Vibration Analysis and Optimization of a Rectangular Plate with Flanging Hyperellipse Cutout

Vibration analysis and optimization of a rectangular plate with a flanging hyperellipse cutout is investigated in this paper, numerically. In the analysis, finite element method (FEM) is applied to perform parametric studies on various plates in different boundary conditions, addressing the influence of different cutout parameters (area, shape, flanging height, position, and rotation) on the firstand second-order natural frequencies of the rectangular plate and providing references for the optimum frequency design. *en, maximization of frequency or the difference of two consecutive frequencies of the rectangular plate is carried out using Multi-island Genetic Algorithm, aiming to achieve the best dynamic characteristics. *e results show that different cutout parameters have great influence on vibration performance of the plate, the existing of the flanging increases the out-of-plane stiffness of the plate. Additionally, the nature frequency of the plate has been improved obviously for different models with the optimal design of the cutout.


Introduction
In the actual engineering structure, such as aerospace, ship, and marine, plate structures are considered as major engineering substructures, especially wherever the weight is a main issue.It is often necessary to fix up an appropriate number of cutouts based on experience for structural maintenance, weight reduction, or performance optimization.On one hand, stress concentration occurs around the cutouts, and the static strength of the component is reduced; on the other hand, the quality and stiffness distribution of the structure will change for the existing cutouts, which have a great influence on the mechanical properties such as natural frequency and structural load-bearing performance of the structure.erefore, analysis of the mechanical properties of the structure with cutouts has been a hot issue in the research, which is of great significance in the engineering structure design.
Many studies [1][2][3] have been conducted on the stress, deformation, vibration, and buckling characteristics of structures with different type of cutouts (square, circular, elliptic, and triangular shapes).In some engineering structures, the plate structure may be subjected to in-plane compressive loading, in which case the buckling phenomenon becomes a critical design criterion.For a rectangular plate with cutout, Komur et al. [4] presented a buckling analysis of a woven-glass-polyester laminated composite plate with a circular/elliptical cutout.e results show that buckling loads are decreased by increasing both c/a and b/a ratios.e increase of cutout positioned angle causes decrease of buckling loads.Ovesy and Fazilati [5] investigated the effects of cutouts on the buckling critical stresses as well as natural frequencies of a plate with central cutout.A numerical study was conducted using the finite element method to determine the effects of square and rectangular cutouts on the buckling behavior of a 16-ply quasi-isotropic graphite/epoxy symmetrically laminated rectangular composite plate [6].Also, the natural frequencies of every structural element are of great significance in order to avoid the so-called resonance conditions.e influences of a super-ellipse cutout on the frequency of a rectangular plate or composite laminate plate were examined by Wang et al. [7,8].Numerical results show that the plate frequencies are highly dependent upon the shape, size, position, and orientation of the cutout.Moreover, the effect is also highly related to the boundary conditions of the plate.Frequency optimization of the plate with cutout is also a concerned research topic.Wang and Wu [9] presented an effective numerical technique for determining the optimal location of a cutout in rectangular plates for maximum fundamental frequency of vibration.e Ritz method was employed for the vibration analysis, and generalized reduced gradient (GRG) method is used to determine the optimal values of location coordinates of the cutout.Pedersen [10] studied the optimization of a cutout of given area which is placed in the interior of a plate with an arbitrary external boundary.Optimal designs were obtained iteratively using mathematical programming, where each of the redesigns is based on finite element (FE) analysis and sensitivity analysis.Wang and Yu [11,12] carried out maximization of eigenfrequency of a rectangular plate with a parameterization ellipse cutout, and the cutout shape optimization is performed by using Genetic Algorithm and a combined mathematical programming algorithm, respectively.
When punching cutouts on the structure in practice, there will be a certain height of flanging around the cutouts simultaneously.Few studies about the influence of flanging cutouts on structural dynamic performance have been reported, and the author of this paper has firstly studied the influence of different parameters of circular [13] and circle-rectangular [14] cutout on the vibration frequency of a rectangular plate since 2015.Considering an effective weight loss of structure and combining with shape optimization of cutout, this paper focuses on the influence analysis and optimization of structural dynamic performance of a rectangular plate with flanging hyperellipse cutout, and the boundary of the cutout is described with several parameterization parameters, including the possibility of going from an ellipse to a rectangle or even to a triangle.In this paper, the influence of different cutout parameters (area, shape, flanging height, position, and rotation) on the first and second order natural frequencies of the rectangular plate in different boundary constraints will be studied firstly, providing references for the optimum frequency design of the structure.en, the optimal design of the rectangular plate is carried out under the constraint condition of cutout area unchanged.e first and the second natural frequency or the difference between the first two natural frequencies is maximized through optimization process, aiming to achieve the best dynamic characteristics.

