# On the Vibration Analysis of Rotating Piezoelectric Functionally Graded Beams Resting on Elastic Foundation with a Higher-Order Theory

Authors: Pham Minh Phuc; Vu Nguyen Thanh
Journal: International Journal of Aerospace Engineering
 (2022)

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## Abstract

This work numerically simulates the natural vibration response of rotating piezoelectric functionally graded (FG) beams resting on two-parameter elastic mediums. This is a common kind of design seen in reality, such as marine engine gas turbine blades, rotating railway bridges, and helicopter rotors, where these components may be thought of as beam models rotating around a fixed axis. For the first time, this study uses the finite element method (FEM) in conjunction with Reddy’s theory of high-order shear deformation to model the vibration response of a beam rotating around one fixed axis. The present theory eliminates the necessity for shear correction factors while precisely describing the structure’s mechanical response. The piezoelectric layers are firmly connected to the top and bottom surfaces of the beam, while the core layer is composed of the FG material, whose material and physical characteristics are expected to gradually change along the thickness direction of the beam in accordance with a power law function as the thickness of the beam is increased. This study is conducted to determine the influences of the structure’s geometric and material characteristics on the beam’s free vibration behavior, including the rotational speed, distance between the fixed axis and beam endpoint, thickness of piezoelectric layers, and elastic foundation parameters, among other things. Due to the obvious calculation results, the free vibration response of this structure can be easily seen by readers, which serves as a foundation for its design and use in engineering practice.


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## Body

## 1. Introduction

Functionally graded materials (FGM) are the smart and advanced materials made by Japanese scientists in the 1980s. Because they are formed from two or more different materials, they have full advantages over the component materials. The most common type of FGM is made of ceramic and metal, while beam, plate, and shell structures made of FG material store many features that increase the efficiency of these structures such as high strength, resistance to friction and abrasion, good heat resistance, and being difficult to crack. The study of the mechanical responses of these components is interested in researching the scientific community [1–5]. Besides, to increase the efficiency of use for structures made of FG materials, scientists also consider the addition of piezoelectric layers, where the piezoelectric effect produces special effects that are much more prominent without the piezoelectric layer.Beams made of FG materials with piezoelectric layers are widely used in technical practice and play a significant role in the field. As a consequence, experts all around the globe have been doing research into FG beam structures, as well as piezoelectric FG beams, with remarkable results. In their study, Zhao et al. [6] used strain gradient theory and Euler-Bernoulli beam theory to investigate the effects of porosity and flexoelectricity on the static bending and free vibration of porous axially functional gradient piezoelectric nanobeams with axially functional gradient piezoelectric properties. Nan et al. [7] explored the static bending and free vibration analysis of porous functionally graded piezoelectric nanobeams utilizing the electric enthalpy variation and Hamilton’s principle, as well as differential equations for regulating the bending and free vibration. Using an analytical method, Singh and Kumari [8] investigated the free vibration analysis of axially functionally graded beams that were integrated with piezoelectric layers and subjected to arbitrarily supported boundary conditions in a free-falling state. Larkin and colleagues [9] used the modified couple stress theory to investigate the impact of small-scale phenomena on the natural frequencies and power density of macro- to nanoscale functionally graded energy harvesters with beam lengths ranging from 62.5 mm to 6.25 m. They found that the natural frequencies and power density of the harvesters were affected by small-scale phenomena. A two-node efficient finite element model combining layer-wise mechanics was used by Yasin and colleagues [10] to assess the active vibration stabilization of piezoelectric functionally graded beams. A functionally graded porous piezoelectric sandwich nanobeam reinforced by graphene platelets was investigated by Chen et al. [11] using the Euler-Bernoulli beam theory and a differential quadrature technique in order to capture the effect of flexoelectricity on the vibration responses of the nanobeam. Askari and colleagues [12] used