# Comparative Analysis of Al-Li Alloy and Aluminum Honeycomb Panel for Aerospace Application by Structural Optimization

Authors: Naihui Yu; Jianzhong Shang; Yujun Cao; Dongxi Ma; Qiming Liu
Journal: Mathematical Problems in Engineering
 (2015)

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## Abstract

Al-Li alloy and aluminum honeycomb panel (AHP) are both excellent materials for aeronautical structures. In this paper, a plate-type aeronautical structure (PAS), which is a base mounting structure for 172 kg functional devices, is selected for comparative analysis with different materials. To compare system-level performance under multidisciplinary constraints, mathematical models for optimization are established and then structural optimization is carried out using Altair OptiStruct. For AHP, its honeycomb core is regarded as orthotropic material and its mechanical properties are calculated by Allen’s model in order to establish finite element model (FEM). The heights of facing sheet and honeycomb core are selected as design variables for size optimization. For Al-Li alloy plate, topology optimization is carried out to obtain its most efficient load path; and then a reconstruction process is executed for practical manufacturing consideration; to obtain its final configuration, accurate size optimization is also used for reconstructed model of Al-Li alloy plate. Finally, the optimized mass and performance of two PASs are compared. Results show that AHP is slightly superior to Al-Li alloy.


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## Body

## 1. Introduction

With the development of aerospace technology, the demand of high-strength-low-density materials is becoming more and more urgent. Severe mechanical environment and aerodynamic coupling are inevitable because of high launch acceleration and high frequency vibration, so the requirements for strength and stiffness of aeronautical structures are extremely high. Moreover, launch costs have strong restrictions on the overall mass of spacecraft, so the mass of aeronautical structures must be minimized as far as possible. Severe contradiction between strength and mass spurs extensive utilization of advanced alloy material and composite material in aerospace applications, such as aluminum lithium (Al-Li) alloys [1], titanium alloy [2, 3], carbon fiber/epoxy composites, and aramid fiber/epoxy composites [4, 5]. The Al-Li products offer opportunities for significant improvements in aerostructural performance through density reduction, stiffness increase, increases in fracture toughness and fatigue crack growth resistance, and enhanced corrosion resistance [6]. It has been found that addition of 1% of lithium to aluminum reduces alloy density up to 3% and increases modulus by 6% [7]. Besides, a basic trend towards increased utilization and integration of laminated anisotropic composites into the construction of aeronautical and aerospace vehicles has manifested in the last decade [8]. And sandwich-type honeycomb panel [9] which is a typical laminated anisotropic composite is an important alternative aeronautical material. Due to their high strength-to-weight ratio and stiffness-to-weight ratio, the use of honeycomb panels is particularly attractive in various aeronautical structures [10, 11].Since high-strength alloy material and honeycomb panels are both excellent options for aeronautical structures, it is necessary to conduct a comparative analysis under same boundary conditions and load case. Currently, most researches concentrate on the performance of separate material [12, 13], but there are very few systematic studies on the performance comparison of AHP and Al-Li alloy. Aeronautical structures usually have multidisciplinary requirements like minimum mass, high strength and stiffness, eased manufacturing and assembly techniques, and functional needs [14]. In the design of aeronautical structures, choosing what kind of materials is one of the key problems which must be considered firstly. However, it may be a very challenging task even for sophisticated designers only based on their professional knowledge and experience. The choice of materials directly determines the dimension design of structures, its processing methods, and even configurations of structures, especially when the honeycomb panels are in the scope of selection. As a laminated cellular structure, honeycomb panel is a type of structural material considering lightweight design and is a typical anisotropic material, so it cannot be directly compared with alloy material. Performance comparison is meaningful only when the optimal structures of two materials are obtained under the same conditions. Therefore, after the functional loads and performance constraints are almost confirmed, structural optimization technology is needed to obtain the eventual configurations.In structural optimization, design variables can be categorized into three groups as topology, shape, and sizing variables. Topological design variables determine an initial structural layout whereas shape and sizing parameters give the shape and dimensions of structures, respectively [15]. The three levels of structure optimization are shown in Figure 1. Topology optimization is used in the conceptual design stage to obtain an initial structural configuration and to optimize material layout within a given design space for a given set of loads and boundary conditions such that the resulting layout meets a prescribed set of performance targets. Shape optimization belongs to preliminary design stage. By modifying the structural boundaries, for example, detailed designs for notches, holes, and fillets, concerned mechanical performances are improved during the optimization procedure [16]. Size optimization is used in a detailed design stage and to determine the ideal thickness of a material based on the performance goals and the forces expected to be placed on the component. In the field of aerospace or aeronautical industry, structural optimization technology is widely adopted for many years and is utilized in the design of most aeronautical structures, such as space station [17], aircraft [18], rockets [19], spacecrafts [20]. Maute and Allen presented a topology optimization methodology for the conceptual design of aeroelastic structures accounting for the fluid-structure interaction and the geometrical layout of the internal structure is optimized by material topology optimization [21]. A topology optimization method is proposed to minimize the resonant response of plates with constrained layer damping treatment under specified broadband harmonic excitations [22]. For honeycomb panels, Ermolaeva et al. [23] presented the application of a structural optimization system to the optimal choice of foams as a core material for sandwiches with aluminum alloy faces. Hansel and Becker [24] present a simple heuristic optimization algorithm implemented by ANSYS-macros to determine weight-minimal laminate structures. However, there are no papers about system-level performance comparison of honeycomb panel and alloy material using structural optimization.Figure 1
Three levels of structural optimization.In the current paper, a PAS, which is a base mounting structure for 13 different functional devices, is selected for comparative analysis. High-strength Al-Li alloy and aluminum honeycomb panel are both ideal material for simple PAS, so it is very important for structure designers to determine which material is more superior. The commercial finite element package HyperMesh and OptiStruct 8.0 [25] are used for structural optimization. Final size optimization of facing sheet and honeycomb core heights could be directly executed for comparative analysis, as the configuration of honeycomb core is almost definite. The pure Al-Li alloy plate needs topology and size optimization to obtain the optimized configuration. Mathematical models for optimization are established and the mass of structure is chosen as objective function. The rest of the paper is organized as follows. Section 2 briefly introduces the plate-type aeronautical structure and its performance requirements considering the launch conditions. Section 3 introduces the structure of AHP and presents its calculation method of orthotropy mechanical properties based on Allen’s model, which is important to established its finite element model; the mathematical models for structural optimization are also presented for AHP and Al-Li alloy. Section 4 presents the results of structural optimization and comparative analysis.