Model of Rectangular Plate with Flanging Hyperellipse Cutout
As shown in Figure 1, a flanging ellipse cutout is opened in the center of a rectangular thin plate.In order to reduce the stress concentration, the cutout boundary must be smooth enough, which is described by hyperelliptic equation: where a and b are half axle length of the ellipse along x, y axis directions, respectively, and η is an exponential of hyperelliptic equations, for example, ellipse (η � 2) or rectangular (η � 5).In order to describe the location and rotation at the same time, the cutout boundary is described in parameter form: where (x 0 , y 0 ) represents the center coordinates of the ellipse and t ∈ (0, 2π) is auxiliary parameter.Area of the cutout is where B(1/η, 1/η) is a beta function, when η � 2, B(1/2, 1/2) � π. en, the cutout rate of the plate is defined as Considering that the boundaries of the rectangular plate can be clamped (C), simple support (S), or free (F), we use 4 letters to describe the boundary support situation, beginning from the left edge (x � −L/2) and according to the order of counterclockwise.Suppose the size of the rectangular plate is 450 (L) × 300 (W) × 2 mm, elastic modulus of the material is 70 GPa, Poisson's ratio is 0.3, and mass density is 2700 kg/m 3 .

Frequency Analysis
Influence of different cutout parameters (area, shape, flanging height, position, and rotation) on the first (f 1 ) and second (f 2 ) order natural frequencies of the rectangular plate in different boundary constraints are analyzed in this section.During the analysis, ANSYS, which is known as general purpose finite element software, was preferred as numerical tool, and SHELL181 element type was used to produce for mesh structure.
In this paper, the first-order vibration frequency (f 1 ) and the second-order vibration frequency (f 2 ) are the first two frequencies of the structural vibration, respectively, in the order of frequency values from small to large.Figures 2 and  3, respectively, show the oscillatory process of the first two modes of the plate with a central flanging ellipse cutout under the CFFF constraint, with 10 frames in 0.5 seconds, and the initial situation is not displayed.As can be seen from the figures, the first-order frequency is a bending vibration around the y-axis, and the second-order frequency is a torsional vibration about the x-axis.e blue to red color in the figures indicates the amplitude of different points on the board during the corresponding vibration, with blue being zero and red being the largest value.Moreover, it is found that the first two-order vibration modes have not changed with the variations of structural parameters, which is 2 Shock and Vibration also applicable to the vibration of the structure under the remaining boundary constraints.

Influence of Cutout Area on the Frequency.
Influence of a central flanging ellipse cutout area on the frequency is studied firstly.e half axle length a of the ellipse is constant, and b changes with different cutout area.e flanging height h is 6 mm.Table 1 shows the first two natural frequencies of the rectangular plate in CFFF.For comparison, the natural frequency of the plate without cutout in CFFF is also simulated.From Table 1, the results show that the natural frequency of the plate has changed with various cutout areas.
Comparing with the natural frequency of the rectangular plate without cutout, the first-order frequency increases continuously with the increase of the cutout area until ϕ � 0.14 and then decreases; however, the value is still greater than the case of without cutout.For the second-order frequency, the frequency increases with a small cutout area, then continues to decrease with the increase of the cutout area, and there will be cases that the frequency will be lower than the case of without cutout.e corresponding vibration mode remains unchanged with the increase of the cutout area.
Figure 4 shows the variation of the first two natural frequencies of the plate with the increase of cutout rate under other different boundaries.With the increase of the cutout rate, it can be seen that the first two frequencies increase continuously under different boundary constraints and are all larger than the corresponding natural frequencies without cutout.e influence of flange cutout on the frequency of the plate is also related to the boundary conditions, and the influence of CCCC constraint is the highest.