the classical, first-order, and higher-order beam theories to analyze the natural frequencies of FG porous beams combined with transverse and shear piezoelectric layers under electrical conditions of short circuit and open circuit.The rotor of a helicopter, railway track in the turning position, and other elements may be represented as a beam moving around a fixed axis, as can be seen in the illustration. Additionally, mechanical behavior research on these rotating beam constructs is being carried out, with early results having already been published. By improving the geometry of rotating beams, Gunjal and Dixit [13] investigated the lowest vibration states of rotating beams. Simulation of the rotating beam was carried out using the finite-element method, and optimization of the working process was conducted out using sequential quadratic programming. A rotating nanobeam was explored by Pradhan and Murmu [14] utilizing Eringen’s nonlocal elasticity theory as well as a single nonlocal beam element to determine its mechanical response. A method known as differential quadrature was used in this investigation. For their study of the free vibration response of a rotating FG beam, Li and colleagues [15] utilized a dynamic model that took the influences of stretching and bending into consideration. With the use of Euler-Bernoulli, Timoshenko, and finite element beam theories, Amir and colleagues [16] examined the topic of lead-lag vibration in rotating microbeams utilizing rotating microbeams. [17] explored the influences of fractures on the free vibration behavior of a rotating Bernoulli-Euler beam utilizing a unique numerical methodology that allowed for the straightforward computation of these effects using the transfer matrix method, as developed by Jung-Woo and Jung-Youn. Das [18] used the Ritz approach to compute the mechanical reaction of rotating FG beams based on the Timoshenko beam element theory, while also accounting for the Coriolis acceleration. A rotating cantilever beam exposed to magnetic excitations was investigated by Xu and colleagues [19] using the Hamilton principle and the Galerkin technique. The flow model and vibration suppression of the cantilever beam were investigated. Alireza and Cai [20] conducted a research of the free vibration response of a spinning rod utilizing Eringen’s nonlocal elasticity to propose a solution. Liang et al. [21] investigated the free vibration control of a rotating piezoelectric FG beam under temperature settings by using high-order coupling models. A method for capturing the free vibration response of rotating microbeams composed of multilayered composite components with initial geometrical defects was proposed by Dejin and colleagues [22]. The method was based on a combination of the Timoshenko beam and a remodified couple stress theory, which was modified to account for initial geometrical defects. Researchers Atanasov and Stojanović [23] examined the free vibration of rotating nanobeams utilizing a variety of methods including the Euler beam, the Bernoulli-nonlocal Eringen’s elasticity theories, and the Galerkin technique. A large number of different parameter experiments were carried out. Mai et al. [24] evaluated mechanical behaviors of hybrid sandwich plates experimentally. It has recently been used in studies [25–28] and [29] to examine the mechanical behavior of beam and plate structures when rotated. The authors of the work [30] researched the mechanical response of plates while considering temperature and numerous theories. Scientists have studied the mechanical behavior of plate and beam constructions [31–49].According to the summary above, no papers exist on the rotating piezoelectric FG beams resting on two-parameter elastic foundations with a higher-order theory. Thus, this paper will use a combination of the FEM and Reddy’s third-order shear deformation theory (TSDT) to numerically model the free vibration responses of this kind of structure. The suggested method is straightforward, since there are no shear correction variables, and it is simple to construct the stress and strain relations, while yet accurately modeling the mechanical processes. The computational findings presented in this study will provide a solid foundation for the design and use of rotating beam constructions incorporating piezoelectric layers, such as propeller rotors, gas turbine rotors, and rotating railway bridges.The remainder of this work is arranged in the following manner. Section2 offers a finite element model of the rotating piezoelectric FG beam based on Reddy beam theory, which takes into consideration the effects of the two-parameter elastic basis on the beam’s rotational characteristics. Section 3 includes instances of verification to demonstrate the suggested approach and mechanical models’ correctness. Section 4 contains numerical findings and comments. Section 5 summarizes various novel points made in this study.


