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7/28/2019 Thermal Fatigue Analysis
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O R IG IN A L PA PE R
Thermal fatigue analysis of small-satellite structure
Gasser Farouk Abdelal Nader Abuelfoutouh Ahmed Hamdy Ayman Atef
Received: 11 November 2006 / Accepted: 12 January 2007 / Published online: 16 February 2007 Springer Science+Business Media B.V. 2007
Abstract The small-satellite thermal subsystemmain function is to control temperature ranges on
equipments, and payload for the orbit specified.
Structure subsystem has to ensure the satellitestructure integrity. Structure integrity should
meet two constraints; first constraint is accepted
fatigue damage due to cyclic temperature, andsecond one is tolerable mounting accuracy at
payload and Attitude Determination and Control
Subsystem (ADCS) equipments seats. First,
thermal analysis is executed by applying finite-difference method (IDEAS) and temperature
profile for satellite components case is evaluated.Then, thermal fatigue analysis is performed
applying finite-element analysis (ANSYS) tocalculate the resultant damage due to on-orbit
cyclic stresses, and structure deformations at the
payload and ADCS equipments seats.
Keywords Aerospace Satellite Structure Finite difference Finite element Thermal Mounting accuracy Fatigue
1 Introduction
Structure made of different materials can experi-
ence thermal stresses without external constraintseven under uniform temperature. Differences in
the materials coefficients of thermal expansionproduce incompatible strains and resulting ther-mal stresses. These stresses balance when no
external constraints are present.Thermally induced loads and stresses are
limited by deformation; once a material reaches
its proportional limit, or once the structure beginsto buckle, thermal stress no longer increases in
proportion to the change in temperature. Ductile
materials seldom rupture or buckle from a singleapplication of thermal stress, but they can fail in
fatigue from the many cycles of thermal loadingcommon to orbiting satellite.
Actual thermal-design problems for satellite
are complicated. The design problem typically
must combine multiple modes of heat transferwith time varying boundary conditions that
require transient instead of steady-state solutions.
To predict satellites temperatures, the thermalanalysis problem combines two types of math
models. The first one is a thermal-radiation model
G. F. Abdelal (&) A. Hamdy A. AtefEgyptian Space Program, National Authority forRemote Sensing and Space Science (NARSS), 23Jozef Broz Teto Street, Elnozha Elgededah, Cairo11769, Egypte-mail: [email protected]
N. AbuelfoutouhAerial Photograph Division Program, NationalAuthority for Remote Sensing and Space Science(NARSS), 23 Jozef Broz Teto Street, ElnozhaElgededah, Cairo 11769, Egypt
123
Int J Mech Mater Des (2006) 3:145159
DOI 10.1007/s10999-007-9019-1
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to calculate external heating rates by simulatingthe external geometry of the satellite including
surface properties. By subjecting this model to a
simulated orbit, the output from this modeconsisting of; the environmental heating rates
due to direct solar, albedo, and planetary emis-
sions; and external radiation between satellitesurfaces; becomes input for the second model.
The second thermal model uses a thermal
analyzer. The satellite is modeled much the sameas the structural analysis model with internal
details but the analysis is based on the finite
difference method. Then the heating sources aredefined. Finally, the model is solved to simulate
the heat transfer paths of conduction, convec-
tion, and radiation. The thermal analyzer calcu-lates temperatures at all nodes for steady-state
or transient conditions by solving energyequations.
A thermoelastic analysis for Small Sat struc-
ture due to on-orbit cyclic temperature is consid-
ered. It calculates stresses and distortions due totemperatures cyclic loading. The results of ther-
moelastic analysis are used to calculate fatigue
damage due to on-orbit cyclic stresses. Moreover,it is used to check mounting accuracy of the
precise equipments (MBIE and ADCS equip-
ments) after on-orbit thermal deformation. The
most critical structural module in Small Satregarding by on-orbit thermal deformation is the
basis unit block module. This module is verysensitive to thermal deformation because it
carries the precise equipments of the satellite.
The rest of structural modules do not havesevere restrictions on their equipment mounting
accuracy.
2 Satellite overview
The satellite configuration is shown below inFig. 1. The structure is a 1.03 0.8 1.0255 m
cube with four solar panels attached to the
satellite by means of rotation mechanism. Fourheat shields are installed on the satellite structure
to prevent internal instruments from direct envi-
ronmental heat loads. The highest power con-suming components will be placed away from hot
heat shields subjected to solar radiation. The
primary main elements of the satellite structureare shown in Fig. 2.
3 Mission requirements and constraints
The temperature constraint is specified for each
component. Table 1 lists temperature ranges for
different satellite components. Component tem-perature constraints contain an upper and a
4 Solar panels
4 Heat shields
Satellite case
Fig. 1 The satellite under study
Fig. 2 3-D model of satellite structure
Table 1 Satellite component temperature limits
Component Temperature constraints
Power subsystem 5 to 45CCommunication subsystem 5 to 45CAttitude control subsystem 5 to 45COnboard computer 0 to 40CSolar panel 100 to 85CStructure 100 to 100C
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lower bound of each components preferredoperating temperature range. The thermal
design of the satellite must not allow any
component to exceed absolute operatingtemperature ranges. Components operate most
efficiently and effectively when preferred oper-
ating temperatures are maintained. In addition,component life span will be degraded by oper-
ating the component outside of its preferred
temperature range.The satellite orbits Earth at the following
orbital parameters:
Sun-synchronous orbit
Altitude: 576 km
Inclination angle: 97.721
Local time of descending node: 9 h: 45 min
b Angle is defined as the angle between the
solar vector and the normal to the orbital plane.According to the orbital parameters listed above,
Beta angle (b) can be calculated mathematicallyas (Gilmore 1994):
b sin1cos dS sin i sinXXS sin dS cos i1
Where, dS = declination of the sun; i = orbit
inclination; (W WS) = local time of descendingnode.
Figure 3 shows the b angle history during one
year. b Angle will reach its maximum value
(about 63) at summer solstice while the min-imum value will be at winter solstice (about
55).
4 Thermal model
Thermal analysis involves constructing a geomet-ric math model (GMM) and a thermal math
model (TMM) of the satellite and identifying
analysis cases to be run. The GMM and the TMM
serve different purposes. The GMM is a mathe-matical representation of the physical surfaces of
the satellite and is used to calculate black bodyradiation couplings between surfaces as well as
heating rates due to environmental fluxes. TheTMM is most often a lumped parameter network
representation of the thermal mass and conduc-
tion and radiation couplings of the satellite, and isused to predict satellite temperatures. The radi-
ation interchange couplings and environmental
heat fluxes calculated by the GMM are used in
constructing the TMM. Both the GMM andTMM are constructed and executed using I-
DEAS TMG. First, the GMM of the satellitewas constructed using I-DEAS TMG. The model
consists of a simple representation of the satellite
and the payload. It was constructed using rectan-gular, circular, and cylindrical surfaces, and each
surface was assigned the appropriate solar
absorptivity and emissive. Dimensions and massof each component of the satellite can be found in
Table 2.
A transient-state analysis was conducted to getthe temperature variation of each component
with during one complete orbit.
The effects of the Beta angle are considered byusing different possible orbital parameters. This
angle plays an important roll in determining the
eclipse and sunlight time periods for the satellite
Fig. 3 b angle historyduring 1 year
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and hence irradiation due to different sources
such as the Sun, Earth and albedo.
Black paint is used to coat the electronic boxesand on the inside surfaces to improve energy
exchange with the other subsystems onboard the
satellite. Moreover, the external structure iscoated by white paint to minimize solar radiation
absorption. Finally, Multilayer insulation (MLI)
is used to control the temperature of the payload.A catalog of the thermal properties of each
material used on the satellites is listed in Table 3.
The element chosen from the I-DEAS TMGlibrary is linear quadrilateral thin shell element.
Table 2 Number of nodes and elements for some selectedstructural modules
Satellite structuremodule
No. of elements No. of nodes
Basis plate 146 242Basis walls 66 104
Star sensor bracket 32 61
Table 3 Mass, material properties, and thermo-optical properties of the different coatings applied
Subsystem and Component Mass (kg) Material Coating
PayloadMulti-band earth imager 45 Titanium alloys Chemglaze Black paint Z306 (inside)
Multi-layer Insulation (outside)
Payload CDHS unit 7.2 Aluminum 2024-Tx Chemglaze White paint A276MEI signal processing unit 3.7 each Aluminum 2024-Tx Chemglaze White paint A276
ADCSStar sensor 4 Aluminum 2024-Tx Chemglaze Black paint Z306Angular velocity meter Gyro 1 each Aluminum 2024-Tx Chemglaze White paint A276Interface unit for each gyro 0.92 each Aluminum 2024-Tx Chemglaze White paint A276Magnetometer 1.5 Aluminum 2024-Tx Chemglaze White paint A276Magnetorquer 0.38 each Aluminum 2024-Tx Chemglaze White paint A276Reaction wheel 3.3 each Aluminum 2024-Tx Chemglaze White paint A276
Communications subsystemX-band equipment
X-band electronic module 3.8 Aluminum 2024-Tx Chemglaze White paint A276X-band antenna 1.6 Aluminum 2024-Tx Uncoated
S-band equipmentS-band electronic module 2.2 each Aluminum 2024-Tx Chemglaze White paint A276S-band conical antenna 0.27 each Aluminum 2024-Tx UncoatedS-band dipole antenna 0.13 Aluminum 2024-Tx Uncoated
GPS receiverGPS electronic module 1.1 Aluminum 2024-Tx Chemglaze White paint A276GPS antenna 0.15 each Aluminum 2024-Tx Uncoated
Platform CDHSOn-board digital computing complex 3.7 each Aluminum 2024-Tx Chemglaze White paint A276Telemetry module 2.8 Aluminum 2024-Tx Chemglaze White paint A276
Power SubsystemBattery cell module 16.5 Ni-Cd Chemglaze Black paint Z306Power-conditioning unit (PCU) 3.6 Aluminum 2024-Tx Chemglaze White paint A276Cells leveling unit (CLU) 1.9 Aluminum 2024-Tx Chemglaze White paint A276
Solar array panels 6.8 Gallium arsenide Cell side: as = 0.75, e = 0.9 Backside:Chemglaze Black paint Z306
Thermal subsystemHeat shields 3.6 Honeycomb structure Chemglaze Black paint Z306Multi-layer Insulation 0.2
Structure and mechanism subsystemSatellite structural modulesRotation mechanism 41 Aluminum 2024-Tx Chemglaze Black paint Z306Locking and releasing mechanism 1.7 Aluminum 2024-TxSeparation transducer 0.5 Aluminum 2024-Tx
0.1 Aluminum 2024-TxSatellite total mass 205
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This type of elements assumes a constant thick-
ness. Because of the small thickness of all theelements, this thin shell was the most appropriate
element which could represent it without using an
excessive number of elements. The thermalmodel consists of 8,574 shell elements with
different thicknesses and 1,0138 nodes. Figure 4
shows the structure of the satellite after completemeshing and Table 2 define the mesh character-
istics for some selected elements.
4.1 Modeling parameters
The I-DEAS TMG software uses a finite differ-
ence method to solve the heat balance equation
and to get the temperature distribution in themodel. The heat balance equation for a transient
run to be solved iteratively at iteration n + 1 and
time t + Dt for element i can be cast in the form(Camack and Edwards 1960):
ci;t Ti;tDt;n1Ti;t Dt
Qi;tDttasAsqsi;tDttaAAqAi;tDtteAEqEi;tDtt
rXNj1
FijAij T4j;tDt;n1T4i;tDt;n1
XN
j
1
Kij Tj;tDt;n1Ti;tDT;n1 2where, Ci,t = the capacitance of the element;Ti, t + dt, n + 1 = the temperature of element i at
time t + dt and iteration n + 1; n = the current
iteration value; Ti,t = the temperature of elementi at time t; Dt = the integration time step;
Qi,t + dt(t) = the heat generation rate of element
i as a function of time at time t + dt; Gij = the sumof the conductive conductances between i and j; r
= Stefan Boltzmann constant; Fij = gray body
view factor between elements i and j; A =radiating surface area of element i.
The Backward method was used to solve Eq.
(2). In particular, it is most effective for thismodel where s min is small compared to the
solution interval. In addition, it is more accuratethan the ForwardBackward method under
conditions of rapid temperature change.
Listing of Transient Analysis Parameters,
1. Start Time = 0.0 s.2. End Time = 116686.8 s.
3. Integration Method: Backward.4. Time Step value = 58.8 s.5. Maximum Number of Iterations = 500.
6. Relaxation Factor = 0.05.
7. Temperature Difference for Convergence =0.1.
Listing of Solution Methods,
1. Solution Method: Conjugate Gradient2. Iteration Limit = 300.
Fig. 4 Satellite structure after meshing on I-DEAS TMG
Fig. 5 Shown temperature distribution of base plate
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3. Convergence Criterion = 0.1.
4. Preconditioning Matrix Fill value = 10.
5 Thermal analysis results
Satellite heating and cooling occurs while it goes
through sunlight and eclipse respectively. Maxi-mum and minimum temperatures for the satellite
will be calculated for the orbits sunlight and
eclipses zones. Temperature variations of basisplate and basis walls during one orbit are shown
in Figs. 6 and 7. Table 4 shows maximum andminimum temperatures for various satellite com-
ponents.
6 Thermo-elastic analysis
The most critical structural module in Small Sat
affect with on-orbit thermal deformation is the
basis unit block module. This module is verysensitive for the thermal deformation because it
carries the precise equipments into the satellite,
Fig. 6 Temperaturevariations of basis wallsduring one orbit
Fig. 7 Temperaturevariations of basis plateduring one orbit
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otherwise, the rest of structural modules have notbig restrictions on their equipments mounting
accuracy. The following points are taken into
consideration during building this model:
I. Basis unit block module consists of basisplate, four basis walls, two diagonal struts,
and star sensor bracket.
II. The material is Aluminum alloy AMg6(E = 7.2 103 MPa, m = 0.33, q = 2,630
kg/m3, ry = 150 MPa, ru = 310 MPa). For
thermal analysis, it has the followingproperties:
III. Thermal conductivity (K) = 117 W/m.C
IV. Coefficient of thermal expansion (a) =24.7 106 m/m/C
V. Assign the location of mounting the high
precise equipments located at basis unit
block module to calculate thermal defor-
mation at their mounting points and hence
their mounting accuracy.VI. Equipment support is designed to elimi-
nate thermal loading as they allow the
sliding of this support under thermal
expansion. Therefore, in the simplifiedthermal model all satellite equipment is
removed to avoid the appearance of anyartificial thermal stresses that may result
from the improper representation of the
sliding support.VII. Basis unit block module is meshed with
35,015 elements for the basis plate and49,096 elements for the basis walls, while
the rest of structural modules are meshed
with coarse meshing. SOLID92 elements
are used during meshing process.VIII. The nodes located at connection areas
between the different structural modulesare coupled at all degrees of freedom.
Figure 8 shows the entire finite element model
of Small Sat used during on-orbit thermal defor-
mation analysis.Thermal deformations are evaluated for the
worst cases, which are defined by the on-orbitthermal analysis for the satellite structure. Ther-
mal satellite engineer performs a complete on-orbit thermal analysis of the satellite and supplyinput data for surface temperatures gradient of
different satellite structure modules. These data
are considered as an input data to perform on-orbit thermal deformation analysis. For Small Sat,
the satellite structure is solved thermally due to
on-orbit Input data for surface temperaturesgradient of different satellite structure modules
of Small Sat are listed in Table 2. It contains
maximum and minimum average temperatures
for each structural module.Displacement boundary conditions are usually
specified at model boundaries to define rigidsupport points. During on-orbit operation, the
satellite is totally free without any fixation points,
but to conduct a thermo-elastic analysis, thedisplacement boundary condition must be defined
for the related model. Therefore, to simulate the
satellite thermal deformation due to on-orbitcycling, the satellite model must be constrained
Table 4 Surface temperatures of different satellite struc-ture modules
Satellitestructuremodule
Corneror Face
Maximumtemperature,( C)
Minimumtemperature,( C)
Base plate I 5.3 10.1
II 1.8 6.2III 7.2 4.9IV 5.4 1.6
Mounting plate I 22 11.9II 4.5 7.3III 21.2 9.4IV 18.6 7.5
Basis plate I 17 9.5II 19.8 4.7III 17 10.6IV 14.6 12
Basis walls I-II 32.8 31.3II-III 21.9 20.2
III-IV 21.9 20.2IV-I 21.9 20.2Upper frame I-II 36.1 35
II-III 28.5 29.6III-IV 32.5 31.7IV-I 36.3 35.2
Lower frame I-II 18.5 16.3II-III 12 5.9III-IV 17.6 12.8IV-I 13.5 7.2II 14.7 10.3III 15.2 8
Diagonal strut I 14.3 13.2IV 16.6 15.5
Star sensor bracket 18.8 17.4
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by rigid support points. Selection of these pointslocations and their fixation manner should
provide minimum effect on satellite deformation.
For Small Sat model represented at Fig. 8, thesupport points are selected at plan of star sensor
mounting with its bracket. This plan is selected
because the mounting accuracy of all preciseequipments installed at the basis unit block is
measured relative to the star sensor bracket.
Displacement boundary conditions are applied byfixing one of the star sensor four points of fixation
(on bracket) in X direction. Then, fix the next
point in the Y and one of the other in the Z.By reviewing the input data listed at Table 2,
some of the satellite structural modules aredivided into more than one division according to
their position. Each division has its maximum and
minimum average surface temperature. Beforeconduct a thermo-elastic analysis, a thermal anal-
ysis process is performed to expand temperatures
through all solid elements and calculate temper-ature distribution for all nodes. This process is
performed twice for the worst cases, maximum
and minimum average surface temperatures.A thermo-elastic analysis is conducted to the
entire satellite model based on the output results
from the thermal analysis. The analysis is per-
formed twice for the worst cases, maximum andminimum average surface temperatures. Dis-
placement boundary conditions are applied as
shown in Fig. 8.Thermal strains are given by a. (T-Tref),
where a is the coefficient of thermal expansion, T
is the current element temperature, and Tref is thereference (ambient) temperature. In thermo-elas-
tic analysis, the reference temperature is the zero
thermal stresses temperature which is the assem-bly room temperature (=20C) in Small Sat case.
7 Thermo-elastic analysis results
Temperature distribution for the entire satellite isdetermined as a result of the thermal analysis.
Fig. 8 F.E model used during on-orbit thermal deforma-tion analysis
Fig. 9 Temperature distribution for the entire satelliteduring maximum average surface temperatures
Fig. 10 Temperature distribution for the entire satelliteduring minimum average surface temperatures
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Figures 9 and 10 show the temperature distribu-
tion (C) for the entire satellite during maximumand minimum average surface temperatures.
Stress-strain state of the basis unit block
structure module is determined as a result of theon-orbit thermal deformation (thermo-elastic)
analysis for both worst cases, maximum and
minimum average surface temperatures. Thediagrams of equivalent stress distribution
(103 MPa) and displacements (mm) of this struc-
tural module are shown in Figs. 1114. The stress
values are determined according to Von-Missescriterion. Displacements are relative to the points
of star sensor attachment to its bracket, which arethe fixation points for the entire model of Small
Sat structure during thermo-elastic analysis as
presented at Fig. 6.The maximum stresses values re for basis unit
block module at each on-orbit thermally worst
load cases and there equivalent yield margin ofsafety (MSy) are given in Table 5.
8 Mounting accuracy due to on-orbit thermaldeformation
From static point of view, the basis unit block
module is safe because the yield margin of safetyis a positive value in both of worst design cases.
But this is not enough to determine that the
design is applicable and can withstand to on-orbitthermal loads. Satisfactory performance of the
satellite requires accurate predictions of thermal
Fig. 11 Basis unit block stress distribution due to on-orbitthermal deformation at maximum average surface tem-peratures
Fig. 14 Basis unit block displacement due to on-orbitthermal deformation at minimum average surface temper-atures
Fig. 12 Basis unit block displacement due to on-orbitthermal deformation at maximum average surface tem-peratures
Fig. 13 Basis unit block stress distribution due to on-orbitthermal deformation at minimum average surface temper-atures
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deformations to verify pointing and alignmentrequirements for Mounting Accuracy. Therefore,
it is important to calculate the angular positioning
deviations for all high precise equipments (pay-load and ADCS devices) relative to the star
sensor due to on-orbit thermal deformation.
These values must not exceed the relative limitingdeviations specified for mounting the precise
equipments. Table 6 lists the limiting angular
positioning deviations for the most precise equip-ments relative to the star sensor which are
derived from the structure requirements.
The angular positioning deviation between anytwo equipments is calculated by measuring the
deviation angle between normal vectors for their
mounting plans. The deviation angle is deter-mined by subtracting the measured angle after
on-orbit thermal deformation from the initialangle before deformation. The criterion used tocalculate the angular positioning deviation
between the precise equipments and the star
sensor is explained below. Figure 15 showsgraphical sketch to explain the criterion used to
calculate the angular positioning deviation be-
tween any two equipments.
All precise equipments mounted on basisunit block are fixed through three or four
fixation points. The mounting plan can be
defined by only two vectors connecting at leastthree fixation points. In case of equipment A,
V*
1A, and V*
2A identify its mounting plan before
on-orbit thermal deformation. While, V*
1B andV*
2B identify the mounting plan of equipment B.
The normal vectors, V*
and V*
nB for mounting
plan of equipment A and B respectively beforeon-orbit thermal deformation, can be calculated
by applying vector cross product as following:
V*
nA V*
1A V*
2A
V*
nB
V*
1B
V*
2B
The angle between both of these normal vectorsis calculated by the next formula:
h cos1
V*
1A V*
2A
j V*
1Aj j V*
2Aj
!
After on-orbit thermal deformation, the equip-
ment mounting plan is usually deformed. And so
the normal vectors, V*
nA and V*
nB, are modified toV* 0nA and V* 0nB respectively. They are calculatedfor the deformed mounting plan as following:
V* 0
nA V* 0
1A V* 0
2A
V* 0
nB V* 0
1B V* 0
2B
Where: V* 0
1A & V* 0
2A and V* 0
1B & V* 0
2B identifythe mounting plan of equipment A and B
respectively after on-orbit thermal deformation.
These vectors are calculated from the displace-ment deformation results of on-orbit thermal
deformation analysis in X, Y, and Z direction.
The modified angle between normal vectors for
the deformed mounting plan is calculated asfollowing:
h0 cos1 V* 0
1A V* 0
2A
j V* 0
1Aj j V* 0
2Aj
0@
1A
Table 5 Maximum Von-Misses equivalent stresses andyield margins of safety for basis unit block module at eachon-orbit thermally worst load cases
Design case re (MPa) MSy
Case 1 94.158 0.59Case 2 125.937 0.19s Case 1 represents the thermal deformation due to
on-orbit maximum temperatures.s Case 2 represents the thermal deformation due to
on-orbit minimum temperatures.
Table 6 Limiting angular positioning deviations for themost precise equipments relative to the star sensor
Equipment Limiting angular positioningdeviations, (arcmin)
MBEI (optical-mechanical unit)
30
Angular velocitymeters (gyro)
60
Reaction wheels 60Magnetometer 60Magnetorquers 60
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The angular positioning deviation angle between
equipment A and B is calculated by the next
formula:
hdev h0 h
For Small Sat, the angular positioning devia-
tion angle hdev (arc-min) is calculated for theprecise equipments mounted on basis unit block
relative to the star sensor. Table 7 lists the valuesof angular positioning deviation angle due to on-
orbit thermal deformation relative to the star
sensor. It shows the results for both maximum
and minimum on-orbit temperatures. By compar-ing these results with the limiting values listed at
Table 6, the performance of the satellite is notaffected with on-orbit thermal deformation under
maximum or minimum temperatures.
9 Fatigue damage due to on-orbit thermal cycling
One of the most essential aspects during perform-
ing on-orbit thermal deformation analysis is to
evaluate the fatigue damage due to on-orbit cyclicthermal stresses. Ductile material (AMg6 alumi-
num alloy), used to manufacture the satellite
structure modules, does not rupture or bucklefrom a single application of thermal stress, which is
clear from the analysis until now. But the material
can fail in fatigue from the many cycles of on-orbitthermal deformation loading. The results data of
thermo-elastic analysis is used to evaluate the
thermal fatigue damage for the basis unit block.
By reviewing the results data of thermal
deformation analysis and the thermal stresses
distribution for the basis unit block module undermaximum and minimum temperatures (Figs. 11
14), the maximum thermal stress is occurred atthe same locations under both of the worst cases.
These locations are illustrated in Fig. 16. The
entire satellite structure is affected by a cyclicthermal stresses along the operation life time of
the satellite. However, these points are the most
locations that are affected by fatigue damage dueto on-orbit thermal cycling.
Thermal fatigue damage must be calculated for
the critical points located at basis plate moduleand basis walls module. For thermal fatigue
damage calculation, the maximum and minimumcyclic thermal stresses for the critical points are
taken from the thermal deformation analysis
results. The time life cycles (Nth) corresponding
to each given stress ratio is calculated (Incroperaand David 1990),
log Nf a1 a2 log Smax 1 R n a3 2
R
Smin=Smax; a1
20:68; a2
9:84; a3
0
Smax = the highest algebraic value of stress in thestress cycle. Smin = the lowest algebraic value of
stress in the stress cycle.
The number of cycles (nth) corresponding tothe operation life time of the satellite is calculated
as following:
The satellite duration period (Tdr), which is thetime interval for completing one orbital cycle
(revolution), is defined in the following way:
Equipment A Equipment B
Mounting plan after
deformation
Mounting plan
before deformation
1Avh
nAvh
2Avh
1A'v
h
2A'v
hnA
'vh
1Bvh
2Bvh
nBvh
nB'v
h
1B'v
h
2B'v
h
Fig. 15 The criterion ofangular positioningdeviation calculationbetween any twoequipments
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Tdr 2pffiffiffiffiffile
p a32(
1 eelea
2 1 e2 2"
2 52
sin2i
1 e2 321 e cosu x 2
1 e cosu x 3
1 e2
1 3sin2i sin2u #) 3Where, a = the major semi axis, (= Re + h); Re =
the mean earth radius, (= 6378.14 km); h = the
satellite altitude; le= the gravitational constant ofthe earth, (= 3.986005 105 km3/s2); ee = the
earth oblateness parameter, (= 2.6333 1010 km5/
s2); i = inclination; e = eccentricity; u = theargument of latitude; x = the argument of perigee
For Small Sat, the following parameter values
are taken during calculation, h = 668 km; i =98.085; e = 0.001; u = 0; x = 0. By substituting
with these values into the previous equation, thedraconian period for Small Sat equals to:
Tdr 5881:9 sThe number of cycles (n) corresponding to the
operation life time is defined as:
nth
Topr
Tdr
Fig. 16 Location of the worst thermal case
Table 7 Angular positioning deviation angle for the precise equipments relative to the star sensor
Equipment Angle before deformation,h (deg)
Modified angle afterdeformation, h (deg)
Angular positioning deviationsangle, hdev (arcmin)
Case 1 Case 2 Case 1 Case 2
MBEI 136 135.9871 135.9955 0.777 0.269AVM, gyro Mx 90 89.9982 90.0063 0.105 0.379AVM, gyro My 46 46.0042 46.0117 0.252 0.7002
AVM, gyro Mz 44 43.9885 43.9908 0.691 0.5512AVM, skewed gyro 44 44.0233 44.0238 1.3996 1.428Reaction wheels Mx 90 90.0127 90.0068 0.7614 0.40734Reaction wheels My-1 134 134.0076 133.9993 0.4549 0.0395Reaction wheels My-2 134 134.0035 133.9959 0.2078 0.2446Reaction wheels Mz 44 44.0221 44.0202 1.3242 1.2117Magnetometer 136 135.9947 135.9979 0.3168 0.1239sMagnetorquers 44 43.9828 43.9892 1.0341 0.6458Note:s Case 1 represents the thermal deformation due to on-orbit maximum temperatures.s Case 2 represents the thermal deformation due to on-orbit minimum temperatures.
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Where: Topr is the operation life time of the
satellite, which equals to 5 years.
Topr 5 365 24 60 60 157:86 106 sec
Hence,
nth 26; 808 cyclesThe thermal damage at the critical points is
calculated by the following relation and listed in
Table 8:
Dthermal nthNth
Thermal fatigue damage calculations show
that the satellite structure can withstand allcyclic stresses due to on-orbit cyclic thermal
loading during its life span, because the totalcumulative fatigue damage does not exceed one
for all critical points located in the basis unit
block modules.
10 Conclusion
Satellite structure thermal analysis is done to
verify functional temperature profile, mountingaccuracy of equipments and validate acceptable
thermal fatigue damage. By referring to the
thermal results gained above applying IDEAS,the structure will not experience high tempera-
tures during the mission. Inspection of the aboveresults appears that the maximum temperatures
occur at the onboard computer frame modules
(25.2C). As one can notice from Table 6, there isa difference of 6C between two sides of the first
onboard computer frame module. This tempera-ture difference is due to the temperatures of the
heat shields. The heat shields have a direct impact
on the temperature of the frame modules as fromfacing the heat shield facing the sun or deep
space. As it has been showed in Fig. 7, the
temperature gradient between the plates did notexceed 5C.
Temperature drop in height of reinforcing ribs
was taken equal to 0.2C. For plates this temper-ature increases in the direction of an mounting
plate, and for a case of a basis unitinwards of a
basic unit. In calculation of thermal strains of theplates and basic unit case, a temperature drop in
height of reinforcing ribs was taken into account.
In calculation of cases of frame modules this dropwas not taken into account, since it effects slightly
on angular deviations of instruments requiring anaccurate installation. These temperature distribu-tions are applied in a finite-element model as
boundary conditions and thermal analysis is
executed but using FE technique this time. Thisstep is done to account for the mesh difference
between finite-difference model and the finite-
element one.During on-orbit operation, the satellite is
totally free without any fixation points. To con-
duct a thermoelastic analysis, displacement
boundary conditions must be defined for therelated model. Therefore, the satellite modelmust be constrained by rigid support points.
Selection of these points locations and their
fixation manner should provide minimum effecton satellite thermal deformation. For Small Sat,
the support points are selected at the plane of star
sensor mounting with its bracket. This plane isselected because the mounting accuracy of all
precise equipment installed on the basis unit
Table 8 Thermal and overall fatigue damage calculation for the critical points
Critical points Thermo-elastic analysis Thermal fatigue analysis
rmax rmin N (cycles) n (cycles) Thermal Damage
MPa Ksi MPa Ksi
12 23.575 3.422 27.956 4.058 1.00E+12 26808 2.68E-0813 29.530 4.286 28.697 4.165 1.00E+12 26808 2.68E-0814 1.855 0.269 4.066 0.590 1.00E+16 26808 2.68E-1224 94.158 13.666 125.937 18.278 5.00E+06 26808 5.36E-03
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block is measured relative to the star sensorbracket. Displacement boundary conditions are
applied by fixing one of the star sensor four points
of fixation (on bracket) in the X direction, fixingthe next point in the Y and one of the other points
in the Z direction.
The stress-strain state of the basis unit blockstructure module is determined as a result of the
on-orbit thermoelastic analysis for both worst
cases, in which the maximum and minimumaverage on-orbit surface temperatures take place.
Displacements are relative to the points of star
sensor attachment to its bracket. From staticpoint of view, the basis unit block module is safe
because the yield margin of safety is a positive
value in both design cases. But this is notsufficient to decide whether the design is satisfac-
tory. Satisfactory performance of the satelliterequires accurate prediction of thermal deforma-tions to verify pointing and alignment accuracy
requirements for sensors. The angular positioning
deviation angle hdev (arcmin) is calculated for theprecise equipments mounted on the basis unit
block relative to the star sensor due to on-orbit
thermal deformation. These results are comparedwith the specified limiting angular positioning
deviations for the most precise equipment rela-
tive to the star sensor. Results show that the
performance of the satellite is not affected withon-orbit thermal deformation under maximum or
minimum temperatures.Fatigue damage due to on-orbit cyclic thermal
stresses is evaluated after performing on-orbit
thermal deformation analysis. The maximumthermal stress occurs at the same location under
both worst cases. This location is specified as
Point 24 as shown in Fig. 15 is most severelyaffected by fatigue damage due to on-orbit
thermal cyclic loading. The total fatigue damage
for any point located in the basis unit blockmodule is the dynamic fatigue damage due to
mechanical vibration acting on the satellite duringtransportation and launch plus the thermal
fatigue damage due to on-orbit cyclic thermal
stresses. Therefore, to calculate the overallfatigue damage for the basis unit block, dynamic
fatigue damage must be calculated for Point 30
based on the fatigue analysis of dynamic vibra-tions. Moreover, thermal fatigue damage must be
calculated for the critical points located in thebasis plate and basis walls modules. Thermal
fatigue damage calculations show that the satel-
lite structure can withstand all cyclic stresses dueto on-orbit cyclic thermal loading during its life
span, because the total cumulative fatigue dam-
age does not exceed one for all critical pointslocated in the basis unit block modules. Fatigue
damage due to thermal loading is evaluated and
the satellite structure is safe for the functionalperiod of life time (5 years).
References
Periodicals
Grooms, H.R., DeBarro, C.F., Paydarfar, S.: What is anoptimal spacecraft structure? J Spacecraft Rockets.29, 480483, No. 4, July-August (1992)
Tsai, J.R.: Overview of satellite thermal analytical model. JSpacecraft Rockets 41, 120125 (2004)
Books
Bruhn, E.F.: Analysis and design of flight vehicle struc-tures. Tri-State Offset Company, USA (1973)
Camack, W.G., Edwards, D.K.: Effect of surface thermal
radiation characteristics on the temperature controlproblem in satellites. In: Clauss, F.J. (ed.) Surfaceeffect on spacecraft material. John Wiley & Sons, Inc.New York (1960)
Crandall, S.H.: Random vibration. Technology Press,Wiley, NY (1958)
Dnepr SLS users guide, Issue 2, Nov. 2001. http://www.kosmotras.ru
Dornheim, M.A.: Planetary flight surge faces budgetrealities. Aviation week and space technology 145,4446, No. 24, 9 Dec. (1996)
Gilmore, D.: Satellite thermal control handbook. TheAerospace Corp. Press, El Segundo, CA (1994)
Hatch, M.: Vibration simulation using MATLAB andANSYS. Chapman & Hall/CRC, Florida (2001)
Hibbeler Russell, C.: Structural Analysis, 3rd. PRENTICEHALL, Inc (1995)
I-DEAS TMG Reference Manual, MAYA Heat TransferTechnologies Ltd., January 2003
Incropera, F.P., David, P.: Introduction to Heat Transfer.John Wiley & Sons, Inc. (1990)
Karam, R.D.: Satellite thermal control for system engi-neer. McGraw-Hill, New York (1998)
Prediction of satellite structure life on-orbit under thermalfatigue effect, National Authority of Remote Sensingand Space Science, NARSS, Egypt (2006)
158 Int J Mech Mater Des (2006) 3:145159
123
http://-/?-http://-/?-http://-/?-http://-/?-7/28/2019 Thermal Fatigue Analysis
15/15
Sarafin Thomas, P., Larson Wiley, J. (eds.): Spacecraftstructures and mechanisms - From concept to launch.Microcosm Press and Kluwer Academic Publishers,Torrance, CA (1995)
Schiff Daniel.: Dynamic analysis and failure modes ofsimple structures. John Wiley & Sons, Inc. NY (1990)
Shegly, J.: Mechanical engineering design, 6th edn.
McGraw-Hill, Boston, MA (2004)Tedesco, J., McDougal, G., Ross, C.: Structural dynam-ics theory and applications. Addison Wesley Long-mann, CA (1999)
Terster, W., NASA Considers Switch to Delta 2, SpaceNews, Vol. 8, No. 2, 13-19 Jan. 1997, pp., 1, 18
Wertz, J.R., Larson, W.J.: Space mission analysis anddesign. Space Microcosm Press and Kluwer AcademicPublishers, Torrance, CA (1992)
Proceedings
Moffitt B.A.: Predictive thermal analysis of the combatsentinel satellite. Proceedings, 16th Annual AIAA/USU Conference on small satellites, Logan, UtahState University (2002)
Computer Software
ANSYS Professional, Software Package, Ver. 10, ANSYS,Inc., Southpointe, 275 Technology Drive Canonsburg,PA 15317
I-DEAS TMG reference manual, MAYA Heat TransferTechnologies Ltd., January 2003.
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