Effect of linear variation in density and circular variation in Poisson’s ratio on time period of vibration of rectangular plate

Anup Kumar1 , Neeraj Lather2 , Reeta Bhardwaj3 , Naveen Mani4 , Amit Sharma5

1, 2, 3, 5Amity University Haryana, Gurgaon, India

4Sandip University, Nashik, Maharashtra, India

5Corresponding author

Vibroengineering PROCEDIA, Vol. 21, 2018, p. 14-19. https://doi.org/10.21595/vp.2018.20367
Received 2 November 2018; accepted 14 November 2018; published 13 December 2018

Copyright © 2018 Anup Kumar, 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.
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Abstract.

In this paper, a theoretical analysis is carried out to investigate the effect of linear variation in density and circular variation in Poisson’s ratio on time period of frequency modes of rectangular plate with variable thickness under temperature field. The thickness variation is considered to be circular and temperature variation on the plate is assumed to be bi-linear. Rayleigh Ritz method is used to solve the differential equation. All the results (time period for first two modes of vibration) are presented with the help of tables.

Keywords: density, Poisson’s ratio, rectangular plate, time period.

1. Introduction

The study of vibration of non-homogeneous plate is essential in these days because non-homogeneous plate with variable thickness are used in almost all engineering structures such as power plants, wings of an aircrafts, machines, bridges etc. Plates with variable thickness along with non-homogeneity have great impact when compared to homogeneous plate with uniform thickness because of their efficiency and strength. The first few modes of vibration provide us good information about the behavior of systems/structures. Therefore, in order to design perfect structures/systems, it is essential to determine natural frequencies and mode shapes. A significant work has been reported in these directions.

The natural vibration of cantilever plates with variable thickness is analyzed by using mixed boundary grid method (FBGM) [1] and obtained characteristic equation and frequency parameters. A model [2] is presented to analyze the nonlinear vibrations of visco elastic thin rectangular plates by using von Kármán nonlinear strain–displacement relationships and obtained fundamental modes of a simply supported square plate with immovable edges. The nonlinear damping of visco elastic rectangular plate [3] is studied and equation of motion is derived using Lagrange equations. The results are also obtained theoretically as well as experimentally. Vibration analysis of rectangular plates with rectangular cutouts is investigated by using extended Hencky bar-net method (HBM) [4]. Method of reverberation ray matrix (MRRM) and golden section search (GSS) algorithm [5] is applied to obtain the exact solution of rectangular plates with arbitrary boundary conditions. Accurate analytic solutions for natural vibration of thick rectangular plates with a free edge is presented in [6]. Natural vibration of thick rectangular plate [7] without two parallel simply supported edges is studied and new analytic solutions are obtained. The effect of crack defects and temperature on vibration of thin isotropic and orthotropic rectangular plates is studied in [8]. The effect of circular variation in density and exponential variation in Poisson’s ratio on vibrational frequency of parallelogram plate under temperature field is examined in [9]. The effect of two-dimensional thickness and temperature effect on natural vibration of parallelogram plate on clamped edges is studied using Rayleigh Ritz method [10]. Rayleigh Ritz method [11] is used to analyze the natural vibration of isotropic rectangular plate with circular variation in thickness and exponential variation in Poisson’s ratio under temperature field. Free vibration of moderately thick laminated composite rectangular plate with non-uniform boundary conditions is presented by using an improved Fourier series method [12]. Closed-form solution [13] is presented to study the effects of rotary inertia and shear deformation on frequency of natural vibration problems. A mathematical model [14] is presented to analyze the free vibration of rectangular plates with various rectangular cutouts and variable thickness.

In this study, authors show the effect of linear variation in density and circular variation in Poisson’s ratio on time period of vibration of non homogeneous rectangular plate on clamped edges. Authors also calculate the time period of vibration corresponding to circular variation in thickness and bi linear variation in temperature. The results are presented with the help of tables.

2. Analysis and assumptions

The differential equation for transverse motion of the plate with variable D1 and ν i.e., flexural rigidity and Poisson’s ratio is given by:

(1)
D 1 4 Φ ζ 4 + 2 4 Φ ζ 2 ψ 2 + 4 Φ ψ 4 + 2 ν ζ 2 2 Φ ψ 2 + 2 D 1 ζ 3 Φ ζ 3 + 3 Φ ζ ψ 2 + ν ζ 2 Φ ψ 2
          + 2 D 1 ζ 2 2 Φ ζ 2 + ν 2 Φ ψ 2 + 2 D 1 ψ 3 Φ ψ 3 + 3 Φ ψ ζ 2 - ν ζ 2 Φ ζ ψ
          + 2 D 1 ψ 2 2 Φ ψ 2 + ν 2 Φ ζ 2 + 2 1 - ν 2 D 1 ζ ψ 2 Φ ζ ψ - ρ l ω 2 Φ = 0 ,

where Φis known as deflection function. The expression for flexural rigidity is D1=El3/121-ν2, where E, l are known as Young’s modulus and thickness of the plate.