## 2. Finite Element Formulations of the Rotating Piezoelectric FG Beam Based on Reddy High-Order Shear Deformation Theory

This paper focuses on a FG beam rotating at a constant speed around a fixed axisΩ (see Figure 1). The length L, the breadth b, and the depth h of the beam are its geometrical dimensions, whereas the distance between the beam’s terminus and the fixed axis is r. The beam is supported by Pasternak’s elastic foundation with two parameters, kw anηd ks.Figure 1
The representation of the rotating piezoelectric FG beam resting on Pasternak’s elastic medium.The structure’s core layer is composed of metal (designated bym) and ceramic (designated by c), with the corresponding material volume ratios of Vm and Vc. According to the following power law function [1, 50–55], the material ratio of ceramic and metal changes in the depth direction of the core component:
(1)Vc=zh+12n;Vm=1−Vc,wheren≥0,where z is the thickness coordinate variable associated with −h/2≤z≤h/2 and n is the volume fraction index and its variation.With the above-mentioned changing law of the material ratio, Young’s modulusE, Poisson’s ratio ν, and density ρ are all functions of the power law dismemberment as follows [1]:
(2)Ez=Em+Ec−Em12+zhn,ρz=ρm+ρc−ρm12+zhn,νz=νm+νc−νm12+zhn.This study makes use of the TSDT in order to develop finite element formulas for estimating the free vibration response of a rotating piezoelectric FG beam, which are then implemented in numerical simulations. Because of this, the displacement components at any location with coordinatesx,y,z inside the structure have the following form [1], which is presented as follows:
(3)ux,z=u0x,0+zβx−43h2z3βx+∂w0∂x,wx,z=w0x,0,where u0x,0 and w0x,0 are the displacements along the beam’s midaxis and u and w are the movement components along the x- and z-axes at any location using the point x,z.The strain field is then expressed as follows:(4)εxx=∂u∂x=∂u0∂x+z∂βx∂x+−4z33h2∂βx∂x+∂2w0∂x2=ε0x+zε1x+z3ε3x,γxz=βx+∂w0∂x+z2−4h2βx+∂w0∂x=γ0xz+z2γ2xz,in which, the strain components are defined as follows:
(5)ε0x=∂u0∂x,ε1x=∂βx∂x,ε3x=−43h2∂βx∂x+∂2w0∂x2,γ0xz=βx+∂w0∂x,γ2xz=−4h2βx+∂w0∂x.The normal and shear stress components of the FGM core layer of the beam are calculated based on Hooke’s law as follows:(6)σxxF=Ezεxx,τxzF=Ez21+νzγxz.It is possible to describe the linear piezoelectric coupling between the elastic field and an electric field using the direct and reverse piezoelectric equations for the sensor and actuator layers, and the stress-strain relationship can be stated as follows [56, 57] for the sensor and actuator layers:
(7)σxp=Epεxx−e31Ev,τxzp=Gpγxz,Dp=e31εxx+p33Ev,where Ep and νp are, respectively, elastic modulus and Poisson’s ratio of sensor and actuator layers, Dp is the electric displacement component, e31 denotes the piezoelectric stress coefficient, and p33 is the dielectric coefficient. In this study, the influence of the electric field is considered only in the depth direction of the structure. Ev is the electric component, which can be calculated through the change of voltage as [58]
(8)Ev=−ϕhp,where hp is the depth of actuator and sensor layers (hp=ha, hp=hs).The energy of the piezoelectric FG beam resting on Pasternak’s elastic medium is calculatedastic medium is calculated as(9)UEdS=12∫S∑i∫hihi+1σxxF+σxxpTεxx+τxzF+τxzpTγxz-DpTEvdz=12∫S∑i∫hihi+1ε0xTEzε0x+ε0xTzEzε1x+ε0xTz3Ezε3x+ε1xTEzzε0x+ε1xTEzz2ε1x+ε1xTEzz4ε3x+ε3xTEzz3ε0x+ε3xTEzz4ε1x+ε3xTEzz6ε3x+ε0xTEpε0x+ε0xTzEpε1x+ε0xTz3Epε3x+ε1xTEpzε0x+ε1xTEpz2ε1x+ε1xTEpz4ε3x+ε3xTEpz3ε0x+ε3xTEpz4ε1x+ε3xTEpz6ε3xdzdS+12∫S∑i∫hihi+1-e31Evε0x-e31Evzε1x-e31Evz3ε3x-ε0xTe31Ev-ε1xTze31Ev-ε3xTz3e31Ev-Evp33EvdzdS+12∫S∑i∫hihi+1γ0xzTEz21+vzγ0xz+γ0xzTGpγ0xz+γ0xzTEz21+vzz2γ2xz+γ0xzTGpz2γ2xz+γ2xzTEz21+vzz2γ0xz+γ2xzTGpz2γ0xz+γ2xzTEz21+vzz4γ2xz+γ2xzTGpz4γ2xzdS+12∫Skww2+ks∂w∂x2dS+b∫LwTPLdx.where kw and ks are the two parameters of the medium, b is the beam’s width, and PL is the external force operating on the beam.The FG beam rotates along an axisΩ; therefore, the potential energy generated by the structure is computed as follows [22, 59]:
(10)UR=12∫LFηx∂w∂x2dx,where centrifugal force Fη is defined in the following form [22]:
(11)Fη=b∑i∫hihi+1ρz+ρpη2rL−x+12L2−x2dz.In this equation,ρp denotes the mass density of the piezoelectric layers. The beam’s kinetic energy is defined as follows:
(12)K=12∫S∑i∫hihi+1ρz+ρp∂u̇∂tT∂u̇∂t+∂ẇ∂tT∂ẇ∂tdzdS.It is necessary to use Hamilton’s concept to get the natural vibration equation for the piezoelectric FG beam, which may be written as follows:(13)δ∫t1t2K−UE−URodt=0.The beam is divided into two-node elements, each with four degrees of freedom:(14)ψe=∑i=12u0iβxiw0i∂w0∂xi.Interpolation functions such as Lagrange (Ni) and Hermit (Hi) are used to estimate displacements at any point within the beam using nodal displacements as follows:
(15)u0=∑i=12Niu0i=Nuψe,βx=∑i=12Niφxi=Nβψe,w0=∑i=12Hiw0i+Hi+1∂w0∂xi=Hwψe,∂w0∂x=∑i=12∂Hi∂xw0i+∂Hi+1∂x∂w0∂xi=Hw1xψe,∂2w0∂x2=∑i=12∂2Hi∂x2w0i+∂2Hi+1∂x2∂w0∂xi=Hw2xψe.In the matrix form, the following is a more concise version of equation (15):
(16)u=u0βxw0∂w0∂x=NuNβHwHw1x.ψe=Hψ.ψe.The strain components are denoted as follows in relation to the nodal displacement vector:(17)ε0x=∂u0∂x=∂Nu∂xψe=B0xψe,ε1x=∂βx∂x=∂Nβ∂xψe=B1xψe,ε3x=−4z33h2∂βx∂x+∂2w0∂x2=−4z33h2∂Nβ∂x+Hw2xψe=B3xψe,γ0xz=βx+∂w0∂x=Nβ+Hw1xψe=B0γψe,γ2xz=−4h2βx+∂w0∂x=−4h2Nφ+Hw1xψe=B2γψe.According to the following equation, the electric components of the actuator and sensor layers may be computed via two DOFs of the actuator and sensor components:(18)Eva=−1haϕa=Bϕaϕea,Evs=−1hsϕs=Bϕsϕes,in which
(19)Bϕa=−1ha;Bϕs=−1hs.Thus, the energy of an element FG beam is estimated in the following manner:(20)UeE=ψeT12∫Se∑i∫hihi+1B0TEzB0+B0TEzzB1+B0TEzz3B3+B1TEzzB0+B1TEzz2B1+B1TEzz4B3+B3TEzz3B0+B3TEzz4B1+B3TEzz6B3+B0γTEz21+νzB0γ+B0γTEzz221+νzB2γ+B2γTEzz221+νzB0γ+B2γTEzz421+νzB2γ+kwHwTHw+ksHw1xTHw1xdzdSψe+ψeT12∫Se∑i∫hihi+1B0TEpB0+B0TEpzB1+B0TEpz3B3+B1TEpzB0+B1TEpz2B1+B1TEpz4B3+B3TEpz3B0+B3TEpz4B1+B3TEpz6B3dzdSψe+ψeT12∫Se∑i∫hihi+1B0γTGpB0γ+B0γTGpz2B2γ+B2γTGpz2B0γ+B2γTGpz4B2γdzdSψe−ψeT12∫Se−B0Te31Bϕa−B1Tze31Bϕa−B3Tz3e31BϕadSϕea−ψeT12∫Se−B0Te31Bϕs−B1Tze31Bϕs−B3Tz3e31BϕsdSϕes−ϕeaT12∫Se−BϕaTe31B0−BϕaTe31zB1−BϕaTe31z3B3dSψe−ϕesT12∫Se−BϕsTe31B0−BϕsTe31zB1−BϕsTe31z3B3dSψe−12ϕeaT∫SeBϕap33BϕdSϕea−12ϕesT∫SeBϕsp33BϕsdSϕes+ψeTb∫LHwTPLdx.When one rewrites equation (20) in the matrix form, the following equation is obtained:
(21)UeE=12ψeTKeψψe+12ψeTKeψϕaϕea+12ψeTKeψϕsϕes+12ϕeaTKeϕaψψe+12ϕesTKeϕsψψe+12ϕeaTKeϕaϕaϕea+12ϕesTKeϕsϕsϕes+ψeTFe.The energy contained in the centrifugal inertia force is expressed as follows:(22)UeR=12ψe∫LFηxHw1xTHw1xdxψe=12ψeTKeRψe.The piezoelectric FGM beam element’s kinetic energy is calculated as follows:(23)Ke=12∫S∑i∫hihi+1u̇Tρz+ρpu̇dzdS=12ψ̇eT∫S∑i∫hihi+1ρz+ρpHψTHψdzdSψ̇e=12ψ̇eTMeψ̇e,where the element mass matrix is calculated as follows:
(24)Me=∫S∑i∫hihi+1ρz+ρpHψTHψdzdS.Substituting equations (21)–(23) into (13), one obtains the formula for obtaining the natural frequencies of the structure as well as the vibration mode as follows:
(25)Me00000000ψ¨eϕ¨eaϕ¨es+Keψ+KeRKeψϕaKeψϕsKeϕaψKeϕaϕa0Keϕsψ0Keϕsϕsψeϕeaϕes=Fe00.In the case the external forces are ignored, equation (25) becomes
(26)Me00000000ψ¨eϕ¨eaϕ¨es+Keψ+KeRKeψϕaKeψϕsKeϕaψKeϕaϕa0Keϕsψ0Keϕsϕsψeϕeaϕes=000.Then, the reduced equation for the degree of displacement freedom of the beam has the following form:(27)Meψ¨e+Keψ+KeR+KeψϕaKeϕaϕa−1Keϕaψ+KeψϕsKeϕsϕs−1Keϕsψψe=0.Finally, the equation for determining the natural frequencies and the vibrational shapes of the structure is expressed as(28)∑eKeψ+KeR+KeψϕaKeϕaϕa−1Keϕaψ+KeψϕsKeϕsϕs−1Keϕsψ−ω2∑eMe∑eψe0=0.Thus, by using the TSDT, the element stiffness matrix is calculated without the requirement for a shear correction coefficient, precisely simulating the mechanical response of this beam. Additionally, in the above equation, the component of element stiffness is proportional to the rotational speed of the structure, which affects the beam’s mechanical reaction differently than it would be without rotation.The following are the boundary conditions that are described in this work:(i)
Simply supported (denoted by S):(29)u0=0,w0=0.(ii)
Clamped (denoted by C):(30)u0=0,w0=0,ψx=0,∂w0∂x=0.In this work, the S-S and C-C boundaries are utilized in this paper.


