = \frac{1}{D e t} (D 1_{N + 1,2}^{1} \sum_{k = 3}^{N - 1} D 1_{1, k}^{1} W_{1, k} - D 1_{1,2}^{1} \sum_{k = 3}^{N - 1} D 1_{N + 1, k}^{1} W_{1, k})

(30)where Det is given by

D e t = (D 1_{1,2}^{1} \times D 1_{N + 1, N}^{1}) - (D 1_{1, N}^{1} \times D 1_{N + 1,2}^{1})

Consequently, the Chebyshev collocation differentiation matrices for beam-1 are modified as

{\bar{D n}}^{1} = \sum_{k = 3}^{N - 1} D n_{i, k}^{1} + D n_{i, 2}^{1} \frac{1}{D e t} (- D 1_{N + 1, N}^{1} \sum_{k = 3}^{N - 1} D 1_{1, k}^{1} + D 1_{1, N}^{1} \sum_{k = 3}^{N - 1} D 1_{N + 1, k}^{1}) + D n_{i, N}^{1} \frac{1}{D e t} (D 1_{N + 1,2}^{1} \sum_{k = 3}^{N - 1} D 1_{1, k}^{1} - D 1_{1,2}^{1} \sum_{k = 3}^{N - 1} D 1_{N + 1, k}^{1})

(31)

for i = 3,4, \dots, N - 1

For a beam with simply supported edges, a similar approach is followed. However, each D1 matrix shown in equations (8–12) is replaced with a D2 matrix. For a cantilever beam, the boundary conditions are discretized as:

\begin{array}{l} W_{1,1} = 0 \\ D 1_{1,1} W_{1,1} + D 1_{1,2} W_{1,2} + D 1_{1, N} W_{1, N} + D 1_{1, N + 1} W_{1, N + 1} = - \sum_{k = 3}^{N - 1} D 1_{1, k} W_{1, k} \\ D 2_{N + 1,2} W_{1,2} + D 2_{N + 1, N} W_{1, N} + D 2_{N + 1, N + 1} W_{1, N + 1} = - \sum_{k = 3}^{N - 1} D 2_{N + 1, k} W_{1, k} \\ (D 3_{N + 1,2} + p D 2_{N + 1,2}) W_{1,2} + (D 3_{N + 1, N} + p D 2_{N + 1, N}) W_{1, N} \\ + (D 3_{N + 1, N + 1} + p D 2_{N + 1, N + 1}) W_{1, N + 1} = - \sum_{k = 3}^{N - 1} (D 3_{N + 1, k} + p D 2_{N + 1, k}) W_{1, k} \end{array}

(32)

Equation (32) could be written in matrix vector form as

[\begin{matrix} D 1_{1,2} & D 1_{1, N} & D 1_{1, N + 1} \\ D 2_{N + 1,2} & D 2_{N + 1, N} & D 2_{N + 1, N + 1} \\ Q_{N + 1,2} & Q_{N + 1, N} & Q_{N + 1, N + 1} \end{matrix}] {\begin{matrix} W_{1,2} \\ W_{1, N} \\ W_{1, N + 1} \end{matrix}} = {\begin{matrix} - \sum_{k = 3}^{N - 1} D 1_{1, k} W_{1, k} \\ - \sum_{k = 3}^{N - 1} D 2_{N + 1, k} W_{1, k} \\ - \sum_{k = 3}^{N - 1} Q_{N + 1, k} W_{1, k} \end{matrix}}

(33)where

Q_{N + 1, i} = D 3_{N + 1, i} + p D 2_{N + 1, i},

and

i = 2, 3, \dots, N + 1

Equation (33) can be written as

{\begin{matrix} W_{1,2} \\ W_{1, N} \\ W_{1, N + 1} \end{matrix}} = {[\begin{matrix} D 1_{1,2} & D 1_{1, N} & D 1_{1, N + 1} \\ D 2_{N + 1,2} & D 2_{N + 1, N} & D 2_{N + 1, N + 1} \\ Q_{N + 1,2} & Q_{N + 1, N} & Q_{N + 1, N + 1} \end{matrix}]}^{- 1} {\begin{matrix} - \sum_{k = 3}^{N - 1} D 1_{1, k} W_{1, k} \\ - \sum_{k = 3}^{N - 1} D 2_{N + 1, k} W_{1, k} \\ - \sum_{k = 3}^{N - 1} Q_{N + 1, k} W_{1, k} \end{matrix}}

(34)