## 2. Plate-Type Aeronautical Structure and Its Performance Requirements

Figure2 shows a typical PAS which is often used in a spacecraft. X direction is rocket’s flight direction. Assume that 13 different function devices which form an independent subsystem are installed on this PAS and their total weight is 172 kg. After the layout of these function devices is determinate, the first thing which must be decided by the structural designers is to select materials for this PAS. According to the requirement of installing space, the dimension of PAS is confirmed and the width M and the length L are 980 mm and 1075 mm, respectively. Two lengths of this rectangle are fixed when the rocket launches. According to the rocket launching environment, performance constraints of the system are given and are shown in Table 1, where G is 9.81 m/s2.Table 1
Performance constraints of the subsystem and its PAS.
Performance
Input loads
Requirement
Strength and stiffness
X direction: 16.2G acceleration field Y direction: 12.9G acceleration fieldZ direction: 9.5G acceleration field
Safety factor is not lower than 1.5Maximum deformation is less than 0.3 mm
Resonance frequency
No external input load
Fundamental frequency is not less than 115 Hz
Harmonic response
X direction: 7.5G∗sin⁡(ωt) harmonic excitationY direction: 5.7G∗sin⁡(ωt) harmonic excitationZ direction: 4.2G∗sin⁡(ωt) harmonic excitationFrequency ω is changing from 0 Hz to 100 Hz
Maximum acceleration of function devices is not more than 22G
Mass
All external input loads
Not more than 30% of total mass of  function devicesFigure 2
Typical PAS and layout of function devices installed on PAS.
(a)
Front
(b)
BackBecause the frequency range of harmonic response is 0 Hz~100 Hz, mechanical resonance will not happen as the fundamental frequency of subsystem is not less than 115 Hz. Therefore, harmonic response constraints need not be considered in the procedure of structural optimization and performance verifications should be carried out after optimized analysis. Lightweight design is one of the most important tasks of structure design for aerospace applications, so the mass of PAS should be selected as optimization objective and structural stress, deformation, and the first order modal as design constraints.AHP and Al-Li alloy are very different aeronautical materials. AHP is a kind of typical structured material and its configuration is almost determinate, so only size optimization is needed to obtain its optimized structure. Different optimization methods for AHP and Al-Li alloy are shown in Figure3. Software types used in the paper are SolidWorks for geometry creation, HyperMesh for meshing, OptiStruct for optimization, and HyperView for postprocessing. CAD models of function devices and PAS created in SolidWorks are imported into the HyperMesh for preprocessing. Preprocessing of models includes creating FE model, selection of material properties, creation of load, and applying boundary conditions on model. For AHP, HyperLaminate module is used to model this orthotropy material. For the optimization purpose, optimization criteria are selected. According to criteria, the designable and nondesignable portions are generated. The optimization process is executed in OptiStruct and the result can be viewed in HyperView.Figure 3
Different optimization methods for AHP and Al-Li alloy.