## 3. Investigation of Verification

In order to substantiate the hypothesis advanced above, this part presents three instances in which the findings of this study are compared to those of previously published data.Example 1.
At first, this problem compares the data of natural frequencies of the S-S piezoelectric FG (Al/Al2O3) beam. The length of the beam L=1m, thickness h=L/10, and two piezoelectric components have the same depth ha=hs=h/5. Material properties of the FGM core layer: Em=70GPa, ρm=2700kg/m3, Ec=380GPa, and ρc=3800kg/m3. Piezoelectric layers are made from PZT-5H: Ep=127.2GPa, Gp=23GPa, e31=−6.6C/m2, p33=15.1nF/m, and ρa=7500kg/m3. In Table 1, the first two fundamental frequencies of the piezoelectric FG beam calculated using the first-order shear deformation beam theory (FBT), classical beam theory (CBT), sinusoidal shear deformation beam theory (SBT), parabolic shear deformation beam theory (PBT), and exponential shear deformation beam theory (EBT) are presented, in which several various mesh sizes ranging from four to twelve elements are calculated in this study. As the number of pieces in this work rises, it becomes clear that the outcomes of this study are becoming more similar to the published findings. This work makes use of a computer with the following characteristics: a core i5 processor with a processing speed of 1.7 GHz and a RAM speed of 2.7 GHz; the calculation time for each mesh is also provided in Table 1. It has been discovered that as the number of components rises, the time required for computing increases as well.Example 2.
Following that, this example compares the fundamental frequency data of a fully supported Al/Al2O3 beam resting on a two-parameter elastic medium. Geometric and material characteristics are length L, depth h, L/h=100, breadth b, Em=70GPa, ρm=2702kg/m3, Ec=380GPa, and ρc=3960kg/m3. The medium’s two nondimensional frequencies are computed as follows:
(31)K^w=kwL4EmI,K^s=ksL2EmIπ2,where
(32)I=bh312.
The following formula is used to get the beam’s nondimensional natural frequency:(33)ƛ=ωL2hρmEm.Table 1
The first two natural frequencies (Hz) of the piezoelectric FGM, S-S (L=1m, L/h=10).
SourceNumber of elementsComputational time (s)Mode 1Mode 2n=0n=1n=10n=0n=1n=10CBT-Exact [12]——435.309374.916349.6831691.2181453.1801353.334FBT-Exact [12]——428.399368.360339.7931600.4351368.3701230.287PBT-Exact [12]——427.996368.151337.7471594.7831365.4601207.247SBT-Exact [12]——427.979368.172337.6241594.5171365.6881205.928EBT-Exact [12]——427.974368.205337.5291594.3981366.0721204.915This work40.869424.300368.400345.6001683.701458.001264.40060.874423.100367.400344.7001656.101434.201263.20080.884422.600367.200344.6001648.7001427.5001262.800100.941422.500367.000344.3001645.9001425.4001262.600120.995422.500366.900343.5001644.2001423.8001262.400The results in Table2 are derived from the analytical technique [60] and current work, in which the grid sizes for various unique mesh sizes are estimated. As seen in Examples 1 and 2, accuracy converges at the 10-element mesh size. Because of this, this one will be utilized for all further research.Table 2
The nondimensional frequencies (ƛ) of the SS FG beam placed on the two-parameter elastic medium (K^w=10, K^s=1, and L/h=100).
nModeExact solution [60]Present work4 elements6 elements8 elements10 elements12 elementsK¯w=0K¯s=0015.4835.5055.4915.4845.4825.480221.93322.50422.12422.02021.97721.958349.35053.54850.62149.91949.66949.533114.2214.2424.2304.2294.2204.220216.88417.33517.04416.96616.93116.919337.98941.27539.03438.42938.26038.211213.8523.8743.8603.8603.8523.854215.40715.82715.56015.48715.45815.442334.66637.66535.63735.10534.92434.867K¯w=10K¯s=1016.0156.0386.0216.0146.0086.007222.44523.02422.63722.53322.49122.471349.85854.07751.15850.44150.16450.056115.0085.0305.0145.0155.0015.000217.66618.12817.82717.74817.70817.697338.7742.04339.79139.24739.03738.930214.7524.7734.7594.7564.7414.740216.31616.74816.47216.39516.36016.353335.57738.58836.53336.00635.84335.733Example 3.
Finally, the rotating beam’s nondimensional fundamental frequencies as a function of speed are examined. In this computation, a cantilever structure with lengthL, depth h=b=L/100, r=0, massdensity=2700kg/m3, and E=70GPa is used. The frequency is normalized as follows:
(34)℘i=ωiL212ρEh2.The first four nondimensional fundamental frequencies of the structure with several speeds are listed in Table3. They were found using the exact solution [61], the novel dynamic modeling method (DMM) [62], and the isogeometric analysis [22].Table 3
The first four nondimensional fundamental frequencies (℘) of the C-F rotating beam.
Vibration modeSourceSpeedϑℵ=0ℵ=3ℵ=6ℵ=12ω~1Present work3.47874.75387.310413.1661Exact [61]3.51604.79737.360413.1702DMM [62]3.51604.79737.3604—Isogeometric [22]3.51184.77337.3276—ω~2Present work22.108323.381126.812637.5336Exact [61]22.034523.320326.809137.6031DMM [62]————Isogeometric [22]————ω~3Present work62.202663.474867.139979.9519Exact [61]61.697262.985066.684079.6145DMM [62]————Isogeometric [22]————ω~4Present work123.037124.361128.234142.523Exact [61]120.902122.236126.140140.534DMM [62]————Isogeometric [22]————


## 4. Numerical Studies and Comments about the Rotating Piezoelectric FG Beam

The numerical investigations on natural vibration behaviors of rotating piezoelectric FG beams resting on Pasternak’s elastic medium are carried out. Let us consider a beam structure with lengthL, depth h, and the same material characteristics for the FG core layer and the piezoelectric components as in Example 1.The nondimensional natural frequency of the structure is normalized as follows:(35)Γ=ωL212ρ0E0h2,in which, two Pasternak’s elastic medium parameters Kw∗ and Ks∗ and the nondimensional rotational speed θ have the following expressions:
(36)Kw∗=kwL4D0;Ks∗=ksL2π2D0;θ=L2η12ρ0E0h2;D0=Emh312.


