International Journal of Antennas and PropagationVolume 2012 (2012), Article ID 829780, 9 pagesdoi:10.1155/2012/829780

Research Article

Development of Full-Scale Ultrathin Shell Reflector

Durmuş Türkmen,¹ Ömer Soykasap,² and Şükrü Karakaya³

¹Department of Mechanical Engineering, Pamukkale University, 20070 Denizli, Turkey²Department of Material Science and Engineering, Afyon Kocatepe University, 03200 Afyonkarahisar, Turkey³Department of Mechanical Education, Afyon Kocatepe University, 03200 Afyonkarahisar, Turkey

Received 16 December 2011; Accepted 21 March 2012

Academic Editor: Carles Fernández-Prades

Copyright © 2012 Durmuş Türkmen et al. This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.

Abstract.

It is aimed that a new ultrathin shell composite reflector is developed considering different design options to optimize the stiffness/mass ratio, cost, and manufacturing. The reflector is an offset parabolic reflector with a diameter of 6 m, a focal length of 4.8 m, and an offset of 0.3 m and has the ability of folding and self-deploying. For Ku-band missions a full-scale offset parabolic reflector antenna is designed by considering different concepts of stiffening: (i) reflective surface and skirt, (ii) reflective surface and radial ribs, and (iii) reflective surface, skirt, and radial ribs. In a preliminary study, the options are modeled using ABAQUS finite element program and compared with respect to their mass, fundamental frequency, and thermal surface errors. It is found that the option of reflective surface and skirt is more advantageous. The option is further analyzed to optimize the stiffness/mass ratio considering the design parameters of material thickness, width of the skirt, and ply angles. Using the TOPSIS method is determined the best reflector concept among thirty different designs. Accordingly, new design can be said to have some advantages in terms of mass, natural frequency, number of parts, production, and assembly than both SSBR and AstroMesh reflectors.

1. Introduction

There have been extensive studies on spaceborne reflectors to increase the performance with a reduced cost. There are a number of reflector concepts; selection of the best concept depends on application and size of the reflectors. The main requirement for large reflectors is that they must be packaged in the limited volume of the launch vehicle, and they must be deployed to required shape in orbit. In order to compactly package a large reflector, the structure is to be folded or bent; the smaller packaged volume is required to lower the launch cost [1, 2]. Folding and self-deploying shell reflector has a thin reflective surface and some reinforcements to stiffen the structure, which are designed to allow folding [3]. Tan et al. studied the stiffened spring-back reflector (SSBR), showing the feasibility, folding, and self-deploying capability of a 0.8 scaled demonstrator. The full-size high-accuracy offset reflector of 6 m diameter met the requirements for Ku-band application [4]. Datashvili et al. studied the technical assessment of the high-accuracy large-spaceborne reflector antenna concepts for Ku-band. Thin shell reflector antenna (SSBR) was selected as one of the best options. The SSBR concept has several advantages over the current state-of-the-art AstroMesh reflector, namely, simplicity, relatively lower manufacturing costs, a lower surface error, and a simpler folding. On the other hand, the main advantages of AstroMesh are its lower mass and its small packaged volume [1, 5].

In this study, it is aimed that a new ultrathin shell composite reflector is developed considering different design options to optimize the stiffness/mass ratio, cost, and manufacturing. SSBR is taken as reference reflector with a diameter of  m, a focal length of  m, and an offset distance of 0.3 m. The concepts of stiffening the reflector structure include (i) reflective surface and skirt, (ii) reflective surface and radial ribs, and (iii) reflective surface, skirt, and radial ribs. In a preliminary study, the options are modeled using the ABAQUS finite element program [6] and compared in terms of their mass and fundamental frequencies. It is found the concept of reflective surface and skirt is more advantageous over the other options. The concept is further analyzed to optimize the stiffness/mass ratio considering the design parameters of thickness of the skirt, width of the skirt, and ply angles. Using the TOPSIS method will be determined the best reflector design among thirty different designs. Then, new design will be compared with SSBR and AstroMesh reflectors.