## 3. Finite Element Models and Mathematical Models for Structure Optimization

### 3.1. Honeycomb Panels

Honeycomb panel, which is shown in Figure4, is a sort of sandwich panel consisting of two alloy or composite plates as face sheet and hexagonal honeycomb cell as core materials, bonded together by bonding adhesive or macromolecule lamination film. In the sandwich construction, the facing sheets are spaced to provide most of the bending rigidity. They also resist all or nearly all the applied edgewise loads and flatwise bending moments. The core material spaces the facing sheets and transmits shear between them so that they are effective about a common neutral axis. The core also provides most of the shear rigidity of the construction. The core-to-facing bonding adhesive must be adequate to transfer the stresses from the facing sheets to the core materials so that the full properties of the two are utilized [10].Figure 4
Typical structure of hexagonal honeycomb panel and its dimensions.As shown in Figure4, H is the height of hexagonal honeycomb core and h is the height of facing sheet. For hexagonal cell, t is cell wall thickness, l is cell wall width, and d is the diameter of inscribed circle of hexagon. In the process of optimization analysis, 2A12-T4 aluminum alloy is selected as the material of facing sheet. Honeycomb core is aluminum hexagonal honeycomb 1/8-2024-0.003 of Hexcel Corporation, in which 1/8 (inch) represents the diameter of inscribed circle of hexagon, 2024 is its material grade, and 0.003 (inch) represents cell wall thickness. So the cell wall width l could be simply calculated by the equation l=d·tan⁡30 and its value is 1.83 mm after unit conversion. The mechanical properties of 2A12-T4 and 2024 are shown in Table 2.Table 2
The mechanical properties of 2A12-T4 and 2024.
Material grade
Density [kg/m−3]
Young's modulus [MPa]
Shear modulus [MPa]
Poisson’s ratio
Yield strength [MPa]
2A12-T4
2780
70600
28000
0.33
280
2024
2700
73000
28000
0.44
75.8In order to establish finite element model of honeycomb panels, honeycomb core can be equivalent to orthotropic material and its mechanical properties be calculated by Allen’s model [26] which is widely used in mechanical engineering [27]:(1)Ex=Ey=43tl3E,Gxy=3γ2tl3E,Gxz=3γ2tlG,Gyz=γ3tlG,uxy=0.33,where E is Young’s modulus of honeycomb core, G is shear modulus, γ is a correction factor, and its value depending on the manufacturing process is generally 0.4~0.6. By the equivalent calculation, mechanical parameters of aluminum hexagonal honeycomb are shown in Table 3.Table 3
Equivalent mechanical parameters of 1/8-2024-0.003.
E
x/MPa
E
y/Mpa
G
x
y/MPa
G
x
z/MPa
G
y
z/MPa
u
x
y
11.3
11.3
1.7
370.2
246.6
0.33A finite element model of this subsystem is established using Altair OptiStruct. Honeycomb panel is meshed in HyperMesh using four-noded linear quad elements (CQUAD4) and composite properties are applied, where the core is orthotropic material and the sheets are isotropic material. All function devices are simplified by shell element and their mass is equivalent to the thickness of shells. Bolt connections are simplified as multipoint constraints and modeled by the flexible unit (RBE3). Two length of honeycomb panel are fixed in all six degrees of freedom. The finite element model is shown in Figure5.Figure 5
Finite element model of subsystem with honeycomb panel.For structure optimization, performance constraints shown in Table1 are used and the height of hexagonal honeycomb core H and the height of facing sheet h are selected as the design variables. The mass of subsystem is objective function. And mathematical models for honeycomb panel optimization could be described as (2)mindMdSubject  to:g1d=σp≤σsSg2d=ε≤0.3mmg3d=f1≥115Hzdmin≤d≤dmax,where M(d) is the total system mass, g(d) is performance constraint, σp is the actual stress value while σs is yield strength of facing sheet material, S is safety factor and the value is selected as 1.5 in this paper, ε is maximum deformation of PAS, f1 is fundamental frequency of this system, d is design variable and d=[h,H], and dmin and dmax are, respectively, lower and upper limit values of design variables and are shown in Table 4.Table 4
Lower and upper limit values of design variables.
Design variable
Initial dimension [mm]
Lower limit value [mm]
Upper limit value [mm]
h
2
0.15
5
H
36
10
100


