Document Type : Research Article
Authors
Department of Mechanical Engineering, Faculty of Engineering, Arak University, Arak, 3815688349, Iran
Abstract
Keywords
Sensitivity Analysis of Vibrating Laminated Composite Rectangular Plates in Interaction with Inviscid Fluid Using EFAST Method
K. Khorshidi^{*}, M. Taheri, M. Ghasemi
Department of Mechanical Engineering, Faculty of Engineering, Arak University, Arak, 3815688349, Iran.
Keywords 

ABSTRACT 
Vibration Sensitivity analysis Laminate composite plate FSI Inviscid fluid 
This work investigates the sensitivity analysis of vibrating laminated composite rectangular plates in interaction with inviscid fluid using the modified higherorder shear deformation plate theory. The EFAST method which is based on variance and is independent of any assumption of linearity and uniformity between inputs and outputs is utilized for sensitivity analysis of laminated composite rectangular plates. Theoretical formulations, both for the laminated rectangular plates in interaction with inviscid, incompressible and irrotational fluid and the sensitivity analysis technique are summarized here. A Cartesian coordinate system is used to describe governing equations of fluidstructure interaction. Hamilton's variational principle is used to derive the Eigen problem of the complex system. A numerical investigation is carried out by using the Galerkin method and the boundary conditions of the plate are simply supported. A set of admissible displacement functions which satisfy identically the geometric boundary conditions are used to calculate the wet natural frequencies of the plate. In the numerical examples, the effect of the aspect ratio, thickness ratio and material orthotropy orientation of the plate, depth ratio and width of the fluid on the fundamental natural frequency of the vibrating laminated composite rectangular plates are examined and discussed. 
The extent to which a fluid can play a role in vibrational behavior of a structure continues to be an issue of interest to researchers. The existence of fluid around a structure changes the kinetic energy of the system and influences the natural frequencies and mode shapes[1, 2]. Hence, knowing about the dynamic response of the structure in contact with the fluid is necessary for various areas of engineering such as submarines, shipbuilding, nuclear, hydrodynamics and ocean engineering. Commonly, to analyze the frequency response of a structure in contact with a fluid is generally known as fluidstructure interaction (FSI). Widely analyzing FSI problems can be categorized into three methods: firstly, numerical methods such as the boundary element method and secondly, the fluid finite element method which needs a large number of computations and can be applied to numerous FSI problems [319]. In addition, sensitivity analysis (SA) investigates how the variation in the output of a numerical model can be attributed to variations of its input factors [20]. Sensitivity analysis is increasingly being used in environmental modeling for a variety of purposes, including uncertainty assessment, model calibration and diagnostic evaluation, dominant control analysis, and robust decisionmaking. Furthermore, sensitivity analysis is increase also being used in statics and dynamics modeling for a variety of scientific and engineering purposes, including vibrational behavior of structures, control analysis of systems, evaluation of material strengths in different conditions, etc. Numerous studies have been performed to investigate the sensitivity analysis of vibrating structures. Khedmati et al. [21] studied the sensitivity analysis of elastic buckling of a cracked plate with simply supported plates, subjected to an axial compressive edge load using the finite element method. Afonso and Hinton [22] used an automated approach to carry out sensitivity analysis and to obtain optimum shapes for plates and shells in which the natural frequencies were maximized. Akoussan et al. [23] proposed a high order continuous sensitivity analysis of the damping properties of viscoelastic composite plates according to their layers thicknesses. Chen and Tan[24], Fung and Chen [25], and Chen and Hsu [26], employing Galerkin and the Runge–Kutta method, presented the imperfection sensitivity of nonlinear vibration of a simply supported ceramic/metal functionally graded plate in a general state of arbitrary initial stresses. ŁaseckaPlura and Lewandowski [27], using EulerBernoulli theory considered the sensitivity analysis of dynamic characteristics of composite beams with viscoelastic layers. In this study, the fractional Zener model was used to express the viscoelastic material properties.in another study, Kotełko et al. [28], presented a sensitivity analysis of thinwalled boxsection girders subjected to pure bending based on the methodology of the MonteCarlo method. Lima et al. [29], also developed the formulation of firstorder sensitivity analysis of complex frequency response functions (FRFs) for composite sandwich plates composed by a combination of fiberreinforced and elastomeric viscoelastic layers, in arrangements that were frequently used for noise and vibration attenuation. Research by Takezawa and Kitamura [30] studied the sensitivity analysis of objective functions including the eigenmodes of continuum systems using scalar Helmholtz equations. Additionally, Li et al. [31] proposed the sensitivityanalysis of vibroacoustic systems by using the interval perturbation method compared with the Monte Carlo method. Li and Liu [32], developed a threedimensional semianalytical model for the static response and sensitivity analysis of the composite stiffened laminated plate with interfacial imperfections. Li et al. [33], investigated the free vibration analysis and eigenvalues sensitivity analysis of composite laminates with interfacial imperfection based on the radial point interpolation method (RPIM) in the Hamilton system. Liu [34], described an analytical method to calculate the sensitivity of the frequencies and modes with respect to fiber Vol. fractions and orientations, for the largescale composite laminated structures with complex boundaries. Furthermore, Hu et al. [35], studied an explicit timedomain method for sensitivity analysis of structural responses under nonstationary random excitations. Yan and Cheng [36], analyzed the sensitivity of residual vibrations of structures subject to impacts using an adjoint method. In other publications, Choi and Byun [37], presented an effective sensitivity analysis algorithm for free vibration of a rectangular plate structure by using the finite elementtransfer stiffness coefficient method. Liu and Paavola [38] also described a general analytical sensitivity analysis method for the composite laminated plates and shells, which was applied to both classical and firstorder shear deformation theories and based on the finite element methods. Li et al. [39], studied the linear statics and free vibration sensitivity analysis of the composite sandwich plates based on a layerwise/solidelement method (LW/SE).
The main purpose of this paper is to present an analytical model for sensitivity analysis of vibrating laminated composite rectangular plates in interaction with inviscid fluid using modified higherorder shear deformation plate theory. Various plate theories are used to model the structure. Governing equations are derived using Hamilton’s principle and solved with the Galerkin method. Using the EFAST method sensitivity of fundamental natural frequency is obtained. After validation, influences of the aspect ratio, thickness ratio and material orthotropy orientation of the plate, depth ratio and width of the fluid on the wet fundamental natural frequencies of the plate are illustrated.
Consider a laminated composite rectangular plate with length , width , total thickness , and elastic orthotropic layers, which is a part of the vertical side of a bounded rigid tank filled with a fluid, as shown in Fig. 1. The tank contains fluid that has width , depth and mass density of fluid . The fluid is considered incompressible, inviscid and irrotational. A Cartesian coordinate system is used to describe governing equations. The coordinate system is placed so that the origin is located in the corner of the studied plate on its middle surface, while axes and lie on the plate’s edges and axis z is perpendicular to the middle plane.
Fig. 1. Platefluid interaction, Coordinates and dimensions
The constitutive equations for kth orthotropic lamina of the plate, in the material principal coordinates, under the hypothesis , are given by:

(1) 
where superscript (k) refers to the kth layer within a laminate, and are the normal stresses and strains, respectively, and are the shear stresses and strains, respectively, and s are transformed material constants and defined by
(2) 
in which:
(3) 

(4) 


where is the lamina material orthotropy orientation, G_{12}, G_{13} and G_{23} are the shear moduli in 12, 13 and 23 directions, respectively, and the coefficients c_{ij} are given by
(5) 

Equation (1) is obtained (i) under the transverse isotropy assumption with respect to planes parallel to the 23 plane, i.e., assuming fibers in the direction parallel to axis 1, so that E_{2} = E_{3}, G_{12} = G_{13} and n_{12} = n_{13}, and (ii) solving the constitutive equations for e_{zz} as function of e_{xx}and e_{yy} and then eliminating it. Three independent displacements variables u_{0}, v_{0} and w_{0} in x, y and z directions, respectively, are used to describe middle surface deformations of the plate. The displacements , , of a generic point of the plate at distance from the plane (see Fig.1) are related to the middle surface displacements u_{0}, v_{0} and w_{0} by:
(6) 

(7) 

(8) 
where and are the rotations of the transverse normals about the y and x axes, respectively, and for exponential, trigonometric and hyperbolic shear deformation plate theories are given by
Exponential SDPT 
(9) 


Trigonometric SDPT 
(10) 
Hyperbolic SDPT 
(11) 
The linear straindisplacement equations for the modify higher order shear deformation plate theory are given by
(12) 

(13) 

(14) 

(15) 

(16) 
The elastic strain and kinetic energies of the plate, including rotary inertia, are given by
(17) 

(18) 
where is the mass density of the kth layer of the plate and the overdot denotes time derivative. The total kinetic energy of the fluid with respect to the bulging modes of the plate and the fluid sloshing can be written[1, 2]
(19) 

(20) 
where and are fluid potential velocity relating to bulging modes and sloshing modes, respectively.

