AAVAdvances in Acoustics and Vibration1687-627X1687-6261Hindawi Publishing Corporation50190210.1155/2010/501902501902Research ArticleFrequency Equations for the In-Plane Vibration of Circular Annular DisksBashmalS.BhatR.RakhejaS.Ayala BottoMiguelDepartment of Mechanical and Industrial EngineeringConcordia University1455 De Maisonneuve Bloulevard W., Montreal, QCCanadaH3G 1M8concordia.ca20100408201020102310200923062010250620102010Copyright © 2010 S. Bashmal et al.This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.

This paper deals with the in-plane vibration of circular annular disks under combinations of different boundary conditions at the inner and outer edges. The in-plane free vibration of an elastic and isotropic disk is studied on the basis of the two-dimensional linear plane stress theory of elasticity. The exact solution of the in-plane equation of equilibrium of annular disk is attainable, in terms of Bessel functions, for uniform boundary conditions. The frequency equations for different modes can be obtained from the general solutions by applying the appropriate boundary conditions at the inner and outer edges. The presented frequency equations provide the frequency parameters for the required number of modes for a wide range of radius ratios and Poisson's ratios of annular disks under clamped, free, or flexible boundary conditions. Simplified forms of frequency equations are presented for solid disks and axisymmetric modes of annular disks. Frequency parameters are computed and compared with those available in literature. The frequency equations can be used as a reference to assess the accuracy of approximate methods.

1. Introduction

The out-of-plane vibration properties of circular disks subjected to a variety of boundary conditions have been extensively investigated (e.g., ). The in-plane vibration analyses of circular disk, however, have been gaining increasing attention only in the recent years. Much of the interest could be attributed to important significance of the in-plane vibration in various practical problems such as the vibration of railway wheels, disk brakes, and hard disk drives contributing to noise and structural vibration .

The in-plane vibration of circular disks was first attempted by Love  who formulated the equations of motion for a thin solid circular disk with free outer edge together with the general solution. The equations of motion were subsequently solved by Onoe  to obtain the exact frequency equations corresponding to different modes of a solid disk with free outer edge. Holland  evaluated the frequency parameters and the corresponding mode shapes for a wide range of Poisson’s ratios and the vibration response to an in-plane force. The in-plane vibration characteristics of solid disks clamped at the outer edge have been investigated in a few recent studies. Farag and Pan  evaluated the frequency parameters and the mode shapes of in-plane vibration of solid disks clamped at the outer edge using assumed deflection modes in terms of trigonometric and Bessel functions. Park  studied the exact frequency equation for the solid disk clamped at the outer edge.

The in-plane vibration analyses in the above reported studies were limited to solid disks with either free or clamped outer edge. The in-plane free vibration of annular disks with different boundary conditions has also been addressed in a few studies. The variations in the in-plane vibration frequency parameters of annular disks with free edges were investigated as function of the size of the opening by Ambati et al. . The variation ranged from a solid disk to a thin ring, while the validity of the analytical results was demonstrated using the experimental data. Another study investigated the free vibration and dynamic response characteristics of an annular disk with clamped inner boundary and a concentrated radial force applied at the outer boundary . Irie et al.  investigated the modal characteristics of in-plane vibration of annular disks using transfer matrix formulation while considering free and clamped inner and outer edges.

The above reported studies on in-plane vibration of solid and annular disks have employed different methods of analyses. The finite-element technique has also been used to examine the validity of analytical methods (e.g., [11, 14]). The exact frequency equations of in-plane vibration, however, have been limited only to solid disks. Such analyses for the annular disks pose more complexities due to presence of different combinations of boundary conditions at the inner and outer edges. This study aims at generalized formulation for in-plane vibration analyses of circular annular disks under different combinations of clamped, free, or flexible boundary conditions at the inner and outer edges. The equations of motion are solved for the general case of annular disks. The exact frequency equations are presented for different combinations of boundary conditions, including the flexible boundaries, for various radius ratios, while the solid disk is considered as special cases of the generalized formulation.