2. Preliminary Design

The full-scale reflector is an offset parabolic reflector with a diameter of  m, a focal length of  m, and an offset of  m. The reflector is modeled in the ABAQUS finite element software; first, the main paraboloid is created; next the offset reflector surface is obtained by a cut using a cylinder with its axis being parallel to the axis of the paraboloid. Figure 1 shows the details of the modeling, where offset distance  m and diameter of the reflector  m. There is also flat skirt with a width of 0.15 m around the rim of the reflector. The SSBR used a triaxial carbon fiber/epoxy for the reflector, but there are thermal distortion problems in the triaxial material; hence, a plain weave carbon/epoxy is chosen instead for the new reflector. The reflector is assumed to be made of plain weave carbon T300B/L160 epoxy, with an areal density of dry cloth of 94 g/m² and a ply thickness of 0.11 mm. Material properties of a single ply are obtained for a fiber volume fraction of as  GPa,  GPa, , and  kg/m³, which is based on the analytical approach developed for plain-woven composite materials [7].

Figure 1: Offset reflector.

The three concepts of stiffening the reflector structure include (i) reflective surface and skirt, (ii) reflective surface and radial ribs, and (iii) reflective surface, skirt, and radial ribs. The reflector surface is modeled as a laminated composite shell, using S4R quadratic elements, with a total number of elements of 14250. The concepts are compared in terms of mass and fundamental frequency.

2.1. The Concept of Reflective Surface and Skirt

It is envisaged that a reflector with much simpler design and significantly lower mass and lower cost is possible by considering some design changes on SSBR. First, several stiffening elements including radial, spiral, central, and rim reinforcements and a skirt were used in the original SSBR. All reinforcing elements except the skirt are removed in the new reflector in order to simplify the structure and to reduce its mass. Second, there were circumferential slits on the skirt near the rim that was introduced to reduce the stress and/or strain in the structure during folding. All slits are removed in the new concept. Hence, we consider only reflective surface with a flat skirt to investigate full advantage of stiffening.

The concept is modeled in ABAQUS as seen in Figure 2. It consists of two parts: reflective surface and skirt that are connected to each other by tie constraints. The skirt is made of three plies (0/45/0) and a width of 0.15 m, whereas the reflective surface is made of either three plies (0/45/0) or two plies (0/45). The case of reflective surface and skirt is denoted as case E.

Figure 2: Reflective surface with flat skirt, case E.

2.2. The Concept of Reflective Surface and Rib

Composite tape springs are commonly used for deployable structures for stiffening the structure. The tape springs exhibit high initial stiffness in deployed configuration and folds and deploys elastically (can be seen in Figure 7).

Therefore, it can be a good choice to stiffen the reflective surface as a rib. Figures 3 and 4 show the modeled reflector with initially curved large tape springs. Two options are considered: (i) the tape springs are attached to the back of the reflective surface and subject to opposite sense bending during folding of the reflector denoted as case T and (ii) the tape springs are attached to the back of the reflective surface and subject to equal sense bending during folding of the reflector denoted as case D. For case T, the tape springs have the same longitudinal curvature as the reflective surface and are connected to the reflective surface tangentially. For case D, the tape springs have the same longitudinal curvature as the reflective surface, but are connected to the reflective surface through their edges. For both cases, eight tape springs are considered and connected to reflective surface by tie constraints. The tape springs have a subtended angle of 60 deg and transverse radius of 0.3 m and are made of three ply (0/45/0) composites of the same material. Again the reflective surface is assumed to be made of either three plies (0/45/0) or two plies (0/45).

Figure 3: Reflective surface with tape springs, case T.

Figure 4: Reflective surface with tape spring, case D.

2.3. Concept of Reflective Surface with Skirt and Ribs

In this concept the reflective surface is stiffened by both skirt and ribs. Flat skirt is added to the models shown in Figures 3 and 4 by tie constraints. The skirt and ribs are assumed to have three plies (0/45/0). The cases of reflective surface with skirt and ribs are denoted as case ED and case ET.

2.4. Results of Preliminary Analysis

The modal analysis is carried out for each reflector under free boundary conditions; the natural frequencies, mass, and the mode shapes are obtained. The results are given in Table 1. The cases of E, D, and ED with reflective surface of two plies are better when high fundamental frequency with low mass is considered. The reflective surface with two plies is advantageous due to less thickness and material cost.

Table 1: Comparison of different design cases.

Designs
Frequency, (Hz)
mass (kg)

Mode 1
Mode 2
Mode 3
Mode 4
Mode 5
Mode 6
Mode 7
Mode 8

case Ea
1.025
1.124
3.362
3.385
6.735
6.775
9.282
9.734
15.91

case Eb
1.110
1.212
3.632
3.654
6.920
6.942
7.712
7.725
11.08

case Ta
0.254
0.274
0.328
0.395
0.407
1.018
1.092
1.097
17.69

case Tb
0.232
0.277
0.295
0.351
0.356
0.796
0.905
1.065
12.86

case Da
1.515
1.536
2.262
2.475
2.605
3.251
3.612
3.674
17.69

case Db
1.448
1.461
2.078
2.290
2.328
2.681
2.865
2.914
12.86

case ETa
1.102
1.190
3.516
3.531
6.789
7.145
9.680
9.796
19.15

case ETb
1.178
1.260
3.712
3.722
6.925
7.353
8.288
8.479
14.32

case EDa
2.254
2.314
5.077
5.089
8.306
8.476
9.990
10.18
19.15

case EDb
2.293
2.342
5.160
5.182
7.972
8.136
8.426
8.635
14.32

a: reflective surface with three plies, b: reflective surface with two plies.

The reflective surface with skirt, case E, has the lowest mass, and it also satisfies the requirement of a minimum fundamental frequency of 1 Hz. It can be manufactured as a single piece. It allows folding and self-deploying. Hence, it is the best option compared to the other cases.

The reflective surface with rib, case D, has a slightly higher mass and a higher fundamental frequency. However, the other modes except mode two have less natural frequencies than that of case E. The reflective surface and the ribs must be manufactured separately. Attachment of the ribs to the reflective surface is another issue that must be further studied. 3D folding behavior of the ribs or the reflective surface with ribs should be investigated.

The reflective surface with skirt and ribs, case ED, has the highest fundamental frequency but with a higher mass. This makes manufacturing even more difficult, and it has still the same drawbacks of case D.

The mode shapes of the options are given in Figure 5. In all cases mode shapes have circumferential sine waves along the rim of the reflector. Two consecutive natural frequencies are close to each other; corresponding modes are similar but with a phase angle.

Figure 5: First four modes of the cases E, T, D, ET, and ED with three-ply reflective surface, from top to down.

2.5. Thermal Analysis

Structural parts that work in space environment are subject to great temperature variance. So, the structural parts need to be made of materials with low coefficient of thermal expansion (CTE). Thermal changes that occur in orbit cause surface errors and reductions in performance. Thermal analysis is carried out under thermal loads for the best three designs of case , case , and case , and then the surface error is estimated, which can be used to estimate the electrical performance. In order to measure the surface accuracy, root mean square error (RMS) is considered. The surface accuracy of reflective surface can be obtained by considering the ideal design surface and the best-fit paraboloid surface. The best-fit paraboloid is defined in coordinate system as , and it is obtained by minimizing the RMS error using parameters of Euler rotation angles (, , ) and the parameters of translations (, , ) from the coordinate system as follows: RMS error in direction is calculated for all the nodes as follows: where is the coordinate of a point of distorted surface and is the corresponding coordinate of the best-fit paraboloid.

The woven carbon/epoxy composite, which is used for the reflective surface and the ribs, has a CTE of between /°C and /°C. However, a lower CTE is obtained when special resin for the space applications is used; hence a CTE of /°C is taken for the analysis. Thermal loading conditions are as follows [1, 8]:LC1:a gradient along the -direction of 100°C over the total length of the reflector,LC2:uniform absolute temperature −150°C,LC3:uniform absolute temperature 170°C.

The thermal loads are applied to the finite element model of three concepts using initial temperature of 20°C. The displacement contours are shown in Figure 6 for each concept. The focal length and RMS error for each concept are given in Table 2. The worst loading is LC2 for both RMS and the focal length. All concepts yield similar results of a low RMS error and small variation in the design focal length; hence they all are acceptable.

Table 2: RMS errors for thermal loads.

Thermal loads
Eb
Db
EDb

RMS (mm)
(mm)
RMS (mm)
(mm)
RMS (mm)
(mm)

LC1
0.003
4800.25
0.06
4800.36
0.045
4800.16

LC2
0.050
4802.52
0.08
4800.75
0.055
4800.90

LC3
0.035
4800.40
0.04
4800.20
0.032
4800.25

(a)

(b)

(c)

Figure 6: Displacement magnitudes due to LC3 thermal loading (units in mm), case (a), case , (b), and case (c).

Figure 7

3. Optimization of the Reflector with Skirt

The preliminary study showed that the option of reflective surface with skirt suits better for low cost, low mass, and sufficient stiffness. Therefore, it is chosen as the best concept for the new thin shell reflector. In order to increase stiffness while keeping low mass the structure is optimized considering design changes. During the optimization the following is considered for the design. First the reflective surface is to have a continuous surface; no discontinuity is allowed. Next the reflector mass should be less than 14 kg. Then the reflector has the minimum number of parts with manufacturing ease and low cost. Last but not least the reflector must be foldable.

The design parameters are the thickness of the skirt, , width of the skirt, , and composite ply angles of the skirt. Three different widths, 150 mm, 200 mm, and 250 mm, for the skirt and a maximum of six plies for the skirt are considered. The reflective surface has the plies 0/45 with a thickness of 0.22 mm, which are taken to be constant. The mass and fundamental frequencies are given in Table 3.

Table 3: Comparison of different designs of reflective surface with skirt.

Design no.

Skirt with plies ,  mm

(mm)
mass (kg)
Freq. (Hz)

1
2
0.22
10.600
0.768

2
3
0.33
11.085
0.850

3
4
0.44
11.550
0.912

4
5
0.55
12.020
0.954

5
6
0.66
12.500
0.988

Skirt with plies ,  mm

(mm)
mass (kg)
Freq. (Hz)

6
2
0.22
10.930
1.025

7
3
0.33
11.560
1.127

8
4
0.44
12.200
1.199

9
5
0.55
12.840
1.245

10
6
0.66
13.475
1.278

Skirt with plies ,  mm

(mm)
mass (kg)
Freq. (Hz)

11
2
0.22
11.260
1.330

12
3
0.33
12.060
1.469

13
4
0.44
12.860
1.533

14
5
0.55
13.660
1.569

15
6
0.66
14.460
1.585

Skirt with plies ,  mm

(mm)
mass (kg)
Freq. (Hz)

16
0
0.22
10.600
1.070

17
1
0.33
11.085
1.195

18
2
0.44
11.550
1.350

19
3
0.55
12.020
1.388

20
4
0.66
12.500
1.399

Skirt with plies ,  mm

(mm)
mass (kg)
Freq. (Hz)

21
0
0.22
10.930
1.470

22
1
0.33
11.560
1.620

23
2
0.44
12.200
1.829

24
3
0.55
12.840
1.851

25
4
0.66
13.475
1.852

Skirt with plies ,  mm

(mm)
mass (kg)
Freq. (Hz)

26
0
0.22
11.260
1.702

27
1
0.33
12.060
1.990

28
2
0.44
12.860
2.145

29
3
0.55
13.660
2.135

30
4
0.66
14.460
2.105

Adding 45 deg plies to the skirt increases the frequency. Increasing the width of the skirt increases both the mass and the frequency of the structure. The design with a skirt of 0/45/45/0 and a width of 250 mm has the highest frequency/mass ratio. However, the frequency is not critical; the design with a skirt of 0/45/0 and a width of 250 mm has the second highest frequency/mass ratio but has a lower mass and frequency.

3.1. Determination of the Best Offset Reflector Model Using TOPSIS Method

The TOPSIS method developed by Hwang and Yoon is one of the multicriteria decision-making techniques. The basis of the method is the decision points based on the proximity of the ideal solution. With this method, the maximum and minimum values can be compared to the ideal state [9–13]. The TOPSIS method consists of six steps. The TOPSIS method steps are described below.

Step 1 (creating the decision matrix). The decision matrix consists of rows of decision point located in the lines. Factors in the evaluation takes place in the columns. The decision matrix is shown as follows: is the matrix, the number of decision point, and the number of assessment factor.

Step 2 (creating standard decision matrix ()). Standard decision matrix is calculated using the following formula: Thus, the matrix is obtained as follows:

Step 3 (constructing the weighted normalized decision matrix ()). Weight values are determined according to purpose (). Then each column of the matrix elements multiplying with value and matrix is created:

Step 4 (ideal () and negative ideal () creating solutions). For creating the ideal solution set, the elders of column values of matrix are selected. Finding the ideal solution set is shown in the following formula: Here, and is maximization and minimization of the value negative ideal.For creating the negative ideal solution set, the smaller of column values of matrix are selected. Finding the negative ideal solution set is shown in the following formula:Here, is shown.