The displacements $W_{1,2}$ , $W_{1, N}$ , and $W_{1, N + 1}$ are expressed as functions of the displacements of other points as

W_{2} = - A_{1,1} \sum_{k = 3}^{N - 1} D 1_{1, k} W_{1, k} - A_{1,2} \sum_{k = 3}^{N - 1} D 2_{N + 1, k} W_{1, k} - A_{1,3} \sum_{k = 3}^{N - 1} Q_{N + 1, k} W_{1, k},

(35)

W_{N} = - A_{2,1} \sum_{k = 3}^{N - 1} D 1_{1, k} W_{1, k} - A_{2,2} \sum_{k = 3}^{N - 1} D 2_{N + 1, k} W_{1, k} - A_{2,3} \sum_{k = 3}^{N - 1} Q_{N + 1, k} W_{1, k},

(36)

W_{N + 1} = - A_{3,1} \sum_{k = 3}^{N - 1} D 1_{1, k} W_{1, k} - A_{3,2} \sum_{k = 3}^{N - 1} D 2_{N + 1, k} W_{1, k} - A_{3,3} \sum_{k = 3}^{N - 1} Q_{N + 1, k} W_{1, k},

(37)where

{[\begin{matrix} D 1_{1,2} & D 1_{1, N} & D 1_{1, N + 1} \\ D 2_{N + 1,2} & D 2_{N + 1, N} & D 2_{N + 1, N + 1} \\ Q_{N + 1,2} & Q_{N + 1, N} & Q_{N + 1, N + 1} \end{matrix}]}^{- 1} = [\begin{matrix} A_{1,1} & A_{1,2} & A_{1,3} \\ A_{2,1} & A_{2,2} & A_{2,3} \\ A_{3,1} & A_{3,2} & A_{3,3} \end{matrix}]

(38)

As a result, each differentiation matrix of order n (Dn) for a clamped-free beam is modified as

\begin{array}{l} \bar{D n} = \sum_{k = 3}^{N - 1} D n_{i, k} - D n_{i, 2} (A_{1,1} \sum_{k = 3}^{N - 1} D 1_{1, k} + A_{1,2} \sum_{k = 3}^{N - 1} D 2_{N + 1, k} + A_{1,3} \sum_{k = 3}^{N - 1} Q_{N + 1, k}) \\ - D n_{i, N} (A_{2,1} \sum_{k = 3}^{N - 1} D 1_{1, k} + A_{2,2} \sum_{k = 3}^{N - 1} D 2_{N + 1, k} + A_{2,3} \sum_{k = 3}^{N - 1} Q_{N + 1, k}) \\ - D n_{i, N + 1} (A_{3,1} \sum_{k = 3}^{N - 1} D 1_{1, k} + A_{3,2} \sum_{k = 3}^{N - 1} D 2_{N + 1, k} + A_{3,3} \sum_{k = 3}^{N - 1} Q_{N + 1, k}) \end{array}

(39)

The equations of motion for DBDFG Euler–Bernoulli beams are expressed using the presented approach as

[\begin{matrix} L H S 1 \\ L H S 2 \end{matrix}] {\begin{matrix} W_{1} \\ W_{2} \end{matrix}} = ω^{2} [\begin{matrix} R H S 1 \\ R H S 2 \end{matrix}] {\begin{matrix} W_{1} \\ W_{2} \end{matrix}}

(40)where

L H S 1 = ([\begin{matrix} 1 & 0 \end{matrix}] \otimes G E 11) + ([\begin{matrix} 0 & 1 \end{matrix}] \otimes G E 12)

(41)

L H S 2 = ([\begin{matrix} 0 & 1 \end{matrix}] \otimes G E 21) + ([\begin{matrix} 1 & 0 \end{matrix}] \otimes G E 22)

(42)

R H S 1 = ([\begin{matrix} 1 & 0 \end{matrix}] \otimes R H 11)

(43)

R H S 2 = ([\begin{matrix} 0 & 1 \end{matrix}] \otimes R H 22)

(44)

G E 11 = {\bar{D 4}}^{1} + (2 m \times {\bar{D 3}}^{1}) + (m^{2} \times {\bar{D 2}}^{1}) + (\frac{k L^{4}}{E I_{1}} \times K)

(45)

G E 12 = - \frac{k L^{4}}{E I_{1}} \times K

(46)

G E 21 = - \frac{k L^{4}}{E I_{2}} \times K

(47)

G E 22 = {\bar{D 4}}^{2} + (2 m \times {\bar{D 3}}^{2}) + (m^{2} \times {\bar{D 2}}^{2}) + (\frac{k L^{4}}{E I_{2}} \times K)