### 3.2. PAS of Al-Li Alloy

The performance of frame structure largely depends on the properties of material. In this paper, Al-Li alloy 2090 is selected for comparative analysis with honeycomb panel while all boundary conditions, input loads, and layout of function devices are identical. 2090 is a kind of high performance material and its elastic modulus increased by about 10% while the density decreased by about 10% compared with the conventional aluminum alloy. So its stiffness-to-weight ratio and strength-to-weight ratio are improved remarkably. The mechanical parameters of 2090 versus conventional aluminum alloy 2Al12 are shown in Table5.Table 5
Mechanical parameters of 2090 versus 2Al12.
Material grade
Densityρ [kg⋅m−3]
Young’s modulusE [MPa]
Yield strengthσs [MPa]
σ
s/ρ [MPa⋅m3/kg]
E/ρ [MPa⋅m3/kg]
2090
2590
78600
530
0.2
30.3
2Al12
2780
70600
280
0.1
25.4For a plane-frame structure of pure Al-Li alloys, topology optimization is firstly used for a conceptual design proposal and then fine-tuned for manufacturability. Initial thickness of the plane-frame structure is a critical factor for topology optimization and the value of initial thickness directly determined the optimization result. Therefore, four values of initial thickness (40 mm, 50 mm, 60 mm, and 70 mm) are used, respectively, and the best thickness is determined by comparing the optimum results. At last, size optimization is executed to obtain a desired thickness of plane-frame structure. Similarly with honeycomb panel, Al-Li alloys plate is meshed with four-noded linear quad elements (CQUAD4) and the function devices are meshed in the same way. The finite element model is shown in Figure6. In order to retain installation points of function devices, the meshed plate will be divided into designable and nondesignable portions. The geometry for the design space is defined by inspection of the bounds. As shown in Figure 5, green areas are selected as nondesignable portions and insure that all fixing points (yellow points) are included.Figure 6
Finite element model for Al-Li alloys structure of PAS.
(a)
Finite element model
(b)
Designable and nondesignable portionsIn the process of topology optimization of Al-Li alloys plate, the initial thickness is defined and the design variable is element density of meshed plateρ. And mathematical model could be described as (3)minρMρSubject  to:g1ρ=σp≤σsSg2ρ=ε≤0.3mmg3ρ=f1≥115Hzρ∈0,1.After topology optimization, size optimization should be carried out to obtain a further optimized thickness of Al-Li alloys plate, so the thickness is selected as design variable and its initial value would be the selected result of topology optimization. The mathematical model of size optimization is shown in(4)mintMtSubject  to:g1t=σp≤σsSg2t=ε≤0.3mmg3t=f1≥115Hzt0-10≤t≤t0+10.


## 3.1. Honeycomb Panels

Honeycomb panel, which is shown in Figure4, is a sort of sandwich panel consisting of two alloy or composite plates as face sheet and hexagonal honeycomb cell as core materials, bonded together by bonding adhesive or macromolecule lamination film. In the sandwich construction, the facing sheets are spaced to provide most of the bending rigidity. They also resist all or nearly all the applied edgewise loads and flatwise bending moments. The core material spaces the facing sheets and transmits shear between them so that they are effective about a common neutral axis. The core also provides most of the shear rigidity of the construction. The core-to-facing bonding adhesive must be adequate to transfer the stresses from the facing sheets to the core materials so that the full properties of the two are utilized [10].Figure 4
Typical structure of hexagonal honeycomb panel and its dimensions.As shown in Figure4, H is the height of hexagonal honeycomb core and h is the height of facing sheet. For hexagonal cell, t is cell wall thickness, l is cell wall width, and d is the diameter of inscribed circle of hexagon. In the process of optimization analysis, 2A12-T4 aluminum alloy is selected as the material of facing sheet. Honeycomb core is aluminum hexagonal honeycomb 1/8-2024-0.003 of Hexcel Corporation, in which 1/8 (inch) represents the diameter of inscribed circle of hexagon, 2024 is its material grade, and 0.003 (inch) represents cell wall thickness. So the cell wall width l could be simply calculated by the equation l=d·tan⁡30 and its value is 1.83 mm after unit conversion. The mechanical properties of 2A12-T4 and 2024 are shown in Table 2.Table 2
The mechanical properties of 2A12-T4 and 2024.
Material grade
Density [kg/m−3]
Young's modulus [MPa]
Shear modulus [MPa]
Poisson’s ratio
Yield strength [MPa]
2A12-T4
2780
70600
28000
0.33
280
2024
2700
73000
28000
0.44
75.8In order to establish finite element model of honeycomb panels, honeycomb core can be equivalent to orthotropic material and its mechanical properties be calculated by Allen’s model [26] which is widely used in mechanical engineering [27]:(1)Ex=Ey=43tl3E,Gxy=3γ2tl3E,Gxz=3γ2tlG,Gyz=γ3tlG,uxy=0.33,where E is Young’s modulus of honeycomb core, G is shear modulus, γ is a correction factor, and its value depending on the manufacturing process is generally 0.4~0.6. By the equivalent calculation, mechanical parameters of aluminum hexagonal honeycomb are shown in Table 3.Table 3
Equivalent mechanical parameters of 1/8-2024-0.003.
E
x/MPa
E
y/Mpa
G
x
y/MPa
G
x
z/MPa
G
y
z/MPa
u
x
y
11.3
11.3
1.7
370.2
246.6
0.33A finite element model of this subsystem is established using Altair OptiStruct. Honeycomb panel is meshed in HyperMesh using four-noded linear quad elements (CQUAD4) and composite properties are applied, where the core is orthotropic material and the sheets are isotropic material. All function devices are simplified by shell element and their mass is equivalent to the thickness of shells. Bolt connections are simplified as multipoint constraints and modeled by the flexible unit (RBE3). Two length of honeycomb panel are fixed in all six degrees of freedom. The finite element model is shown in Figure5.Figure 5
Finite element model of subsystem with honeycomb panel.For structure optimization, performance constraints shown in Table1 are used and the height of hexagonal honeycomb core H and the height of facing sheet h are selected as the design variables. The mass of subsystem is objective function. And mathematical models for honeycomb panel optimization could be described as (2)mindMdSubject  to:g1d=σp≤σsSg2d=ε≤0.3mmg3d=f1≥115Hzdmin≤d≤dmax,where M(d) is the total system mass, g(d) is performance constraint, σp is the actual stress value while σs is yield strength of facing sheet material, S is safety factor and the value is selected as 1.5 in this paper, ε is maximum deformation of PAS, f1 is fundamental frequency of this system, d is design variable and d=[h,H], and dmin and dmax are, respectively, lower and upper limit values of design variables and are shown in Table 4.Table 4
Lower and upper limit values of design variables.
Design variable
Initial dimension [mm]
Lower limit value [mm]
Upper limit value [mm]
h
2
0.15
5
H
36
10
100