Step 5 (calculating the separation measure). For finding the deviations of solution set the Euclidian distance approach is utilized. Here, the obtained deviation values are called ideal () and negative ideal separation ( measures. Ideal and negative ideal separation are calculated using the following formula:

Step 6 (calculating the relative closeness for the ideal solution). To calculate the ideal solution proximity (), the ideal and negative ideal separation measure is used. Calculation of the relative proximity to the ideal solution is shown in the following formula: Here, value gets the range of [14].

3.2. Determining the Best Reflector Design

The natural frequency and mass constitute the first two-column decision matrix of values in Table 4. The other two columns are manufacturing costs and packaging volume. While skirt thickness and skirt width increase, the manufacturing cost increases. The same situation is valid for packing volume. The package volume increases with the skirt thickness. This is due to the fact that the minimum bend radius increases with the thickness of material. For these reasons, these criteria are taken into account using scores from 1 to 5. Weight coefficients of decision matrix are determined as , , , and .

Table 4: Reflector designs.

Weight coefficients

Value of proximity to decision

Designs
Mass, (kg)
Fundamental frequency (Hz)
Manufacturing cost
Packing volume

1
10.60
0.768
1
5
0.405

2
11.08
0.850
2
4
0.355

3
11.55
0.912
3
3
0.286

4
12.02
0.954
4
2
0.223

5
12.50
0.988
5
1
0.214

6
10.93
1.025
1
5
0.458

7
11.56
1.127
2
4
0.430

8
12.20
1.199
3
3
0.388

9
12.84
1.245
4
2
0.351

10
13.47
1.278
5
1
0.340

11
11.26
1.330
1
5
0.549

12
12.06
1.469
2
4
0.564

13
12.86
1.533
3
3
0.539

14
13.66
1.569
4
2
0.498

15
14.46
1.585
5
1
0.464

16
10.60
1.070
1
5
0.465

17
11.08
1.195
2
4
0.444

18
11.55
1.350
3
3
0.435

19
12.02
1.388
4
2
0.391

20
12.50
1.399
5
1
0.361

21
10.93
1.470
1
5
0.587

22
11.56
1.620
2
4
0.612

23
12.20
1.829
3
3
0.636

24
12.84
1.851
4
2
0.578

25
13.47
1.852
5
1
0.525

26
11.26
1.702
1
5
0.672

27
12.06
1.990
2
4
0.750

28
12.86
2.145
3
3
0.725

29
13.66
2.135
4
2
0.654

30
14.46
2.105
5
1
0.588

The decision-making process is evaluated with the TOPSIS method by taking into account four different criteria and thirty different designs. Value of proximity to decision is seen in Table 4. The ideal design is obtained when value of proximity to decision is the highest. According to this, the best design is the twenty-seventh design. The optimized results are compared with SSBR and Astromesh reflector as given in Table 5. The new design has some advantages in terms of lower mass, number of parts, ease of manufacturing and assembly. The 1/3 scale predesign reflector is accomplished and a part of ground tests such as folding, modal, and deploying have been completed. Predesign reflector made of three-ply (0/45/0) plain weave carbon/epoxy can be seen in Figure 8.

Table 5: Comparison of new design, SSBR, and AstroMesh.

New Design
SSBR [1–4]
AstroMesh [15]

Aperture Diameter, m
6
6
6

F/D
0.8
0.8
0.64

Offset, m
0.3
0.3
0.75

Mass, kg
12.06
23.6
14.50

Fundamental frequency, Hz
1.99
1.87
2.00

Number of parts
Monolithic
Monolithic
Many (nets, meshes, ring truss, etc.)

Manufacturing and assembly
Easier
Easy
Difficult

Figure 8

4. Conclusions

A new ultrathin shell composite reflector is developed considering different design options to optimize the stiffness/mass ratio, cost, and manufacturing. The stiffened spring-back reflector is taken as reference reflector. Preliminary design study shows that the reflective surface with only a skirt has simpler design with high stiffness/mass ratio. This option is further analyzed to optimize the stiffness/mass ratio considering the design parameters of material thickness, width of the skirt, and ply angles. The optimized reflector has a mass of 12.06 kg and a fundamental frequency of 1.99 Hz. The new design has some advantages compared with previous design of both the stiffened spring-back reflector and AstroMesh reflector.

Acknowledgments

This research work is supported by the Scientific and Technological Research Council of Turkey under Grant 109M421 and the Pamukkale University Scientific Research Center.

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