(21) 
(22) 

where is the unknown coefficients related to fluid sloshing; and express the number of necessary terms to get desirable accuracy. Furthermore, are Fourier coefficients associated with the bulging modes


(23) 

, , and are nonnegative integers. Moreover, Using the assumption of linearized sloshing [1, 2] at the free surface of fluid leads to
(24) 
In which g is the acceleration of gravity and is the wet natural frequency of platefluid interaction.
Hamilton’s principle is employed to obtain the governing equations and associated boundary conditions of the system as follows
(25) 
In which is variation operator. Now by inserting Eqs. (17), (18), (19) and (20) into Eq. (25) and then integrating by parts and setting the coefficients of , , , and to zero, boundary conditions and governing equations in terms of stress resultants can be derived as follows
(26) 

(27) 

(28) 

(29) 

(30) 

(31) 
where
(3237) 

(3843) 

(4449) 

(5055) 

(60) 
Governing equation systems (26)(30) cannot be solved unless unknown coefficients are determined. Hence, linear sloshing equation (31) must be added to Eqs. (26)(30) as the seventh equation. For the sake of simplicity, the lefthand side of Eqs. (26)(31) are denoted as (i=1,2,..6) respectively. So applying the Galerkin method to Eqs. (26)(31) leads to
(61) 

(62) 

(63) 

(64) 

(65) 

(66) 
According to the Galerkin method, unknown functions of , , , and propose in the following form
(67) 

(68) 

(69) 

(70) 

(71) 
where and indicate truncated orders of series. , , , and are undetermined coefficients which are calculated after minimizing residuals. , , , and are independent functions which satisfy at least essential boundary conditions. For simply supported boundary conditions , , , and can be written as
(72) 

(73) 

(74) 

(75) 

(76) 
m and n are numbers of halfwaves along x and y axis, respectively. After solving the above equations, one can find natural frequencies and mode shapes which are related to the eigenvalues and eigenfunctions of the system.
One of the parts of general sensitivity analysis techniques that has attracted more attention is the variancebased techniques. In these techniques, the sensitivity index is computed as the share of each parameter in the overall output variance of the model. The general sensitivity analysis techniques are implemented in four steps: (1) defining the inputs and the type of distribution of each input, (2) generating the samples for the input values, (3) computing the model’s output for each set of input samples and (4) determining the effect of each input factor on the output [40]. In this section, the variancebased sensitivity analysis techniques have been reviewed. The variancebased general sensitivity analysis approaches can be used to obtain the firstorder effect and the secondorder effect (which include the interaction between other parameters) [41].
Moreover, the Sobol method [42] is a modelindependent general sensitivity analysis technique which is based on variance analysis. This method can be used for nonlinear and nonuniform functions and models. For the model defined by function , where is the model output and is the vector of input parameters, Sobol’ suggested to decompose the function f into summands of increasing dimensionality, where the integral of each term over its own input variables is zero. Sobol showed that, when all the inputs were perpendicular to one another, this resolution was unique and the output variance of the model (V) was the set of variances of each resolved term [42]:
(77) 
In Eq. (77), denotes the firstorder effect for each input factor and to indicate the interactions between n factors. Therefore, the shares allocated to parameters, and the interactions of parameters can be determined from the total output variance. The sensitivity index is obtained as the ratio of each order’s variance to the total variance variance ( denotes the firstorder sensitivity index, represents the secondorder sensitivity index, and so on). The total sensitivity index (i.e., the overall effect of each parameter) is obtained as the summand of all the orders of sensitivity index for that parameter [42]:
(78) 
The general equation has been presented by Sobol in 1990, which will be given as follows [43]:
(79) 

(80) 
f_{0} can be defined as:
(81) 
Sobol showed that all the terms of f(X) could be calculated through multiple integrals:
(82) 