## 3.2. PAS of Al-Li Alloy

The performance of frame structure largely depends on the properties of material. In this paper, Al-Li alloy 2090 is selected for comparative analysis with honeycomb panel while all boundary conditions, input loads, and layout of function devices are identical. 2090 is a kind of high performance material and its elastic modulus increased by about 10% while the density decreased by about 10% compared with the conventional aluminum alloy. So its stiffness-to-weight ratio and strength-to-weight ratio are improved remarkably. The mechanical parameters of 2090 versus conventional aluminum alloy 2Al12 are shown in Table5.Table 5
Mechanical parameters of 2090 versus 2Al12.
Material grade
Densityρ [kg⋅m−3]
Young’s modulusE [MPa]
Yield strengthσs [MPa]
σ
s/ρ [MPa⋅m3/kg]
E/ρ [MPa⋅m3/kg]
2090
2590
78600
530
0.2
30.3
2Al12
2780
70600
280
0.1
25.4For a plane-frame structure of pure Al-Li alloys, topology optimization is firstly used for a conceptual design proposal and then fine-tuned for manufacturability. Initial thickness of the plane-frame structure is a critical factor for topology optimization and the value of initial thickness directly determined the optimization result. Therefore, four values of initial thickness (40 mm, 50 mm, 60 mm, and 70 mm) are used, respectively, and the best thickness is determined by comparing the optimum results. At last, size optimization is executed to obtain a desired thickness of plane-frame structure. Similarly with honeycomb panel, Al-Li alloys plate is meshed with four-noded linear quad elements (CQUAD4) and the function devices are meshed in the same way. The finite element model is shown in Figure6. In order to retain installation points of function devices, the meshed plate will be divided into designable and nondesignable portions. The geometry for the design space is defined by inspection of the bounds. As shown in Figure 5, green areas are selected as nondesignable portions and insure that all fixing points (yellow points) are included.Figure 6
Finite element model for Al-Li alloys structure of PAS.
(a)
Finite element model
(b)
Designable and nondesignable portionsIn the process of topology optimization of Al-Li alloys plate, the initial thickness is defined and the design variable is element density of meshed plateρ. And mathematical model could be described as (3)minρMρSubject  to:g1ρ=σp≤σsSg2ρ=ε≤0.3mmg3ρ=f1≥115Hzρ∈0,1.After topology optimization, size optimization should be carried out to obtain a further optimized thickness of Al-Li alloys plate, so the thickness is selected as design variable and its initial value would be the selected result of topology optimization. The mathematical model of size optimization is shown in(4)mintMtSubject  to:g1t=σp≤σsSg2t=ε≤0.3mmg3t=f1≥115Hzt0-10≤t≤t0+10.