In order to avoid complexity, the present study requires some assumptions as:

a) Since the plate has variable thickness l, therefore authors considered one dimensional circular variation in thickness as shown in Fig. 1 as:

(2)
l = l 0 1 + β 1 - 1 - ζ 2 a 2 ,

where β, (0 ≤ β ≤ 1) is known as tapering parameter. Thickness of plate becomes constant at ζ= 0.

b) For non-homogeneity consideration, authors assumed one dimensional linear variation in density and one dimensional circular variation in Poisson’s ratio as:

(3)
ρ = ρ 0 1 + m 1 ζ a ,
(4)
ν = ν 0 1 - m 2 1 - 1 - ζ 2 a 2 ,

where m1, (0 ≤ m1 ≤ 1) and m2, (0 ≤ m2 < 1) are known as non-homogeneity constants corresponding to density and Poisson’s ratio.

c) The plate is subjected to steady two-dimensional linear temperature distributions as:

(5)
τ = τ 0 1 - ζ a 1 - ψ b ,

where τ and τ0 denotes the temperature excess above the reference temperature on the plate at any point and at the origin respectively. The temperature dependence modulus of elasticity for engineering structures is given by:

(6)
E = E 0 1 - γ τ ,

where E0 is the Young’s modulus at mentioned temperature (i.e., τ= 0) and γ is called slope of variation.

Using Eq. (5), Eq. (6) becomes:

(7)
E = E 0 1 - α 1 - ζ a 1 - ψ b ,

where α, (0 ≤ α < 1) is called temperature gradient, which is the product of temperature at origin and slope of variation i.e., α=γτ0.

Fig. 1. Rectangular plate with one dimensional circular variation

 Rectangular plate with one dimensional circular variation

3. Solution for frequency equation and time period

We are using Rayleigh Ritz technique (i.e., maximum strain energy Vs must equal to maximum kinetic energy Ts) in order to obtain frequency equation and time period for both modes of vibrations. Therefore, we must have:

(8)
δ V s - T s = 0 .

Here the expression for Vs and Ts are given by:

(9)
V s = 1 2 0 a     0 b D 1 × 2 Φ ζ 2 2 + 2 Φ ψ 2 2 + 2 ν 2 Φ ζ 2 2 Φ ψ 2 + 2 1 - ν 2 Φ ζ ψ 2 d ψ d ζ ,
(10)
T s = 1 2 ω 2 0 a   0 b ρ l Φ 2 d ψ d ζ .

Here, we are computing time period on C-C-C-C condition (i.e., all the four edges are clamped), therefore the boundary conditions are:

(11)
Φ ζ , ψ = Φ ζ , ψ ζ = 0 ,         ζ = 0 ,   a ,           Φ ζ , ψ = Φ ζ , ψ ψ = 0 ,       ψ = 0 ,   b .

Therefore, deflection function (i.e., maximum displacement) which satisfy boundary condition given in Eq. (11) is taken as:

(12)
Φ ζ , ψ = ζ a 2 ψ b 2 1 - ζ a 2 1 - ψ b 2 Ω 1 + Ω 2 ζ a ψ b 1 - ζ a 1 - ψ b ,

where Ω1 and Ω2 are arbitrary constants.

Now converting ζ and ψ into non-dimensional variable as:

(13)
ζ 1 = ζ a ,       ψ 1 = ψ a .

Using Eqs. (2)-(4), (7), (9), (10) and (13), Eq. (8) becomes:

(14)
δ V s * - λ 2 T s * = 0 ,

where:

V s * = 0 1 0 b a 1 - α 1 - ζ 1 1 - a ψ 1 b 1 + β 1 - 1 - ζ 1 2 3 1 - ν 0 2 1 - m 2 1 - 1 - ζ 1 2 2
          2 Φ ζ 1 2 2 + 2 Φ ψ 1 2 2 + 2 ν 0 1 - m 2 1 - 1 - ζ 1 2 2 Φ ζ 1 2 2 Φ ψ 1 2 + 2 1 - ν 0 1 - m 2 1 - 1 - ζ 1 2 2 Φ ζ 1 ψ 1 2 d ψ 1 d ζ 1 ,
T s * = 0 1   0 b a 1 + m 1 ζ 1 1 + β 1 - 1 - ζ 1 2 Φ 2 d ψ 1 d ζ 1 ,

and λ2=12ρ0ω2a4/E0l02 is known as frequency parameter. Eq. (14) consists of two unknown constants Ω1 and Ω2 (because of substitution of deflection function Φζ,ψ). These two unknowns could be calculated as follows:

(15)
Ω n V s * - λ 2 T s * = 0 ,       n = 1,2 .

After simplifying Eq. (15), we get system of homogeneous equations as:

(16)
c 11 Ω 1 + c 12 Ω 2 = 0 , c 21 Ω 2 + c 22 Ω 2 = 0 .