(83) 
Sensitivity index based on variance can be obtained as follows:
(84) 
In which D is the variance of .
Sensitivity value can be obtained by dividing of every group of variables variance to total variance.
It should be noted that any professional and official titles or academic degrees (Dr, chief, sir) must not show in Author details. In addition, first name should be written in abbreviation and family name in complete form.
(85) 
is the first order sensitivity index for factor which presents the sensitivity effect of parameter on output and is the second order sensitivity index which shows the interaction effect on total variance.
(86) 
Total sensitivity index is a summation of all the sensitivity indices.
The EFAST method was presented by Cukier et al.[44] and was later improved by Saltelli et al. [45] Like the Sobol method, this approach is also based on variance and it is independent of any assumption of linearity and uniformity between inputs and output(s). Contrary to the Sobol method, which uses multidimensional integrals to obtain the total variance and the partial variances, this method converts the multidimensional integrals to onedimensional ones by defining a transfer function and simplifies the procedure for the calculation of sensitivity indexes.
The EFAST method searches the ndimensional space of the input factors (Unit Hypercube ) by using a Search Curve defined by a set of parametric equations [45]:
(87) 
Where is the frequency related to factor , s is a variable that changes from –π to +π, and specifies the starting point of the curve. The output variance of the model is approximated by means of Fourier analysis:
(88) 
In the above equation , G(s) are the transfer functions, and and are the Fourier coefficients . By calculating the Fourier coefficients for the basic frequency and its higher harmonics , the partial firstorder input variance can be obtained.
(89) 
Also, like the Sobol method, the ratio of the firstorder partial variance to total variance is used to compute the main sensitivity index. The total sensitivity index is obtained from Eq. (82)[46]:
(90) 
variance is obtained by changing all the parameters except parameter .
The Sobol method employs the Monte Carlo integral to obtain each partial variance; and in comparison, with the EFAST method, it does not use a transfer function; that is why, it has a low computational efficiency.
In this section, the wet natural frequency parameters are obtained from the Galerkin method for the free vibrations of a laminated composite rectangular plate interacting with the bounded fluid. Numerical results have been performed for simply supported boundary conditions. Materials chosen for the plate is graphite/epoxy with the material properties; Poisson’s ratio , , , and . Calculations have been performed for 4 layers symmetric laminated plates ( / / / ). Presented results are obtained for the thickness ratios , aspect ratios , material orthotropy orientation , depth of the fluid ratios and width of the tank . Also, fluid density is considered as .
The comparison of the fundamental wet natural frequencies of the simply supported laminated composite plates obtained by Galerkin method are compared with those of Khorshidi and Farhadi [2] which are based on third order shear deformation plate theory (TSDT) and finite element analysis are presented in Table 1 for different thickness ratios including , 0.1 and 0.2. In Table 1, the numerical results are obtained for a four layer (0º/90º)s squared plate with different depth of the fluid which is varies from 0 to 1. This comparison confirmed reliability of the proposed method and those that were presented by Khorshidi and Farhadi [2].
In this section, the effects of the various parameters such as aspect ratio (a/b), thickness ratio (h/a), material orthotropy orientation ( ), depth of the fluid ratio ( ) and width of the tank are illustrated in Figs. 26. according to the EFAST model that is used for sensitivity analysis, for each parameter in xaxis there exists several outputs in the yaxis because when a parameter has a particular value other parameter can be changed. For example, in Fig. 2 when the aspect ratio is equal to 1 other parameter such as thickness ratio (h/a) and... can be changed.
Figure. 2 illustrates the fundamental natural frequency versus the aspect ratios parameter. It is realized that aspect ratios parameter is the most sensitive parameter, since its changes have the steepest slope relative to other parameters.
Table 1. Comparison study of fundamental natural frequencies of a simply supported square laminated composite plate between analytical and FEM results.