## 4. Optimization Results and Comparative Analysis

### 4.1. Optimization Results of Honeycomb Panel

After seven times of iteration, the results of structure optimization are obtained and shown in Figure7. The ultimate dimensions of design variables h and H are 1 mm and 99.4 mm, respectively. The ultimate mass of subsystem is 213.40 kg and the mass of honeycomb panel is 41.40 kg. However, bolt sockets embedded in honeycomb panel are inevitable and their mass must be taken into account. The number of bolt sockets used to fix function devices by M5 bolt is 103 and the mass of each bolt socket is 0.005 kg. Similarly, the number of bolt sockets used to fix honeycomb panel by M10 bolt is 32 and the mass of each bolt socket is 0.025 kg. Therefore, the total mass of bolt sockets is 1.315 kg and the mass of honeycomb panel including bolt sockets is 42.72 kg, which is 24.84% of total mass of all function devices. The maximum von Mises stress and deformation of honeycomb panel under input loads of three directions are shown in Table 6.Table 6
Maximum von Mises stress and deformation under input loads.
Input loads
Maximum von Mises stress [MPa]
Maximum deformation [mm]
X direction: 16.2G acceleration field
1.822
0.086
Y direction: 12.9G acceleration field
1.795
0.05237
Z direction: 9.5G acceleration field
1.25
0.1926Figure 7
Iterative process curve of honeycomb panel optimization.
(a)
Iterations of core’s height
(b)
Iterations of facing sheet’s height
(c)
Iterations of subsystem’s massModal analysis is carried out after structure optimization, and first two order modes of subsystem are shown in Figure8. Natural frequencies of first eight order modes are shown in Table 7. Harmonic response analysis is also conducted using performance constraints shown in Table 1. Modal damping is a critical parameter for harmonic response. The damping coefficient of composite material is commonly 5%~8% and 6% is taken for honeycomb panel in this paper. 13 codes of each function device are selected as output nodes during harmonic analysis. The maximum acceleration response of all nodes in X, Y, and Z directions is 16.0G, 9.3G, and 18.5G, respectively. So the acceleration response cannot exceed the requirement of subsystem, namely, 22G.Table 7
Natural frequencies of first eight order modes.
Mode order
1
2
3
4
5
6
7
8
Natural frequency [Hz]
114.8
137
164.7
169.6
186.9
216.5
234.4
238.9Figure 8
First and second order mode of subsystem.
(a)
First order mode
(b)
Second order mode


### 4.2. Optimization Results of Al-Li Alloy Structure

The topology optimization result using material distribution method is a density distribution of the finite elements in the design domain [16]. Density contours of Al-Li alloy structure are shown in Figure 9. Different thicknesses, 40 mm, 50 mm, 60 mm, and 70 mm, are chosen to implement topology optimization.Figure 9
Density contours of Al-Li alloy structure with different thickness.
(a)
40 mm
(b)
50 mm
(c)
60 mm
(d)
70 mmThe iterative process curves of Al-Li alloy structure of different thickness are shown in Figure10. The ultimate mass of 40 mm plate is 54.71 kg, 50 mm plate is 48.30 kg, 60 mm plate is 47.43 kg, and 70 mm plate is 48.54 kg. Therefore, the best thickness is 60 mm considering the light weight design. And a successive size optimization is necessary to obtain a more optimized thickness. Since boundaries of topology optimization result are discontinuous, the optimized structure cannot satisfy practical manufacturing requirements. So model reconstruction is needed according to density contour. The structure of topology optimization is most efficient load path for various constraints, so reconstructed model would inevitably lead to degrading the performance or augmenting the mass, or even degrading the performance while augmenting its mass. The reconstructed model of Al-Li alloy plate considering manufacturing requirements is shown in Figure 11. All inclined beams or irregular structures are modified to straight ones. In order to enhance the strength of fixed lengths, all of the other color parts of two lengths are changed to red parts. Other details are also adjusted to meet the requirements of processing. The mass of reconstructed plate is 47.23 kg and slightly lower than original 47.43 kg. Fundamental frequency is 110.7 Hz, so the performance of reconstructed plate degraded and further optimization is needed.Figure 10
Iterative process curve of Al-Li alloy plate with different thickness.Figure 11
The topology optimization modal versus reconstructed model of Al-Li alloy plate.Size optimization of reconstructed model is carried out based on the mathematical model presented in Section3.2. After two times of iteration, the optimized thickness of Al-Li alloy plate is got and the value is 62.54 mm. The mass of Al-Li alloy plate increases to 48.39 kg and the fundamental frequency increases to 115.4 Hz, simultaneously. The maximum von Mises stress and deformation of Al-Li alloy plate under input loads of three directions are shown in Table 8. Stress nephogram of subsystem in the X direction is shown in Figure 12. The damping coefficient of Al-Li alloy plate is supposed to be 3% and its maximum acceleration response of all function devices in X, Y, and Z directions is 17.4G, 10.5G, and 19.6G, respectively.Table 8
Maximum von Mises stress and deformation under input loads.
Input loads
Maximum von Mises stress [MPa]
Maximum deformation [mm]
X direction: 16.2G acceleration field
11.3
0.07868
Y direction: 12.9G acceleration field
16.48
0.05293
Z direction: 9.5G acceleration field
17.24
0.1687Figure 12
Stress nephogram of subsystem in theX direction.Modal analysis is carried out after size optimization, and first two order modes of subsystem are with Al-Li alloy plate shown in Figure13. Natural frequencies of first eight order modes are shown in Table 9.Table 9
Natural frequencies of first eight order modes.
Mode order
1
2
3
4
5
6
7
8
Natural frequency [Hz]
115.3
190
215.2
251
186.9
279.6
294.3
317Figure 13
First and second order mode of subsystem with Al-Li alloy plate.
(a)
First order mode
(b)
Second order mode