(48)

R H 11 = \frac{ρ A_{1} L^{4}}{E I_{1}} \times I

(49)

R H 22 = \frac{ρ A_{2} L^{4}}{E I_{2}} \times I

(50)where I is an (M-4) X (M-4) identity matrix,

K

is a diagonal (M-4)

\times

(M -4) matrix with the entries

1 + α^{*} x_{i} + β^{*} x_{i}^{2}

, and

{\bar{D n}}^{j}

is the modified Chebyshev collocation differentiation matrix of order n for beam j, and M=N+1. The natural frequencies for the DBDFG beams can be determined by solving the standard eigenvalue problem given in equation (40).

Results and discussion

To illustrate the validity and the effectiveness of the suggested model and the presented CSCM, a comparison study is carried out. As shown in Table 1, the first six transverse frequencies of isotropic Euler–Bernoulli double beams with SS-SS and SS-CF boundary conditions are calculated and compared with those obtained by Mirzabeigy et al. ⁸ The beams are joined by a variable Winkler elastic layer, and it is obvious that the present results agree with Mirzabeigy et al. ⁸ solutions, which verify the accuracy of the present model and the CSCM. The parameters of the prismatic and isotropic parallel Euler–Bernoulli beams are considered as reported in Mirzabeigy et al.⁸

E_{1} = E_{2} = \frac{10^{10} N}{m^{2}}, ρ_{1} = ρ_{2} = 2000 k g / m^{3}, A_{1} = 0.05 m^{2}, I_{1} = 0.0004 m^{4}, L = 10 m

Table 1.

First six frequencies (rad/s) for two parallel prismatic and isotropic Euler–Bernoulli beams with different boundary conditions (η = 1).

BC			$ω_{1}$	$ω_{2}$	$ω_{3}$	$ω_{4}$	$ω_{5}$	$ω_{6}$
SS-SS	Case I	Ref. [8]	19.7392	56.1066	78.9568	99.5873	177.653	188.266
		Present study	19.7392	56.1065	78.9568	99.5875	177.653	188.268
	Case II	Ref. [8]	19.7392	68.4975	78.9568	101.535	177.653	188.668
		Present study	19.7392	68.4975	78.9568	101.535	177.653	188.668
SS-CF	Case I	Ref. [8]	23.9750	55.0501	62.8953	90.9709	131.586	182.987
		Present study	23.9762	55.0491	62.8939	90.9713	131.586	182.989
	Case II	Ref. [8]	22.8319	49.0454	72.7759	90.3464	132.473	183.042
		Present study	22.8320	49.045	72.7759	90.3465	132.474	183.042

As the beams may have different heights, a height ratio that is expressed as $η = h_{2} / h_{1}$ can be used to express the area and the second moment of inertia of beam 2 in terms of those for beam-1 as

A_{2} = b h_{2} = η b h_{1} = η A_{1}

(51)

I_{2} = \frac{1}{12} b h_{2}^{3} = \frac{1}{12} b {(η h_{1})}^{3} = η^{3} \frac{1}{12} b h_{1}^{3} = η^{3} I_{1}

(52)

For the sake of verification, two different cases are considered for the connecting layer as follows ⁸

Case I:

k = 4 \times 10^{5} N / m^{2}, α^{*} = - 3, β^{*} = 3

Case II:

k = 1.5 \times 10^{5} N / m^{2}, α^{*} = 2, β^{*} = - 2

In the current research, the values of the properties for the ceramic and the metal materials used in the DBDFG beams are¹⁸: $E_{c} = 390$ GPa, $ρ_{c} = 3960$ kg/m,³ $E_{m} = 210$ GPa, and $ρ_{m} = 7800$ kg/m.³