2. Theory

The equations of the in-plane vibration of a circular disk are formulated for an annular disk shown in Figure 1. The disk is considered to be elastic with thickness h, outer radius b and inner radius a. The material is assumed to be isotropic with mass density ρ, Young's modulus E, and Poisson ratio v. The equations of dynamic equilibrium in terms of in-plane displacements along the radial and circumferential directions can be found in many reported studies (e.g., [11, 16]). These equations of motion in the polar coordinate system (r,θ) can be written as 2urt2-CL2[2urr2+1rurr-urr2]-CT2r22urθ2-CT21r1+v1-v2uθrθ+CT21r23-v1-vuθθ=0,2uθt2-CT2[2uθr2+1r  uθr-uθr2]-CL2r22uθθ2-CT21r1+v1-v2urrθ+CT21r23-v1-vurθ=0, where ur and uθ are the radial and circumferential displacements, respectively, along the r and θ directions, CL2=E/ρ(1-v2) and CT2=E/2ρ(1+v).

Geometry and coordinate system used for in-plane vibration analysis of an annular disk.

Following Love’s theory , the radial and circumferential displacements can be expressed in terms of the Lamé Potentials ϕ and ψ , asur=1b(ϕξ+1ξψθ),uθ=1b(1ξϕθ-ψξ), where ξ=r/b.

Assuming harmonic oscillations corresponding to a natural frequency ω, the potential functions ϕ and ψ can be represented by ϕ(ξ,θ,t)=Φ(ξ)cosnθsinωt,ψ(ξ,θ,t)=Ψ(ξ)sinnθsinωt, where n is the circumferential wave number or nodal diameter number. Upon substituting for ur and uθ in terms of ξ, Φ, and Ψ from (2) to (5), in (1), the equations of motion reduce to the following uncoupled form:2Φ=-λ12Φ,2Ψ=-λ22Ψ, where λ1 and λ2 are nondimensional frequency parameters defined asλ12=ω2(1-v2)ρb2E,λ22=2ω2(1+v)ρb2E,2=2ξ2+1ξξ-n2ξ2.

Equations (6) and (7) are the parametric Bessel equations and their general solutions are attainable in terms of the Bessel functions as  Φ={AnJn(λ1ξ)+BnYn(λ1ξ)},Ψ={CnJn(λ2ξ)+DnYn(λ2ξ)}, where Jn  and  Yn are the Bessel functions of the first and second kind of order n, respectively, and An,Bn,Cn, and Dn are the deflection coefficients.

The radial and circumferential displacements can then be expressed in terms of the Bessel functions by substituting for Φ and Ψ in (2) and (3). The resulting expressions for the radial and circumferential displacements can be expressed as: ur=1b{nξAnXn(λ1ξ)+BnZn(λ1ξ)+nξ[CnJn(λ2ξ)+DnYn(λ2ξ)]}cosnθsinωt,uθ=-1b{nξCnXn(λ2ξ)+DnZn(λ2ξ)+nξ[AnJn(λ1ξ)+BnYn(λ1ξ)]}sinnθsinωt, whereXn(λiξ)=ξJn(λiξ)=-nξJn(λiξ)+λiJn-1(λiξ),Zn(λiξ)=ξYn(λiξ)=(-nξYn(λiξ)+λiYn-1(λiξ)),i=1,2.

2.1. Free and Clamped Boundary Conditions

Equations (11) represent the solutions for distributions of the radial and circumferential displacements for the general case of an annular disk. The evaluations of the natural frequencies and arbitrary deflection coefficients (An,Bn,Cn and Dn), however, necessitate the consideration of the in-plane free vibration response under different combinations of boundary conditions at the inner and the outer edges. For the annular disk clamped at the outer edge (ξ=1), the application of boundary conditions (ur=0 and uθ=0) must satisfy the following for the general solutions (11): AnXn(λ1)+BnZn(λ1)+n[CnJn(λ2)+DnYn(λ2)]=0,CnXn(λ2)+DnZn(λ2)+n[AnJn(λ1)+BnYn(λ1)]=0.