### 4.3. Comparative Analysis of Two Materials

After structural optimization, the optimized performance of two materials is obtained and shown in Table10. All performance indices met the requirements and the eventual mass of APH is slightly lighter than Al-Li alloy. The first order modals of two structures are both the vibration perpendicular to the plate face (Z direction) and the deformation of Z direction is maximum. The maximum von Mises stress of Al-Li alloy structure is much larger than that of honeycomb panel. Fundamental frequency and harmonic response are almost same. As can be seen from the comparison results, the performance of honeycomb panel is slightly superior to Al-Li alloy.Table 10
Comparative analysis of optimization results of two materials.
Performance
Requirements
Optimization results of AHP
Optimization results of Al-Li alloy
Maximum stress
≤187 MPa
1.82 MPa (X direction)
17.24 MPa (Z direction)
Maximum deformation
≤0.3 mm
0.19 mm (Z direction)
0.17 mm (Z direction)
Fundamental frequency
≥115 Hz
114.8 Hz
115.3 Hz
Harmonic response
≤22G
18.5G
19.6G
Mass
Minimized mass
42.72 kg
48.39 kg


## 4.1. Optimization Results of Honeycomb Panel

After seven times of iteration, the results of structure optimization are obtained and shown in Figure7. The ultimate dimensions of design variables h and H are 1 mm and 99.4 mm, respectively. The ultimate mass of subsystem is 213.40 kg and the mass of honeycomb panel is 41.40 kg. However, bolt sockets embedded in honeycomb panel are inevitable and their mass must be taken into account. The number of bolt sockets used to fix function devices by M5 bolt is 103 and the mass of each bolt socket is 0.005 kg. Similarly, the number of bolt sockets used to fix honeycomb panel by M10 bolt is 32 and the mass of each bolt socket is 0.025 kg. Therefore, the total mass of bolt sockets is 1.315 kg and the mass of honeycomb panel including bolt sockets is 42.72 kg, which is 24.84% of total mass of all function devices. The maximum von Mises stress and deformation of honeycomb panel under input loads of three directions are shown in Table 6.Table 6
Maximum von Mises stress and deformation under input loads.
Input loads
Maximum von Mises stress [MPa]
Maximum deformation [mm]
X direction: 16.2G acceleration field
1.822
0.086
Y direction: 12.9G acceleration field
1.795
0.05237
Z direction: 9.5G acceleration field
1.25
0.1926Figure 7
Iterative process curve of honeycomb panel optimization.
(a)
Iterations of core’s height
(b)
Iterations of facing sheet’s height
(c)
Iterations of subsystem’s massModal analysis is carried out after structure optimization, and first two order modes of subsystem are shown in Figure8. Natural frequencies of first eight order modes are shown in Table 7. Harmonic response analysis is also conducted using performance constraints shown in Table 1. Modal damping is a critical parameter for harmonic response. The damping coefficient of composite material is commonly 5%~8% and 6% is taken for honeycomb panel in this paper. 13 codes of each function device are selected as output nodes during harmonic analysis. The maximum acceleration response of all nodes in X, Y, and Z directions is 16.0G, 9.3G, and 18.5G, respectively. So the acceleration response cannot exceed the requirement of subsystem, namely, 22G.Table 7
Natural frequencies of first eight order modes.
Mode order
1
2
3
4
5
6
7
8
Natural frequency [Hz]
114.8
137
164.7
169.6
186.9
216.5
234.4
238.9Figure 8
First and second order mode of subsystem.
(a)
First order mode
(b)
Second order mode


## 4.2. Optimization Results of Al-Li Alloy Structure

The topology optimization result using material distribution method is a density distribution of the finite elements in the design domain [16]. Density contours of Al-Li alloy structure are shown in Figure 9. Different thicknesses, 40 mm, 50 mm, 60 mm, and 70 mm, are chosen to implement topology optimization.Figure 9
Density contours of Al-Li alloy structure with different thickness.
(a)
40 mm
(b)
50 mm
(c)
60 mm
(d)
70 mmThe iterative process curves of Al-Li alloy structure of different thickness are shown in Figure10. The ultimate mass of 40 mm plate is 54.71 kg, 50 mm plate is 48.30 kg, 60 mm plate is 47.43 kg, and 70 mm plate is 48.54 kg. Therefore, the best thickness is 60 mm considering the light weight design. And a successive size optimization is necessary to obtain a more optimized thickness. Since boundaries of topology optimization result are discontinuous, the optimized structure cannot satisfy practical manufacturing requirements. So model reconstruction is needed according to density contour. The structure of topology optimization is most efficient load path for various constraints, so reconstructed model would inevitably lead to degrading the performance or augmenting the mass, or even degrading the performance while augmenting its mass. The reconstructed model of Al-Li alloy plate considering manufacturing requirements is shown in Figure 11. All inclined beams or irregular structures are modified to straight ones. In order to enhance the strength of fixed lengths, all of the other color parts of two lengths are changed to red parts. Other details are also adjusted to meet the requirements of processing. The mass of reconstructed plate is 47.23 kg and slightly lower than original 47.43 kg. Fundamental frequency is 110.7 Hz, so the performance of reconstructed plate degraded and further optimization is needed.Figure 10
Iterative process curve of Al-Li alloy plate with different thickness.Figure 11
The topology optimization modal versus reconstructed model of Al-Li alloy plate.Size optimization of reconstructed model is carried out based on the mathematical model presented in Section3.2. After two times of iteration, the optimized thickness of Al-Li alloy plate is got and the value is 62.54 mm. The mass of Al-Li alloy plate increases to 48.39 kg and the fundamental frequency increases to 115.4 Hz, simultaneously. The maximum von Mises stress and deformation of Al-Li alloy plate under input loads of three directions are shown in Table 8. Stress nephogram of subsystem in the X direction is shown in Figure 12. The damping coefficient of Al-Li alloy plate is supposed to be 3% and its maximum acceleration response of all function devices in X, Y, and Z directions is 17.4G, 10.5G, and 19.6G, respectively.Table 8
Maximum von Mises stress and deformation under input loads.
Input loads
Maximum von Mises stress [MPa]
Maximum deformation [mm]
X direction: 16.2G acceleration field
11.3
0.07868
Y direction: 12.9G acceleration field
16.48
0.05293
Z direction: 9.5G acceleration field
17.24
0.1687Figure 12
Stress nephogram of subsystem in theX direction.Modal analysis is carried out after size optimization, and first two order modes of subsystem are with Al-Li alloy plate shown in Figure13. Natural frequencies of first eight order modes are shown in Table 9.Table 9
Natural frequencies of first eight order modes.
Mode order
1
2
3
4
5
6
7
8
Natural frequency [Hz]
115.3
190
215.2
251
186.9
279.6
294.3
317Figure 13
First and second order mode of subsystem with Al-Li alloy plate.
(a)
First order mode
(b)
Second order mode


## 4.3. Comparative Analysis of Two Materials

After structural optimization, the optimized performance of two materials is obtained and shown in Table10. All performance indices met the requirements and the eventual mass of APH is slightly lighter than Al-Li alloy. The first order modals of two structures are both the vibration perpendicular to the plate face (Z direction) and the deformation of Z direction is maximum. The maximum von Mises stress of Al-Li alloy structure is much larger than that of honeycomb panel. Fundamental frequency and harmonic response are almost same. As can be seen from the comparison results, the performance of honeycomb panel is slightly superior to Al-Li alloy.Table 10
Comparative analysis of optimization results of two materials.
Performance
Requirements
Optimization results of AHP
Optimization results of Al-Li alloy
Maximum stress
≤187 MPa
1.82 MPa (X direction)
17.24 MPa (Z direction)
Maximum deformation
≤0.3 mm
0.19 mm (Z direction)
0.17 mm (Z direction)
Fundamental frequency
≥115 Hz
114.8 Hz
115.3 Hz
Harmonic response
≤22G
18.5G
19.6G
Mass
Minimized mass
42.72 kg
48.39 kg


## 5. Conclusion

In order to compare the performance of Al-Li alloy and honeycomb panel which are both excellent materials for aeronautical structures, the mathematical models of structural optimization are established for these two distinctively different materials. Altair OptiStruct is used to carry out the optimized analysis. Honeycomb panel is seen as an integral structure and only size optimization is used to obtain its optimized heights. Topology and size optimization are applied to obtain the optimized configuration and thickness of the Al-Li alloy plate. The mass of optimized AHP including bolt sockets is 42.72 kg and that of Al-Li alloy plate is 48.39 kg, so AHP is superior to Al-Li alloy for weight reduction consideration. The optimization procedure shows that structural optimization is an excellent method for material selection in the conceptual design phase.



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*Source: 815257-2015-09-29.xml*