### 4.1. Influence of Rotational Speed

To determine the impact of rotational speed on the natural vibration behavior of a rotating piezoelectric FG beam, vary the speedθ between 0 and 15, while maintaining the following parameters: L/h=10, hp/ha=10, Kw∗=10, Ks∗=2, and distance ratio r/L=0. Figure 2 illustrates the first nondimensional fundamental frequency as a consequence of the volume fraction index n and the rotation speed. This finding demonstrates that the nondimensional natural frequency rises as the rotational speed increases. It is stated that when rotational speed rises, the structure’s rigidity increases proportionately to centrifugal force. When the volume fraction index n is increased, the percentage of metal in the structure rises. As the ratio of metal in the structure increases, both the stiffness and mass of the structure drop, with the mass decreasing more than the stiffness. Thus, the natural frequency of the structure drops, but the reduction is not progressive; the greatest fall in the natural frequency of the beam occurs when n is changed from 0 to 2. Additionally, this reduction is very dependent on the boundary conditions; the C-C boundary exhibits a more pronounced drop than the S-S boundary, and when n is larger than 2, both the C-C and S-S instances exhibit a small fall in natural frequency.Figure 2
The subordination of the first nondimensional fundamental frequencies of piezoelectric FG beam on the rotational speed and volume fraction indexn, Kw∗=10, and Ks∗=2.
(a)
S-S(b)
C-CThe influence of the piezoelectric beam’s first five fundamental natural frequencies on the speed is shown in Figure3 for the volume exponent n=0.5. As the rotational speed increases, the degree of expression of the rise in various free vibrations does not remain constant, with the third natural frequency slightly raised and the third natural frequency’s dependent line nearly horizontal.Figure 3
The subordination of the first five nondimensional frequencies of piezoelectric FG beam on the rotational speed,n=0.5, Kw∗=10, and Ks∗=2.
(a)
S-S(b)
C-CFigure4 presents the first four vibrational mode shapes of the piezoelectric FG structure with speeds of 0 and 15; it can be observed easily that the rotational speed has a significant influence on the vibration shapes of the structure. As the speed of rotation is 0, the first natural vibration of the beam is symmetrical through the midposition of the beam (x=L/2); however, for the case of speed θ=15, the vibrational mode shapes of the structure are all deflected to the right side of the beam, that is, away from the axis of rotation. This may be explained by the fact that as the beam rotates at the rotational speed θ, the geometry of the vibration mode is not any clearly symmetric all along the x=L/2 axis and tends to move right of the beam’s center. It is noteworthy that the structure does not exist without axial rotation.Figure 4
The first four vibrational mode shapes of the rotating piezoelectric FG beam (n=10, r=0).
(a)
θ=0(b)
θ=15


### 4.2. Effect of ther/L Ratio

This section evaluates the effect of the distancer between the beam’s endpoint and the fixed axis; this distance value is given incrementally from 0 to 4L; Figure 5 illustrates the subordination of the first four fundamental frequencies on the r/L ratio at various rotational speeds, Figure 6 illustrates the subordination of the first four fundamental frequencies on the r/L ratio and the volume fraction proportion, and Figure 7 illustrates the first four vibrational modes. The numerical findings indicate the following:
(i)
As the distancer rises, the centrifugal force associated with the distance r increases as well, increasing the stiffness of the piezoelectric FG structure and, thus, increasing the frequency of the beam(ii)
For the small values of the rotational speedθ (θ<5), when the distance r increases, the fundamental frequency of the structure increases slightly. Nevertheless, for higher values of the rotational speed θ (θ>5), this distance r greatly affects the natural frequency of this beam(iii)
Figure6 shows that for all the values of the volume fraction proportion n, the subordination of the first fundamental frequency on n with four values of the distance r is nearly identical and parallel to each other. This implies that when r rises, the fundamental frequency of the structure increases proportionately and is independent of the material composition proportions. As for structure subjected to the C-C boundary, this only happens when the volume exponent n>2(iv)
As shown in Figure7, when r rises, the first vibrational mode of the structure’s vibration changes and tends to move to the right. This demonstrates that r influences not only the magnitude of the natural frequency but also the form of the piezoelectric FG beam’s vibration modeFigure 5
The subordination of the first fundamental frequency of the piezoelectric FG beam on the ratior/L and on the rotating speed (n=0.5).
(a)
S-S(b)
C-CFigure 6
The subordination of the first fundamental frequency of the piezoelectric FG beam on the ratior/L and n (θ=10).
(a)
S-S(b)
C-CFigure 7
The first four vibrational shapes of the rotating piezoelectric FG beam (n=10, r=0).
(a)
S-S(b)
C-C


