# Free Vibration of Embedded Porous Plate Using Third-Order Shear Deformation and Poroelasticity Theories

Authors: Ali Ghorbanpour Arani; Zahra Khoddami Maraghi; Mehdi Khani; Iman Alinaghian
Journal: Journal of Engineering
 (2017)

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## Abstract

This research aims at studying free vibration of rectangular plate made of porous materials in whichY-foam,G-foam, and Coustone are used and compared with each other. To obtain the Biot formulation of the constitutive equations for a porous material, linear poroelasticity theory is used. Young modulus and density of porous plate are different in transverse direction versus porosity. In order to increase the accuracy of results in comparison with classical plate and first-order shear deformation theories, Reddy’s theory was utilized in this research. Besides, five coupled equations of motion have been studied using Hamilton’s principle and are solved by differential quadrature method (DQM). Detailed results of this study show the significant effect of aspect ratio, thickness ratio, boundary conditions, and porosity on dimensionless frequency and deflection of porous plate. Results of this study can contribute to the design of pneumatic conveying, handling, and control systems.


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## Body

## 1. Introduction

Porous materials are materials which can be both organic and inorganic and contain pores (cavities, channels, and interstices) which are deeper than they are. These materials are mainly used in energy absorbing systems, porous electrodes, sound absorbers, filters, insulating materials, heat exchangers, construction materials, electromagnetic shielding, membrane, and membrane support [1].This paper focuses on the vibration analysis of porous plate regarding its application in mechanical systems. In what follows, some of the works related to this issue are reviewed. Biot and Willis [2] studied the methods of measurement to determine the elastic coefficients based on the theory of the deformation of a porous elastic solid containing a compressible fluid. They also discussed the physical interpretation of the coefficients in various alternate forms. Mansutti et al. [3] presented steady flows of non-Newtonian fluids using a porous plate with suction or injection. In this study, the flow is the counterpart of the classical “asymptotic suction” problem, within the context of the non-Newtonian fluid models. Numerical solutions were compared with the solutions from a regular perturbation approach, as well as a singular perturbation. Leclaire et al. [4] presented the vibrations of a rectangular porous plate described by two coupled equations involving the time and space derivatives of the deflection and of the relative fluid-solid motion. Using Galerkin’s variational method and classical theory of plates (nonporous), the equations were solved. The Rayleigh-Ritz decomposition on the basis of orthogonal or quasi-orthogonal Eigen-functions was used and the solutions were inserted in the vibrational equations. Results of the study showed that if the viscoelastic damping of the solid is accounted, comparison between experimental and theoretical results on the plate defection is conveniently good. A simple model of the transverse vibrations of a thin rectangular porous plate saturated by a fluid was studied by Leclaire et al. [5]. The classical theory of homogeneous plates and Biot’s stress-strain relations in an isotropic porous medium with a uniform porosity was used. They come to this conclusion that the resonance frequency is an increasing function of porosity and permeability and a decreasing function of tortuosity. A comparative study of Biot’s theory and the linear theory of porous media for wave propagation problems was presented in Schanz and Diebels’s article [6]. Regarding the results, a positive correlation between two approaches was observed in case of incompressible constituents, whereas in case of compressible constituents large differences appeared. Debowski and Magnucki [7] explored the dynamic stability of a porous rectangular plate to study an axial compressed porous-cellular rectangular plate which is a generalization of sandwich or multilayer plates. The result of this study shed light on the nonlinear hypothesis of deformation of the plane cross section for porous-cellular plate that includes the linear hypothesis for homogenous plate and the shear deformable effect. They proved that the mathematical model of the dynamic stability of the porous-cellular rectangular plate under pulsating compression load could be reduced to Mathieu’s equation. Khorshidvand et al. [8] studied buckling analysis of radially solid circular plate made of porous material bounded with the layers of piezoelectric actuators. The results of their study showed that increasing the porosity decreases the critical load and the plate will be unstable. They also concluded that the plate with high porosity with the piezo layer has a better effect on stability of the plate in comparison to increasing the thickness of the porous plate. Reducing the porosity makes the behavior of the plate tend to incline to homogeneous/isotropic behavior. Jabbari et al. [9] investigated the buckling analysis of radially loaded solid circular plate made of porous material. Properties of their plate varied across the thickness. They derived the equilibrium and stability equations through the variational formulation based on Sander’s nonlinear strain-displacement relation. In this study, the pores of the porous plate were saturated with a fluid. They come to the conclusion that increasing porosity decreases buckling load and the plate will be unstable by then. They also found that the Monotonous porosity is more unstable than symmetric and nonsymmetric porosity and the critical buckling load will be reduced by increasing the compressibility of fluid within the pores. An analysis of buckling of thin circular FG plates made of saturated porous-soft ferromagnetic materials in transverse magnetic field was done by Jabbari et al. [10]. The energy method based on the classical plate theory with the assumption of power-law composition for the constituent materials was used in the research. The research indicated that increasing the porosity makes the critical magnetic field decrease, the plate will be unstable, and the critical magnetic field will increase by increasing the thickness. Finally they concluded that Monotonous porosity is more unstable than the symmetric and nonsymmetric porosity in the aforementioned research. Joubaneh et al. [11] studied the thermal buckling analysis of solid circular plate made of porous material bounded with piezoelectric sensor-actuator patches in her research. The basic assumption under her research was that porous material properties vary with respect to thickness. The governing equations were obtained for clamped boundary condition based on mechanical nonlinear equilibrium and linear stability equations. The effects of porous plate’s thickness, porosity, and piezoelectric thickness on thermal stability of the plate were investigated and studied in the research. A detailed analysis of complicated and general problem of a functionally graded (FG) porous variable thickness circular plate subjected to nonaxisymmetric and nonuniform shear and normal tractions was done by Behravan Rad and Shariyat [12]. In their research, the plate was supported by a nonuniform Kerr elastic foundation based on the differential quadrature and state space vector techniques in the radial and thickness directions, respectively. The results showed that the induced magnetic quantities are mainly affected by the radial displacement component. They concluded that the material properties index, porosity, and the elastic foundation have positive effect and the compressibility parameter has an adverse and negative effect on the rigidity of the plate. Thermomechanical vibration characteristics of FG Reddy beams made of porous material subjected to various thermal loadings were investigated by Ebrahimi and Jafari [13]. They discussed the influences of several important parameters such as power-law exponents, porosity distributions, porosity volume fractions, and thermal effects on natural frequencies of the temperature-dependent FG beams.Bending and vibration of FG beams were analyzed with a simple and refined trigonometric higher-order beam theory by Bourada et al. [14]. In this theory the thickness stretching effect (εz≠0) was also included and the transverse shear deformation effects were considered without requiring shear correction factors. In this paper the material properties varied in the thickness direction. Numerical results of the present theory were compared with other theories to show the effect of the inclusion of transverse normal strain on the deflections and stresses.Bending and free vibration analysis of FG plates were developed using an original hyperbolic sine shear deformation theory by Neves et al. [15]. They used Carrera’s Unified Formulation to derive the equations of motion for through-the-thickness deformations. They showed the meshless technique in several numerical examples.Hebali et al. [16] presented a new quasi-three-dimensional (3D) hyperbolic shear deformation theory for the bending and free vibration analysis of FG plates. This theory reduced the number of unknowns by dividing the transverse displacement into bending, shear, and thickness stretching parts. Also their theory satisfied the zero traction boundary conditions on the surfaces of the plate without using shear correction factor.None of the aforementioned papers have investigated the vibration of porous plate using linear poroelasticity theory besides changing in Young modulus and density. The significance of this paper lies in using the third-order shear deformation theory (TSDT) to derive the equation of motions according to thickness ratio of plate for thin and thick plates. Variation of Young modulus and density in transvers direction of plate provides computational complexity that was solved by MAPLE and MATLAB software programs. Three different materials are compared with each other and different boundary conditions are applied on porous plate. The results show the effect of aspect ratio, thickness ratio, elastic medium, and porosity on dimensionless frequency of porous plate accordingly. This paper provides an initial platform for research on free and forced vibration of porous plates according to the many uses for this material. This article will help researchers to continue the studies about forced vibration of porous plate, drain and undrain states, nonconsolidated materials, and different states of fluid in porous materials.Porous plate can be used in aerospace industry and nuclear reactor as a vibration damper, in sea structures, vessels, and submarines due to very low density and in reformer and catalysts due to the high specific surface. The results of this research can be applied in all cases.