In Figure 2, the influence of the height ratio on the first four natural frequencies of a CC-CF double beam with n=1, k $= 10^{5}$ $N / m^{2}$ , $α^{*} = - 3, β^{*} = 3$ at different values of the axial FG index p is presented. As depicted from the figure, $ω_{1}$ decreases as the height ratio $η$ rises. Furthermore, as the axial FG index p increases, $ω_{1}$ slightly decays for $η$ $ϵ$ [0.5, 0.825] and [1.5, 2], whereas $ω_{1}$ marginally rises for $η$ $ϵ$ [0.825, 1.5]. Moreover, $ω_{2}$ decays until $η$ reaches a certain value; then, the second natural frequency grows as $η$ increases; after that, it reaches a steady value. Additionally, the axial FG index p has a softening effect on $ω_{2}$ for $η$ $ϵ$ [0.5, 1.38] and a hardening effect for $η$ $ϵ$ [1.7, 2]. In Figure 2(c), $ω_{3}$ almost remains constant until $η$ reaches a value; afterward, it rises as $η$ grows. The axial FG index p has a hardening effect on $ω_{3}$ as $η$ varies over the range 0.5 to 1.075, whereas p has a softening effect on $ω_{3}$ for $η$ $ϵ$ [1.5, 2]. It is illustrated in Figure 2(d) that the fourth natural frequency linearly increases with $η$ over a specific range; then, it remains constant. Besides, the p index has a softening effect on $ω_{4}$ for $η$ $ϵ$ [0.5, 1.1], and a hardening effect on $ω_{4}$ for $η$ $ϵ$ [1.1, 2].

Figure 2.

Variations of the first four natural frequencies as functions of the height ratio of CC-CF beams with n=1, k $= 10^{5}$ $N / m^{2}$ , $α^{*} = - 3, β^{*} = 3, L = 20 m, h_{1} = 0.2 m$ at different values of the axial FG index p.

The variations of the first four natural frequencies of CC-CF double FG parallel beams (p=1, k $= 10^{5}$ $N / m^{2}$ , $α^{*} = - 3, β^{*} = 3$ ) versus the height taper ratio ( $η$ ) at different values of the lateral FG index n are presented in Figure 3(a)–(d). From these plots, it is noted that $ω_{1}$ and $ω_{3}$ nonlinearly decay and grow, respectively, as $η$ increases. However, $ω_{2}$ declines as $η$ varies over the range 0 to 0.725; afterward, it grows as the height ratio increases. In Figure 3(d), $ω_{4}$ rises as $η$ varies over the range 0 to 1.1; then, it remains constant as $η$ grows from 1.1 to 2.

Figure 3.

The height ratio of beam effects on the first four natural frequencies (CC-CF BC), p=1, k $= 10^{5}$ $N / m^{2}$ , $α^{*} = - 3, β^{*} = 3$ , $L = 20 m, h_{1} = 0.2 m$ at different values of the lateral FG index n.

In Figure 4 (a-d), the effect of the height ratio on the first four natural frequencies of SS-SS DBDFG beams with n=1, k $= 4 \times 10^{5}$ $N / m^{2}$ , $α^{*} = 2, and β^{*} = - 2$ at different values of the axial FG index p is plotted versus the height taper ratio. The notation SS-SS denotes that the lower and the upper beams are both simply supported at x=0 and at x=L. Figure 4(a) and (b) indicate that $ω_{1}$ and $ω_{2}$ rise as the taper ratio grows. As depicted from these two figures, the axial FG index p has a softening effect on $ω_{1}$ and a stiffening influence on $ω_{2}$ . From Figure 3(c), it is noticed that $ω_{3}$ increases for the height ratio η $ϵ$ [0.5, 0.63]; then, it drops as η grows. Additionally, it is observed that the p index has a negligible impact on $ω_{3}$ . As revealed from Figure 4(d), the height ratio has a softening effect on $ω_{4}$ for η $ϵ$ [0.5, 0.64] and [0.71, 1.05], whereas it has a hardening influence on $ω_{4}$ for η $ϵ$ [0.64, 0.71] and [1.05, 2]. Besides, it is observed that $ω_{4}$ marginally increases as the axial FG index p progresses.

Figure 4.

The first four natural frequencies of SS-SS DBDFG beams as functions of the height ratio of beams with n=1, k $= 4 \times 10^{5}$ $N / m^{2}$ , $α^{*} = 2, β^{*} = - 2$ , $L = 20 m, h_{1} = 0.2 m$ at different values of the axial FG index p.

The variation of the first four natural frequencies of CF-CF FG double beam (n=1, k $= 4 \times 10^{5}$ $N / m^{2}$ , $α^{*} = 2,$ and $η = 1.5$ ) versus the $β^{*}$ parameter at different values of the axial FG index p is presented in Figure 5(a)–(d). As expected, the frequencies increase as the $β^{*}$ parameter progresses due to the increase of the stiffness of the elastic layer that is connecting the beams. Furthermore, the axial FG index p has a softening effect on the frequencies, and it is observed that the fundamental natural frequency is more sensitive to the increase in $β^{*}$ when compared to the second, third, and fourth natural frequencies. In Figure 6(a)–(d), the first four natural frequencies of SS-CF FG double beam (p=3, k $= 2 \times 10^{5}$ $N / m^{2}$ , $α^{*} = 3$ , $η = 1.0$ ) are plotted against the $β^{*}$ parameter at different values of the lateral FG index n. The figures reveal that the $β^{*}$ parameter has a hardening effect on the frequencies, whereas the lateral FG index n has a softening effect on these frequencies. It is observed that the fundamental frequency is less sensitive to the increase in $β^{*}$ when compared to the second, third, and fourth natural frequencies.