### 4.3. Influence of the Thickness of the Piezoelectric Layerha

Next, this section examines the effect of the thickness of the piezoelectric layer on the vibration behavior of the structure. A piezoelectric FG structure with the ratioL/h=10 is unchanged (i.e., the thickness of the FG core layer does not change), ha is changed so that h/ha gets the values from 8 to 200, Kw∗=10, and Ks∗=2. The subordination of the first natural frequency on the h/ha ratio and the volume fraction index is presented in Figure 8; Figure 9 presents the subordination of the first fundamental frequency on the h/ha ratio and the rotating speed. One can see the following:
(i)
For the S-S boundary, when the depth of the piezoelectric layerha is decreased, the fundamental frequency of the piezoelectric FG structure increases(ii)
For the C-C boundary, when the volume fraction indexn increases gradually from 0 to around 1.2-1.4, the decrease in the thickness ha enhances the fundamental frequency of the structure. When n>1.4, the decrease in the thickness ha reduces the fundamental frequency of the structure. This indicates that there is a suitable value for the volume exponent n and that the fundamental frequency of the piezoelectric FG structure varies very minimally as a function of the depth of the piezoelectric component; i.e., the natural frequency of this beam depends less on the value of the thickness of the piezoelectric layer. This also proves that the boundary constraints and the thickness of the piezoelectricity component both affect the vibration response of this beamFigure 8
The subordination of the first frequencies of the piezoelectric FG structure on the ratioha/h and n, r/L=1, and θ=10.
(a)
S-S(b)
C-CFigure 9
The subordination of the first frequencies of the piezoelectric FG structure on the ratioha/h and θ, r/L=1, and n=5.


### 4.4. Influence of Elastic Foundation

Finally, the impact of the elastic medium on the vibrational behavior of the piezoelectric FG structure is explored in this study. Let us consider a beam with theL/h ratio of 10, h/ha ratio of 10, r/L ratio of 1, and rotating speed θ of 10. Two elastic foundation parameters are modified to progressively rise from 0 to 20, and Ks∗ gets the values in a range of 0 to 10. The dependence of the beam’s first natural frequency is seen in Figure 10. As can be seen, raising the values of two elastic medium parameters raises the piezoelectric FG beam’s inherent frequency. As the elastic medium parameters increase, the energy of the structure increases accordingly and the overall stiffness of the piezoelectric FG structure increases, but the mass of the structure remains unchanged; the frequency of the structure increases.Figure 10
The subordination of the first fundamental frequencies of the piezoelectric FG beam onKw∗ and Ks∗ and h/ha=10.
(a)
S-S(b)
C-C


## 4.1. Influence of Rotational Speed

To determine the impact of rotational speed on the natural vibration behavior of a rotating piezoelectric FG beam, vary the speedθ between 0 and 15, while maintaining the following parameters: L/h=10, hp/ha=10, Kw∗=10, Ks∗=2, and distance ratio r/L=0. Figure 2 illustrates the first nondimensional fundamental frequency as a consequence of the volume fraction index n and the rotation speed. This finding demonstrates that the nondimensional natural frequency rises as the rotational speed increases. It is stated that when rotational speed rises, the structure’s rigidity increases proportionately to centrifugal force. When the volume fraction index n is increased, the percentage of metal in the structure rises. As the ratio of metal in the structure increases, both the stiffness and mass of the structure drop, with the mass decreasing more than the stiffness. Thus, the natural frequency of the structure drops, but the reduction is not progressive; the greatest fall in the natural frequency of the beam occurs when n is changed from 0 to 2. Additionally, this reduction is very dependent on the boundary conditions; the C-C boundary exhibits a more pronounced drop than the S-S boundary, and when n is larger than 2, both the C-C and S-S instances exhibit a small fall in natural frequency.Figure 2
The subordination of the first nondimensional fundamental frequencies of piezoelectric FG beam on the rotational speed and volume fraction indexn, Kw∗=10, and Ks∗=2.
(a)
S-S(b)
C-CThe influence of the piezoelectric beam’s first five fundamental natural frequencies on the speed is shown in Figure3 for the volume exponent n=0.5. As the rotational speed increases, the degree of expression of the rise in various free vibrations does not remain constant, with the third natural frequency slightly raised and the third natural frequency’s dependent line nearly horizontal.Figure 3
The subordination of the first five nondimensional frequencies of piezoelectric FG beam on the rotational speed,n=0.5, Kw∗=10, and Ks∗=2.
(a)
S-S(b)
C-CFigure4 presents the first four vibrational mode shapes of the piezoelectric FG structure with speeds of 0 and 15; it can be observed easily that the rotational speed has a significant influence on the vibration shapes of the structure. As the speed of rotation is 0, the first natural vibration of the beam is symmetrical through the midposition of the beam (x=L/2); however, for the case of speed θ=15, the vibrational mode shapes of the structure are all deflected to the right side of the beam, that is, away from the axis of rotation. This may be explained by the fact that as the beam rotates at the rotational speed θ, the geometry of the vibration mode is not any clearly symmetric all along the x=L/2 axis and tends to move right of the beam’s center. It is noteworthy that the structure does not exist without axial rotation.Figure 4
The first four vibrational mode shapes of the rotating piezoelectric FG beam (n=10, r=0).
(a)
θ=0(b)
θ=15