Galekin 
RayleighRitz [2] 
FEM[2] 
Galekin 
RayleighRitz [2] 
FEM [2] 
Galekin 
RayleighRitz [2] 
FEM [2] 
0 
29.9696 
29.9778 
29.89544 
240.427 
240.440 
239.2477 
343.776 
343.370 
339.8131 
0.1 
29.6192 
29.6885 
29.50947 
240.618 
240.209 
238.6906 
343.696 
343.207 
341.7148 
0.2 
26.0108 
26.0253 
25.90472 
235.806 
236.976 
233.9471 
340.213 
340.906 
335.384 
0.3 
18.6970 
18.6746 
18.51837 
226.655 
225.097 
224.3595 
332.300 
332.108 
331.5882 
0.4 
13.0885 
13.1129 
12.96254 
201.873 
202.967 
199.8331 
313.840 
313.689 
313.5351 
0.5 
9.59987 
9.5182 
9.443441 
176.281 
176.190 
174.5336 
286.528 
288.387 
282.9549 
0.6 
7.35094 
7.33229 
7.230984 
149.390 
150.209 
147.9097 
256.077 
257.746 
256.7761 
0.7 
5.78140 
5.84451 
5.766942 
127.453 
128.156 
127.4243 
228.383 
228.903 
226.8065 
0.8 
4.81267 
4.85699 
4.796181 
108.948 
110.932 
108.9018 
203.312 
203.924 
199.8549 
0.9 
4.12690 
4.18535 
4.113669 
96.7814 
97.9970 
96.75008 
183.198 
183.728 
183.5335 
1 
3.67188 
3.71927 
3.656121 
86.9989 
88.4552 
86.98845 
167.351 
168.052 
165.5156 
Fig. 2. Fundamental natural frequency versus the aspect ratios
Fig. 3. Fundamental natural frequency versus the material orthotropy orientation
At roughness values close to zero, the slope of this diagram is too sharp; but as the roughness values increase, the critical force of movement approaches a constant number; thus, this parameter is very sensitive at nearzero values, and from values in the vicinity of 2, its sensitivity diminishes considerably.
In view of Fig. 3, the material orthotropy orientation can be introduced as the second sensitive parameter after aspect ratios. With the increase of this parameter, first the fundamental natural frequency increases and then decreases, with a sharp, albeit milder, slope relative to aspect ratios.
The diagram of the fundamental natural frequency versus depth of the fluid ratios has been shown in Fig. 4 with a positive, and near zero, slope. With the change of depth of the fluid ratios in its range of variations, a minor change is observed in the fundamental natural frequency, and so this parameter is not considered as a sensitive parameter for the fundamental natural frequency. Figure 5 shows the fundamental natural frequency versus the thickness ratios parameter. The parameter of thickness ratios is an input parameter with negligible effects on the fundamental natural frequency; and with the changes of this parameter in its relevant intervals, no tangible change is observed in the fundamental natural frequency.
The diagram of the fundamental natural frequency versus width of the tank has been shown in Fig. 6 with a nearzero slope. With the change of width of the tank in its range of variations, a minor change is observed in the fundamental natural frequency, and so this parameter is not considered as a sensitive parameter for the fundamental natural frequency.
Figure. 7 shows the percent sensitivity of fundamental natural frequency to parameters of aspect ratios, material orthotropy orientation, depth of the fluid, thickness ratios and width of the tank, which have been obtained by means of the EFAST method. According to this figure, the aspect ratios parameter (with 70% sensitivity) is the most important parameter, and the material orthotropy orientation (with 25% sensitivity) is the other effective parameter.
Fig. 4. Fundamental natural frequency versus depth of the fluid ratios
Fig.5. Fundamental natural frequency versus the thickness ratios parameter
Fig.6. Fundamental natural frequency versus width of the tank
In the present paper, sensitivity analysis of vibrating laminated composite rectangular plates in interaction with inviscid fluid has been presented. For the formulation, the modified higher order shear deformation plate theory is employed. Differential equations of motion were derived using Hamilton’s variational principle. Natural frequencies of the plate were calculated using the Galerkin’s method and the boundary conditions of the plate was simply supported. For sensitivity analysis, the EFAST model was utilized. This method was based on variance and it was independent of any assumption of linearity and uniformity between inputs and output(s).
Fig.7. Percent sensitivity of fundamental natural frequency to parameters