Figure 5.

Variations of the first four natural frequencies of CC-CF DBDFG beams (n=1, k $= 4 \times 10^{5}$ $N / m^{2}$ , $α^{*} = 2, η = 1.5, L = 20 m, h_{1} = 0.2 m$ ) with $β^{*}$ at different values of the axial FG index p.

Figure 6.

The first four natural frequencies of SS-CF DBDFG beams with p=3, k $= 2 \times 10^{5}$ $N / m^{2}$ , $α^{*} = 3$ , and $η = 1.0$ , $L = 20 m, h_{1} = 0.2 m$ as functions of $β^{*}$ at different values of the lateral FG index n.

The effect of the $α^{*}$ parameter on the first four natural frequencies of DBDFG beams (p=n=1, k $= 4 \times 10^{5}$ $N / m^{2}$ , $β^{*} = 3$ , $η = 1.2$ ) with several boundary conditions is displayed in Figure 7(a)–(d). Figure 7(a) and (b) illustrate that $α^{*}$ has no impact on the fundamental and the second natural frequencies of SS-SS DBDFG beams, whereas these frequencies increase as $α^{*}$ progresses for SS-CC and SS-CF FG DBDFG beams. As observed from Figures 7(c) and (d), the third and fourth natural frequencies noticeably rise as $α^{*}$ increases for SS-SS, SS-CC, and SS-CF DBDFG beams. It is noticed that the third natural frequencies for SS-SS and SS-CF DBDFG beams are almost equal.

Figure 7.

The first four natural frequencies of DBDFG beams with p=n=1, k $= 4 \times 10^{5}$ $N / m^{2}$ , $β^{*} = 3$ , $η = 1.2, L = 20 m, h_{1} = 0.2 m$ versus $α^{*}$ for different boundary conditions.

The impact of the height ratio $η$ on the first four natural frequencies of DBDFG beams with different boundary conditions is illustrated in Figure 8(a)–(d). Depending on the frequency mode and the boundary conditions, several behaviors are found. For instance, $ω_{1}$ increases as $η$ progresses and it is noticed that $ω_{1}$ of the CF-CF DBDFG beams is less sensitive to the change in $η$ when compared to $ω_{1}$ of the SS-SS and the CC-CC DBDFG beams. From Figure 7(b), it is observed that $ω_{1}$ for the CC-CC DBDFG beams drops as $η$ varies over the range of 0.5 to 0.95; then, it rises for $η$ >0.95. On the other hand, $ω_{1}$ for the SS-SS DBDFG beams grows as $η$ varies over the range 0.5 to 0.725; after that, it decays for $η$ >0.725. Additionally, the height ratio has a softening effect on $ω_{1}$ for the CF-CF DBDFG beams. Similar observations can be depicted in Figure 7(c) and Figure 7(d) regarding the effect of $η$ on $ω_{3}$ and $ω_{4}$ .

Figure 8.

The height ratio of beam effects on the first four natural frequencies, n=p=1, k $= 4 \times 10^{5}$ $N / m^{2}$ , $α^{*} = - 3, β^{*} = 3$ , $L = 20 m, h_{1} = 0.2 m$ with different boundary conditions.

The variations of the first four natural frequencies against the axial FG index p for CC-CC, SS-SS, and CF-CF DBDFG beams with n= $η$ =1, k $= 4 \times 10^{5}$ $N / m^{2}$ , $α^{*} = - 3$ , and $β^{*} = 3$ are presented in Figure 9(a)–(d). It is indicated that the index p has a hardening effect on the first four natural frequencies of CC-CC DBDFG beams. On the other hand, the index p has a softening impact on $ω_{1}$ of SS-SS DBDFG beams, and a small influence on $ω_{2}$ , $ω_{3}$ , and $ω_{4}$ of SS-SS DBDFG beams. Moreover, the fundamental and the second natural frequencies of CF-CF DBDFG beams rise when the index p is increased up to p= 0.12; then, they decrease as the index p grows. The index p has almost no impact on the third natural frequency of CF-CF DBDFG beams. In fact, several parameters play a role in determining the values and the characteristics of the natural frequencies. It is worthwhile to point out that the stiffness of the double-beam system depends on the boundary conditions of the beams, the stiffness of the elastic layer connecting the beams, the beams’ height, and the beams’ area moment of inertia, the lateral FG index, and the axial FG index. Hence, in some cases, the trend of the variation of the natural transverse frequencies with respect to several factors may not be monotonic. Besides, it can be concluded from equations (11) and (12) that the area moment of inertia can be enhanced or reduced with rising the value of the axial FG index p, depending on the value of the lateral FG index n.