In a similar manner, the solution must satisfy the following for the clamped inner edge (ξ=β), where β=a/b is the radius ratio between inner and outer radii of the disk: AnXn(λ1β)+BnZn(λ1β)+nβ[CnJn(λ2β)+DnYn(λ2β)]=0,CnXn(λ2β)+DnZn(λ2β)+nβ[AnJn(λ1β)+BnYn(λ1β)]=0. The conditions involving at the free edges are satisfied when the radial (Nr) and circumferential (Nrθ) in-plane forces at the edge are zero , such thatNr=-Eh(1-v2)b[urξ+vξuθθ+vξuξ]=0,Nrθ=-Eh2(1+v)b[1ξurθ+uθξ-uθξ]=0. A direct substitution of ur and uθ from (11) in the above equations would result in second derivatives of the Bessel functions. Alternatively, the above equation for the boundary conditions may be expressed in terms of Φ and Ψ through direct substitution of ur and uθ from (2) and (3), respectively. The boundary conditions in terms of Nr can thus be obtained as(2Φξ2+nξΨξ-nξ2Ψ)-n2vξ2Φ-nvξΨξ+vξ(Φξ+nξΨ)=0. Rearranging (19) results in(2ξ2+vξξ-n2vξ2)Φ+(1-v)(nξξ-nξ2)Ψ=0. The second order derivative term (2Φ/ξ2) in (20) can be eliminated by adding and subtracting the term ((1/ξ)(/ξ)-(n2/ξ2)+λ12)Φ, which yields[(2ξ2+1ξξ-n2ξ2+λ12)-(1ξξ-n2ξ2+λ12)+vξξ-n2vξ2]Φ+(1-v)(nξξ-nξ2)Ψ=0. From (6), it can be seen that the terms within the first parenthesis are identically equal to zero. Equation (21) describing the boundary condition associated with Nr can be further simplified upon substitutions for λ12=λ22(1-v)/2, which yields (n2ξ2-1ξξ-12λ22)Φ+n(1ξξ-1ξ2)Ψ=0. Similarly, the boundary condition equation associated with Nrθ (18) can be simplified as2nξ(-ξ+1ξ)Φ+(2ξξ-2n2ξ2+λ22)Ψ=0. Upon substitutions for Φ and Ψ from (16) in (26) and (27), the boundary condition equations for the free edges are obtained, which involve only first derivatives of the Bessel functions. For an annular disk with free inner and outer edges, (22) and (23) represent the conditions at both the inner and the outer boundaries (ξ=1   and ξ=β). The equations for the free edge boundary conditions can be expressed in the matrix form in the four deflection coefficients, as[(n2-λ222)Jn(λ1)-Xn(λ1)(n2-λ222)Yn(λ1)-Zn(λ1)nXn(λ2)-nJn(λ2)nZn(λ2)-nYn(λ2)2nJn(λ1)-2nXn(λ1)2nYn(λ1)-2nZn(λ1)2Xn(λ2)-(2n2-λ22)Jn(λ2)2Zn(λ2)-(2n2-λ22)Yn(λ2)(n2β2-λ222)Jn(λ1β)-1βXn(λ1β)(n2β2-λ222)Yn(λ1β)-1βZn(λ1β)nβXn(λ2β)-nβ2Jn(λ2β)nβZn(λ2β)-nβ2Yn(λ2β)2nβ2Jn(λ1β)-2nβXn(λ1β)2nβ2Yn(λ1β)-2nβZn(λ1β)2βXn(λ2β)-(2n2β2-λ22)Jn(λ2β)2βZn(λ2β)-(2n2β2-λ22)Yn(λ2β)]×{AnBnCnDn}={0}. The determinant of the above matrix yields the frequency equation for the annular disk with free inner and outer edge conditions.

For the clamped inner and outer edges, the equations for the boundary conditions can be obtained directly from (13) to (16), such that [Xn(λ1)Zn(λ1)nJn(λ2)nYn(λ2)nJn(λ1)nYn(λ1)Xn(λ2)Zn(λ2)Xn(λ1β)Zn(λ1β)nβJn(λ2β)nβYn(λ2β)nβJn(λ1β)nβYn(λ1β)Xn(λ2β)Zn(λ2β)]{AnBnCnDn}={0}. In the above equations, (24) and (25), the top two rows describe the boundary condition at the outer edge, while the bottom two rows are associated with those at the inner edge. The equations for the boundary conditions involving combinations of free and clamped edges can thus be directly obtained from the above two equations. For the free inner edge and clamped outer edge, denoted as “free-clamped” condition, the matrix equation comprises the tip two rows of the matrix in (25) and the lower two rows from (24). For the clamped inner edge and free outer edge, denoted as “Clamped-Free” condition, the matrix equation is formulated in the similar manner using the lower and upper two rows from (25) and (24), respectively.

