# Vibration of Elastic Functionally Graded Thick Rings

Authors: Guang-Hui Xu; Huai-Wei Huang; Yong-Qiang Zhang
Journal: Shock and Vibration
 (2017)

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## Abstract

The free vibration behaviors of functionally graded rings were investigated theoretically. The material graded in the thickness direction according to the power law rule and the rings were assumed to be in plane stress and plane strain states. Based on the first-order shear deformation theory and the kinetic relation of von Kárman type, the frequency equation for free vibration of functionally graded ring was derived. The derived results were verified by those in literatures which reveals that the present theory can be appropriate to predict the free vibration characteristics for quite thick rings with the radius-to-thickness ratio from 60 down to 2.09. Comparison between the plane stress case and the plane strain case indicates a slight difference. Meanwhile, the effects of the structural dimensional parameters and the material inhomogeneous parameter are examined. It is interesting that the value of the logarithmic form of vibration frequency is inversely proportional to the logarithmic form of the radius-to-thickness ratio or the mean radius.


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## Body

## 1. Introduction

Circular ring structures are widely employed in industrial systems. Their applications can be found in planetary gears, rotors, gyroscopic actuators, measuring instruments, and hollow axle used on subway and high-speed trains. Their mechanical performances have been investigated extensively, among which the vibration characteristics are one of the most important aspects [1–7].Matsunaga [1] presented an approximate theory to study the effects of higher-order deformations on natural frequencies and buckling critical loads of a thick circular ring with rectangular cross-sections. Wong et al. [2] considered in-plane vibration problem for thermoelastic damping rings. Lacarbonara et al. [7] analyzed flexural vibration problem of elastic circular rings considering nonlinearity of structural deformation.The new emergence of ceramic/metallic compound functionally graded materials (FGMs) has attracted tremendous research interests on vibration characteristics for their plate and shell structures [8–10]. For FGM rings, Filipich et al. [11] introduced a general model for FGM thick arches or rings under transient forced vibration conditions. Wang and Luo [12] presented an exact solution for the electromechanical vibration of FGM piezoelectric ring transducers. Among these works, the free vibration behaviors of FGM circular rings under either the plane stress or plane strain states have yet not been investigated.In this paper, free vibration characteristics of FGM ring under either the plane stress or plane strain states were investigated by using the first-order shear deformation theory. The accuracy of the present theory was well verified through the free vibration frequencies of homogeneous rings. It reveals that the present theory can be appropriate to predict the free vibration characteristics for the quite thick ring with the radius-to-thickness ratio from 60 down to 2.09. Meanwhile, the effects of the structural dimensional parameters and the material inhomogeneous parameter are examined.