Figure 9.

The first four natural frequencies of DBDFG beams with different boundary conditions as functions of the axial FG index p (n = $η$ =1, k $= 4 \times 10^{5}$ $N / m^{2}$ , $α^{*} = - 3$ , $β^{*} = 3$ , $L = 20 m, h_{1} = 0.2 m$ ).

The variations of the first four natural frequencies as functions of the axial FG index p at different values of the lateral FG index n for SS-SS FG DBDFG beam with $η$ =1, k $= 5 \times 10^{5}$ $N / m^{2}$ , $α^{*} = 2$ , and $β^{*} = 2$ are displayed in Figure 10(a)–(d). These plotted figures reveal that the natural frequencies decline as the lateral FG index n rises. Besides, it is depicted that the fundamental natural frequency declines as the axial FG index p progresses, whereas the second, third, and fourth natural frequencies increase as the index p grows.

Figure 10.

The variations of the first four natural frequencies of SS-SS DBDFG beams ( $η$ =1, k $= 5 \times 10^{5}$ $N / m^{2}$ , $α^{*} = 2$ , $β^{*} = 2, L = 20 m, h_{1} = 0.2 m$ ) with the axial FG index p at different values of the lateral FG index n.

Figure 11 is devoted to present the first four mode shapes of CC-CC DBDFG beams with $η$ =0.5, $p = n = α = β = 2$ , L=20 m, $h_{1} = 0.2 m$ , k $= 5 \times 10^{5}$ $N / m^{2}$ , where all the modes of the two beams are in phase except for the fourth mode in which the beams become out of phase with each other. The first four mode shapes of SS-SS DBDFG beams with $η$ =2.0, $p = n = 1$ , $α = β = 2$ , L=20 m, $h_{1} = 0.2 m$ , k $= 5 \times 10^{5}$ $N / m^{2}$ are shown in Figure 12 where the third and fourth mode shapes are out of phase.

Figure 11.

The first four mode shapes of CC-CC DBDFG beams with $η$ =0.5, $p = n = α = β = 2$ , L=20 m, $h_{1} = 0.2 m$ , k $= 5 \times 10^{5}$ $N / m^{2}$ .

Figure 12.

The first four mode shapes of SS-SS DBDFG beams with $η$ =2.0, $p = n = 1$ , $α = β = 2$ , L=20 m, $h_{1} = 0.2 m$ , k $= 5 \times 10^{5}$ $N / m^{2}$ .

Conclusion

The free transverse vibrations of the two-dimensional functionally graded double beams connected by variable Winkler-type elastic layer were conducted. It was assumed that the modulus of elasticity and the density of the material vary along the thickness and the axial direction of the beams according to a power-law and exponential distribution functions, respectively. The governing differential equations of motion were established by applying Hamilton’s principle, and the CSCM was utilized to discretize the differential equations and convert them into a set of algebraic equations. The natural transverse frequencies were determined, and the effects of the axial and transverse FG indexes, the height ratio of the beams, the stiffness of the Winkler layer, and the boundary conditions were examined. The results show that increasing the stiffness of the connecting layer has a growing effect on the frequencies, whereas the height ratio and the FG lateral and axial indexes may have softening or hardening impacts on the natural frequencies. The author believes that the findings and the introduced method may be interesting for the researchers working on the analysis of bi-directional FG double beams. For the future work, it is recommended to extend the investigation to include other structures such as bi-directional rods, plates, and shells. Moreover, it is suggested to deal with viscoelastic and nonlinear layers.

Footnotes

Declaration of conflicting interests

The author(s) declared no potential conflicts of interest with respect to the research, authorship, and/or publication of this article.

Funding

The author(s) received no financial support for the research, authorship, and/or publication of this article.