## 2. Structural Definition

A schematic diagram of a porous plate is illustrated in Figure1 in which geometrical parameters of length a, width b, and thickness h are shown as well.Figure 1
A schematic diagram of a porous plate.


## 3. Linear Poroelasticity Theory

The Biot formulation of the constitutive equations for a fluid-filled porous material assumes the linearity between the stress and the strain and reversibility of the deformation process. Detournay and Chen [17] stated the linear poroelasticity theory of Biot in two statements:(1)
An increase of pore pressure induces a dilation of pore.(2)
Compression of the pore causes an increase in pore pressure.According to the above-mentioned assumptions, stress-strain relation for porous material is shown in [8, 9](1)σij=C-ijεij-Ppαδijin which(2)σxxσyyσyzσxzσxy=C-11-Mα2C-12000C-21C-22-Mα200000C-4400000C-5500000C-66εxxεyyεyzεxzεxy,where σij and εij are normal and shear stresses and the terms of engineering constant are as follows [18]:(3)C-11=Ez1-υ2;C-12=C-21=υEz1-υ2;C-44=C-55=C-66=Ez1+υin which E and υ are Young modulus and Poisson’s ratio, respectively. (i)
The constantM is sometimes called the Biot modulus. The constant α is known as the ratio of the fluid volume gained (or lost) in a material element to the volume change of that element, when the pore pressure is allowed to return to its initial state and it varies between 0 and 1. These parameters are introduced as follows [4, 17]:(4)Pp=-Mαεkk;α=1-c1-ϕ.(ii)
Coefficientc can be regarded as a coefficient which characterizes the consolidation state of the heterogeneous material. c is between 0 for nonconsolidated materials and 1 for consolidated materials [4]; here c=1.(iii)
Porosityϕ is defined as ratio of volume of pore space to the volume of porous material. Change in the compressibility of the fluid or porosity affects the bulk constants [17].The variation of Young modulus and density in transverse direction of porous plate is shown as follows [10, 11]:(5)Ez=E01-e1cos⁡π2hz+h2,ρz=ρ01-e1cos⁡π2hz+h2.In this equation,e1 is the coefficient of plate porosity, E1 and E0 are Young’s modulus of elasticity at z=h/2 and z=-h/2, and ρ1 and ρ0 are the density at z=h/2 and z=-h/2, respectively. G=E/(1+2υ) is the relationship between the modulus of elasticity and shear modulus and υ is Poisson’s ratio, which is assumed to be constant across the plate thickness. Mechanical properties of the porous material vary across the thickness of the plate e1=1-G1/G0=1-E1/E0, in which 0≤e1≤1.Simplified expressions can be extracted for the poroelastic parameters for limiting cases in particular [17].For highly compressible fluid constituentKf/K≪1,f:fluid, the approximate expressions for M are(6)M=Kfϕ,K=E31-2υ.In the limit,Kf→0 and M→0. In other words, the porous material behaves as an elastic material without fluid where ϕ is called porosity and K is bulk modulus.