## 4.2. Effect of ther/L Ratio

This section evaluates the effect of the distancer between the beam’s endpoint and the fixed axis; this distance value is given incrementally from 0 to 4L; Figure 5 illustrates the subordination of the first four fundamental frequencies on the r/L ratio at various rotational speeds, Figure 6 illustrates the subordination of the first four fundamental frequencies on the r/L ratio and the volume fraction proportion, and Figure 7 illustrates the first four vibrational modes. The numerical findings indicate the following:
(i)
As the distancer rises, the centrifugal force associated with the distance r increases as well, increasing the stiffness of the piezoelectric FG structure and, thus, increasing the frequency of the beam(ii)
For the small values of the rotational speedθ (θ<5), when the distance r increases, the fundamental frequency of the structure increases slightly. Nevertheless, for higher values of the rotational speed θ (θ>5), this distance r greatly affects the natural frequency of this beam(iii)
Figure6 shows that for all the values of the volume fraction proportion n, the subordination of the first fundamental frequency on n with four values of the distance r is nearly identical and parallel to each other. This implies that when r rises, the fundamental frequency of the structure increases proportionately and is independent of the material composition proportions. As for structure subjected to the C-C boundary, this only happens when the volume exponent n>2(iv)
As shown in Figure7, when r rises, the first vibrational mode of the structure’s vibration changes and tends to move to the right. This demonstrates that r influences not only the magnitude of the natural frequency but also the form of the piezoelectric FG beam’s vibration modeFigure 5
The subordination of the first fundamental frequency of the piezoelectric FG beam on the ratior/L and on the rotating speed (n=0.5).
(a)
S-S(b)
C-CFigure 6
The subordination of the first fundamental frequency of the piezoelectric FG beam on the ratior/L and n (θ=10).
(a)
S-S(b)
C-CFigure 7
The first four vibrational shapes of the rotating piezoelectric FG beam (n=10, r=0).
(a)
S-S(b)
C-C


## 4.3. Influence of the Thickness of the Piezoelectric Layerha

Next, this section examines the effect of the thickness of the piezoelectric layer on the vibration behavior of the structure. A piezoelectric FG structure with the ratioL/h=10 is unchanged (i.e., the thickness of the FG core layer does not change), ha is changed so that h/ha gets the values from 8 to 200, Kw∗=10, and Ks∗=2. The subordination of the first natural frequency on the h/ha ratio and the volume fraction index is presented in Figure 8; Figure 9 presents the subordination of the first fundamental frequency on the h/ha ratio and the rotating speed. One can see the following:
(i)
For the S-S boundary, when the depth of the piezoelectric layerha is decreased, the fundamental frequency of the piezoelectric FG structure increases(ii)
For the C-C boundary, when the volume fraction indexn increases gradually from 0 to around 1.2-1.4, the decrease in the thickness ha enhances the fundamental frequency of the structure. When n>1.4, the decrease in the thickness ha reduces the fundamental frequency of the structure. This indicates that there is a suitable value for the volume exponent n and that the fundamental frequency of the piezoelectric FG structure varies very minimally as a function of the depth of the piezoelectric component; i.e., the natural frequency of this beam depends less on the value of the thickness of the piezoelectric layer. This also proves that the boundary constraints and the thickness of the piezoelectricity component both affect the vibration response of this beamFigure 8
The subordination of the first frequencies of the piezoelectric FG structure on the ratioha/h and n, r/L=1, and θ=10.
(a)
S-S(b)
C-CFigure 9
The subordination of the first frequencies of the piezoelectric FG structure on the ratioha/h and θ, r/L=1, and n=5.


## 4.4. Influence of Elastic Foundation

Finally, the impact of the elastic medium on the vibrational behavior of the piezoelectric FG structure is explored in this study. Let us consider a beam with theL/h ratio of 10, h/ha ratio of 10, r/L ratio of 1, and rotating speed θ of 10. Two elastic foundation parameters are modified to progressively rise from 0 to 20, and Ks∗ gets the values in a range of 0 to 10. The dependence of the beam’s first natural frequency is seen in Figure 10. As can be seen, raising the values of two elastic medium parameters raises the piezoelectric FG beam’s inherent frequency. As the elastic medium parameters increase, the energy of the structure increases accordingly and the overall stiffness of the piezoelectric FG structure increases, but the mass of the structure remains unchanged; the frequency of the structure increases.Figure 10
The subordination of the first fundamental frequencies of the piezoelectric FG beam onKw∗ and Ks∗ and h/ha=10.
(a)
S-S(b)
C-C


## 5. Conclusions

This work combines the finite element method and the third-order shear deformation theory of Reddy to simulate the free vibration responses of the rotating piezoelectric FG structure resting on the two-parameter elastic medium. The numerical investigations show numerous novel phenomena, and some remarkable points can be pointed out as follows:(i)
As the rotational speed increases, the centrifugal force becomes greater and the fundamental frequency of the piezoelectric FG beam rises. Besides, the vibrational mode shapes of the structure change impressively as the speed rises; they tend to deviate significantly to the right side of theL/2 position(ii)
As the distance from the endpoint of the beam to the rotation axis of the beamr is increased, the fundamental frequency of the beam increases due to the increase in the whole stiffness of the beam(iii)
When the depth of the piezoelectric component is reduced, the boundary conditions significantly affect the fundamental frequency response of the piezoelectric FG beam. For the S-S case, the fundamental frequency increases as the thickness of the piezoelectric layer decreases. However, under the C-C case, there will exist a value of volume exponentn whose natural frequency is almost constant with different values of the depth of the piezoelectric layer(iv)
As the values of the elastic foundation become greater, the natural frequency of the beams increasesThe above computed results show that the vibration response of the piezoelectric beam rotating around one fixed axis is different from that of the beam without rotation phenomenon because of the centrifugal inertia force generated by the rotational motion. This is a scientific basis for the design and use of beams with rotational motion in practice, taking into account the sensitivity of the speed parameter to the behavior of the rotating beam.



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*Source: 9998691-2022-01-28.xml*