ORCID iD

Ma'en S Sari

Appendix

Nomenclature

References

Shibing

Bingen

. A closed-form analytical solution method for vibration analysis of elastically connected double-beam systems. Compos Structures 2019; 212: 598–608

Chen

Goto

. Functionally graded materials. In: Handbook of advanced ceramics: Materials, applications, process properties; 2003, London, UK: Academic Press, pp. 445–464. DOI: 10.1016/B978-012654640-8/50043-2

Shariati

Jung

Sedighi

, et al. On the vibrations and stability of moving viscoelastic axially functionally graded nanobeams. Materials 2020; 13: 1707. DOI: 10.3390/ma13071707

Shariati

Jung

Sedighi

, et al. Stability and dynamics of viscoelastic moving Rayleigh beams with an asymmetrical distribution of material parameters. Symmetry 2020; 12: 586. DOI: 10.3390/sym12040586

Hieu

Hoa

Duy

, et al. Nonlinear vibration of an electrostatically actuated functionally graded microbeam under longitudinal magnetic field. J Appl Comput Mech 2021; 7(3): 1537–1549

Ton-That

. A new C0 third-order shear deformation theory for the nonlinear free vibration analysis of stiffened functionally graded plates. Facta Universitatis, Ser Mech Eng 2021; 19(2): 285–305

Shanab

Attia

. Semi-analytical solutions for static and dynamic responses of bi-directional functionally graded nonuniform nanobeams with surface energy effect. Eng Comput 2020. DOI: 10.1007/s00366-020-01205-6

Mirzabeigy

Madoliat

Vahabi

. Free vibration analysis of two parallel beams connected together through variable stiffness elastic layer with elastically restrained ends. Adv Struct Eng 2016; 20(3): 275–287

Xiong

Xie

, et al. State-space approach for transverse vibration of double-beam systems. Int J Mech Sci 2021; 189: 105974.

10.

Kim

Han

, et al. Free vibration analysis of functionally graded double-beam system using Haar wavelet discretization method. Eng Sci Technology 2021; 24: 414–427. DOI: 10.1016/j.jestch.2020.07.009

11.

Zhao

Chen

, et al. Forced vibration analysis of Timoshenko double-beam system under compressive axial load by means of Green's functions. J Sound Vibration 2020; 464: 115001

12.

Deng

Chen

Cheng

, et al. Vibration and buckling analysis of double-functionally graded Timoshenko beam system on Winkler-Pasternak elastic foundation. Compos Structures 2017; 160: 152–168

13.

Gul

Aydogdu

. Noncoaxial vibration and buckling analysis of embedded double-walled carbon nanotubes by using doublet mechanics. Composites Part B 2018; 137: 60–73

14.

Lei

Hua

. Axial–bending coupling vibration of mass eccentric double-beam system with discrete elastic connections. J Eng Maritime Environ 2017; 231(2): 555–568

15.

. Nonlinear bending of a two-dimensionally functionally graded beam. Compos Structures 2018; 184: 1049–1061.

16.

Shafiei

Mirjavadi

Afshari

, et al. Vibration of two-dimensional imperfect functionally graded 2D-FG porous nano-/micro-beams. Computer Methods Appl Mech Eng 2017; 322: 615–632

17.

Nejad

Hadi

. Non-local analysis of free vibration of bi-directional functionally graded Euler–Bernoulli nano-beams. Int J Eng Sci 2016; 105: 1–11

18.

Mohammadian

Nonlinear free vibration of damped and undamped bi-directional functionally graded beams using a cubic-quintic nonlinear model. Compos Structures 2012; 255: 112866

19.

Şimşek

Bi-directional functionally graded materials (BDFGs) for free and forced vibration of Timoshenko beams with various boundary conditions. Compos Structures 2015; 133: 968–978

20.

Tang

Yang

. Bi-directional functionally graded beams: asymmetric modes and nonlinear free vibration. Compos B Eng 2019; 156: 319–331.

21.

Pavlović

Janevski

, et al. Dynamic behavior of two elastically connected nanobeams under a white noise process. Facta Universitatis-Series Mech Eng 2020; 18(2): 219–227

22.

Nazmul

Devnath

. Exact analytical solutions for bending of bi-directional functionally graded nanobeams by the nonlocal beam theory using the Laplace transform. Forces Mech 2020; 1: 100002

23.

Zheng

Chen

. Porosity-dependent isogeometric analysis of bi-directional functionally graded plates. Thin-Walled Structures 2020; 156: 106999

24.

Allahkarami

Ghassabzadeh

Tohidi

. Dynamic buckling analysis of bi-directional functionally graded porous truncated conical shell with different boundary conditions. Compos Structures 2020; 252: 112680

25.

Tang

Ding

. Nonlinear vibration analysis of a bi-directional functionally graded beam under hygro-thermal loads. Compos Structures 2019; 225: 111076

26.

Lei

, et al. Postbuckling analysis of bi-directional functionally graded imperfect beams based on a novel third-order shear deformation theory. Compos Structures 2019; 209: 811–829

27.

Esmaeilzadeh

Kadkhodayan

. Dynamic analysis of stiffened bi-directional functionally graded plates with porosities under a moving load by dynamic relaxation method with kinetic damping. Aerospace Sci Technology 2019; 93: 105333

28.

Chen

Zhu

, et al. Nonlinear resonant behaviors of bi-directional functionally graded material microbeams: One-/two-parameter bifurcation analyses. Compos Structures 2019; 223: 110896

29.

Bakhsheshy

Mahbadi

. The effect of multidimensional temperature distribution on the vibrational characteristics of a size-dependent thick bi-directional functionally graded microplate. Noise & Vibration Worldwide 2019; 50(9–11): 267–290

30.

Apalak

Demirbas

. Thermal stress analysis of in-plane two-directional functionally graded plates subjected to in-plane edge heat fluxes. Proc Inst Mech Eng Part L: J Mater Des Appl 2016; 232(8): 693–716

31.

Sahmani

Safaei

. Nonlinear free vibrations of bi-directional functionally graded micro/nano-beams including nonlocal stress and microstructural strain gradient size effects. Thin-Walled Structures 2019; 140: 342–356

32.

Nguyen

Q H

Tran

, et al. Vibration of bi-dimensional functionally graded Timoshenko beams excited by a moving load. Acta Mech 2017; 228: 141–155

33.

Huang

Liu

. Substructural Method for Vibration Analysis of the Elastically Connected Double-Beam System. Adv Struct Eng 2016; 16(2): 365–377

34.

Wang

. Thermal vibration of double-walled carbon nanotubes predicted via double-Euler-beam model and molecular dynamics. Acta Mechanica 2012; 223: 2107–2115

35.

Wang

Geng

Yang

, et al. Dynamics of the double-beam piezo–magneto–elastic nonlinear wind energy harvester exhibiting galloping-based vibration. Nonlinear Dyn 2020; 100: 1963–1983

36.

Hao

Zhai

Chen

. Free vibration of connected double-beam system with general boundary conditions by a modified Fourier–Ritz method. Archive Appl Mech 2018; 88: 741–754

37.

Hashemi

Khaniki

. Dynamic response of multiple nanobeam system under a moving nanoparticle. Alexandria Eng J 2018; 57: 343–356

38.

Wang

. Exact solitary wave solution for fractal shallow water wave model by he’s variational method. Mod Phys Lett B 2022; 36(7): 2150602. DOI: 10.1142/S0217984921506028

39.

Wang

. Solitary wave solution of nonlinear Bogoyavlenskii system by variational analysis method. Int J Mod Phys B 2022; 36: 2250015. DOI: 10.1142/S0217979222500151

40.

Wang

. New variational theory for coupled nonlinear fractal Schrodinger system. Int J Numer Methods Heat Fluid Flow 2022; 32(2): 589–597.

41.

. A modified Li-He’s variational principle for plasma. Int J Numer Methods Heat Fluid Flow 2021; 31(5): 1369–1372.

42.

Anjum

Ain

, et al. Li-He’s modified homotopy perturbation method for doubly-clamped electrically actuated microbeams-based microelectromechanical system. Facta Univ Mech Eng 2021; 19(4): 601–612. DOI: 10.22190/FUME210112025A

43.

Trefethen

. Spectral methods in MATLAB, software, environments, and tools. Philadelphia, PA: SIAM, 2000.

44.

Sari

Al-Dahidi

. Vibration characteristics of multiple functionally graded nonuniform beams. J Vibration Control 2020; 27(19-20): 1–14. DOI: 10.1177/1077546320956768

45.

Sari

Shaat

Abdelkefi

. Frequency and mode veering phenomena of axially functionally graded non-uniform beams with nonlocal residuals. Compos Structures 2016; 163: 280–292.

Natural vibrations of double bi-directional functionally graded Euler–Bernoulli beams connected by a variable Winkler elastic layer

Abstract

Keywords

Introduction

Theory problem formulation

Mathematical model

Chebyshev spectral collocation method

Solution procedure

Results and discussion

Conclusion

Footnotes

Declaration of conflicting interests

Funding

ORCID iD

Appendix

Nomenclature

References