## 4. Third-Order Shear Deformation Theory (TSDT)

TSDT expands the first-order shear deformation theory (FSDT) by assuming the following:(i)
Shear strain and consequently shear stress are not constant through the plate thickness, where TSDT leads to better results for a moderately thick plate.(ii)
A shear correction factor is not required for the strain equations.(iii)
The displacement field accommodates a quadratic variation of the transverse shear through the thickness and the vanishing of transverse shear is mainly highlighted on the top and bottom surfaces of the plate [18, 19].The displacement field of TSDT for plates is presented here [5]: (7)U~x,y,z,t=u0x,y,t+zθ1x,y,t-43z3h2θ1x,y,t+∂∂xw0x,y,t,V~x,y,z,t=v0x,y,t+zθ2x,y,t-43z3h2θ2x,y,t+∂∂yw0x,y,t,W~x,y,z,t=w0x,y,t,where u0(x,y,t),v0(x,y,t),w0(x,y,t) are displacement functions along (x,y,z) directions and θ1(x,y,t),θ2x,y,t are rotations about x- and y-axes and t is time. Using Hooke’s law, the linear strain field for TSDT is being calculated.


## 5. Energy Method in Porous Plate

In this part, the energy method is used to work out the governing equations. Strain and kinetic energy of the rectangular porous plate is calculated and presented [20, 21]:(8)U=12∫Vσxxεxx+σyyεyy+τxyγxy+τxzγxz+τyzγyzdV,(9)K=12ρh∫0b∫0a∂U~∂t2+∂V~∂t2+∂W~∂t2dxdy.Using (1) and (7), the strain energy of porous plate can be derived.ρ is the density of porous plate and τij is tractions. By substituting (7) into (9), the kinetic energy is obtained.


### 5.1. External Work

Pasternak foundation is able to consider transverse shear loads and normal loads. The effect of surrounding elastic medium on the porous plate which is simulated with Pasternak model is considered as follows [21]:(10)FEx=KwW~-KG∂2W~∂x2+∂2W~∂y2,where Kw and KG are Winkler modulus for normal load and shear modulus for transverse shear loads, respectively. Therefore, the external work due to elastic medium is calculated as(11)Σ=12∫0b∫0aFExW~dxdy.