Influence of Ellipse Shape on the Frequency.
Assuming that the central ellipse cutout has the same cutout rate (eg., a � 100 mm, b � 50 mm, ϕ � 0.116), the influence of ellipse shape on the frequency is investigated.e two half axle length a and b can take different values, which are not independent and must satisfy Equation (4).And the flange height h � 6 mm.Table 2 lists the variation of the first-and second-order natural frequency results of the clamped-free plate.With the increase of a and decrease of b gradually, the first-order frequency increases continuously, and the second-order frequency decreases firstly, and then significantly increases when a � 125 mm and b � 40 mm.
Figure 5 plots variations of the natural frequencies with a central ellipse cutout of different shape under different boundary constraints.With the increase of a and decrease of b gradually, it can be found that the first-order frequency decreases and the second-order frequency increases for most boundary constraints, in addition to CFCF boundary, the results of which are contrary.When a � 125 mm and b � 50 mm, the second frequency under CSCS suddenly dropped, which is needed for further consideration.

Influence of Flanging Height on the Frequency.
To study the influence of different flange height on the frequency of the plate, the cutout area is kept unchanged (a � 100 mm, b � 50 mm), and the cutout location is still located in the center.
Table 3 shows the variations of the first two frequencies with the change of the flanging height.From Table 3, it can be seen that the changes of the flanging height have a large influence on the frequency of the CFFF rectangular plate.As the flanging height increases, the first two frequencies of the rectangular plate are continuously increasing.Comparing with the corresponding frequency of the plate without cutout (see the first row of Table 1), it can be found that when the flanging height is small, the frequency value of the plate is smaller than that of the plate without cutout.When the flange height increases to a certain extent, the frequency value of the plate is larger than that of the plate without cutout.As shown in Table 3, the first-order frequency value is greater than the corresponding noncutout condition when h ≥ 2 mm.For the second-order frequency, the flange height h ≥ 10 mm is required.
e vibration frequency results under different constraints are shown in Figure 6.As can be seen from Figure 6, with the increase of the flange height, the first two-order frequency of the rectangular plate shows an overall trend of increasing.Comparing with the nonflanged plate (h � 0 mm), the first two-order vibration Shock and Vibration frequency of the anged plate is larger than that of the non anged plate.Similar to the ribbed sti eners, the outof-plane sti ness of the rectangular plate is increased by the presence of anging, whereas the rst two-order vibrations of the rectangular plate mainly show out-ofplane vibrations.At the same time, it is noted that when the height of the ange reaches a certain value, the frequency of the rectangular plate is not obviously changed, indicating that the in uence of the ange height on the frequency is decreasing.

In uence of Cutout Location on the Frequency.
e inuence of cutout location on the frequency of the rectangular plate is studied, assuming that the position of the cutout center moves in the positive direction of x-axis.e    Shock and Vibration cutout area is also kept unchanged (a 100 mm, b 50 mm), and the ange height h 6 mm.For the CFFF plate, changes of the rst two-order natural frequencies with the position of the cutout center are shown in Table 4.As the central position of the cutout moves along the positive direction of the x-axis, the mass distribution of the clamped end increases, and the frequency of the rectangular plate should continue to increase for a cantilever structure, which is consistent with the data listed in Table 4.
It can be seen from Figure 7 that the rst-order frequency shows a decreasing trend as the position of the opening moves in the positive direction of the x-axis, and the second-order frequency shows a trend of increasing.For the  CFCF and FCFC constraints, the change of the first two natural frequencies is insignificant.

