# Design, Analysis, Optimization, Manufacturing, and Testing of a 2U Cubesat

Authors: Andreas Ampatzoglou; Vassilis Kostopoulos
Journal: International Journal of Aerospace Engineering
 (2018)

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## Abstract

The design optimization, development, and verification by analysis and testing of the 1st Greek cubesat, developed by the University of Patras and Libre Space Foundation (UPSat (University of Patras Satellite)), is presented. The key innovative approach includes the replacement of the aluminum side faces with structural composite components, keeping the commonly used aluminum frame. A “hybrid” double-unit (2U) cubesat structure was optimized, built, and tested for all launch and thermal loads/specifications required for launch and mission operations as imposed from the EU-funded FP7-QB50 project. Results show that the new design of the structure using CFRP can offer similar levels of performance in terms of stiffness, while saving 30% of the mass, for the entire cubesat platform.


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## Body

## 1. Introduction

In the last few decades, a fast-growing small satellite industry has enabled increasingly capable and cost-effective space missions, by embracing reduced requirements and integrating commercial technology. Academic research has been active in this field for many years and has resulted in the development of nanosatellites (<10 kg) and picosatellites (<1 kg) with an emphasis on decreasing the platform size through application of advanced technologies. In this framework, California Polytechnic State University (CalPoly) and Stanford University’s Space Systems Development Laboratory developed the cubesat program and published a standard [1] that specifies major requirements and constrains as well as important guidelines that each cubesat must deal with as the design progresses.As for all space missions, including cubesats, the structure is one of the main satellite subsystems. In principle, the purpose of the structural subsystem is to provide a simple and robust structure that shall survive launch loads and provide a suitable environment for the operation of all subsystems. Furthermore, the structure mechanically supports all other spacecraft subsystems, attaches the spacecraft to the launch vehicle, and provides for ordnance-activated separation [2]. Generally, structural design shall aim for simple load paths, simplified interfaces, and easy integration.The design of space structural systems is dictated by mass, stiffness, and strength requirements. On the one hand, stiffness is required to ensure the survivability of the instrumentation; on the other hand, by reducing the weight, it is possible to increase the payload, which extends the mission goals and also reduces the launch cost [3]. The structural and mechanical parts of a satellite generally represent a large percentage of its mass, and therefore, it is important to choose the proper material [4] and structural configuration to minimize mass. Finally, cubesat design is bound by the general constrains and requirements of stiffness and principal eigenfrequency [5].Until now, numerous cubesat missions have successfully been launched. An extensive survey of current cubesat missions and their capabilities can be found in [6, 7]. The primary choice for structural systems is aluminum alloys with the most common being 6061 or 7075 and respective grades, materials that meet the requirement of having thermal expansion factors equal to the Poly Picosat Orbital Deployer (P-POD) material [1].The current work focuses on the design, verification by analysis, and test of a 2U cubesat for a specific LEO (low Earth orbit) mission (FP7-QB50 project) and also on the investigation of the use of CFRP (carbon fiber reinforced plastic) materials in space structural design. Their application has advantages concerning mass and strength, and the required stiffness can be achieved by an appropriate choice of fiber types and orientation in a laminate [8].Given the mass, stiffness, and strength requirements of the spacecraft and the interfaces to the separation module, we attempt to design and prove the feasibility of designing and qualifying a cubesat structure made of both composite materials and aluminum alloy. The structure design follows the commonly used scenario of an aluminum frame, and all side faces were replaced with CFRP parts. Both the finite element analysis (FEA) and testing campaigns included all the launch loads according to cubesat and QB50 specifications and concluded successfully.


## 2. Cubesat Structure Design and Modelling

### 2.1. Cubesat Structural Design

The design process of the structure is an iterative process as is the case with the other subsystems. The process accounts for the upcoming necessary changes evolving from the interaction between the subsystems [9]. In the previous work [10], a comparison between a full composite 1U structure and cubesat-kit design in terms of mass and stiffness took place, showing that considering the proper lamination for the composite structure, the 1st eigenfrequency of the structure was increased and at the same time, a significant mass reduction was achieved (close to 35%). Furthermore, using CFRP as the primary structural component, the structural behavior at launch loads (quasistatic and random vibration) is improving, in terms of the maximum stresses and displacements developed.Having as baseline the design for the 1U UPSat [11], the lamination of the composite parts, and the QB50 Design Requirements [11], the optimized “hybrid” structure presented in Figure 1 was designed. This design was based on an aluminum frame, giving ease of access in the internal, with all side faces bolted together. For the UPSat scenario, the side faces are four; the +Z face must be available for accommodating a Science Unit and the −Z face for accommodating the antenna system.Figure 1
CAD design for the “hybrid” structure (a) and the fully assembled cubesat (b).
(a)
(b)The assembly was realized in two different ways: one using solid bodies for all parts for visualization reasons and one using surfaces for the CFRP components and all electronic components. The surface assembly was created for the finite element analysis, so meshing could be done with shell elements. This was feasible because of the small thickness-to-length (0.004) ratio and thickness-to-width (0.011) ratio of each structural component and also for creating a more simplified finite element model. A shell element finite element model is not time consuming regarding both the building process of the model and the analysis run time.The design was realized in such a way that all the necessary subsystems for a cubesat mission are included in the analysis. These components/subsystems were designed from scratch and included the electronic equipment (PCBs (printed circuit board)), solar panels on the external faces, a camera, and the antenna system on the −Z face. For PCB mounting, the commonly used solution of spacers was followed, and all PCBs along with the spacers were modelled during the finite element analysis campaign. On the +Z face, a Science Unit was attached (provided by von Karman Institute, QB50 project coordinator).


### 2.2. Cubesat Structure Materials

A space-approved composite material, namely, HTM143/M55J (6K) Cyanate-Ester/Carbon unidirectional pre-preg made by CYTEC, was selected for the present application. Table1 shows the necessary set of properties of the pre-preg material considered during finite element modeling. After a trade-off study considering stiffness and mass requirements [10], a quasi-isotropic lay-up was concluded. The resulting lay-up is [0/45/90/−45] S, an eight-layer lay-up which ends up to a total thickness of 1 mm. This lay-up was considered for all side faces of the cubesat.Table 1
Material properties.
(a)
HTM143/M55J properties
E11 (GPa)
181
E2 (GPa)
10.3
G12 (GPa)
7.17
v12
0.28
G13 (GPa)
3.38
ρc (kg/m3)
1600
(b)
Alum. alloy7075 properties
St. steel properties
E (GPa)
71.7
200
v
0.33
0.33
ρ (kg/m3)
2710
7800All aluminum components were made of 7075 aluminum alloy (T6), one of the two most commonly used aluminum alloys for such applications (the second one is the 6061 alloy). The properties of aluminum alloy 7075 used in the analysis are also given in Table1. Finally, all bolts used for the connection of the different components considered to be made of stainless steel and the relevant properties used are given in Table 1.A preliminary calculation took place inside the SolidWorks environment considering the mass saving from the replacement of the aluminum sides with composite parts. The total mass of four components was calculated to be 133 grams with the use of a composite material and 227 grams using aluminum alloy. This 94 grams is equivalent to a mass reduction close to 40% and used for extra scientific equipment for fulfilling the mission’s objectives.


### 2.3. Launch Environment and Analysis Scenarios

A typical cubesat device will be launched on a variety of launching rockets. To qualify for acceptance, the cubesat structure must not fail under certain static and dynamic loading that will be calculated based on the launching conditions. The launching rocket puts out random excitation, and for avoiding channeling this energy into violent resonance of the structure, the first frequency of free vibration should be above 70–90 Hz.Thus, based on current qualification by analysis procedures [12], all launch loading scenarios required by QB50 mission were considered: a modal analysis, a quasistatic analysis, and the random vibration (PSD) analysis. The specific details of each are given hereafter. In addition, considering the thermal loads during cubesat operation in low Earth orbit, a thermal analysis is also conducted.


#### 2.3.1. Modal Analysis

The first step during a dynamic analysis is the determination of natural frequencies (eigenfrequencies) and mode shapes of structure, considering zero damping. The results of this analysis characterize the dynamic behavior of the structure and can show how the structure will respond under dynamic loads [13]. The most important modal characteristic of a space structure, like the cubesat, is the natural frequency threshold—meaning that the first natural frequency of the structure must be above a specific value, which usually is determined by the launch vehicle. The typical range for such missions is between 50 and 90 Hz.At first, a modal analysis of the system under free-free boundary conditions is performed. This is done as an intermediate verification step for the connectivity of developed FE models. Then, the boundary conditions of the P-POD are applied, and another modal analysis is performed. This part shall reveal the real case scenario of the structural system.


#### 2.3.2. Quasistatic Analysis

During the second scenario, the extreme quasistatic loading conditions of a cubesat were identified. The quasistatic event is loads that are independent of time or vary slowly, so that the dynamic response of the structure is not significant. In this base, for design purposes, the quasistatic loads are normally calculated by combining both static and dynamic load contributions. In this context, the quasistatic loads are equivalent to static loads, typically expressed as equivalent accelerations at the CoG [14].The maximum amplitude of these loads is generally encountered at the end of the first-stage burn because of the weaker mass of the launcher (the burned fuel mass being no longer present) for the same amount of thrust [15, 16]. Concerning the QB50 mission, the launch vehicle has already been identified [17], and thus for the worst loading case, a 13 g inertial load was applied at all three axes (three different loading scenarios).


#### 2.3.3. Vibrations

One of the most severe loads for the integrity of the cubesat structure (both internal and external) is the random vibrations coming from the spacecraft launch. The purpose of random vibration analysis is the verification of strength and structural integrity of the satellite by introducing random vibrations through the mechanical interface. This kind of analysis is best suited for subsystem/equipment-level tests and serves for the verification of the satellite structure [18].The typical way to describe the severity of loading and the possible damage under random vibration is in terms of the application of the PSD (power spectral density) that the satellite will face during its own launching, a measure of vibration amplitude power intensity in the frequency domain (Figure2). The way to evaluate the constantly changing acceleration amplitude is to determine the average value of all the amplitudes within a given frequency range. Although acceleration amplitude at a given frequency constantly changes, its average value tends to remain relatively constant.Figure 2
Frequency (Hz) versus amplitude (g2/Hz) chart (QB50 mission).Random vibration analysis is usually performed over a large range of frequencies: from 20 to 2000 Hz, in the case of the most microsatellites. Such a study does not look at a specific frequency or amplitude at a specific moment in time but rather statistically looks at the response of the structure to a given random vibration environment. Finally, the aim of the analysis is to know the overall response of the structure throughout the frequency range of interest [19, 20].


### 2.4. Cubesat Platform Finite Element Model

The design of the structure is given in Figure3, in a configuration with both solid and surface parts. All the aluminum parts were modelled as solid parts, while the CFRP side faces and the PCBs were considered as surface parts. Then, the CAD design was inserted in the MSC PATRAN preprocessor and the meshing strategy applied. Shell elements (QUAD4 that defines isoparametric membrane bending quadrilateral plate elements with rotational degrees of freedom normal to the plate) were used for the discretization of all surface parts following the Paver mesher methodology. On the other hand, solid tetrahedral elements (Tet10) were used for the discretization of all solid parts. The concluded finite element model is shown in Figure 4.Figure 3
CAD design using surfaces and solid parts.Figure 4
Finite element model.All bolted connections were modelled using beam elements (RBE3 Interpolation Element; the interpolation elements allow to model the motion of one or more grid points as a function of the motion of the other points) offering multipoint constrains (MPCs) [21]. For these elements (Figure 5(a)), stainless steel properties were assigned.Figure 5
(a) Bolted connections, (b) inner structure, and (c) boundary conditions.
(a)
(b)
(c)Concerning the inner structure, all four PCBs (EPS (electrical power supply), ADCS (attitude determination and control system), OBC (on-board computer), and COMM (communication)) were modelled as surface parts and meshed as described before using QUAD4 elements and FR4 material (continuous filament-woven fiberglass sheets bonded with flame-resistant epoxy resin) properties were considered (Table2). The PCBs connected with the aluminum square parts using 1D-Bar elements, as Figure 5(b) shows, simulating the Brass spacers. All other major components (the camera, the batteries, the antenna system, and the mNLP unit) were modelled as 0D lumped masses. This practice helped to save computational time, but it was at the cost of the accuracy of vibration response at the lower frequencies.Table 2
FR4 properties.
ρ (kg/m3)
1850
E (GPa)
22
v
0.136Finally, the boundary conditions (Figure5(c)) were applied according to the position of the cubesat inside the separation Poly Picosat Orbital Deployer module; all four rails were considered fully clumped. P-POD [22] is the standard deployment system that carries the cubesat during the launch mission and set it in orbit.Prior to any analysis, a connectivity check of the model was performed, and after that a detailed convergence study of the developed model was implemented. The final mesh used for the rest of the analysis fulfills both the aforementioned checks.


## 2.1. Cubesat Structural Design

The design process of the structure is an iterative process as is the case with the other subsystems. The process accounts for the upcoming necessary changes evolving from the interaction between the subsystems [9]. In the previous work [10], a comparison between a full composite 1U structure and cubesat-kit design in terms of mass and stiffness took place, showing that considering the proper lamination for the composite structure, the 1st eigenfrequency of the structure was increased and at the same time, a significant mass reduction was achieved (close to 35%). Furthermore, using CFRP as the primary structural component, the structural behavior at launch loads (quasistatic and random vibration) is improving, in terms of the maximum stresses and displacements developed.Having as baseline the design for the 1U UPSat [11], the lamination of the composite parts, and the QB50 Design Requirements [11], the optimized “hybrid” structure presented in Figure 1 was designed. This design was based on an aluminum frame, giving ease of access in the internal, with all side faces bolted together. For the UPSat scenario, the side faces are four; the +Z face must be available for accommodating a Science Unit and the −Z face for accommodating the antenna system.Figure 1
CAD design for the “hybrid” structure (a) and the fully assembled cubesat (b).
(a)
(b)The assembly was realized in two different ways: one using solid bodies for all parts for visualization reasons and one using surfaces for the CFRP components and all electronic components. The surface assembly was created for the finite element analysis, so meshing could be done with shell elements. This was feasible because of the small thickness-to-length (0.004) ratio and thickness-to-width (0.011) ratio of each structural component and also for creating a more simplified finite element model. A shell element finite element model is not time consuming regarding both the building process of the model and the analysis run time.The design was realized in such a way that all the necessary subsystems for a cubesat mission are included in the analysis. These components/subsystems were designed from scratch and included the electronic equipment (PCBs (printed circuit board)), solar panels on the external faces, a camera, and the antenna system on the −Z face. For PCB mounting, the commonly used solution of spacers was followed, and all PCBs along with the spacers were modelled during the finite element analysis campaign. On the +Z face, a Science Unit was attached (provided by von Karman Institute, QB50 project coordinator).


## 2.2. Cubesat Structure Materials

A space-approved composite material, namely, HTM143/M55J (6K) Cyanate-Ester/Carbon unidirectional pre-preg made by CYTEC, was selected for the present application. Table1 shows the necessary set of properties of the pre-preg material considered during finite element modeling. After a trade-off study considering stiffness and mass requirements [10], a quasi-isotropic lay-up was concluded. The resulting lay-up is [0/45/90/−45] S, an eight-layer lay-up which ends up to a total thickness of 1 mm. This lay-up was considered for all side faces of the cubesat.Table 1
Material properties.
(a)
HTM143/M55J properties
E11 (GPa)
181
E2 (GPa)
10.3
G12 (GPa)
7.17
v12
0.28
G13 (GPa)
3.38
ρc (kg/m3)
1600
(b)
Alum. alloy7075 properties
St. steel properties
E (GPa)
71.7
200
v
0.33
0.33
ρ (kg/m3)
2710
7800All aluminum components were made of 7075 aluminum alloy (T6), one of the two most commonly used aluminum alloys for such applications (the second one is the 6061 alloy). The properties of aluminum alloy 7075 used in the analysis are also given in Table1. Finally, all bolts used for the connection of the different components considered to be made of stainless steel and the relevant properties used are given in Table 1.A preliminary calculation took place inside the SolidWorks environment considering the mass saving from the replacement of the aluminum sides with composite parts. The total mass of four components was calculated to be 133 grams with the use of a composite material and 227 grams using aluminum alloy. This 94 grams is equivalent to a mass reduction close to 40% and used for extra scientific equipment for fulfilling the mission’s objectives.


## 2.3. Launch Environment and Analysis Scenarios

A typical cubesat device will be launched on a variety of launching rockets. To qualify for acceptance, the cubesat structure must not fail under certain static and dynamic loading that will be calculated based on the launching conditions. The launching rocket puts out random excitation, and for avoiding channeling this energy into violent resonance of the structure, the first frequency of free vibration should be above 70–90 Hz.Thus, based on current qualification by analysis procedures [12], all launch loading scenarios required by QB50 mission were considered: a modal analysis, a quasistatic analysis, and the random vibration (PSD) analysis. The specific details of each are given hereafter. In addition, considering the thermal loads during cubesat operation in low Earth orbit, a thermal analysis is also conducted.


### 2.3.1. Modal Analysis

The first step during a dynamic analysis is the determination of natural frequencies (eigenfrequencies) and mode shapes of structure, considering zero damping. The results of this analysis characterize the dynamic behavior of the structure and can show how the structure will respond under dynamic loads [13]. The most important modal characteristic of a space structure, like the cubesat, is the natural frequency threshold—meaning that the first natural frequency of the structure must be above a specific value, which usually is determined by the launch vehicle. The typical range for such missions is between 50 and 90 Hz.At first, a modal analysis of the system under free-free boundary conditions is performed. This is done as an intermediate verification step for the connectivity of developed FE models. Then, the boundary conditions of the P-POD are applied, and another modal analysis is performed. This part shall reveal the real case scenario of the structural system.


### 2.3.2. Quasistatic Analysis

During the second scenario, the extreme quasistatic loading conditions of a cubesat were identified. The quasistatic event is loads that are independent of time or vary slowly, so that the dynamic response of the structure is not significant. In this base, for design purposes, the quasistatic loads are normally calculated by combining both static and dynamic load contributions. In this context, the quasistatic loads are equivalent to static loads, typically expressed as equivalent accelerations at the CoG [14].The maximum amplitude of these loads is generally encountered at the end of the first-stage burn because of the weaker mass of the launcher (the burned fuel mass being no longer present) for the same amount of thrust [15, 16]. Concerning the QB50 mission, the launch vehicle has already been identified [17], and thus for the worst loading case, a 13 g inertial load was applied at all three axes (three different loading scenarios).


### 2.3.3. Vibrations

One of the most severe loads for the integrity of the cubesat structure (both internal and external) is the random vibrations coming from the spacecraft launch. The purpose of random vibration analysis is the verification of strength and structural integrity of the satellite by introducing random vibrations through the mechanical interface. This kind of analysis is best suited for subsystem/equipment-level tests and serves for the verification of the satellite structure [18].The typical way to describe the severity of loading and the possible damage under random vibration is in terms of the application of the PSD (power spectral density) that the satellite will face during its own launching, a measure of vibration amplitude power intensity in the frequency domain (Figure2). The way to evaluate the constantly changing acceleration amplitude is to determine the average value of all the amplitudes within a given frequency range. Although acceleration amplitude at a given frequency constantly changes, its average value tends to remain relatively constant.Figure 2
Frequency (Hz) versus amplitude (g2/Hz) chart (QB50 mission).Random vibration analysis is usually performed over a large range of frequencies: from 20 to 2000 Hz, in the case of the most microsatellites. Such a study does not look at a specific frequency or amplitude at a specific moment in time but rather statistically looks at the response of the structure to a given random vibration environment. Finally, the aim of the analysis is to know the overall response of the structure throughout the frequency range of interest [19, 20].


## 2.3.1. Modal Analysis

The first step during a dynamic analysis is the determination of natural frequencies (eigenfrequencies) and mode shapes of structure, considering zero damping. The results of this analysis characterize the dynamic behavior of the structure and can show how the structure will respond under dynamic loads [13]. The most important modal characteristic of a space structure, like the cubesat, is the natural frequency threshold—meaning that the first natural frequency of the structure must be above a specific value, which usually is determined by the launch vehicle. The typical range for such missions is between 50 and 90 Hz.At first, a modal analysis of the system under free-free boundary conditions is performed. This is done as an intermediate verification step for the connectivity of developed FE models. Then, the boundary conditions of the P-POD are applied, and another modal analysis is performed. This part shall reveal the real case scenario of the structural system.


## 2.3.2. Quasistatic Analysis

During the second scenario, the extreme quasistatic loading conditions of a cubesat were identified. The quasistatic event is loads that are independent of time or vary slowly, so that the dynamic response of the structure is not significant. In this base, for design purposes, the quasistatic loads are normally calculated by combining both static and dynamic load contributions. In this context, the quasistatic loads are equivalent to static loads, typically expressed as equivalent accelerations at the CoG [14].The maximum amplitude of these loads is generally encountered at the end of the first-stage burn because of the weaker mass of the launcher (the burned fuel mass being no longer present) for the same amount of thrust [15, 16]. Concerning the QB50 mission, the launch vehicle has already been identified [17], and thus for the worst loading case, a 13 g inertial load was applied at all three axes (three different loading scenarios).


## 2.3.3. Vibrations

One of the most severe loads for the integrity of the cubesat structure (both internal and external) is the random vibrations coming from the spacecraft launch. The purpose of random vibration analysis is the verification of strength and structural integrity of the satellite by introducing random vibrations through the mechanical interface. This kind of analysis is best suited for subsystem/equipment-level tests and serves for the verification of the satellite structure [18].The typical way to describe the severity of loading and the possible damage under random vibration is in terms of the application of the PSD (power spectral density) that the satellite will face during its own launching, a measure of vibration amplitude power intensity in the frequency domain (Figure2). The way to evaluate the constantly changing acceleration amplitude is to determine the average value of all the amplitudes within a given frequency range. Although acceleration amplitude at a given frequency constantly changes, its average value tends to remain relatively constant.Figure 2
Frequency (Hz) versus amplitude (g2/Hz) chart (QB50 mission).Random vibration analysis is usually performed over a large range of frequencies: from 20 to 2000 Hz, in the case of the most microsatellites. Such a study does not look at a specific frequency or amplitude at a specific moment in time but rather statistically looks at the response of the structure to a given random vibration environment. Finally, the aim of the analysis is to know the overall response of the structure throughout the frequency range of interest [19, 20].


## 2.4. Cubesat Platform Finite Element Model

The design of the structure is given in Figure3, in a configuration with both solid and surface parts. All the aluminum parts were modelled as solid parts, while the CFRP side faces and the PCBs were considered as surface parts. Then, the CAD design was inserted in the MSC PATRAN preprocessor and the meshing strategy applied. Shell elements (QUAD4 that defines isoparametric membrane bending quadrilateral plate elements with rotational degrees of freedom normal to the plate) were used for the discretization of all surface parts following the Paver mesher methodology. On the other hand, solid tetrahedral elements (Tet10) were used for the discretization of all solid parts. The concluded finite element model is shown in Figure 4.Figure 3
CAD design using surfaces and solid parts.Figure 4
Finite element model.All bolted connections were modelled using beam elements (RBE3 Interpolation Element; the interpolation elements allow to model the motion of one or more grid points as a function of the motion of the other points) offering multipoint constrains (MPCs) [21]. For these elements (Figure 5(a)), stainless steel properties were assigned.Figure 5
(a) Bolted connections, (b) inner structure, and (c) boundary conditions.
(a)
(b)
(c)Concerning the inner structure, all four PCBs (EPS (electrical power supply), ADCS (attitude determination and control system), OBC (on-board computer), and COMM (communication)) were modelled as surface parts and meshed as described before using QUAD4 elements and FR4 material (continuous filament-woven fiberglass sheets bonded with flame-resistant epoxy resin) properties were considered (Table2). The PCBs connected with the aluminum square parts using 1D-Bar elements, as Figure 5(b) shows, simulating the Brass spacers. All other major components (the camera, the batteries, the antenna system, and the mNLP unit) were modelled as 0D lumped masses. This practice helped to save computational time, but it was at the cost of the accuracy of vibration response at the lower frequencies.Table 2
FR4 properties.
ρ (kg/m3)
1850
E (GPa)
22
v
0.136Finally, the boundary conditions (Figure5(c)) were applied according to the position of the cubesat inside the separation Poly Picosat Orbital Deployer module; all four rails were considered fully clumped. P-POD [22] is the standard deployment system that carries the cubesat during the launch mission and set it in orbit.Prior to any analysis, a connectivity check of the model was performed, and after that a detailed convergence study of the developed model was implemented. The final mesh used for the rest of the analysis fulfills both the aforementioned checks.


## 3. Verification by Analysis

In this section, the structural analysis of the UPSat 2U cubesat platform is presented. All necessary data concerning the launcher loads (quasistatic and random vibration) and operation loads (trajectory for thermal analysis) were taken from the QB50 mission requirements [23] and concern only this particular mission.


### 3.1. Modal Analysis Results

Figure6 shows the first 4 eigenfrequencies together with the corresponding eigenmodes (bending modes) for the UPSat structure. The lower limit for the first eigenfrequency for the specific mission is set above 90 Hz. In the present analysis, the 1st eigenfrequency is close to 500 Hz and thus the structure can be considered adequately robust concerning its modal characteristics.Figure 6
The first 4 eigenfrequencies and mode shapes for “hybrid” UPSat.


### 3.2. Quasistatic Analysis Results

For the current mission, an inertial load equal to 13 g was considered, along the 3 major axes under clamped boundary conditions, as it was earlier discussed. Table3 summarizes the results of the quasistatic analysis performed for all loading cases. As the structure consists of both aluminum and composite parts, both von Mises and maximum principal stresses were calculated and reported along with the maximum displacements and strain for all cases.Table 3
Quasistatic analysis results.
x-axis
y-axis
z-axis
Displacement (mm)
0.031
0.034
0.00372
STRESS—CFRP(max principal) (MPa)
6.95
6.55
1.18
STRESS—ALUM(von Mises) (MPa)
15.2
11.6
25.6
STRESS—PCBs (MPa)
4.4
4.7
2.06
STRESS—spacers (MPa)
3.8
4
1.5
STRAIN
6.73∗10−5
6.89∗10−5
7.39∗10−6As it is evident from the results, all maximum stresses and displacements for all cases are extremely low, considering the strength of both materials. This is expected, since the structure was designed on the basis of a stiffness-driven approach, in order to push eigenfrequencies to higher values. The stress and displacement distributions are shown in Figures7 and 8, respectively, for the worst-case scenario (x-axis loading), and Figure 9 illustrates the stress distribution in the deformed structure, for the z-axis case.Figure 7
Stress distribution (x-axis).Figure 8
Displacement distribution (x-axis).Figure 9
Stress distribution (z-axis).Summarizing, the developed maximum stresses, displacements, and strains are very low, considering the strength of all materials used in the FE model. For example, the failure strain for the CFRPs is 1% (0.01) and the values for the strain atx- and y-loading cases are 10–5, and thus the cubesat chassis, and therefore the entire system, can be considered adequately robust.


### 3.3. Random (PSD) Vibration

The input chart [frequency (Hz) versus amplitude (g2/Hz)] presented in Figure 2 and the margin of safety (MoS=0.25) were given by the project coordinator [23] and, similarly to the quasistatic analysis, should be applied at all the three axes of the coordinate system. Figure 10 illustrates the responses in g2/Hz and displacement (mm) of the central node of each PCB versus frequency at the range up to 2000 Hz in the z-direction.Figure 10
PSD results: (a) acceleration and (b) displacement.
(a)
(b)The square root of the area under the PSD curve (grey area) in Figure2 gives the root mean square (RMS) value of the acceleration, or Grms, which is a qualitative measure of intensity of vibration. The maximum stress for all three scenarios was identified around the PCB holes (Figure 11 illustrates the stress distribution for the z-axis case).Figure 11
RMS stress distribution (PSD analysis).Similar results are concluded for both the g2/Hz and the displacement responses as well as for the RMS stress distribution when the input acceleration profile was applied on the x- and y-axes. All RMS stresses for the three scenarios of PSD analysis are extremely low and not capable of raising any concerns regarding the structure’s integrity.


### 3.4. Orbital Case: Thermal Analysis

As the cubesat will be deployed from the International Space Station, the trajectory of ISS was considered for the thermal analysis. This trajectory is a low-Earth orbit with the characteristics given in Table4.Table 4
Orbit characteristics.
ISS orbit
Semimajor axis (km)
6780
Eccentricity (degrees)
0
Ascending node longitude (degrees)
−94.354
Inclination (degrees)
51.64
Mean anomaly (degrees)
254.215The FE model was presented earlier for the mechanical analysis, simplified according to the needs of the Thermal Analysis software (MSC Thermica) and all the necessary covers and coatings (MLI, solar cell, etc.) included. Figure12 presents the mean absorbed solar flux and the mean absorbed Earth IR flux applied into the cubesat structure.Figure 12
(a) Mean absorbed solar flux (872.66 W/m2) and (b) mean absorbed Earth IR flux (172.52 W/m2).
(a)
(b)The next step was the calculation of the temperature distribution for the entire cubesat system. The results for both the steady-state and transient state analyses are presented in Table5. Both maximum and minimum temperatures were noticed at the outer faces of the cubesat while the temperatures for all internal electronic subsystems were inside the permitted limits for normal operation (Table 6). For example, the maximum/minimum temperatures noticed on the EPS system, during the transient state analysis, were + 28°C/+2°C.Table 5
Operational temperature limits.
Component
Operational temp limit (°C)
OBC (mother board)
−40 to +85
OBC (processor board)
−40 to +85
EPS
−40 to +85
Battery
−10 to +50
Magnetometer
−120 to +50
Sun sensor
−40 to +125
Solar cell
−100 to +65Table 6
Maximum/minimum temperatures.
Max temp (°C)
Min temp (°C)
Steady state
+26 (+Y face)
−38 (−Y face)
Transient state
+56 (+Y face)
−35 (−Y face)


## 3.1. Modal Analysis Results

Figure6 shows the first 4 eigenfrequencies together with the corresponding eigenmodes (bending modes) for the UPSat structure. The lower limit for the first eigenfrequency for the specific mission is set above 90 Hz. In the present analysis, the 1st eigenfrequency is close to 500 Hz and thus the structure can be considered adequately robust concerning its modal characteristics.Figure 6
The first 4 eigenfrequencies and mode shapes for “hybrid” UPSat.


## 3.2. Quasistatic Analysis Results

For the current mission, an inertial load equal to 13 g was considered, along the 3 major axes under clamped boundary conditions, as it was earlier discussed. Table3 summarizes the results of the quasistatic analysis performed for all loading cases. As the structure consists of both aluminum and composite parts, both von Mises and maximum principal stresses were calculated and reported along with the maximum displacements and strain for all cases.Table 3
Quasistatic analysis results.
x-axis
y-axis
z-axis
Displacement (mm)
0.031
0.034
0.00372
STRESS—CFRP(max principal) (MPa)
6.95
6.55
1.18
STRESS—ALUM(von Mises) (MPa)
15.2
11.6
25.6
STRESS—PCBs (MPa)
4.4
4.7
2.06
STRESS—spacers (MPa)
3.8
4
1.5
STRAIN
6.73∗10−5
6.89∗10−5
7.39∗10−6As it is evident from the results, all maximum stresses and displacements for all cases are extremely low, considering the strength of both materials. This is expected, since the structure was designed on the basis of a stiffness-driven approach, in order to push eigenfrequencies to higher values. The stress and displacement distributions are shown in Figures7 and 8, respectively, for the worst-case scenario (x-axis loading), and Figure 9 illustrates the stress distribution in the deformed structure, for the z-axis case.Figure 7
Stress distribution (x-axis).Figure 8
Displacement distribution (x-axis).Figure 9
Stress distribution (z-axis).Summarizing, the developed maximum stresses, displacements, and strains are very low, considering the strength of all materials used in the FE model. For example, the failure strain for the CFRPs is 1% (0.01) and the values for the strain atx- and y-loading cases are 10–5, and thus the cubesat chassis, and therefore the entire system, can be considered adequately robust.


## 3.3. Random (PSD) Vibration

The input chart [frequency (Hz) versus amplitude (g2/Hz)] presented in Figure 2 and the margin of safety (MoS=0.25) were given by the project coordinator [23] and, similarly to the quasistatic analysis, should be applied at all the three axes of the coordinate system. Figure 10 illustrates the responses in g2/Hz and displacement (mm) of the central node of each PCB versus frequency at the range up to 2000 Hz in the z-direction.Figure 10
PSD results: (a) acceleration and (b) displacement.
(a)
(b)The square root of the area under the PSD curve (grey area) in Figure2 gives the root mean square (RMS) value of the acceleration, or Grms, which is a qualitative measure of intensity of vibration. The maximum stress for all three scenarios was identified around the PCB holes (Figure 11 illustrates the stress distribution for the z-axis case).Figure 11
RMS stress distribution (PSD analysis).Similar results are concluded for both the g2/Hz and the displacement responses as well as for the RMS stress distribution when the input acceleration profile was applied on the x- and y-axes. All RMS stresses for the three scenarios of PSD analysis are extremely low and not capable of raising any concerns regarding the structure’s integrity.


## 3.4. Orbital Case: Thermal Analysis

As the cubesat will be deployed from the International Space Station, the trajectory of ISS was considered for the thermal analysis. This trajectory is a low-Earth orbit with the characteristics given in Table4.Table 4
Orbit characteristics.
ISS orbit
Semimajor axis (km)
6780
Eccentricity (degrees)
0
Ascending node longitude (degrees)
−94.354
Inclination (degrees)
51.64
Mean anomaly (degrees)
254.215The FE model was presented earlier for the mechanical analysis, simplified according to the needs of the Thermal Analysis software (MSC Thermica) and all the necessary covers and coatings (MLI, solar cell, etc.) included. Figure12 presents the mean absorbed solar flux and the mean absorbed Earth IR flux applied into the cubesat structure.Figure 12
(a) Mean absorbed solar flux (872.66 W/m2) and (b) mean absorbed Earth IR flux (172.52 W/m2).
(a)
(b)The next step was the calculation of the temperature distribution for the entire cubesat system. The results for both the steady-state and transient state analyses are presented in Table5. Both maximum and minimum temperatures were noticed at the outer faces of the cubesat while the temperatures for all internal electronic subsystems were inside the permitted limits for normal operation (Table 6). For example, the maximum/minimum temperatures noticed on the EPS system, during the transient state analysis, were + 28°C/+2°C.Table 5
Operational temperature limits.
Component
Operational temp limit (°C)
OBC (mother board)
−40 to +85
OBC (processor board)
−40 to +85
EPS
−40 to +85
Battery
−10 to +50
Magnetometer
−120 to +50
Sun sensor
−40 to +125
Solar cell
−100 to +65Table 6
Maximum/minimum temperatures.
Max temp (°C)
Min temp (°C)
Steady state
+26 (+Y face)
−38 (−Y face)
Transient state
+56 (+Y face)
−35 (−Y face)


## 4. Cubesat Verification Tests

### 4.1. Manufacturing and Assembly

The development of all UPSat subsystems took place at AML/UPAT and LSF facilities following a non-COTS component philosophy, and the final assembly and integration were performed inside a clean room area (ISO-7) following all recommendations described in [24].Concerning the manufacturing of CFRP sides, the space-approved composite material HTM143/M55J (6K) Cyanate-Ester/Carbon unidirectional pre-preg (CYTEC manufacturer) was selected as a material that was previously used in a flight-proven aerospace structure [25]. The standard pre-preg autoclave procedure was followed, and the entire process was completed at AML/UPAT facilities.The assembly and integration (system level) of the 2U cubesat is illustrated in Figure13, showing on the right the actual flight model, ready for the testing campaigns. The total mass of the flight model was found at 1.75 kg, meaning that there was almost a kilogram available for use of any extra scientific instrumentation (max allowable mass of a 2U cubesat is 2.66 kg).Figure 13
Assembly and integration procedure of UPSAT.


### 4.2. Testing Campaigns

For the need of the vibration campaign, an intermediate structure is required. The test pod simulates the actual boundary conditions that the cubesat will experience during launch, and it is necessary to be as rigid as possible for transferring the vibration loads from the shaker table to the cubesat without any resonances. The test pod, made of aluminum alloy (7075), was designed and manufactured in-house and passed all design (cubesat fit check) and test criteria (no resonance below 90 Hz).The experimental setup shown in Figure14 is the same for all required vibration tests (resonance, quasistatic, random, and sine vibration). For the x- and y-axis loading cases, the right setup was used and the cubesat rotated 90 degrees inside the test pod. For the z-axis case, the entire system (cubesat and test pod) was rotated and the left setup was used. The vibration campaign was performed at the Hellenic Aerospace Industry (HAI) facilities, and two different campaigns were completed: a qualification campaign using several dummy masses (solar panels, camera) and QM models for the PCBs and an acceptance campaign using the actual flight model of the fully assembled cubesat.Figure 14
Vibration campaign test setup.The first and most important test during the vibration campaign is the resonance survey test. The resonance survey serves as reference for the entire campaign, as this test is performed before and after a test at full level for each axis (quasistatic, sine, and random). By comparing the results of the resonance survey tests, a change in cubesat integrity due to settling or possible damage can be predicted.The resonance frequency test is the experimental way to verify that the assembled system’s natural frequencies are within the specification limits. According to QB50 functional specifications [11], the required frequency profile is from 5 to 100 Hz, in order to verify that the structures’ lowest natural frequency is above 90 Hz. The variation of natural frequencies before and after each axis test at full level is the actual test pass criterion for the vibration campaign.In our case, this variation was found to be no more than 1% for all three loading scenarios. Although similar responses were recorded for all cases, only the results for thez-axis are presented here, as this case was of greater interest, due to the changes at the experimental setup: a 90-degree rotation of test fixture. The detailed results of all loading cases of the campaign are presented in [26].Figure15 illustrates the system’s response for the z-axis case (PSD vibration) and Figure 16 the variation on resonance test (before and after full level) for the same case. The spike at frequencies below 100 Hz is attributed to the vibration table setup; the same spike was noticed during the test of the test pod (without the cubesat inside) and also during the standalone test of the table setup prior to any other test.Figure 15
PSD response (z-axis).Figure 16
z-axis response and resonance test.Using the resonance survey results, visual inspection on the satellite after each full cycle, and a short reference functional testing campaign after all full cycles, the vibration campaign was deemed as successful and the T-VAC campaign started.The thermal testing campaign requires a thermal vacuum chamber, capable of offering the necessary vacuum and thermal/cooling conditions for the needs of required tests. Such a chamber is designed and manufactured in-house (AML), following the literature survey [27], and is presented in Figure 17. The T-VAC setup offers vacuum up to 10–1 mbar, controlled heating up to 60°C (halogen lamp), and controlled cooling by a cooling coil up to −40°C (R404 cooling agent). Finally, 6 temperature sensors were used for control and monitoring as Table 7 shows.Figure 17
Thermal vacuum chamber (setup and internal view).Table 7
Position of temperature sensors.
TC-1
+Y (control)
TC-2
+X
TC-3
−X
TC-4
+Y (zenith—sun face)
TC-5
−Y (nadir—earth face)
TC-6
Attachment frame (control)The two different tests required by [23] are the thermal cycling and the thermal bake-out. During the thermal cycling test, the cubesat was subjected in 4 thermal cycles (−20°C to +50°C) and remained for one hour at the extreme temperatures (after TC-6 and then TC-1, indicating temperature stabilization). The cubesat was fully functional and operational as several functional tests had to be performed (as specified in [11]).On the other hand, during the thermal bake-out test, the satellite is not operational as the success criterion of this test is the total mass loss of the satellite. The total outgassing of the materials from all subsystems should not exceed 1% of the total mass of the satellite.The thermocouples’ response is illustrated in Figure18(a) showing the experiment’s four cycles from −20°C to +50°C and finally the cooling down to room temperature (25°C). The total test duration was 7 hours, and the only malfunction during the test was a sudden shutdown of the halogen lamp for 5 seconds, which caused the sharp temperature drop (TC-2, TC-3, and TC-4) shown in Figure 18. The temperatures on the PCBs during the test never reached values of high risk, and all required functional tests performed during the plateaus did not indicate any malfunction on any of the PCBs. Some of the completed functional tests are shown in Figure 18(b).Figure 18
(a) Thermal cycling TC response (temperatures monitoring) and (b) some of the reference tests during thermal cycling.
(a)
(b)The test duration of the thermal bake-out test was increased to 24 hours, instead of 3 hours (after the coordinator’s suggestion), due to low vacuum inside the chamber (the desired vacuum was 10−5 mbar). The satellite’s weight before (1753.5 grams) and after (1752.7 grams) the test offered a total mass loss close to 0.045% (should be <1% by requirements).After the successful completion of both testing campaigns, the flight readiness phase concluded successfully and the cubesat was ready for shipment. The cubesat was delivered to ISISpace in Delft on the 18th of August 2016 for the check-out process, which included several health checks on the satellite, the fit check inside a dummy POD, and full charging of the batteries. The integration on NanoRacks deployers took place on the 22nd of November (Figure19(a)) and the deployers were delivered to Orbital ATK, for the final integration into the Cygnus CRS OA-7 cargo and then atop the Atlas V launcher on February 14th (Figures 19(c) and 19(d)).Figure 19
(a) UPSat inside the NanoRacks deployers, (b) integration into the Cygnus cargo, (c) ready for launch, (d) cargo berthed on ISS, and (e) UPSat deployment from ISS.
(a)
(b)
(c)
(d)
(e)The launch, from Cape Canaveral, took place on 18th of April, and the Cygnus cargo berthed successfully on ISS on the 22nd of April (Figure19(d)). Finally, UPSat was deployed from ISS, on May 18th (Figure 19(e)), and after one hour, successful contact with UPSat was achieved, with the received CW beacon and Whole Orbit Data (WOD) verifying the perfect condition of the cubesat and thus the mission success. Currently, attempts for commissioning from the local ground segment are ongoing.


## 4.1. Manufacturing and Assembly

The development of all UPSat subsystems took place at AML/UPAT and LSF facilities following a non-COTS component philosophy, and the final assembly and integration were performed inside a clean room area (ISO-7) following all recommendations described in [24].Concerning the manufacturing of CFRP sides, the space-approved composite material HTM143/M55J (6K) Cyanate-Ester/Carbon unidirectional pre-preg (CYTEC manufacturer) was selected as a material that was previously used in a flight-proven aerospace structure [25]. The standard pre-preg autoclave procedure was followed, and the entire process was completed at AML/UPAT facilities.The assembly and integration (system level) of the 2U cubesat is illustrated in Figure13, showing on the right the actual flight model, ready for the testing campaigns. The total mass of the flight model was found at 1.75 kg, meaning that there was almost a kilogram available for use of any extra scientific instrumentation (max allowable mass of a 2U cubesat is 2.66 kg).Figure 13
Assembly and integration procedure of UPSAT.


## 4.2. Testing Campaigns

For the need of the vibration campaign, an intermediate structure is required. The test pod simulates the actual boundary conditions that the cubesat will experience during launch, and it is necessary to be as rigid as possible for transferring the vibration loads from the shaker table to the cubesat without any resonances. The test pod, made of aluminum alloy (7075), was designed and manufactured in-house and passed all design (cubesat fit check) and test criteria (no resonance below 90 Hz).The experimental setup shown in Figure14 is the same for all required vibration tests (resonance, quasistatic, random, and sine vibration). For the x- and y-axis loading cases, the right setup was used and the cubesat rotated 90 degrees inside the test pod. For the z-axis case, the entire system (cubesat and test pod) was rotated and the left setup was used. The vibration campaign was performed at the Hellenic Aerospace Industry (HAI) facilities, and two different campaigns were completed: a qualification campaign using several dummy masses (solar panels, camera) and QM models for the PCBs and an acceptance campaign using the actual flight model of the fully assembled cubesat.Figure 14
Vibration campaign test setup.The first and most important test during the vibration campaign is the resonance survey test. The resonance survey serves as reference for the entire campaign, as this test is performed before and after a test at full level for each axis (quasistatic, sine, and random). By comparing the results of the resonance survey tests, a change in cubesat integrity due to settling or possible damage can be predicted.The resonance frequency test is the experimental way to verify that the assembled system’s natural frequencies are within the specification limits. According to QB50 functional specifications [11], the required frequency profile is from 5 to 100 Hz, in order to verify that the structures’ lowest natural frequency is above 90 Hz. The variation of natural frequencies before and after each axis test at full level is the actual test pass criterion for the vibration campaign.In our case, this variation was found to be no more than 1% for all three loading scenarios. Although similar responses were recorded for all cases, only the results for thez-axis are presented here, as this case was of greater interest, due to the changes at the experimental setup: a 90-degree rotation of test fixture. The detailed results of all loading cases of the campaign are presented in [26].Figure15 illustrates the system’s response for the z-axis case (PSD vibration) and Figure 16 the variation on resonance test (before and after full level) for the same case. The spike at frequencies below 100 Hz is attributed to the vibration table setup; the same spike was noticed during the test of the test pod (without the cubesat inside) and also during the standalone test of the table setup prior to any other test.Figure 15
PSD response (z-axis).Figure 16
z-axis response and resonance test.Using the resonance survey results, visual inspection on the satellite after each full cycle, and a short reference functional testing campaign after all full cycles, the vibration campaign was deemed as successful and the T-VAC campaign started.The thermal testing campaign requires a thermal vacuum chamber, capable of offering the necessary vacuum and thermal/cooling conditions for the needs of required tests. Such a chamber is designed and manufactured in-house (AML), following the literature survey [27], and is presented in Figure 17. The T-VAC setup offers vacuum up to 10–1 mbar, controlled heating up to 60°C (halogen lamp), and controlled cooling by a cooling coil up to −40°C (R404 cooling agent). Finally, 6 temperature sensors were used for control and monitoring as Table 7 shows.Figure 17
Thermal vacuum chamber (setup and internal view).Table 7
Position of temperature sensors.
TC-1
+Y (control)
TC-2
+X
TC-3
−X
TC-4
+Y (zenith—sun face)
TC-5
−Y (nadir—earth face)
TC-6
Attachment frame (control)The two different tests required by [23] are the thermal cycling and the thermal bake-out. During the thermal cycling test, the cubesat was subjected in 4 thermal cycles (−20°C to +50°C) and remained for one hour at the extreme temperatures (after TC-6 and then TC-1, indicating temperature stabilization). The cubesat was fully functional and operational as several functional tests had to be performed (as specified in [11]).On the other hand, during the thermal bake-out test, the satellite is not operational as the success criterion of this test is the total mass loss of the satellite. The total outgassing of the materials from all subsystems should not exceed 1% of the total mass of the satellite.The thermocouples’ response is illustrated in Figure18(a) showing the experiment’s four cycles from −20°C to +50°C and finally the cooling down to room temperature (25°C). The total test duration was 7 hours, and the only malfunction during the test was a sudden shutdown of the halogen lamp for 5 seconds, which caused the sharp temperature drop (TC-2, TC-3, and TC-4) shown in Figure 18. The temperatures on the PCBs during the test never reached values of high risk, and all required functional tests performed during the plateaus did not indicate any malfunction on any of the PCBs. Some of the completed functional tests are shown in Figure 18(b).Figure 18
(a) Thermal cycling TC response (temperatures monitoring) and (b) some of the reference tests during thermal cycling.
(a)
(b)The test duration of the thermal bake-out test was increased to 24 hours, instead of 3 hours (after the coordinator’s suggestion), due to low vacuum inside the chamber (the desired vacuum was 10−5 mbar). The satellite’s weight before (1753.5 grams) and after (1752.7 grams) the test offered a total mass loss close to 0.045% (should be <1% by requirements).After the successful completion of both testing campaigns, the flight readiness phase concluded successfully and the cubesat was ready for shipment. The cubesat was delivered to ISISpace in Delft on the 18th of August 2016 for the check-out process, which included several health checks on the satellite, the fit check inside a dummy POD, and full charging of the batteries. The integration on NanoRacks deployers took place on the 22nd of November (Figure19(a)) and the deployers were delivered to Orbital ATK, for the final integration into the Cygnus CRS OA-7 cargo and then atop the Atlas V launcher on February 14th (Figures 19(c) and 19(d)).Figure 19
(a) UPSat inside the NanoRacks deployers, (b) integration into the Cygnus cargo, (c) ready for launch, (d) cargo berthed on ISS, and (e) UPSat deployment from ISS.
(a)
(b)
(c)
(d)
(e)The launch, from Cape Canaveral, took place on 18th of April, and the Cygnus cargo berthed successfully on ISS on the 22nd of April (Figure19(d)). Finally, UPSat was deployed from ISS, on May 18th (Figure 19(e)), and after one hour, successful contact with UPSat was achieved, with the received CW beacon and Whole Orbit Data (WOD) verifying the perfect condition of the cubesat and thus the mission success. Currently, attempts for commissioning from the local ground segment are ongoing.


## 5. Conclusions

In this study, the structural design optimization and development of a 2U cubesat were investigated. The goal of the study was to design, build, and verify by analysis and test a “hybrid” cubesat structure while attempting to quantify the benefits for such a choice.The first and most important conclusion from the current work was that a successful design optimization and verification by analysis of a 2U cubesat was one using a novel hybrid composite structure which could bring significant mass savings. The UPSat structure offered a first frequency higher than the lower limit required (90 Hz). Furthermore, a reduction of mass close to 30% was attained between the “hybrid” structure and a full aluminum one, leading to an overall lighter cubesat system. This means that using composite materials and after evaluation for the moat optimum design and proper lamination, the structure could be more stiff and lighter than a conventional aluminum cubesat structure. This reduction could allow adding an extra payload and expanding the mission’s objectives; this was one of the team’s goals during the preliminary design review phase. For the 2U cubesat analyzed, the overall mass savings in the platform design allowed for a 1 kg payload mass available. Unfortunately, by the end of the critical design review phase, such a payload was not available, and the system design concluded with a 34% free mass budget.All types of analysis (quasistatic, PSD, and thermal) gave also quite satisfactory results, and no need for redesign occurred during the critical design review phase of the project.The proposed design was manufactured, fulfilling the required cubesat design tolerances, and the fully assembled cubesat system was subjected to all required tests according to mission specifications. Both vibration and T-VAC campaigns were completed successfully, and for all subsystems, the normal operation before, during, and after the tests was verified, thus making the cubesat flight ready.The UPSat cubesat was delivered and integrated into the Atlas V launcher and set successfully into orbit fulfilling its main mission objective by returning successful housekeeping in orbit data. The CW beacon and WOD files confirmed the normal operation of all subsystems and make UPSat the first Greek open-source, designed-from-scratch, nanosatellite ever launched.



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*Source: 9724263-2018-06-12.xml*