## 2. Formulation

The geometry and the coordinate system are illustrated in Figure1, in which the coordinate system is represented by r-θ-x. R is the mean radius, and h and b are, respectively, the thickness in r and x directions. z indicates the distance measure from the geometrical middle plane of the ring and we have z=r-R.Figure 1
The geometry and the coordinate system of FGM rings.FGMs are usually prepared by mixing ceramic and metallic constituents. The volume fraction of one of the constituentsfii=corm through the thickness h submits to a power law rule [8] and the elastic material properties Pz, representing the elastic modulus Ez and the poison ratio νz, can be expressed as the weight average of their constituents.(1)fi=0.5+zhk,fc+fm=1,P=Pmfm+Pcfc,where the subscripts c and m denote, respectively, the ceramic and metallic constituents and f and P are the volume fraction and the material properties. Herein, the FGM ring with metallic internal surface is named Type I configuration, in which i=c, while the FGM ring with ceramic internal surface is named Type II configuration, in which i=m.For the plane strain rings,εxx=0, and for the plane stress rings, σxx=0. Thus, the general constitutive relation of FGM rings can be obtained as (2)σxxσθθτrθ=C12C13C22C23C32C33εθθγrθ,where (3)C12C13C22C23C32C33=ϑEν1-ν201-ϑE+ϑE1-ν200E21+νand ϑ=0,1 respectively, indicate the plane stress state and the plane strain state.The kinetic relation of von Kárman type reads in the following form [14] with the subscript comma representing partial derivative.(4)εθθ=V,θ+Wr+W,θ-V22r2,γrθ=W,θ-Vr+V,r,in which, the circumferential displacement Vθ,z,t and the radial displacement Wθ,z,t can be expressed as the following form according to the first-order shear deformation theory [15]. t is time.(5)V=v+zφ,W=w,where vθ,t, wθ,t, and φθ,t are, respectively, the circumferential, radial, and angle displacements on the geometrical middle plane. Generally, r≈R, z/R≪1; thus we have(6)εθθγrθ=εθθ0γrθ0+zεθθ10,where (7)εθθ0=v,θ+wR+w,θ-v/R22,εθθ1=φ,θR,γrθ0=φ+w,θ-vR.The internal forceN and shear force Q, as well as the internal moment M, can be obtained as follows:(8)NMQT=∫-h/2h/2σθθzσθθKsτrθTdz,where Ks=5/6 is the shear correction factor. Submitting (6) into (2) and then into (8) derives(9)NMQ=C220C221C230C221C222C231C320C321C330εθθ0εθθ1Ksγrθ0,where Cijl=∫-h/2h/2zlCijdzi,j=2,3,l=0,1,2.According to the principle of virtual displacement, the virtual potential energyδU should vanish at the equilibrium state of the system. (10)δU=δUin-δUke=0in which (11)δUin=∫0b∫02π∫-h/2h/2σθθδεθθ+KsτrθδγrθdzRdθdxδUke=∫0b∫02π∫-h/2h/2ρR+z×w,tδw,t+v,tδv,t+h212φ,tδφ,tdzdθdx,where ρz is the density of FGMs. After integration, we have (12)δUin=bR∫02πNδεθθ0+Mδεθθ1+Qδγrθ0dθ,δUke=bρ^∫02πw,tδw,t+v,tδv,t+h2φ,tδφ,t12dθ,where ρ^=∫-h/2h/2ρR+zdz. Then (10) turns into(13)∫02πRNδεθθ0+Mδεθθ1+Qδγrθ0-ρ^w,tδw,t+v,tδv,t+h2φ,tδφ,t12dθ=0.The above relation should hold for arbitrary virtual displacementsδw, δv, and δφ which reaches the dynamic equilibrium equation set of FGM rings, by combining the virtual form of εθθ0, εθθ1, and γrθ0 with (11) and then utilizing the procedure of part integration.(14)Nw,θ-v,θR-N+Q,θ=ρ^w,tt,N,θ+Q+Nw,θ-vR=ρ^v,tt,M,θ-RQ=h2ρ^φ,tt12.With the aid of (9), the above dynamic equilibrium equations can be expressed by displacement components.(15)C330KsRφ+w,θ-v,θ-C220w+v,θ-C221φ,θ=Rρ^w,tt,C330KsRφ+w,θ-v+C220w+v,θ,θ+C221φ,θθ=Rρ^v,tt,-C330KsRRφ+w,θ-v+C221w+v,θ,θ+C222φ,θθ=Rh2ρ^φ,tt12.


## 3. Solving of the Problem

Herein, the vibration modal functions are set as the following form:(16)w=ξwsinnθeiωt,v=ξvcosnθeiωt,φ=ξφcosnθeiωt,where ξw, ξv, and ξφ are the unknown amplitudes and n is the wave number. ω=2πf is the angle frequency.By substituting (16) into (15), one obtains (17)χ11χ12χ13χ12χ22χ23χ13χ23χ33+Rω2ρ^10001000h212ξwξvξφ=0in which(18)χ11=-C220-n2C330Ks,χ12=nC220+C330Ks,χ13=nC221-RC330Ks,χ22=-n2C220-C330Ks,χ23=-n2C221-RC330Ks,χ33=-n2C222-R2C330Ks.From (17), the zero value of the determinant of the coefficient matrix leads to the frequency equation for FGM rings, a six-degree polynomial, which can be used to solve for the free vibration frequency of FGM rings(19)∑j=03γjω2j=0.