The EFAST model was used to qualitative and quantitative analysis of the effect of 5 parameters includes aspect ratio (a/b), thickness ratio (h/a), material orthotropy orientation (θ), depth of the fluid ratio and width of the tank on the natural frequency of plate. It was observed that the aspect ratios parameter (with 70% sensitivity) was the most important parameter and after that material orthotropy orientation (with 25% sensitivity) was the second effective parameter on the natural frequency of plate. Also, results showed that other parameters such as thickness ratio and depth of the fluid ratio did not have a significant effect with 4% and 1% sensitivity respectively. Finally, the width of the tank with 0% did not have any effect on the natural frequency of the plate.
Acknowledgements
The authors gratefully acknowledge the funding by Arak University, under grant No 97/5115.
References
[1] Khorshidi K, Bakhsheshy A. Free vibration analysis of a functionally graded rectangular plate in contact with a bounded fluid. Acta Mechanica 2015; 226(10): 340123.
[2] Khorshid K, Farhadi S. Free vibration analysis of a laminated composite rectangular plate in contact with a bounded fluid. Composite structures 2013; 104: 17686.
[3] Khorshidi K, Akbari F, Ghadirian H. Experimental and analytical modal studies of vibrating rectangular plates in contact with a bounded fluid. Ocean Engineering 2017; 140: 14654.
[4] Yildizdag ME, Ardic IT, Demirtas M, Ergin A. Hydroelastic vibration analysis of plates partially submerged in fluid with an isogeometric FEBE approach. Ocean Engineering 2019; 172: 31629.
[5] Khorshidi K, Bakhsheshy A. Free natural frequency analysis of an FG composite rectangular plate coupled with fluid using Rayleigh–Ritz method. Mechanics of Advanced Composite Structures 2014; 1(2): 13143.
[6] Omiddezyani S, JafariTalookolaei RA, Abedi M, Afrasiab H. The sizedependent free vibration analysis of a rectangular Mindlin microplate coupled with fluid. Ocean Engineering 2018; 163: 61729.
[7] Liao CY, Wu YC, Chang CY, Ma CC. Theoretical analysis based on fundamental functions of thin plate and experimental measurement for vibration characteristics of a plate coupled with liquid. Journal of Sound and Vibration 2017; 394: 54574.
[8] Carra S, Amabili M, Garziera R. Experimental study of large amplitude vibrations of a thin plate in contact with sloshing liquids. Journal of Fluids and Structures 2013; 42: 88111.
[9] Jeong KH, Kim KJ. Hydroelastic vibration of a circular plate submerged in a bounded compressible fluid. Journal of Sound and Vibration 2005; 283(12): 15372.
[10] Khorshidi K. Effect of Hydrostatic Pressure on vibrating rectangular plates coupled with fluid. Scientia Iranica Transaction A, Civil Engineering 2010; 17(6): 415.
[11] Tubaldi E, Amabili M. Vibrations and stability of a periodically supported rectangular plate immersed in axial flow. Journal of Fluids and Structures 2013; 39: 391407.
[12] Carra S, Amabili M, Ohayon R, Hutin PM. Active vibration control of a thin rectangular plate in air or in contact with water in presence of tonal primary disturbance. Aerospace Science and Technology 2008; 12(1): 5461.
[13] Jeong KH. Hydroelastic vibration of two annular plates coupled with a bounded compressible fluid. Journal of fluids and structures 2006; 22(8): 107996.
[14] Khorshidi K. Effect of hydrostatic pressure and depth of fluid on the vibrating rectangular plates partially in contact with a fluid. In: Proceedings of the.: Trans Tech Publ.
[15] Khorshidi K, Bakhsheshy A. Free Vibration analysis of Functionally Graded Rectangular plates in contact with bounded fluid. Modares Mechanical Engineering 2014; 14(8): 16573.
[16] Ghasemi AR, Meskini M. Free vibration analysis of porous laminated rotating circular cylindrical shells. Journal of Vibration and Control 2019: 1077546319858227.
[17] Ghasemi AR, Mohandes M, Dimitri R, Tornabene F. Agglomeration effects on the vibrations of CNTs/fiber/polymer/metal hybrid laminates cylindrical shell. Composites Part B: Engineering 2019; 167: 70016.
[18] Mohandes M, Ghasemi AR. A new approach to reinforce the fiber of nanocomposite reinforced by CNTs to analyze free vibration of hybrid laminated cylindrical shell using beam modal function method. European Journal of MechanicsA/Solids 2019; 73: 22434.
[19] Ghasemi AR, Mohandes M. Nonlinear free vibration of laminated composite EulerBernoulli beams based on finite strain using generalized differential quadrature method. Mechanics of Advanced Materials and Structures 2017; 24(11): 91723.
[20] Pianosi F, Beven K, Freer J, Hall JW, Rougier J, Stephenson DB, et al. Sensitivity analysis of environmental models: A systematic review with practical workflow. Environmental Modelling & Software 2016; 79: 21432.