Influence of Cutout Rotation on the Frequency.
e rectangular plate with a central ellipse cutout (a � 100 mm, b � 50 mm, h � 6 mm) is used to study the influence of counterclockwise turning of the cutout on the frequency.e influence of the rotation angle θ on the natural frequency of the rectangular plate in CFFF is shown in Table 5. e change of the rotation angle θ has a distinctly different effect on the first two-order frequencies.e first order natural frequency reaches maximum at θ � 0 °and then decreases gradually, while the second-order natural frequency shows the trend of increasing first, then decreasing, and then increasing again.
e first-order vibration frequency shows increasing trend with the angle increasing for most boundary constraints; however, the result in CFCF constraints is decreasing, as shown in Figure 8. e second-order frequency decreases with the increase of the angle under the constraints of CCCC, SSSS, CSCS, and SCSC.e other two types of boundary conditions have little influence on the frequency variations.

Influence of Cutout Shape on the Frequency.
It is assumed that there are different shapes of hyperellipses cutout in the center of the rectangular plate, considering the hyperelliptic equations exponential η � 1.5-5.0,respectively, and taking a � 100 mm, b � 50 mm, and h � 6 mm.6 lists the changes of the rst two natural frequencies with exponential variation of the hyperelliptic equation for the CFFF-supported rectangular plate.As the shape of the cutout changes from an ellipse to a rectangle, the opening rate gradually increases.e rst natural frequency gradually increases, and the second natural frequency gradually decreases.
Variations of the natural frequencies the rectangular plate with various η are shown in Figure 9. e rstorder natural frequency is gradually increased with the increase of exponential.
e second-order natural frequency is also gradually increased with the increase of exponential under CCCC, SSSS, and SCSC constraints.For the CSCS boundary, the second-order frequency increases when value of η is small (η ≤ 2.5) and then decreases when η becomes large.
e other two types of boundary CFCF and FCFC have little in uence on the frequency variations.

Frequency Optimization
In this paper, optimal frequency design of the rectangular plate with cutout is processed by using Multi-island Genetic Algorithm in ISIGHT software, keeping constant cutout area.From Equation (3), the size of the cutout area is related to parameters of a, b, and η. e location, rotation of the cutout, and anging height are also taking into account in optimization process for the impact of frequency, expanding the optimization range.Parameters con guration of Multi-island Genetic Algorithm adopt the default mode in ISIGHT.
e natural frequency of the rectangular plate with cutout is maximized through the optimization process, with design variables of parameters a, b, η, x 0 , y 0 , θ in Equation ( 2) and anging height h.Under the constant cutout area condition, the design variable b is calculated by Equation (3).If the design variables a, b, and η appear in the code string at the same time, it is not guaranteed that the constraint of the cutout area can be satis ed after the crossover and mutation operation.
e optimization mathematical model is expressed as max f, ( In Equation ( 5), f represents the rst-order natural frequency f 1 , the second-order frequency f 2 , or the difference between the rst-and second-order frequencies (f 2 − f 1 ), respectively; A 0 is a given cutout area; d x and d y are the largest dimensions of the cutout boundary along the x-axis and y-axis, respectively; and δ is the minimum allowed distance between the cutout boundary and the plate edge, preventing the cutout if it is too close to the edge of the plate and a ecting the accuracy of frequency calculation.

Shock and Vibration
Frequency optimization of the rectangular plate in CCCC boundaries is investigated in this paper, requiring a anging cutout design in the interior of the plate.Assuming δ 25 mm and A 0 75 2 π mm 2 , the rst-order frequency f 1 is maximized (Model 1).When there is no cutout in the plate, rst natural frequency is 147.16Hz.A anging circular cutout with 75 mm radius (as indicated by the dashed line in Figure 10) and 6 mm anging height is opened in the center of the plate rstly as the initial optimization condition; the rst-order natural frequency reaches 206.49Hz.After the optimization design (shown by the solid line in Figure 10), the rst-order frequency reached 210.53 Hz, which is 4.04 Hz higher than that before optimization.
Sometimes it is desirable to control the second-order natural frequency of the rectangular plate.For this purpose, the parameters of the cutout of the rectangular plate are reoptimized, aiming to maximize the second-order natural frequency (Model 2).Keeping δ 25 mm and A 0 75 2 π mm 2 unchanged, the natural frequency of the plate with a central circular cutout with a 75 mm radius (shown in dashed line in Figure 11) and 6 mm anging height is 241.49Hz.After optimization (as shown by the solid line in Figure 11), the second-order natural frequency of the plate can reach 313.79 Hz, increased by 72.3 Hz; the optimization e ect is obvious.
e optimization process is shown in Figure 12.
In addition, the di erence of the rst and second natural frequencies of the plate is also maximized (Model 3).Keeping all parameters same as Model 1 and Model 2, the di erence between the two natural frequencies is 35 Hz.After optimization, the di erence between the two natural frequencies reached 147.53 Hz, increased by 112.53 Hz.Shapes of Model 3 before and after optimization are given in Figure 13.
If the cutout area of Model 1 is increased to A 0 100 2 π mm 2 , the other parameters keep unchanged (Model 4).A central anging circular cutout is opened in the plate, with 100 mm radius and 6 mm anging height.e second natural frequency is 267.2Hz, which can reach 364.86 Hz after the optimization, and the optimization e ect is quite obvious.From the optimization results of Model 2 and Model 4, it can be seen that the second-order natural frequency of the plate increases with the cutout area.At the same time, the optimization design of the cutout is more obvious.Figure 14 gives the shapes of Model 4 before and after optimization.
e optimal parameters of di erent models are given in Table 7.

Conclusions
e in uence of a anging ellipse cutout on the vibration performance of a rectangular plate is studied rstly in this paper.e results show that the cutout area, shape, position, rotation, anging height, and the boundary conditions have great in uence on vibration performance of the plate, the existing of the anging increases the out-of-plane sti ness

Figure 1 :
Figure 1: A rectangular plate with a central flanging ellipse cutout.

Figure 4 :
Figure 4: Variations of the natural frequencies of the plate supposed differently with various cutout areas.

(Figure 5 :
Figure 5: Variations of the natural frequencies with a central ellipse cutout of di erent shapes.

Figure 6 :
Figure 6: Variations of the natural frequencies of a rectangular plate supposed di erently with various h.

Figure 7 :
Figure 7: Variations of the natural frequencies of a rectangular plate supposed di erently with various x.

Figure 8 :
Figure 8: Variations of the natural frequencies of a rectangular plate supposed di erently with various θ.

Figure 9 :
Figure 9: Variations of the natural frequencies of a rectangular plate supposed di erently with various η.

Figure 10 :
Figure 10: Shapes of Model 1 before and after optimization.

10
Shock and Vibration of the plate.en, the frequency of the plate is optimized by using Multi-island Genetic Algorithm in ISIGHT software, and the natural frequency of the plate has been improved obviously for di erent models, and increasing of cutout area can also improve the e ect of optimal design.

Figure 14 :
Figure 14: Shapes of Model 4 before and after optimization.

Figure 13 :
Figure 13: Shapes of Model 3 before and after optimization.

Figure 11 :
Figure 11: Shapes of Model 2 before and after optimization.

Table 1 :
Influence of central cutout area on the first two frequencies of clamped-free plate.

Table 2 :
Influence of ellipse shape on the first two frequencies of clamped-free plate.

Table 3 :
In uence of anging height on the rst two frequencies of clamped-free plate.

Table 4 :
In uence of cutout location on the rst two frequencies of clamped-free plate.

Table 5 :
In uence of cutout rotation on the rst two frequencies of clamped-free plate.

Table 6 :
In uence of η on the rst two frequencies of clamped-free plate.

Table 7 :
Optimal results of a rectangular plate with anging cutout.