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FEM Simulation of a FML Full Scale Aeronautic Panel Undergoing Static Load | OMICS International
ISSN: 2169-0316
Industrial Engineering & Management
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FEM Simulation of a FML Full Scale Aeronautic Panel Undergoing Static Load

R. Citarella1*, E Armentani2, R Sepe2 and F Caputo3

1 Department of Industrial Engineering, University of Salerno, Fisciano (SA), Italy

2 Department of Materials Engineering and Production, University of Naples, P.le V. Tecchio, 80–80125 Naples, Italy

3 Department of Industrial and Information Engineering, Second University of Naples, via Roma 29 – 81031 Aversa (CE) Italy

*Corresponding Asuthor:
R Citarella
Department of Industrial Engineering
University of Salerno, Fisciano (SA), Italy
E-mail: [email protected]

Received December 10, 2013; Accepted January 22, 2014; Published January 29, 2014

Citation: Citarella R, Armentani E, Sepe R, Caputo F (2014 FEM Simulation of a FML Full Scale Aeronautic Panel Undergoing Static Load. Ind Eng Manage 3:122. doi:10.4172/2169-0316.1000122

Copyright: © 2014 Citarella R, et al. This is an open-access article distributed under the terms of the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original author and source are credited.

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Abstract

This paper concerns the numerical characterization of the static strength of a flat stiffened panel, designed as a fiber metal laminates (FML) and made of Aluminium alloy and Fiber Glass FRP. The panel is full scale and was tested under static loads, applied by means of an in house designed and built multi-axial fatigue machine. The static test is simulated by the Finite Element Method (FEM) in a three-dimensional approach. The strain gauge outcomes are compared with corresponding numerical results, getting a satisfactory correlation.

Keywords

Multiaxial fatigue; FEM simulation; FML; Full scale panel

Introduction

To achieve high-performance aircraft structures new tailored and cost-effective materials are continuosly designed and tested. Nowadays the Fibres Metal Laminate (FML) technology is optimised for fatigue and damage tolerance properties, that is one of the reasons for its application in the upper shells of the A380 fusolage, but a balanced performance in terms of static properties is also obtainable, leading to a significant reduction in terms of weight and operating cost. This paper concerns an investigation on the application of innovative materials obtained by the use of improved lamina and fibre reinforcements (FML) to panels of a typical wide body fuselage section. The requirements for a numerical model, based on the Finite Element Method (FEM), capable of assessing the static behaviour of selected details made of FML (Glare is an example of such hybrid material with considerably good damage tolerance properties), are provided. The forward side panel of the DIALFAST fuselage has been considered (DIALFAST is acronym of Development of Innovative and Advanced Laminates for Future Aircraft Structures, an European project in which such panel was developed and analysed).

Panel description and experimental test

A Metal Barrel, which is representative of Airbus A330/340 fuselage section 16 (Figure 1a), has been considered as a reference structure in order to define the design solution for a stiffened panel made of innovative FML. The panel, whose dimensions are 2181 x 2181 mm (excluding the aluminium gripping plates), consists of three bays joined together by butt-straps and z-shape stringer coupling; windows cut-outs are included in the structure (Figure 1b). The stringer pitch and the frame pitch are equal to, respectively, 172.3 mm and 533 mm. The panel is made of two parts: an upper and a lower panel, joined by a lap joint at the stringer N.4 (Figure 2). The frames are applied on both panel sides to minimize the secondary bending effects. In detail the panel consists of the following parts: FML skin, FML stringers bonded to the skin, metallic frames and cleats (Al 2024-T3 clad sheet) riveted to the skin, metallic window frames (7075 – T651 Hand forming) bonded to the skin. (Tables 1a and 1b) show the FML skin (3/2-0.3mm-0°/90°) and stringer (3/2-0.3 mm-0°/0°) layups and the used materials. The tested panel has been instrumented with strain gages that are located on both sides in order to provide information about the secondary bending relevance. Specifically ten strain rosettes with three legs disposed at 0°- 45°-90° (type CEA-13-250UR-350) and 8 strain gages (type CEA-13- 250UW-350) were installed on the specimen. The strain gages were bonded on both sides of the panel (side A and B) by a two-component epoxy adhesive in order to assure good performance also with large strains. The layout of strain rosettes and strain gages on the side A is shown in (Figure 2); whereas the positioning coordinates (x, y) of strain gages and rosettes are reported in (Table 2). The tested specimen has been subjected to a load test (load values are taken from previous studies developed within DIALFAST project) by the Multiaxial test machine shown in (Figure 1b) [1]. Eight clamps on each side of the panel transfer the load by 4 properly shaped pins, either by shear or by pin clamping friction. The 8 clamps are linked by a lever system to their respective traction load-applying cylinders. To apply the external loads without causing damages on the panel borders, six aluminium plates are joined to the panel. This loading system allows independent deformations along different directions on the skin plane. The same set of grips applies both normal and shear loads; a balancing system assures that the normal load is uniformly distributed on the edge. The boundary conditions are “simply supported edges” constraints, i.e. the in-plane displacements are allowed, whereas the out-of-plane displacements at the panel edges are constrained by means of a rolling bearing system. Loads are applied along one direction by two hydraulic cylinders and the maximum value is equal to Py = 250 kN, with loads applied in load control with a ramp of 1 kN/sec.

industrial-engineering-dialfast-barrel-tested-panel

Figure 1: a-b DIALFAST barrel and tested panel loaded by the Multi-axial fatigue machine.

industrial-engineering-strain-gage-rosette-configuration

Figure 2: Strain gage and rosette configuration on side A.