### 5.2. Hamilton’s Principle

Hamilton’s principle is utilized to obtain equations of motion. The principle can be stated in an analytical form in which the first variation form of equations must be zero [20].(12)δ∫t1t2U-K+Σdt=0.In this equation,δU,δK, and δΣ are variations of strain energy, variation of Kinetic energy, and variation of external work. We substituted (8) and (9) and external work into (12) for TSDT and used dimensionless parameters afterwards which were introduced in(13)ζ,η=xa,yb,U,V,W=u0a,v0b,w0h,γ=ab,Cij=C-ijE,αc,βc=ha,hb,kw=KwhE,kg=KGa·E,τ=taEρ,Ipdi=Ipihi+1i=2,4,6,Idi=Iihi+1.The equations of motion are worked out by setting the coefficientsδU,δV,δW,δθ1,δθ2 equal to zero:(14a)δU=-12I0γβcC44∂2∂η2U+23βc2C44I3∂2∂η2θ1-αc2C11I1∂2∂ζ2θ1+23βc2αcC21I3∂3∂η2∂ζW+23βcαcC21I3∂2∂η∂ζθ2+43αc3C11I3∂3∂ζ3W+23βcαcC44I3∂2∂η∂ζθ2+23βc2αcC12I3∂3∂η2∂ζW+43βc2αcC44I3∂3∂η2∂ζW+23βcαcC12I3∂2∂η∂ζθ2-12βc2C44I1∂2∂η2θ1+43αc2C11I3∂2∂ζ2θ1-12I0αcC21∂2∂η∂ζV-I0αcC11∂2∂ζ2U-12βcαcC44I1∂2∂η∂ζθ2-12βcαcC12I1∂2∂η∂ζθ2-12βcαcC21I1∂2∂η∂ζθ2-12I0αcC44∂2∂η∂ζV-12I0αcC12∂2∂η∂ζV-Mα2αc∂2∂η∂ζV-Mα2αc∂2∂ζ2U+I0αc∂2∂τ2U+αc2I1∂2∂τ2θ1-43αc2I3∂2∂τ2θ1-43αc3I3∂3∂τ2∂ζW=0,(14b)δV=-12γI0αcC44∂2∂ζ2V+23αc2βcC12I3∂3∂η∂ζ2W+43βc3C22I3∂3∂η3W+23αc2βcC21I3∂3∂η∂ζ2W-23αcβcC21I3∂2∂η∂ζθ1+23αcβcC12I3∂2∂η∂ζθ1+43αc2βcC44I3∂3∂η∂ζ2W+23αcβcC44I3∂2∂η∂ζθ1-12αc2C44I1∂2∂ζ2θ2-C22βc2I1∂2∂η2θ2+23αc2C44I3∂2∂ζ2θ2-12I0αcβcC21∂2∂η∂ζU+43βc2C22I3∂2∂η2θ2-12αcβcC12I1∂2∂η∂ζθ1-12αcβcC44I1∂2∂η∂ζθ1-12αcβcC21I1∂2∂η∂ζθ1-I0βcC22∂2∂η2V-12I0βcC44∂2∂η∂ζU-12I0βcC12∂2∂η∂ζU-Mα2βc∂2∂η∂ζU-Mα2βc∂2∂η2V+αcγI0∂2∂τ2V+αc2I1∂2∂τ2θ2-43αc2I3∂2∂τ2θ2-43αc2βcI3∂3∂τ2∂ηW=0,(14c)δW=89αc2βcC21I6∂3∂η∂ζ2θ2-23αc2βcC12I4∂3∂η∂ζ2θ2+169αc2βc2C12I6∂4∂η2∂ζ2W+169αc2βc2C21I6∂4∂η2∂ζ2W+329αc2βc2C44I6∂4∂η2∂ζ2W+169αc2βcC44I6∂3∂η∂ζ2θ2+89αcβc2C21I6∂3∂η2∂ζθ1-23αcβc2C21I4∂3∂η2∂ζθ1-23αcβc2C12I4∂3∂η2∂ζθ1+89αcβc2C12I6∂3∂η2∂ζθ1-23αc2βcC21I4∂3∂η∂ζ2θ2+169αcβc2C44I6∂3∂η2∂ζθ1-43αc2βcC44I4∂3∂η∂ζ2θ2-43αcβc2C44I4∂3∂η2∂ζθ1-12I0αc2C55∂2∂ζ2W-12I0αcC55∂∂ζθ1-12I0βc2C66∂2∂η2W-12I0βcC66∂∂ηθ2-8αcC55I4∂∂ζθ1+4αcC55I2∂∂ζθ1+4βcC66I2∂∂ηθ2-8βcC66I4∂∂ηθ2-43αc3C11I4∂3∂ζ3θ1+89αc2βcC12I6∂3∂η∂ζ2θ2-23βc2C21I3∂3∂η2∂ζU-23C12αc2I3∂3∂η∂ζ2V-43αc2C11I3∂3∂ζ3U-43βc2C22I3∂3∂η3V+169αc4C11I6∂4∂ζ4W+169βc4C22I6∂4∂η4W-8βc2C66I4∂2∂η2W+4βc2C66I2∂2∂η2W+8αc2C55I4∂2∂ζ2W+4αc2C55I2∂2∂ζ2W+169βc3C22I6∂3∂η3θ2-43βc2C44I3∂3∂η2∂ζU+169αc3C11I6∂3∂ζ3θ1-23βc2C12I3∂3∂η2∂ζU-43αc2C44I3∂3∂η∂ζ2V-43βc3C22I4∂3∂η3θ2-23αc2C21I3∂3∂η∂ζ2V169Mα2Ip6βc4∂4∂η4W+169Mα2Ip6αc4∂4∂ζ4W+169Mα2Ip6βc2αc∂3∂η2∂ζθ1+169Mα2Ip6βcαc2∂3∂η∂ζ2θ2+329Mα2Ip6βc2αc2∂4∂η2∂ζ2W+169Mα2Ip6βc3∂3∂η3θ2+169Mα2Ip6αc3∂3∂ζ3θ1-43Mα2Ip4βcαc2∂3∂η∂ζ2θ2-43Mα2Ip4αc3∂3∂ζ3θ1-43Mα2Ip4βc2αc∂3∂η2∂ζθ1-43Mα2Ip4βc3∂3∂η3θ2+43αc2I3∂3∂τ2∂ζU+43αc3I4∂3∂τ2∂ζθ1-169αc3I6∂3∂τ2∂ζθ1-169αc4I6∂4∂τ2∂ζ2W-43αc2I3∂3∂τ2∂ηV+43αc2βcI4∂3∂τ2∂ηθ2-169αc2βcI6∂3∂τ2∂ηθ2-169αc2βc2I6∂4∂τ2∂η2W+αc2I0∂2∂τ2W=0,(14d)δθ1=12I0αcC55∂∂ζW-4C55I2θ1+8C55I4θ1+23βc2αcC21I4∂3∂η2∂ζW-89βc2αcC21I6∂3∂η2∂ζW-169βc2αcC44I6∂3∂η2∂ζW-89βcαcC12I6∂2∂η∂ζθ2+43βcαcC12I4∂2∂η∂ζθ2-89βcαcC44I6∂2∂η∂ζθ2+43βcαcC44I4∂2∂η∂ζθ2+23βc2αcC12I4∂3∂η2∂ζW-89βc2αcC12I6∂3∂η2∂ζW+43βcαcC21I4∂2∂η∂ζθ2+43βc2αcC44I4∂3∂η2∂ζW-89βcαcC21I6∂2∂η∂ζθ2+23βcγC44I3∂2∂η2U-12βcγC44I1∂2∂η2U-12βcαcC44I2∂2∂η∂ζθ2-12βcαcC12I2∂2∂η∂ζθ2-12βcαcC21I2∂2∂η∂ζθ2-αc2C11I2∂2∂ζ2θ1-αcC11I1∂2∂ζ2U+83αc2C11I4∂2∂ζ2θ1-169αc2C11I6∂2∂ζ2θ1+23αcC44I3∂2∂η∂ζV+43αcC11I3∂2∂ζ2U-89βc2C44I6∂2∂η2θ1+43βc2C44I4∂2∂η2θ1-12βc2C44I2∂2∂η2θ1-169αc3C11I6∂3∂ζ3W+43αc3C11I4∂3∂ζ3W-12αcC12I1∂2∂η∂ζV+23αcC212I3∂2∂η∂ζV-4αcC55I2∂∂ζW+8αcC55I4∂∂ζW+23αcC12I3∂2∂η∂ζV-12αcC44I1∂2∂η∂ζV-12αcC21I1∂2∂η∂ζV+12I0C55θ1-169Mα2Ip6αc2∂2∂ζ2θ1-Mα2Ip2βcαc∂2∂η∂ζθ2+83Mα2Ip4αc2∂2∂ζ2θ1-169Mα2Ip6βcαc∂2∂η∂ζθ2-169Mα2Ip6βc2αc∂3∂η2∂ζW-169Mα2Ip6αc3∂3∂ζ3W+43Mα2Ip4αc3∂3∂ζ3W+83Mα2Ip4βcαc∂2∂η∂ζθ2+43Mα2Ip4βc2αc∂3∂η2∂ζW-Mα2Ip2αc2∂2∂ζ2θ1+I1∂2∂τ2U-43I3∂2∂τ2U+αc2I2∂2∂τ2θ1-83αc2I4∂2∂τ2θ1-43αc3I4∂3∂τ2∂ζW+169αc2I6∂2∂τ2θ1+169αc3I6∂3∂τ2∂ζW=0,(14e)δθ2=43βcαcC12I4∂2∂η∂ζθ1+23αc2βcC21I4∂3∂η∂ζ2W-89βcαcC44I6∂2∂η∂ζθ1+23γαcC44I3∂2∂ζ2V+43βcαcC44I4∂2∂η∂ζθ1-89βcαcC12I6∂2∂η∂ζθ1-89αc2βcC21I6∂3∂η∂ζ2W+43βcαcC21I4∂2∂η∂ζθ1-89βcαcC21I6∂2∂η∂ζθ1-12βcαcC12I2∂2∂η∂ζθ1-12βcαcC21I2∂2∂η∂ζθ1-169αc2βcC44I6∂3∂η∂ζ2W-89αc2βcC12I6∂3∂η∂ζ2W+43αc2βcC44I4∂3∂η∂ζ2W+23αc2βcC12I4∂3∂η∂ζ2W-12βcαcC44I2∂2∂η∂ζθ1-12γαcC44I1∂2∂ζ2V-βcC22I1∂2∂η2V-βc2C22I2∂2∂η2θ2+23βcC21I3∂2∂η∂ζU-169βc3C22I6∂3∂η3W+23βcC44I3∂2∂η∂ζU+43βc3C22I4∂3∂η3W-12βcC12I1∂2∂η∂ζU-12βcC21I1∂2∂η∂ζU-12βcC44I1∂2∂η∂ζU-12αc2C44I2∂2∂ζ2θ2+83βc2C22I2∂2∂η2θ2-169βc2C22I6∂2∂η2θ2+43βcC22I3∂2∂η2V+43αc2C44I4∂2∂ζ2θ2+23βcC12I3∂2∂η∂ζU-89αc2C44I6∂2∂ζ2θ2-4βcC66I2∂∂ηW+8βcC66I4∂∂ηW+12I0βcC66∂∂ηW-4C66I2θ2+8C66I4θ2+12I0C66θ2-Mα2Ip2βcαc∂2∂η∂ζθ1+83Mα2Ip4βc2∂2∂η2θ2-169Mα2Ip6βc2∂2∂η2θ2-169Mα2Ip6βcαc∂2∂η∂ζθ1-169Mα2Ip6βcαc2∂3∂η∂ζ2W-169Mα2Ip6βc3∂3∂η3W+43Mα2Ip4βcαc2∂3∂η∂ζ2W+83Mα2Ip4βcαc∂2∂η∂ζθ1+43Mα2Ip4βc3∂3∂η3W-Mα2Ip2βc2∂2∂η2θ2+1γαcI1∂2∂τ2V-43γαcI3∂2∂τ2V+αc2I2∂2∂τ2θ2-83αc2I4∂2∂τ2θ2-43αc2βcI4∂3∂τ2∂ηW+169αc2I6∂2∂τ2θ2+169αc2βcI6∂3∂τ2∂ηW=0in which(15)Ipdi=∫-h/2h/2zidz;Ipd2=h312;Ipd4=h580;Ipd6=h7448fori=2,4,6Ipdi=0fori=1,3,5Idi=∫-h/2h/2zi·1-e1cos⁡π2hz+h2dz;fori=0,1,…,6.