[21] Khedmati MR, Edalat P, Javidruzi M. Sensitivity analysis of the elastic buckling of cracked plate elements under axial compression. ThinWalled Structures 2009; 47(5): 52236.
[22] Afonso SMB, Hinton E. Free vibration analysis and shape optimization of variable thickness plates and shells—II. Sensitivity analysis and shape optimization. Computing Systems in Engineering 1995; 6(1): 4766.
[23] Akoussan K, Boudaoud H, Koutsawa Y, Carrera E. Sensitivity analysis of the damping properties of viscoelastic composite structures according to the layers thicknesses. Composite Structures 2016; 149: 1125.
[24] Chen CS, Tan AH. Imperfection sensitivity in the nonlinear vibration of initially stresses functionally graded plates. Composite Structures 2007; 78(4): 52936.
[25] Fung CP, Chen CS. Imperfection sensitivity in the nonlinear vibration of functionally graded plates. European Journal of MechanicsA/Solids 2006; 25(3): 42536.
[26] Chen CS, Hsu CY. Imperfection sensitivity in the nonlinear vibration oscillations of initially stressed plates. Applied mathematics and computation 2007; 190(1): 46575.
[27] ŁaseckaPlura M, Lewandowski R. Sensitivity Analysis of Dynamic Characteristics of Composite Beams with Viscoelastic Layers. Procedia engineering 2017; 199: 36671.
[28] Kotełko M, Lis P, Macdonald M. Load capacity probabilistic sensitivity analysis of thinwalled beams. ThinWalled Structures 2017; 115: 14253.
[29] De Lima AMG, Faria AW, Rade DA. Sensitivity analysis of frequency response functions of composite sandwich plates containing viscoelastic layers. Composite Structures 2010; 92(2): 36476.
[30] Takezawa A, Kitamura M. Sensitivity analysis and optimization of vibration modes in continuum systems. Journal of Sound and Vibration 2013; 332(6): 155366.
[31] Li Y, Wang X, Zhang H, Chen X, Xu M, Wang C. An interval algorithm for sensitivity analysis of coupled vibroacoustic systems. Applied Mathematical Modelling 2017; 50: 394413.
[32] Li D, Liu Y. Threedimensional semianalytical model for the static response and sensitivity analysis of the composite stiffened laminated plate with interfacial imperfections. Composite Structures 2012; 94(6): 194358.
[33] Li Dh, Xu Jx, Qing Gh. Free vibration analysis and eigenvalues sensitivity analysis for the composite laminates with interfacial imperfection. Composites Part B: Engineering 2011; 42(6): 158895.
[34] Liu Q. Analytical sensitivity analysis of frequencies and modes for composite laminated structures. International Journal of Mechanical Sciences 2015; 90: 25877.
[35] Hu Z, Su C, Chen T, Ma H. An explicit timedomain approach for sensitivity analysis of nonstationary random vibration problems. Journal of Sound and Vibration 2016; 382: 12239.
[36] Yan K, Cheng G. An adjoint method of sensitivity analysis for residual vibrations of structures subject to impacts. Journal of Sound and Vibration 2018; 418: 1535.
[37] Choi MS, Byun JH. Sensitivity analysis for free vibration of rectangular plate. Journal of Sound and Vibration 2013; 332(6): 161025.
[38] Liu Q, Paavola J. General analytical sensitivity analysis of composite laminated plates and shells for classical and firstorder shear deformation theories. Composite Structures 2018; 183: 2134.
[39] Li DH, Liu Y, Zhang X. Linear statics and free vibration sensitivity analysis of the composite sandwich plates based on a layerwise/solidelement method. Composite Structures 2013; 106: 175200.
[40] Tong C. Selfvalidated variancebased methods for sensitivity analysis of model outputs. Reliability Engineering & System Safety 2010; 95(3): 3019.
[41] Nossent J, Elsen P, Bauwens W. Sobol’sensitivity analysis of a complex environmental model. Environmental Modelling & Software 2011; 26(12): 151525.
[42] Im S. Sensitivity estimates for nonlinear mathematical models. Math Model Comput Exp 1993; 1(4): 40714.
[43] Sobol I. Sensitivity estimates for nonlinear mathematical models, Mater. Model; 1990.
[44] Cukier RI, Levine HB, Shuler KE. Nonlinear sensitivity analysis of multiparameter model systems. Journal of computational physics 1978; 26(1): 142.
[45] Saltelli A, Tarantola S, Chan KS. A quantitative modelindependent method for global sensitivity analysis of model output. Technometrics 1999; 41(1): 3956.
[46] Homma T, Saltelli A. Importance measures in global sensitivity analysis of nonlinear models. Reliability Engineering & System Safety 1996; 52(1): 117.