To obtain non-zero solution (frequency equation), the determinant of coefficient matrix obtain from Eq. (16) must be zero i.e.,

(17)
c 11 c 12 c 21 c 22 = 0 .

From Eq. (17), we get a quadratic equation from which we get frequency modes.

The time period of frequency modes is calculated as:

(18)
K = 2 π λ ,

where λ is frequeny modes obtained from Eq. (17).

4. Results and discussion

The effect of variation of different plate parameters (non-homogeneity constants m1, m2, thermal gradient α and tapering parameter β) on time period (in seconds) of vibrations are calculated for fixed value of aspect ratio a/b= 1.5 and presented in tabular form.

Table 1 provides the time period K of vibration corresponding to non-homogeneity m1 for two cases i.e., β=m2=α= 0.2 and β=m2=α= 0.6. From Table 1, we can see that time period is increasing with the increasing value of non-homogeneity constant m1 for both the cases. While the time period is decreasing with the combined increasing value of taper constant β, non-homogeneity m2 and thermal gradient α.

Table 2 accommodates the time period K corresponding to non-homogeneity constant m2 for two different cases i.e., m1=β=α= 0.2 and m1=β=α= 0.6. Here, time period is increasing (almost constant) for first case. But for second case, time period is increasing for first mode and time period is decreasing for second mode. The time period is also decreasing when the combined value of thermal gradient α, taper constant β and non-homogeneity constant m1 varies from 0.2 to 0.6.

Table 1. Non-homogeneity m1 vs. time period K[s] for a/b= 1.5

m 1
α = β = m 2 = 0.2
α = β = m 2 = 0.6
λ 1
λ 2
λ 1
λ 2
0.0
0.02214
0.08729
0.01848
0.07226
0.2
0.02323
0.09157
0.01941
0.07584
0.4
0.02428
0.09566
0.02030
0.07925
0.6
0.02528
0.09959
0.02115
0.08253
0.8
0.02646
0.10336
0.02197
0.08568
1.0
0.02717
0.10701
0.02276
0.08872

Table 2. Non-homogeneity m2 vs. time period K[s] for a/b= 1.5

m 2
α = β = m 1 = 0.2
α = β = m 1 = 0.6
λ 1
λ 2
λ 1
λ 2
0.0
0.02322
0.09155
0.02113
0.08272
0.2
0.02323
0.09157
0.02114
0.08269
0.4
0.02324
0.09158
0.02114
0.08263
0.6
0.02325
0.09156
0.02115
0.08253
0.8
0.02326
0.09151
0.02115
0.08239

Table 3. Taper constant β vs. time period K[s] for a/b= 1.5

β
α = m 1 = m 2 = 0.4
α = m 1 = m 2 = 0.8
λ 1
λ 2
λ 1
λ 2
0.0
0.02837
0.11209
0.03252
0.12384
0.2
0.02492
0.09815
0.02851
0.11193
0.4
0.02211
0.08677
0.02524
0.09864
0.6
0.01979
0.07741
0.02256
0.08776
0.8
0.01786
0.06963
0.02033
0.07877
1.0
0.01623
0.06310
0.01846
0.07125

Table 4. Thermal gradient α vs. time period K[s] for a/b= 1.5

α
β = m 1 = m 2 = 0.4
β = m 1 = m 2 = 0.8
λ 1
λ 2
λ 1
λ 2
0.0
0.02107
0.08273
0.01848
0.07183
0.2
0.02157
0.08468
0.01890
0.07339
0.4
0.02211
0.08677
0.01934
0.07505
0.6
0.02269
0.08903
0.01982
0.07684
0.8
0.02333
0.09148
0.02033
0.07877

Time period K corresponding to taper constant β is tabulated in Table 3 for the two different cases i.e., m1=m2=α= 0.4 and m1=m2=α= 0.8. Time period is decreasing with the increasing value of taper constant β for both the cases. When we move from first case to second case, the time period is increasing with the increasing value of taper constant β.

Table 4 presents the time period K corresponding to thermal gradient α for two different cases i.e., m1=m2=β= 0.4 and m1=m2=β= 0.8. From Table 4, we conclude that time period is increasing with the increasing value of thermal gradient α for both the cases and decreasing with the combined increasing value of taper constant β and non-homogeneity constants m1, m2.

5. Conclusions

The present study reveals the effect of plate parameters especially density and Poisson’s ratio on time period of vibration of clamped rectangular plate with variable thickness under temperature field. The rate of increment in time period corresponding to non-homogeneity m1 (linear variation) is higher than the rate of increment in time period corresponding to non-homogeneity m2 (circular variation). Initially, time period (at m2= 0) is high in case of circular variation in non-homogeneity when compared to time period (at m1= 0) in case of linear variation in non-homogeneity. The time period is decreasing corresponding to circular variation in thickness and increasing corresponding to linear temperature variation on plate.

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