## 5.1. External Work

Pasternak foundation is able to consider transverse shear loads and normal loads. The effect of surrounding elastic medium on the porous plate which is simulated with Pasternak model is considered as follows [21]:(10)FEx=KwW~-KG∂2W~∂x2+∂2W~∂y2,where Kw and KG are Winkler modulus for normal load and shear modulus for transverse shear loads, respectively. Therefore, the external work due to elastic medium is calculated as(11)Σ=12∫0b∫0aFExW~dxdy.


## 5.2. Hamilton’s Principle

Hamilton’s principle is utilized to obtain equations of motion. The principle can be stated in an analytical form in which the first variation form of equations must be zero [20].(12)δ∫t1t2U-K+Σdt=0.In this equation,δU,δK, and δΣ are variations of strain energy, variation of Kinetic energy, and variation of external work. We substituted (8) and (9) and external work into (12) for TSDT and used dimensionless parameters afterwards which were introduced in(13)ζ,η=xa,yb,U,V,W=u0a,v0b,w0h,γ=ab,Cij=C-ijE,αc,βc=ha,hb,kw=KwhE,kg=KGa·E,τ=taEρ,Ipdi=Ipihi+1i=2,4,6,Idi=Iihi+1.The equations of motion are worked out by setting the coefficientsδU,δV,δW,δθ1,δθ2 equal to zero:(14a)δU=-12I0γβcC44∂2∂η2U+23βc2C44I3∂2∂η2θ1-αc2C11I1∂2∂ζ2θ1+23βc2αcC21I3∂3∂η2∂ζW+23βcαcC21I3∂2∂η∂ζθ2+43αc3C11I3∂3∂ζ3W+23βcαcC44I3∂2∂η∂ζθ2+23βc2αcC12I3∂3∂η2∂ζW+43βc2αcC44I3∂3∂η2∂ζW+23βcαcC12I3∂2∂η∂ζθ2-12βc2C44I1∂2∂η2θ1+43αc2C11I3∂2∂ζ2θ1-12I0αcC21∂2∂η∂ζV-I0αcC11∂2∂ζ2U-12βcαcC44I1∂2∂η∂ζθ2-12βcαcC12I1∂2∂η∂ζθ2-12βcαcC21I1∂2∂η∂ζθ2-12I0αcC44∂2∂η∂ζV-12I0αcC12∂2∂η∂ζV-Mα2αc∂2∂η∂ζV-Mα2αc∂2∂ζ2U+I0αc∂2∂τ2U+αc2I1∂2∂τ2θ1-43αc2I3∂2∂τ2θ1-43αc3I3∂3∂τ2∂ζW=0,(14b)δV=-12γI0αcC44∂2∂ζ2V+23αc2βcC12I3∂3∂η∂ζ2W+43βc3C22I3∂3∂η3W+23αc2βcC21I3∂3∂η∂ζ2W-23αcβcC21I3∂2∂η∂ζθ1+23αcβcC12I3∂2∂η∂ζθ1+43αc2βcC44I3∂3∂η∂ζ2W+23αcβcC44I3∂2∂η∂ζθ1-12αc2C44I1∂2∂ζ2θ2-C22βc2I1∂2∂η2θ2+23αc2C44I3∂2∂ζ2θ2-12I0αcβcC21∂2∂η∂ζU+43βc2C22I3∂2∂η2θ2-12αcβcC12I1∂2∂η∂ζθ1-12αcβcC44I1∂2∂η∂ζθ1-12αcβcC21I1∂2∂η∂ζθ1-I0βcC22∂2∂η2V-12I0βcC44∂2∂η∂ζU-12I0βcC12∂2∂η∂ζU-Mα2βc∂2∂η∂ζU-Mα2βc∂2∂η2V+αcγI0∂2∂τ2V+αc2I1∂2∂τ2θ2-43αc2I3∂2∂τ2θ2-43αc2βcI3∂3∂τ2∂ηW=0,(14c)δW=89αc2βcC21I6∂3∂η∂ζ2θ2-23αc2βcC12I4∂3∂η∂ζ2θ2+169αc2βc2C12I6∂4∂η2∂ζ2W+169αc2βc2C21I6∂4∂η2∂ζ2W+329αc2βc2C44I6∂4∂η2∂ζ2W+169αc2βcC44I6∂3∂η∂ζ2θ2+89αcβc2C21I6∂3∂η2∂ζθ1-23αcβc2C21I4∂3∂η2∂ζθ1-23αcβc2C12I4∂3∂η2∂ζθ1+89αcβc2C12I6∂3∂η2∂ζθ1-23αc2βcC21I4∂3∂η∂ζ2θ2+169αcβc2C44I6∂3∂η2∂ζθ1-43αc2βcC44I4∂3∂η∂ζ2θ2-43αcβc2C44I4∂3∂η2∂ζθ1-12I0αc2C55∂2∂ζ2W-12I0αcC55∂∂ζθ1-12I0βc2C66∂2∂η2W-12I0βcC66∂∂ηθ2-8αcC55I4∂∂ζθ1+4αcC55I2∂∂ζθ1+4βcC66I2∂∂ηθ2-8βcC66I4∂∂ηθ2-43αc3C11I4∂3∂ζ3θ1+89αc2βcC12I6∂3∂η∂ζ2θ2-23βc2C21I3∂3∂η2∂ζU-23C12αc2I3∂3∂η∂ζ2V-43αc2C11I3∂3∂ζ3U-43βc2C22I3∂3∂η3V+169αc4C11I6∂4∂ζ4W+169βc4C22I6∂4∂η4W-8βc2C66I4∂2∂η2W+4βc2C66I2∂2∂η2W+