The in-plane vibration analysis of a solid disk can be shown as a special case of the above generalized formulations. Upon eliminating the coefficients associated with Bessel function of the second kind, Equations (24) and (25) reduce to those reported by Onoe  for free solid disk and by Park  for the clamped solid disk. The frequency equation corresponding to different values of n for the solid disks involving the two boundary conditions are summarized in Table 1, where Xn(λ1) is the derivative of the Bessel function Jn evaluated at the outer edge (ξ=1). For annular disks, simplified frequency equations can be obtained for the axisymmetric modes. These equations where expressed in Table 2 for the four combinations of boundary conditions.

Frequency equations for the solid disks corresponding to free and clamped edge conditions.

 Boundary conditions at ξ=1 Clamped Free n=0 Radial J1(λ1)=0 λ1J0(λ1)=(1-v)J1(λ1) Circumferential J1(λ2)=0 λ2J0(λ2)=2J1(λ2) n=1 Xn(λ1)Xn(λ2) = n2Jn(λ1)Jn(λ2) [X1(λ2)J1(λ1)]+[X1(λ1)J1(λ2)]=(2-(λ22/2))J1(λ2)J1(λ1) n>1 [Xn(λ2)-QJn(λ2)][Xn(λ1)-QJn(λ1)]=n2(Q-1)2 where Q=λ22/2(n2-1)

Frequency equations of axisymmetric modes for annular disks.

 Boundary conditions radial Circumferential inner outer Clamped Clamped J1(λ1)Y1(λ1β)-J1(λ1β)Y1(λ1)=0 J1(λ2)Y1(λ2β)-J1(λ2β)Y1(λ2)=0 Free Free [(-λ1/(1-v))J0(λ1)+J1(λ1)][(-λ1/(1-v))Y0(λ1β)+(1/β)Y1(λ1β)]-λ1/(1-v)Y0(λ1)+Y1(λ1)[(-λ1/(1-v))J0(λ1β)+(1/β)J1(λ1β)]=0 [-2J1(λ2)+λ2  J0(λ2)][-(2/β)Y1(λ2β)+λ2Y0(λ2β)]-[-(2/β)J1(λ2β)+λ2J0(λ2β)][-2Y1(λ2)+λ2Y0(λ2)]=0 Clamped Free [(λ1/(1-v))J0(λ1)-J1(λ1)]Y1(λ1β)-J1(λ1β)[(λ1/(1-v))Y0(λ1)-Y1(λ1)]=0 [2J1(λ2)-λ2J0(λ2)]Y1(λ2β)-J1(λ2β)[2Y1(λ2)-λ2Y0(λ2)]=0 Free Clamped J1(λ1)[(-λ1/(1-v))Y0(λ1β)+(1/β)Y1(λ1β)]+[(-λ1/(1-v))J0(λ1β)+(1/β)J1(λ1β)]Y1(λ1)=0 J1(λ2)[-  (2/β)Y1(λ2β)+λ2Y0(λ2β)]-[-(2/β)J1(λ2β)+λ2J0(λ2β)]Y1(λ2)=0
2.2. Flexible Boundary Conditions

In the above analysis, the boundary conditions considered are either clamped or free. However, Flexible boundary conditions may be considered more representative of many practical situations. The proposed formulations can be further employed to study the in-plane vibration of solid as well as annular disks with flexible boundary conditions. Artificial springs may be applied to describe the flexible boundary conditions at the inner or the outer edge of an annular disk. A number of studies on the analysis of out-of-plane vibration characteristics of circular plates and cylindrical shells have employed uniformly distributed artificial springs around the edge to represent a flexible boundary conditions or a flexible joint .