PLY MATL SKIN ORIENT. STRINGER ORIE. THK [mm] Component Material
P1 LAMINA N/A N/A 0.3 Lamina Skin Alloy 7475 – T761
P2 F/G 0.125 FG Prepreg FG FM 94-22% - S2 GLASS – 187-460
P3 F/G 90° 0.125
P1 LAMINA N/A N/A 0.3 Frame Alloy 2024 – T3 CLAD
P3 F/G 90° 0.125 Shear cleats Alloy 2024 – T3 CLAD
P2 F/G 0.125 Window frame Alloy 7075 – T651
P1 LAMINA N/A N/A 0.3 Plates Alloy 6056 – T4

Table 1: a-b Skin and stringer lay-up and adopted material.

Side A R1 R2 R3 R4 R5 R6 S1 S2
x [mm] 1017 1430 1220 1220 1220 2104 970 1500
y [mm] 1835 1475 2010 1320 631 1655 787 787
Side B R7 R8 R9 R10 S3 S4 S5 S6
x [mm] 1220 1220 1017 1430 1500 970 1332 1332
y [mm] 2010 1320 1835 1475 787 787 1767 1543

Table 2: Strain gages and rosette positions on sides A and B of the panel.

FEM model

The FEM model (Figure 3) is based on 194983 nodes belonging to 227451 elements. More in details: 199862 shell elements (Shell 181 from the ANSYS element library) with 4 nodes to model skin and stiffeners, 2377 beam elements (Beam4) to simulate the rivets whereas the remaining 25212 are spring elements (Combin14) to simulate the bonding between the two joined skins (Figure 4).

industrial-engineering-fe-geometric-model-global-view

Figure 3: FE geometric model: global view with highlight of skin layers (up) and details of stringer and frame connection to the underlying skin (down).

industrial-engineering-overall-fem-model

Figure 4: Overall FEM model with mesh close-up around the windows.

The shell elements adopted for the skin modelling incorporates the properties of each single FML layer (Figure 3): in particular the composite layer has the mechanical properties listed in (Table 3). A geometric non linear static analysis was developed [2-3].

E1 E2 E3 V12 V13 V23 G12 G13 G23 ρ
GPa GPa GPa [-] [-] [-] GPa GPa GPa kg/mm3
53.2 9.3 9.3 0.279 0.279 0.49 5.495 5.495 3.121 1.974.10-6

Table 3: Mechanical properties of FG FM 94-27%-S2-Glass-187-460.

Results

The FEM contour plots of strains in the directions provided by the strain gauges are shown in (Figure 5) and can be compared with the corresponding Boundary Element Method (BEM) [4-7] results presented in [8]. In (Table 4) the strains calculated by the FEM analysis are compared with the corresponding values coming from measurements on the test article.

industrial-engineering-contour-plot-strains

Figure 5: Contour plot of strains [ ] in the direction defined by the corresponding strain gauges (listed in the captions of each image).

Strain gauge Experimental strain [μm] Numerical strain [μm] Error (%)
R1-1 156 287 84%
R1-2 806 881 9%
R1-3 285 213 -25%
R9-1 307 267 -13%
R9-2 883 945 7%
R9-3 335 393 17%
R2-1 82 377 360%
R2-2 839 854 2%
R2-3 316 275 -13%
R10-1 253 380 50%
R10-2 809 883 9%
R10-3 243 227 -7%
R3-1 408 361 -12%
R3-2 892 823 -8%
R3-3 369 358 -3%
R7-1 387 415 7%
R7-2 902 925 3%
R7-3 414 411 -1%
R4-1 343 450 31%
R4-2 927 925 0%
R4-3 368 420 14%
R8-1 340 337 -1%
R8-2 788 723 -8%
R8-3 285 340 19%
R5-1 357 405 13%
R5-2 986 1079 9%
R5-3 355 420 18%
R6-1 43 43 0%
R6-2 498 554 11%
R6-3 270 392 45%
S1 915 1004 10%
S4 787 740 -6%
S2 1000 1069 7%
S3 849 752 -11%
S5 612 698 14%
S6 639 761 19%
S7 -141 -136 -4%
S8 -133 -147 11%

Table 4: Numerical (FEM) and experimental correlation.

The correlation between numerical (FEM) and experimental results is judged satisfactory but some margins of improvements are still available, considering that a simplified two dimensional BEM approach (characterized by a straightforward modeling and meshing process) allowed analogous accuracy [8]. The next step will be the introduction of a crack in the model and the simulation of its propagation with the approach used in [9-10].

Conclusions

Even if in most of the strain gauge positions the correlation between numerical and experimental deformations is satisfactory, there is still some needed work to improve the FEM model as pointed out by the mismatch between the strains calculated and measured on positions R1-1, R1-3, R2-1, R10-1, R4-1, and R6-3. Sometimes the reason of the aforementioned mismatch can be found in a failure or malfunctioning of the involved strain gauge whereas in other cases it depends on the numerical model accuracy: the precise assessment of the two cases is currently under investigation.

Some margins of simplification of the FEM model have been already devised and could consist in the replacement of the detailed rivet connection (hundreds of rivets have been explicitly modelled) with continuous bonding between the layers in which the “density” of such rivets is sufficiently high.

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