8αc2C55I4∂2∂ζ2W+4αc2C55I2∂2∂ζ2W+169βc3C22I6∂3∂η3θ2-43βc2C44I3∂3∂η2∂ζU+169αc3C11I6∂3∂ζ3θ1-23βc2C12I3∂3∂η2∂ζU-43αc2C44I3∂3∂η∂ζ2V-43βc3C22I4∂3∂η3θ2-23αc2C21I3∂3∂η∂ζ2V169Mα2Ip6βc4∂4∂η4W+169Mα2Ip6αc4∂4∂ζ4W+169Mα2Ip6βc2αc∂3∂η2∂ζθ1+169Mα2Ip6βcαc2∂3∂η∂ζ2θ2+329Mα2Ip6βc2αc2∂4∂η2∂ζ2W+169Mα2Ip6βc3∂3∂η3θ2+169Mα2Ip6αc3∂3∂ζ3θ1-43Mα2Ip4βcαc2∂3∂η∂ζ2θ2-43Mα2Ip4αc3∂3∂ζ3θ1-43Mα2Ip4βc2αc∂3∂η2∂ζθ1-43Mα2Ip4βc3∂3∂η3θ2+43αc2I3∂3∂τ2∂ζU+43αc3I4∂3∂τ2∂ζθ1-169αc3I6∂3∂τ2∂ζθ1-169αc4I6∂4∂τ2∂ζ2W-43αc2I3∂3∂τ2∂ηV+43αc2βcI4∂3∂τ2∂ηθ2-169αc2βcI6∂3∂τ2∂ηθ2-169αc2βc2I6∂4∂τ2∂η2W+αc2I0∂2∂τ2W=0,(14d)δθ1=12I0αcC55∂∂ζW-4C55I2θ1+8C55I4θ1+23βc2αcC21I4∂3∂η2∂ζW-89βc2αcC21I6∂3∂η2∂ζW-169βc2αcC44I6∂3∂η2∂ζW-89βcαcC12I6∂2∂η∂ζθ2+43βcαcC12I4∂2∂η∂ζθ2-89βcαcC44I6∂2∂η∂ζθ2+43βcαcC44I4∂2∂η∂ζθ2+23βc2αcC12I4∂3∂η2∂ζW-89βc2αcC12I6∂3∂η2∂ζW+43βcαcC21I4∂2∂η∂ζθ2+43βc2αcC44I4∂3∂η2∂ζW-89βcαcC21I6∂2∂η∂ζθ2+23βcγC44I3∂2∂η2U-12βcγC44I1∂2∂η2U-12βcαcC44I2∂2∂η∂ζθ2-12βcαcC12I2∂2∂η∂ζθ2-12βcαcC21I2∂2∂η∂ζθ2-αc2C11I2∂2∂ζ2θ1-αcC11I1∂2∂ζ2U+83αc2C11I4∂2∂ζ2θ1-169αc2C11I6∂2∂ζ2θ1+23αcC44I3∂2∂η∂ζV+43αcC11I3∂2∂ζ2U-89βc2C44I6∂2∂η2θ1+43βc2C44I4∂2∂η2θ1-12βc2C44I2∂2∂η2θ1-169αc3C11I6∂3∂ζ3W+43αc3C11I4∂3∂ζ3W-12αcC12I1∂2∂η∂ζV+23αcC212I3∂2∂η∂ζV-4αcC55I2∂∂ζW+8αcC55I4∂∂ζW+23αcC12I3∂2∂η∂ζV-12αcC44I1∂2∂η∂ζV-12αcC21I1∂2∂η∂ζV+12I0C55θ1-169Mα2Ip6αc2∂2∂ζ2θ1-Mα2Ip2βcαc∂2∂η∂ζθ2+83Mα2Ip4αc2∂2∂ζ2θ1-169Mα2Ip6βcαc∂2∂η∂ζθ2-169Mα2Ip6βc2αc∂3∂η2∂ζW-169Mα2Ip6αc3∂3∂ζ3W+43Mα2Ip4αc3∂3∂ζ3W+83Mα2Ip4βcαc∂2∂η∂ζθ2+43Mα2Ip4βc2αc∂3∂η2∂ζW-Mα2Ip2αc2∂2∂ζ2θ1+I1∂2∂τ2U-43I3∂2∂τ2U+αc2I2∂2∂τ2θ1-83αc2I4∂2∂τ2θ1-43αc3I4∂3∂τ2∂ζW+169αc2I6∂2∂τ2θ1+169αc3I6∂3∂τ2∂ζW=0,(14e)δθ2=43βcαcC12I4∂2∂η∂ζθ1+23αc2βcC21I4∂3∂η∂ζ2W-89βcαcC44I6∂2∂η∂ζθ1+23γαcC44I3∂2∂ζ2V+43βcαcC44I4∂2∂η∂ζθ1-89βcαcC12I6∂2∂η∂ζθ1-89αc2βcC21I6∂3∂η∂ζ2W+43βcαcC21I4∂2∂η∂ζθ1-89βcαcC21I6∂2∂η∂ζθ1-12βcαcC12I2∂2∂η∂ζθ1-12βcαcC21I2∂2∂η∂ζθ1-169αc2βcC44I6∂3∂η∂ζ2W-89αc2βcC12I6∂3∂η∂ζ2W+43αc2βcC44I4∂3∂η∂ζ2W+23αc2βcC12I4∂3∂η∂ζ2W-12βcαcC44I2∂2∂η∂ζθ1-12γαcC44I1∂2∂ζ2V-βcC22I1∂2∂η2V-βc2C22I2∂2∂η2θ2+23βcC21I3∂2∂η∂ζU-169βc3C22I6∂3∂η3W+23βcC44I3∂2∂η∂ζU+43βc3C22I4∂3∂η3W-12βcC12I1∂2∂η∂ζU-12βcC21I1∂2∂η∂ζU-12βcC44I1∂2∂η∂ζU-12αc2C44I2∂2∂ζ2θ2+83βc2C22I2∂2∂η2θ2-169βc2C22I6∂2∂η2θ2+43βcC22I3∂2∂η2V+43αc2C44I4∂2∂ζ2θ2+23βcC12I3∂2∂η∂ζU-89αc2C44I6∂2∂ζ2θ2-4βcC66I2∂∂ηW+8βcC66I4∂∂ηW+12I0βcC66∂∂ηW-4C66I2θ2+8C66I4θ2+12I0C66θ2-Mα2Ip2βcαc∂2∂η∂ζθ1+83Mα2Ip4βc2∂2∂η2θ2-169Mα2Ip6βc2∂2∂η2θ2-169Mα2Ip6βcαc∂2∂η∂ζθ1-169Mα2Ip6βcαc2∂3∂η∂ζ2W-169Mα2Ip6βc3∂3∂η3W+43Mα2Ip4βcαc2∂3∂η∂ζ2W+83Mα2Ip4βcαc∂2∂η∂ζθ1+43Mα2Ip4βc3∂3∂η3W-Mα2Ip2βc2∂2∂η2θ2+1γαcI1∂2∂τ2V-43γαcI3∂2∂τ2V+αc2I2∂2∂τ2θ2-83αc2I4∂2∂τ2θ2-43αc2βcI4∂3∂τ2∂ηW+169αc2I6∂2∂τ2θ2+169αc2βcI6∂3∂τ2∂ηW=0in which(15)Ipdi=∫-h/2h/2zidz;Ipd2=h312;Ipd4=h580;Ipd6=h7448fori=2,4,6Ipdi=0fori=1,3,5Idi=∫-h/2h/2zi·1-e1cos⁡π2hz+h2dz;fori=0,1,…,6.