The effects of flexible boundary conditions on the in-plane free vibration of circular disks have been considered in a recent study by the authors  using the Rayleigh-Ritz approach. Artificial springs, distributed along the radial and circumferential directions at the free outer and/or inner edges, were considered to simulate for flexible boundary conditions. The exact solution of the frequency equations for the disk with flexible supports can be attained from (11) together with the consideration of the flexible boundary conditions. The conditions involving flexible edge supports at the inner and outer edges are satisfied when the radial (Nr) and circumferential (Nrθ) in-plane forces at the edges are equal to the respective radial and circumferential spring forces, such thatNr=-Eh(1-v2)b[  urξ+vξuθθ+vξur]=Krur(ξ,θ),Nrθ=-Eh2(1+v)b[1ξurθ+uθξ-uθξ]=Kθuθ(ξ,θ), where Kr and Kθ are the radial and circumferential stiffness coefficients, respectively. Introducing the nondimensional stiffness parameters, K̅r=Krb(1-v2)/Eh and K̅θ=Kθb(1+v)/Eh, (26) can be written as(n2ξ2-1ξξ-12λ22+K̅rξ)Φ+n(1ξξ-1ξ2+1ξK̅r)Ψ=0,n(1ξξ-1ξ2-1ξK̅θ)Φ+(n2ξ2-1ξξ-12λ22-K̅θξ)Ψ=0. The application of the above conditions yields the matrix equations for the disk with flexible supports at the inner and outer edges, similar to (24). The frequency parameters are subsequently obtained through solution of the matrix equations. The above boundary equations reduce to those in (22) and (23) for the free edge conditions by letting K̅r=0 and K̅θ=0. Furthermore, the clamped edge condition can be represented by considering infinite values of K̅r and K̅θ. Equations (27) further show that the flexible edge support conditions involve combinations of the free and clamped edge conditions.

3. Results

The frequency parameters (λ1) derived for different combinations of boundary conditions are compared with those reported in different studies to demonstrate the validity of the proposed formulation. For this purpose, the frequency parameters of a solid disk with free and clamped outer edge are initially evaluated and compared with those reported by Holland  and Park , respectively. The results presented in Tables 3 and 4 for the free and clamped outer edge conditions, respectively, were found to be identical to those reported in [10, 12] for solid disks with clamped edge.

Exact frequency parameters of in-plane vibration of a solid disk with free edge (v=0.3).

Moden=1n=2n=3n=4
11.61761.38772.13042.7740
23.52912.51123.45174.4008
34.04744.52085.34926.1396
45.88615.20296.36957.4633
56.91136.75497.61868.5007
67.79808.26399.347010.2350
79.65948.73429.836611.0551

Exact frequency parameters of in-plane vibration of a solid disk with clamped edge (v=0.33).

Moden=1n=2n=3n=4
11.94413.01853.01854.7021
23.11264.01274.01275.8985
34.91045.73985.73987.3648
45.35706.70796.70798.9816
56.77637.64427.64429.5296
68.49389.43569.435611.1087
78.64589.98949.989412.5940

The exact frequency parameters for the annular disks were subsequently obtained under different combinations of boundary conditions at the inner and outer edges. The edge conditions are presented for the inner followed by that of the outer edge. For instance, a “Free-Clamped” condition refers to free inner edge and clamped outer edge. The solutions obtained for conditions involving free and clamped edges (“Free-Free”, “Free-Clamped”, “Clamped-Clamped”, and “Clamped-Free”) are compared with those reported by Irie et al.  in Tables 5, 7, 8, 9, respectively. The simulations results were obtained for two different values of the radial ratios (β=0.2 and 0.4), and v=0.3. The results show excellent agreements of the values obtained in the present study with those reported in , irrespective of the boundary condition and radius ratio considered.

Frequency parameters of in-plane vibration of an annular disk with “Free-Free” conditions.

 Radius ratio (β) n=1 n=2 n=3 n=4 Reference  present study Reference  Present study Reference  Present study Reference  Present study 0.2 1.652 1.651 1.110 1.110 2.071 2.071 2.767 2.766 3.842 3.842 2.403 2.402 3.401 3.400 4.389 4.388 0.4 1.683 1.682 0.721 0.721 1.618 1.619 2.482 2.482 4.044 4.044 2.451 2.450 3.346 3.346 4.227 4.226

Frequency parameters of in-plane vibration of an annular disk with “Free-Clamped” conditions.

 Radius ratio (β) n=1 n=2 n=3 n=4 Reference  Present study Reference  Present study Reference  Present study Reference  Present study 0.2 2.104 2.103 2.553 2.553 3.688 3.688 4.712 4.711 3.303 3.302 3.948 3.948 4.859 4.858 5.894 5.893 0.4 2.517 2.517 2.721 2.721 3.214 3.214 3.955 3.956 3.508 3.508 4.147 4.147 4.998 4.998 5.874 5.873

Frequency parameters of in-plane vibration of an annular disk with “Clamped-Clamped” conditions.