## 4. Verification

To verify the present theoretical results, Table1 lists comparisons of the present theoretical results with the theoretical and experimental results in literatures with regard to homogeneous rings and the results from ANSYS simulation.Table 1
Verification of free vibration frequency [Hz].
n Bisegna and Caruso [3] ANSYS The present theory Plane stress Plane stress Plane strain 2 36.78 35.10 35.08 36.77 3 104.03 99.29 99.19 103.98 4 199.46 190.42 190.13 199.3 5 322.57 308.05 307.35 322.16  n Exp. of Kuhl [13] Kirkhope [13] The present theory Plane stress Plane strain  2 7635 7527 7300 7566 3 19060 19122 18269 18830 4 32150 32529 30898 31694 5 46050 46614 114803 45246 6 60400 60857 57997 59068 7 74200 75045 71828 72962 8 88000 89104 85673 86838For moderate FGM rings withR/h=60, the present plane stress results are in excellent agreement with the results from ANSYS, and the present plane strain results are well verified by the results from Bisegna and Caruso [3]. For thick FGM rings with R/h=2.09, the present plane strain results are close to the theoretical predictions of Kirkhope [13] and the experimental results of Kuhl listed in [13]. The maximal difference of the present plane strain results from the experimental ones is only −2.2%. Since both the cases R/h=60 and 2.09 indeed stand for a moderate thick and even quite thick rings, the present theories are appropriate to predict the free vibration characteristics for FGM rings of thick configuration.


## 5. Result Analyses

The following calculations are presented for rings made from Si3N4/SUS304 FGMs, with the material properties given as(20)ρm=8166kg/m3,Em=107GPa,νm=0.34,ρc=2370kg/m3,Ec=375GPa,νc=0.14.For briefness, the calculation parameters are listed in all the following figures as well. Figure2 shows the vibration modes under different values of the modal parameter n. In the figure, n=0 represents an undeformed ring, and n=1 indicates a rigid body displacement. For Type I FGM rings, Figure 3 shows the effect of the modal parameter on the free vibration frequency f. The vibration frequency (plotted in the logarithmic form) increases dramatically with the increasing value of n. The lowest value of vibration frequency generally corresponds to a low order vibration mode, that is, n=2, which is the first concern for engineering structures. Comparison between the plane stress and the plane strain cases reveals that the vibration frequency in the plane strain case is slightly higher than that in the plane stress case.Figure 2
The vibration mode of FGM rings (n=0,1,2,…,7).Figure 3
Effect of the modal parameter on vibration frequency.The changing rules of the vibration frequency versus different values ofR/h are illuminated in Figure 4(a), where both the horizontal and the longitudinal coordinates are given in the logarithmic form. It is obvious that the value of the logarithmic f is inversely proportional to the logarithmic value of R/h. Similarly, when the value of R/h is set to be 50, Figure 4(b) shows that the logarithmic value of f is also inversely proportional to the logarithmic value of R.Figure 4
Dimensional effect on vibration frequency.
(a) (b)By considering both Type I and Type II configurations of FGM rings, Figure5 provides the relation of the vibration frequency versus the inhomogeneous parameter k. For Type I FGM rings, the vibration frequency increases with the rising value of k, while, for Type II ones, there is an opposite tendency.Figure 5
Effect of the inhomogeneous parameter on the vibration frequency for the plane stress case.As the aforementioned, the vibration frequency of FGM rings in the plane strain case is usually larger than that in the plane stress case. To quantitatively determine the deviations between them, Figure6 plots the differences versus the dimensional parameter R/h, the inhomogeneous parameter, and the modal parameter as well. As shown, the differences under different value of n tend to be a constant 3.4% when R/h≥50. In the case of thick rings with 3≤R/h<50, the differences range from 2.5% to 3.5%. The difference between them increases with the rising value of k. For a nearly pure ceramic ring with k=0.001, it tends to be 1%, but for a nearly pure metallic ring with k=1000, it is up to 6.2%.Figure 6
Differences of the vibration frequencies between the plane strain and the plane stress cases.
(a) (b)


## 6. Concluding Remark

This paper is addressed for free vibration characteristics of FGM rings under either the plane stress or the plane strain cases; the frequency equation is derived based on the first-order shear deformation theory and the kinetic relation of von Kárman type. Results well agree with those in literatures and ANSYS simulation. It is also shown that the vibration frequency of FGM rings under the plane strain case is slightly higher than that under the plane stress case, and it increases dramatically with the rising modal parameter. Under a given value of radius, the vibration frequency decreases sharply with the increase of radius-to-thickness ratio, and the value of the logarithmic vibration frequency is inversely proportional to the logarithmic value of radius-to-thickness ratio. Under a given value of the radius-to-thickness ratio, the vibration frequency also decreases sharply with the increase of the mean radius. For Type I FGM rings, the vibration frequency increases with the rising value of the inhomogeneous parameter, while, for Type II ones, there is an opposite tendency.



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*Source: 1803710-2017-02-16.xml*