## 6. Solution Procedure Using DQM

The first (16) is used to separate the spatial and temporal distribution:(16)Uζ,η,τ=Uζ,ηeωτ,Vζ,η,τ=Vζ,ηeωτ,Wζ,η,τ=Wζ,ηeωτ,θ1ζ,η,τ=θ1ζ,ηeωτ,θ2ζ,η,τ=θ2ζ,ηeωτ,in which ω=Ωaρ/E is the dimensionless frequency (Ω is the dimensional frequency). In DQM, the differential equations change into the first algebraic equations. According to what was mentioned, the partial derivations of the function (F) are estimated by a specific variable at discontinuous points using a set of weighting series. It is supposed that F has been a function representing U,V,W,θ1, and θ2 regarding variables ξ and η (0<ξ<1,0<η<1) when Nξ×Nη is the grid points along these variables with the following derivation [22]:(17)dnFξi,ηjdξn=∑k=1NξAiknFξk,ηjn=1,…,Nξ-1.In this equation,Aik(n) are the weighting coefficients which are derived using Chebyshev polynomials for the positions of the grid points whose recursive formulae can be found in [23]. The standard form of the equation of motion (MX¨+KX=0) is obtained by applying DQM and using (16) into governing (14a), (14b), (14c), (14d), and (14e) considering simply supported boundary conditions as mentioned below:(18)Wi1=Vi1=Ui1=φyi1=ψyi1=0,Mxxi1=0,Mxx=∫zσxxdz,WNi=VNi=UNi=φyNi=ψyNi=0,Mxx1N=0.In this part, the eigenvalue problem is encountered in which the eigen-values ofK/M are introduced as dimensionless frequencies. It is worth mentioning that M is the mass matrix and K is the stiffness.In order to ensure the correct results, linear frequencyω=Ωa2ρ·h/D,D=EI/(1-υ2) for an isotropic square plate is compared in Table 1 for two modes. The results of the present work and other published papers have been matched well ([24–26]) and it shows that the correct solution has been used in the process of the research.Table 1
Comparison of the results.
ω 1 ω 2 Bardell [24] 19.7392 49.3480 Wang et al. [25] 19.7392 49.3453 Wang and Shen [26] 19.7384 49.3431 Present work 19.4250 49.3392


## 7. Numerical Results and Discussion

In this study, TSDT was used to work out the equations of motion of rectangular porous plate. The effects of aspect ratio, thickness ratio, boundary condition, porosity, and material properties are included in the results of the study. Detournay and Chen [17] have presented the material properties of saturated porous plate (Tennessee marble) and it is listed in Table 2. Besides, Table 2 reports on the properties ofY-foam,G-foam, andCoustone.Table 2
Mechanical properties of porous materials.
Y-foam G-foam C o u s t o n e ρ  ( k g / m 3 ) 353 348 1295 E  ( M P a ) 21 4.0 340 υ 0.35 0.35 0.35 ϕ 0.69 0.74 0.36 Tennessee marble:  G=24(GPa),υ=0.3Figure2 illustrates the effect of porosity on dimensionless natural frequency of porous plate. It is crystal clear that natural frequency is reduced by increasing the porosity. In fact, according to (5), the porosity affects Young modulus of porous plate.Figure 2
Effect of porosity and thickness ratio on dimensionless natural frequency.Based on the thickness ratio, plates are classified, where0.05<h/a<0.3 has been determined for thick plates. Classical theory of plates is applicable to very thin and moderately thin plates, while HSDT applies to thick plates. Figure 2 also shows that increasing α leads to decrease in the dimensionless frequency for all values of porosity.Figure3 displays the effect of aspect ratio on dimensionless natural frequency of porous plate in different porosities. Aspect ratio γ is defined as a geometrical parameter of porous plate introducing the ratio of length to width. As it can be seen from Figure 3, the vibration frequency of porous plate does not necessarily follow the determined trend for γ<4 and the results are redundant in this range. But for larger aspect ratios γ≥4, the dimensionless natural frequency is increased by increasing γ.Figure 3
Effect of porosity and aspect ratio on dimensionless natural frequency.Figures4(a) and 4(b) show the impact of five different boundary conditions on frequency response of porous plate including clamped and simple support. Five boundary conditions of CCCC, CCCS, CCSS, CSSS, and SSSS have been compared in this figure in which the value of dimensionless frequency for CCCC is larger than the rest of values. Results show that CCCC boundary condition provides the maximum value for natural frequency and the minimum value is related to SSSS boundary condition. On the one hand, it can be also concluded that, in Figure 4(b) when the aspect ratio of porous plate increases, the difference among above boundary conditions decreases at a higher porosity. On the other hand, the geometrical parameters highly affect vibration behavior of porous plate.Figure 4
Effect of boundary conditions on dimensionless natural frequency.
(a) (b)Dimensionless frequency of porous plate versus porosity has been shown in Figure5 for four primary modes. It is obvious from the figure that higher mode is associated with a greater frequency and also none of modes have overlap in 0.1≤e1≤0.5.Figure 5
Variation of dimensionless natural frequency versus porosity for four primary modes.Figure6 displays the deflection of porous plate versus porosity for four primary modes in e1=0.2,α=0.2,γ=1,SSSS.Figure 6
Deflection of porous plate versus porosity for four primary modes ine1=0.2,α=0.2,γ=1,SSSS.Figure7 illustrates the variation of dimensionless natural frequency with porosity of porous plate in different elastic mediums. Figure 7 shows the role of elastic medium in stability of system in which the lowest curve reports the values of dimensionless frequency without elastic medium. In this figure, ω has the minimum value to the other cases. 2th curve belongs to the Winkler foundation with spring constant kw=108. Pasternak modules create the larger values for natural frequency of porous plate due to normal and shear modules kw=108,kg=108.Figure 7
Effect of elastic medium on dimensionless natural frequency.According to Figure8, dimensionless natural frequency of porous plate changes three materials ofY-foam,G-foam, and Coustone.Y-foam,G-foam, and Coustone are known as porous materials with different Young modulus and porosities. According to Table 1, comparisons have been made: Young modulus of Coustone is larger than foams and the porosity of foams is higher than Coustone. Among foams,Y-foam has a larger Young modulus and a lower porosity, so the most dimensionless natural frequency belongs to Coustone plate and the lowest one is forG-foam.Figure 8
Effect of material properties on dimensionless natural frequency.


## 8. Conclusion

The significance and novelty of this research lie in studying free vibration of embedded porous which is a relatively new and prosperous topic in this field. The linear poroelasticity theory was used to work out the stress-strain relations in porous material while the Young modulus and density vary in transverse direction of porous plate. To evaluate the effect of normal and shear modulus on the stability of porous plate, Pasternak foundation was developed. TSDT with five unknown functions was used to derive the equation of motions. A set of equations were solved by two-dimensional DQM and the following results were concluded:(i)
Regarding the relationship between porosity, Young modulus, and density in porous materials, the high porosity leads to reduction of dimensionless frequency of porous plate. On the other hand, porosity reduces the density and Young modulus of matter. Thus, porous materials have the lower natural frequency due to porosity. The porosity in porous materials also creates the damping that it can be used in the aerospace industry.(ii)
Pasternak with normal(kbw) and shear (Kbg) modulus can be regarded as important factors in stability of porous plate in which the dimensionless frequency increases with increasing the stiffness. So the vibration frequency of porous plate can be increased by providing a hard bed.(iii)
Aspect ratio and thickness ratio as geometrical parameters have an efficient and vital role in vibration behavior of porous plate. Therefore, choosing the right dimensions and thickness can be achieved to a certain natural frequency.(iv)
Result shed light on the ground that CCCC boundary condition provides maximum value for natural frequency of porous plate and minimum value relates to SSSS boundary condition. It is evident that CCCC boundary condition increases the stiffness of porous plate.(v)
Coustone as a porous material has larger natural frequency in comparison toY-foam andG-foam due to high Young modulus and density.The result of this study can benefit the designers and manufacturers of aircrafts, cars, automobiles, and pneumatic conveying and material handling systems including aerators, airlocks, bins, blenders, blowers, boosters, control systems, air and gas compressors, ship, and barge loaders and unloaders.



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*Source: 1474916-2017-01-24.xml*