 Radius ratio (β) n=1 n=2 n=3 n=4 Reference  present study Reference  present study Reference  present study Reference  present study 0.2 2.783 2.783 3.378 3.378 4.066 4.065 4.802 4.800 4.060 4.060 4.360 4.359 5.104 5.103 6.003 6.001 0.4 3.429 3.429 4.023 4.022 4.707 4.707 5.287 5.286 5.306 5.306 5.311 5.311 5.619 5.619 6.289 6.288

Frequency parameters of in-plane vibration of an annular disk with “Clamped-Free” conditions.

 Radius ratio (β) n=1 n=2 n=3 n=4 Reference  present study Reference  present study Reference  present study Reference  present study 0.2 0.919 0.919 1.542 1.541 2.157 2.157 2.778 2.777 2.121 2.121 2.605 2.604 3.473 3.472 4.408 4.406 0.4 1.281 1.281 1.965 1.964 2.445 2.445 2.911 2.911 2.691 2.691 2.908 2.907 3.604 3.603 4.492 4.491

Frequency parameters of in-plane vibration of an annular disk with flexible boundary conditions.

 Boundary conditions n=1 n=2 n=3 n=4 Reference  present study Reference  present study Reference  present study Reference  present study Elastic-Free 0.771 0.771 1.408 1.408 2.121 2.121 2.772 2.772 1.906 1.906 2.524 2.524 3.444 3.444 4.397 4.397 Elastic-Clamped 2.590 2.590 3.117 3.116 3.928 3.926 4.759 4.760 3.625 3.625 4.134 4.136 5.000 5.001 5.957 5.957 Elastic-Elastic 1.494 1.492 1.815 1.813 2.474 2.472 3.123 3.120 2.603 2.601 3.209 3.207 4.004 4.002 4.859 4.857 Free-Elastic 1.040 1.046 1.505 1.504 2.414 2.416 3.114 3.116 2.432 2.432 3.018 3.018 3.895 3.896 4.833 4.834 Clamped-Elastic 1.686 1.686 1.960 1.959 2.514 2.512 3.129 3.127 2.764 2.765 3.319 3.317 4.061 4.060 4.879 4.877

The exact frequency parameters of the annular disk are further investigated for boundary conditions involving different combinations of free, clamped, and elastic edges. The solutions corresponding to selected modes are obtained for (“Elastic-Free”, “Elastic-Clamped”, “Elastic-Elastic”, “Free-Elastic”, and “Clamped-Elastic”) conditions are presented in Table 9. The results were attained for β=0.2 and v=0.3. The nondimensional radial and circumferential stiffness parameters were chosen as K̅r=1 and K̅θ=1. The results are also compared with those obtained using the Raleigh-Ritz methods, as reported in . The comparisons reveal very good agreements between the analytical and the reported results irrespective of the boundary condition considered. The results suggest that the proposed frequency equations could serve as the reference for approximate methods on in-plane vibration characteristics of the annular disks with different combinations of edge conditions.

4. Conclusions

The characteristics of in-plane vibration for circular disks are investigated under different combinations of boundary conditions. The governing equations are solved to obtain the exact frequency equation of solid and annular disks. Frequency equations are presented for different combinations of boundary conditions, including flexible boundaries, at the inner and outer edges. The nondimensional frequency parameters obtained by the present approach compare very well with those available in literature, irrespective of the boundary condition and radius ratio considered. The exact frequency parameters can serve as a reference to assess the accuracy of approximate methods. The presented frequency equations can be numerically evaluated to obtain the in-plane modal characteristics of circular disk for a wide range of constraints conditions and geometric parameters.

NomenclatureAn,Bn,Cn,Dn:

Deflection coefficients of the exact solution

a:

Inner radius of the annular disk

b:

Outer radius of the annular disk

CL2:

E/ρ(1-v2)

CT2:

E/2ρ(1+v)

E:

Young’s modulus of disk

h:

Thickness of the annular disk

Jn(ξ):

Bessel function of the first kind of order n

Kr,Kθ:

K̅r,K̅θ:

Nondimensional radial and circumferential stiffness parameters

n:

Nodal diameter number

Nr,Nrθ:

r:

ur,uθ,uz:

Radial, circumferential, and normal displacements of the disk

Yn(ξ):

Bessel function of the second kind of order n

z:

Normal coordinate

β:

θ:

Circumferential coordinate

λ:

Nondimensional frequency parameters

v:

Poisson’s ratio

ξ:

Nondimensional radial coordinate of the disk

ρ:

Mass density of the disk

ϕ,ψ:

Lamé Potentials

Φ,Ψ: