SIST-TP CEN/CLC/TR 17603-31-08:2021
(Main)Space Engineering - Thermal design handbook - Part 8: Heat Pipes
Space Engineering - Thermal design handbook - Part 8: Heat Pipes
Heat pipes are a solution to many thermal dissipation problems encountered in space systems.
The types of heat pipes that can be used in spacecrafts are described. Details on design and construction, usability, compatibility and the limitations of each type are given.
The Thermal design handbook is published in 16 Parts
TR 17603-31-01 Part 1
Thermal design handbook – Part 1: View factors
TR 17603-31-01 Part 2
Thermal design handbook – Part 2: Holes, Grooves and Cavities
TR 17603-31-01 Part 3
Thermal design handbook – Part 3: Spacecraft Surface Temperature
TR 17603-31-01 Part 4
Thermal design handbook – Part 4: Conductive Heat Transfer
TR 17603-31-01 Part 5
Thermal design handbook – Part 5: Structural Materials: Metallic and Composite
TR 17603-31-01 Part 6
Thermal design handbook – Part 6: Thermal Control Surfaces
TR 17603-31-01 Part 7
Thermal design handbook – Part 7: Insulations
TR 17603-31-01 Part 8
Thermal design handbook – Part 8: Heat Pipes
TR 17603-31-01 Part 9
Thermal design handbook – Part 9: Radiators
TR 17603-31-01 Part 10
Thermal design handbook – Part 10: Phase – Change Capacitors
TR 17603-31-01 Part 11
Thermal design handbook – Part 11: Electrical Heating
TR 17603-31-01 Part 12
Thermal design handbook – Part 12: Louvers
TR 17603-31-01 Part 13
Thermal design handbook – Part 13: Fluid Loops
TR 17603-31-01 Part 14
Thermal design handbook – Part 14: Cryogenic Cooling
TR 17603-31-01 Part 15
Thermal design handbook – Part 15: Existing Satellites
TR 17603-31-01 Part 16
Thermal design handbook – Part 16: Thermal Protection System
Raumfahrttechnik - Handbuch für thermisches Design - Teil 8: Wärmerohre
Ingénierie spatiale - Manuel de conception thermique - Partie 8: Caloducs
Vesoljska tehnika - Priročnik o toplotni zasnovi - 8. del: Toplotne cevi
General Information
Buy Standard
Standards Content (Sample)
SLOVENSKI STANDARD
SIST-TP CEN/CLC/TR 17603-31-08:2021
01-oktober-2021
Vesoljska tehnika - Priročnik o toplotni zasnovi - 8. del: Toplotne cevi
Space Engineering - Thermal design handbook - Part 8: Heat Pipes
Raumfahrttechnik - Handbuch für thermisches Design - Teil 8: Wärmerohre
Ingénierie spatiale - Manuel de conception thermique - Partie 8: Caloducs
Ta slovenski standard je istoveten z: CEN/CLC/TR 17603-31-08:2021
ICS:
49.140 Vesoljski sistemi in operacije Space systems and
operations
SIST-TP CEN/CLC/TR 17603-31-08:2021 en,fr,de
2003-01.Slovenski inštitut za standardizacijo. Razmnoževanje celote ali delov tega standarda ni dovoljeno.
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SIST-TP CEN/CLC/TR 17603-31-08:2021
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SIST-TP CEN/CLC/TR 17603-31-08:2021
TECHNICAL REPORT
CEN/CLC/TR 17603-31-
08
RAPPORT TECHNIQUE
TECHNISCHER BERICHT
August 2021
ICS 49.140
English version
Space Engineering - Thermal design handbook - Part 8:
Heat Pipes
Ingénierie spatiale - Manuel de conception thermique - Raumfahrttechnik - Handbuch für thermisches Design -
Partie 8 : Caloducs Teil 8: Wärmerohre
This Technical Report was approved by CEN on 21 June 2021. It has been drawn up by the Technical Committee CEN/CLC/JTC 5.
CEN and CENELEC members are the national standards bodies and national electrotechnical committees of Austria, Belgium,
Bulgaria, Croatia, Cyprus, Czech Republic, Denmark, Estonia, Finland, France, Germany, Greece, Hungary, Iceland, Ireland, Italy,
Latvia, Lithuania, Luxembourg, Malta, Netherlands, Norway, Poland, Portugal, Republic of North Macedonia, Romania, Serbia,
Slovakia, Slovenia, Spain, Sweden, Switzerland, Turkey and United Kingdom.
CEN-CENELEC Management Centre:
Rue de la Science 23, B-1040 Brussels
© 2021 CEN/CENELEC All rights of exploitation in any form and by any means Ref. No. CEN/CLC/TR 17603-31-08:2021 E
reserved worldwide for CEN national Members and for
CENELEC Members.
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SIST-TP CEN/CLC/TR 17603-31-08:2021
CEN/CLC/TR 17603-31-08:2021 (E)
Table of contents
European Foreword . 10
1 Scope . 11
2 References . 12
3 Terms, definitions and symbols . 13
3.1 Terms and definitions . 13
3.2 Symbols . 13
4 General introduction . 17
5 Heat pipe wicks . 19
5.1 General . 19
5.2 Basic properties . 20
5.2.1 Equilibrium capillary height . 20
5.2.2 Permeability . 20
5.2.3 Effective thermal conductivity of the wick . 20
5.3 Low resistance wicks . 22
6 Heat pipe working fluids . 28
6.1 General . 28
6.2 Empirical correlations . 29
6.3 Physical properties . 31
6.4 Compatibility with wicks . 47
7 Simple heat pipe . 48
7.1 General . 48
7.2 Operating limits . 48
7.2.1 Capillary heat transfer limit . 49
7.2.2 Sonic limit (choking) . 54
7.2.3 Entrainment limit . 56
7.2.4 Boiling limit . 56
7.3 Performance . 57
8 Variable conductance heat pipes . 70
2
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8.1 General . 70
8.2 Design considerations . 72
8.2.1 Diffusion of the working fluid . 72
8.2.2 Working fluid selection . 73
8.2.3 Reservoir sizing . 74
9 Existing System . 78
9.1 Eads Astrium . 78
9.2 Euro Heat Pipes . 91
9.2.1 Aluminium Heat Pipes . 91
9.2.2 STAINLESS STEEL HEAT PIPES. This part deals with the products
from Technical Data Sheet n° 1B: EHP Stainless Steel . 101
9.3 Iberespacio . 106
9.3.1 Axial Grooved Heat Pipes . 106
9.3.2 Arterial Heat Pipes . 109
9.4 Thales Alenia Space . 111
9.4.1 Technical Description . 111
9.4.2 External Geometries . 113
10 Cryogenic heat pipes . 116
10.1 General . 116
10.2 Working fluids . 116
10.3 Wicks . 118
10.3.1 Lab wicks . 120
10.3.2 Tunnel artery . 120
10.3.3 Graded-porosity wicks . 120
10.4 Operating limits . 121
10.4.1 Capillary heat transfer limit . 121
10.5 Transient operating characteristics . 127
10.5.1 Mathematical modelling of static transient . 127
10.5.2 Mathematical modelling of fluid dynamic transient. 128
10.6 Reduced gravity testing of cryogenic heat pipes . 129
10.7 Thermal diode cryogenic heat pipes . 131
10.7.2 Reversal requirements . 132
10.8 Superfluid heat pipes . 134
10.9 Existing systems . 138
Bibliography . 146
3
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Figures
−1
Figure 5-1: Measured values of the inverse permeability, K , vs. mass flow rate per
unit area, m .> From Phillips & Hinderman (1969) [67]. . 27
−1
Figure 5-2: Measured values of the inverse permeability, K , vs. mass flow rate per
unit area, m .> From Phillips & Hinderman (1969) [67]. . 27
Figure 6-1: Relevant physical properties of Ammonia as a function of temperature, T,
The labels correspond to experimental points. The expressions used to
calculate the tabulated values are given below. Calculated by the compiler. . 32
Figure 6-2: Relevant physical properties of Ethanol as a function of temperature, T, The
labels correspond to experimental points. The expressions used to
calculate the tabulated values are given below. Calculated by the compiler. . 34
Figure 6-3: Relevant physical properties of Freon 11 as a function of temperature, T,
The labels correspond to experimental points. The expressions used to
calculate the tabulated values are given below. Calculated by the compiler. . 36
Figure 6-4: Formulae Used for Calculating the Values of the Physical Properties. . 38
Figure 6-5: Relevant physical properties of Nitrogen as a function of temperature, T,
The labels correspond to experimental points. The expressions used to
calculate the tabulated values are given below. Calculated by the compiler. . 40
Figure 6-6: Relevant physical properties of Propane as a function of temperature, T,
The labels correspond to experimental points. The expressions used to
calculate the tabulated values are given below. Calculated by the compiler. . 42
Figure 6-7: Relevant physical properties of Water as a function of temperature, T, The
labels have been drawn to guide in the selection of the appropriate curve,
and do not correspond to experimental values. After Schmidt (1969) [82]. . 44
Figure 6-8: Figure of Merit, N, as a function of temperature, T, for several heat pipe
working fluids. For each curve, the range of temperature variation is
bounded between the largest and smallest operating pressures. Calculated
by the compiler. . 46
Figure 7-1: Sketch illustrating design variables in grooved heat pipes. From Frank et al.
(1967) [27], quoted by Winter & Barsch (1971) [96]. . 51
Figure 7-2: Relation between the dimensionless parameter 16/β(ν /ν )F and the
v l
geometrical parameter, ψ. From Frank et al. (1967) [27], quoted by Winter
& Barsch (1971) [96]. . 52
3
Figure 7-3: Optimum value of the dimensionless maximum heat transfer, Q /Γr , vs.
max w
the geometrical parameter, ψ. From Frank et al. (1967) [27], quoted by
Winter & Barsch (1971) [96]. . 53
Figure 7-4: Graph for determining F. From Frank et al. (1967) [27], quoted by Winter &
Barsch (1971) [96]. . 53
Figure 7-5: Optimum value of the aspect ratio of the grooves, α, vs. the geometrical
parameter, ψ. From Frank et al. (1967) [27], quoted by Winter & Barsch
(1971) [96]. . 54
Figure 7-6: Maximum heat transfer, Q , based on sonic limit, vs. evaporator
max
temperature, TE, for several values of the shear streets, τ, and of the
convective heat transfer, Q . Sodium heat pipe. A: τ = 0 and Q = 0; B:
conv conv
τ ≠ 0 and Qconv≠ 0; C: τ≠ 0 and Qconv = 0; D: τ≠ 0 and Qconv ≠ 0. In this case
the heat pipe had an adiabatic length. In curves A, B, and C choking is
4
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reached at the evaporator, while in curve D choking is reached at the
adiabatic length end. From Levy (1972) [49]. . 55
Figure 7-7: Heat Transfer, Q , and Integral Heat Transport Factor, [Q.l ] , vs. wick
max eff max
thickness, δ, for several mesh sizes and two heat pipe diameters, D .
o
Circumferential screen wick. Solid lines: vapour laminar flow; dotted lines:
vapour turbulent flow. From Skrabek (1972) [88]. . 58
Figure 7-8: Heat Transfer, Q , and Integral Heat Transport Factor, [Q.l ] , vs. wick
max eff max
thickness, δ, for several mesh sizes and two heat pipe diameters, D .
o
Circumferential screen wick. Solid lines: vapour laminar flow; dotted lines:
vapour turbulent flow. From Skrabek (1972) [88]. . 59
Figure 7-9: Heat Transfer, Q , and Integral Heat Transport Factor, [Q.l ] , vs. wick
max eff max
thickness, δ, for several mesh sizes and two heat pipe diameters, D .
o
Circumferential screen wick. Solid lines: vapour laminar flow; dotted lines:
vapour turbulent flow. From Skrabek (1972) [88]. . 60
Figure 7-10: Heat Transfer, Q , and Integral Heat Transport Factor, [Q.l ] , vs. wick
max eff max
thickness, δ, for several mesh sizes and two heat pipe diameters, D .
o
Porous slab wick. Solid lines: vapour laminar flow; dotted lines: vapour
turbulent flow. From Skrabek (1972) [88]. . 61
Figure 7-11: Heat Transfer, Q , and Integral Heat Transport Factor, [Q.l ] , vs. wick
max eff max
thickness, δ, for several mesh sizes and two heat pipe diameters, D .
o
Porous slab wick. Solid lines: vapour laminar flow; dotted lines: vapour
turbulent flow. From Skrabek (1972) [88]. . 62
Figure 7-12: Heat Transfer, Q , and Integral Heat Transport Factor, [Q.l ] , vs. wick
max eff max
thickness, δ, for several mesh sizes and two heat pipe diameters, D .
o
Porous slab wick. Solid lines: vapour laminar flow; dotted lines: vapour
turbulent flow. From Skrabek (1972) [88]. . 63
Figure 7-13: Heat pipe conductance, C, vs. wick thickness, δ, for several wick
conductivities, k , and two heat pipe diameters, D . Circumferential screen
eff o
wick. From Skrabek (1972) [88]. . 64
Figure 7-14: Heat pipe conductance, C, vs. wick thickness, δ, for several wick
conductivities, k , and two heat pipe diameters, D . Circumferential screen
eff o
wick. From Skrabek (1972) [88]. . 65
Figure 7-15: Heat pipe conductance, C, vs. wick thickness, δ, for several wick
conductivities, k , and two heat pipe diameters, D . Circumferential screen
eff o
wick. From Skrabek (1972) [88]. . 66
Figure 7-16: Heat pipe conductance, C, vs. wick thickness, δ, for several values of the
heat transfer coefficient of the wick, h, and heat pipe diameters, D . Porous
o
slab wick. From Skrabek (1972) [88]. . 67
Figure 7-17: Heat pipe conductance, C, vs. wick thickness, δ, for several values of the
heat transfer coefficient of the wick, h, and heat pipe diameters, D . Porous
o
slab wick. From Skrabek (1972) [88]. . 68
Figure 7-18: Heat pipe conductance, C, vs. wick thickness, δ, for several values of the
heat transfer coefficient of the wick, h, and heat pipe diameters, D . Porous
o
slab wick. From Skrabek (1972) [88]. . 69
Figure 8-1: VCHP with cold reservoir. . 71
Figure 8-2: VCHP with hot reservoir. (a) Internal hot reservoir. (b) External hot
reservoir. . 72
5
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Figure 8-3: Vapor concentration at the reservoir, n(t), over its steady-state value, n(∞),
and control temperature range, ∆T, as functions of time, t. From
Hinderman. Waters & Kaser (1972) [35]. . 73
Figure 8-4: Dimensionless pressure ratio, π , vs. control temperature range, T −T ,
r Emax Emin
for several working fluids. From Hinderman, Waters & Kaser (1972) [35]. . 74
Figure 8-5: Sketch of a variable conductance heat pipe. 1: Evaporator. 2: Adiabatic
Section. 3: Condenser. 4: Adiabatic Section. 5: Reservoir. . 75
Figure 8-6: Dimensionless reservoir to condenser volume ratio, V /V , vs. evaporator
R C
temperature variation, (T −T ), for two different working fluids, and a
Emax Emin
given reservoir temperature variation, (T −T ) = 28 K. From Edelstein
Rmax Rmin
& Hembach (1972) [23]. . 75
Figure 8-7: Dimensionless reservoir to condenser volume ratio, V /V , vs. reservoir
R C
temperature variation, (T −T ), with fixed evaporator control
Rmax Rmin
temperature variation, (T −T ) = 6 K. From Edelstein & Hembach
Emax Emin
(1972) [23]. . 76
Figure 8-8: Dimensionless reservoir to condenser volume ratio, V /V , vs. evaporator
R C
temperature variation, (T −T ), for ammonia working fluid. From
Emax Emin
Edelstein & Hembach (1972) [23]. . 76
Figure 8-9: Dimensionless reservoir to condenser volume ratio, V /V , vs. evaporator
R C
temperature variation, (T −T ). Solid lines: cold reservoir. Dashed
Emax Emin
lines: hot reservoir. (A) and (M) correspond to ammonia and methanol
respectively. T is the sink temperature; in one case the back of the radiator
s
is pained black (222 K < T < 254 K), and in the other it is aluminized (196 K
s
< T < 245 K). Evaporator temperature, T = (287 + (T −T )/2) K. From
s E Emax Emin
Kirkpatrick & Marcus (1972) [42]. . 77
Figure 9-1: WR7 Heat Pipe Profile (Cryogenic Application) . 83
Figure 9-2: WR12 Heat Pipe Profile. 84
Figure 9-3: WR18 Heat Pipe Profile. 84
Figure 9-4: WR19 Heat Pipe Profile. 85
Figure 9-5: WR20 Heat Pipe Profile. 85
Figure 9-6: WR22 Heat Pipe Profile. 86
Figure 9-7: WR24 Heat Pipe Profile. 86
Figure 9-8: WR25 Heat Pipe Profile. 87
Figure 9-9: WR26 Heat Pipe Profile. 87
Figure 9-10: WR27 Heat Pipe Profile . 88
Figure 9-11: WR28 Heat Pipe Profile . 88
Figure 9-12: WR29 Heat Pipe Profile . 89
Figure 9-13: WR7 Heat Pipe used for SCIAMACHY on ENVISAT . 89
Figure 9-14: EADS ASTRIUM HP experience . 90
Figure 9-15: EHP: typical Aluminium extruded HP . 91
Figure 9-16: Heat transport capability – NH3 (Note: AG110 = size 11 mm in tens of
millimetres.) . 94
Figure 9-17: HP Profile Tolerances. 97
6
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Figure 9-18: HP Profile Tolerances (cont.). 98
Figure 9-19: HP Profile Tolerances (cont.). 99
Figure 9-20: ESA SMART 1 with HP . 100
Figure 9-21: ESA AEOLUS – ALADIN instrument with HP network . 100
Figure 9-22: Constant Conductance Heat Pipe . 101
Figure 9-23: Variable Conductance Heat Pipe . 101
Figure 9-24: Heat Pipe Profiles examples Table 9.2-3. Stainless Steel Heat Pipes
types. . 102
Figure 9-25: “Thank to 40 state-of-the art variable conductance heat pipes located in
the avionics bay the ATV is able to carry away the heat and release the
energy directly into space or, otherwise, to warm up other parts in a very
economic fashion” Astrium – ESA “Jules Verne goes hot and cold” –
Successful achievement of the Qualification Thermal Test campaign – 14
Dec 2006. . 104
Figure 9-26: Stainless Steel HP Performance curves . 105
Figure 9-27: Stainless Steel HP Performance curves (cont.) . 105
Figure 9-28: Axial Grooved HP profiles . 106
Figure 9-29: Axial Grooved HP profiles drawings . 107
Figure 9-30: Dependence of AGHP Heat Transfer Capacity on Working Fluid
(Ammonia) . 108
Figure 9-31: Influence of tilt angle on AGHP maximum Heat Transfer Capacity at 20°C . 108
Figure 9-32: Thermal performance of Arterial HP with different working fluids . 109
Figure 9-33: Experimental data for Arterial HP with ammonia . 109
Figure 9-34: Arterial HP profile schematics . 110
Figure 9-35: Arterial HP typical configurations . 110
Figure 9-36: Arterial HP for rotator application. Length 2400 mm. Power 150 W. . 111
Figure 9-37: 0g guaranteed heat transport capability for ThalesAlenia Space Heat
Pipes . 112
Figure 9-38: Mono-core heat pipe profile . 113
Figure 9-39: Dual-core heat pipe profiles . 114
Figure 9-40: Minimal dimensions of straight parts for Ø 12.2 bent heat pipe . 115
Figure 10-1: Operating temperature range for cryogenic working fluids. Data from
ECSS-E-HB-31-01 Part 14, Table 8-1, clause 8.1.1. For fluorine: melting
point, T = 53,5 K, critical point, T = 144 K. . 117
Figure 10-2: Figure of Merit, N, as a function of temperature, T, for several cryogenic
working fluids. Compare with Figure 6-8, clause 6.3. Replotted after Chi &
Cygnarowicz (1970) [15]. . 118
Figure 10-3: Axial distribution of porosity, Φ, and cross section of a graded-porosity
slab wick. From Groll, Pittman & Eninger (1976) [30]. . 121
Figure 10-4: Maximum heat transport factor, (Q.l ), for a homogeneous wick heat pipe
eff
as a function of inner diameter, D, for different gravity levels. a) Working
i
fluid is Nitrogen at 77 K. b) Oxygen at 77 K. From Joy (1970) [38]. . 124
7
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Figure 10-5: Maximum heat transport factor, (Q.l ), for an axially grooved heat pipe
eff
and for a homogeneous wick heat pipe vs. inner diameter of the pipe, D , for
i
different gravity levels. Working fluid is Oxygen at 77 K. From Joy (1970)
[38]. . 125
Figure 10-6: Axial temperature drop, ∆T, for Oxygen heat pipes at 77 K vs. inner
diameter of the pipe, D. Also shown are data for an axially grooved heat
i
pipe and for aluminium rods of the same diameter. From Joy (1970) [38].
Calculation procedure is outlined in the text. . 126
Figure 10-7: Nodal points in the static transient model of a heat pipe. From Smirnov,
Barsookov & Mishchenko (1976) [89]. . 127
Figure 10-8: Schematic of the heat pipe considered by Chang & Colwell (1985) [13]. . 128
Figure 10-9: ERTS-C (Landsat III) cryogenic heat pipe experiment configuration. From
Brennan & Kroliczek (1975) [45]. . 130
Figure 10-10: Schematic of a blocking orifice thermal diode heat pipe. From Kosson,
Quadrini & Kirckpatrick (1974) [44] . 131
Figure 10-11: a) Axial temperature profiles during reverse mode tests of a cryogenic
heat pipe diode. No tilt. Tests performed in an insulated LN cooled
2
enclosure. At time 0 power (3 W) is removed from the evaporator, and the
reservoir heater is on. T is the ambient temperature within the enclosure.
o
b) Shut-down temperature response of evaporator and upstream end of
blocked transport section. From Quadrini & McCreight (1977) [66]. . 133
Figure 10-12: Axial temperature profiles during reverse mode tests. Tests performed as
in Figure 10-11a except 1 W heat load on the evaporator continuously fed
during the run. T is the ambient temperature within the enclosure. From
o
Quadrini & McCreight (1977) [66]. . 134
Figure 10-13: Cross section of Heat Pipe 2. From Murakami & Kaido (1980) [61]. All
the dimensions are in mm. . 135
Figure 10-14: Temperature, T, vs. heat transfer rate, Q, in Heat Pipe 3. T is the
1
-3
evaporator temperature, T and T are in the adiabatic clause 88 x 10 m
2 3
-3
and 78 x 10 m from the evaporator end. The sink temperature is T = 1,9
s
K. From Murakami (1982) [60]. .
...
SLOVENSKI STANDARD
kSIST-TP FprCEN/CLC/TR 17603-31-08:2021
01-maj-2021
Vesoljska tehnika - Priročnik za toplotno zasnovo - 8. del: Toplotne cevi
Space Engineering - Thermal design handbook - Part 8: Heat Pipes
Raumfahrttechnik - Handbuch für thermisches Design - Teil 8: Wärmerohre
Ingénierie spatiale - Manuel de conception thermique - Partie 8: Caloducs
Ta slovenski standard je istoveten z: FprCEN/CLC/TR 17603-31-08
ICS:
49.140 Vesoljski sistemi in operacije Space systems and
operations
kSIST-TP FprCEN/CLC/TR 17603-31- en,fr,de
08:2021
2003-01.Slovenski inštitut za standardizacijo. Razmnoževanje celote ali delov tega standarda ni dovoljeno.
---------------------- Page: 1 ----------------------
kSIST-TP FprCEN/CLC/TR 17603-31-08:2021
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kSIST-TP FprCEN/CLC/TR 17603-31-08:2021
TECHNICAL REPORT
FINAL DRAFT
FprCEN/CLC/TR 17603-
RAPPORT TECHNIQUE
31-08
TECHNISCHER BERICHT
February 2021
ICS 49.140
English version
Space Engineering - Thermal design handbook - Part 8:
Heat Pipes
Ingénierie spatiale - Manuel de conception thermique - Raumfahrttechnik - Handbuch für thermisches Design -
Partie 8: Caloducs Teil 8: Wärmerohre
This draft Technical Report is submitted to CEN members for Vote. It has been drawn up by the Technical Committee
CEN/CLC/JTC 5.
CEN and CENELEC members are the national standards bodies and national electrotechnical committees of Austria, Belgium,
Bulgaria, Croatia, Cyprus, Czech Republic, Denmark, Estonia, Finland, France, Germany, Greece, Hungary, Iceland, Ireland, Italy,
Latvia, Lithuania, Luxembourg, Malta, Netherlands, Norway, Poland, Portugal, Republic of North Macedonia, Romania, Serbia,
Slovakia, Slovenia, Spain, Sweden, Switzerland, Turkey and United Kingdom.
Recipients of this draft are invited to submit, with their comments, notification of any relevant patent rights of which they are
aware and to provide supporting documentation.
Warning : This document is not a Technical Report. It is distributed for review and comments. It is subject to change without
notice and shall not be referred to as a Technical Report.
CEN-CENELEC Management Centre:
Rue de la Science 23, B-1040 Brussels
© 2021 CEN/CENELEC All rights of exploitation in any form and by any means Ref. No. FprCEN/CLC/TR 17603-31-08:2021 E
reserved worldwide for CEN national Members and for
CENELEC Members.
---------------------- Page: 3 ----------------------
kSIST-TP FprCEN/CLC/TR 17603-31-08:2021
FprCEN/CLC/TR 17603-31-08:2021 (E)
Table of contents
European Foreword . 10
1 Scope . 11
2 References . 12
3 Terms, definitions and symbols . 13
3.1 Terms and definitions . 13
3.2 Symbols . 13
4 General introduction . 17
5 Heat pipe wicks . 19
5.1 General . 19
5.2 Basic properties . 20
5.2.1 Equilibrium capillary height . 20
5.2.2 Permeability . 20
5.2.3 Effective thermal conductivity of the wick . 20
5.3 Low resistance wicks . 22
6 Heat pipe working fluids . 28
6.1 General . 28
6.2 Empirical correlations . 29
6.3 Physical properties . 31
6.4 Compatibility with wicks . 47
7 Simple heat pipe . 48
7.1 General . 48
7.2 Operating limits . 48
7.2.1 Capillary heat transfer limit . 49
7.2.2 Sonic limit (choking) . 54
7.2.3 Entrainment limit . 56
7.2.4 Boiling limit . 56
7.3 Performance . 57
8 Variable conductance heat pipes . 70
2
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8.1 General . 70
8.2 Design considerations . 72
8.2.1 Diffusion of the working fluid . 72
8.2.2 Working fluid selection . 73
8.2.3 Reservoir sizing . 74
9 Existing System . 78
9.1 Eads Astrium . 78
9.2 Euro Heat Pipes . 91
9.2.1 Aluminium Heat Pipes . 91
9.2.2 STAINLESS STEEL HEAT PIPES. This part deals with the products
from Technical Data Sheet n° 1B: EHP Stainless Steel . 101
9.3 Iberespacio . 106
9.3.1 Axial Grooved Heat Pipes . 106
9.3.2 Arterial Heat Pipes . 109
9.4 Thales Alenia Space . 111
9.4.1 Technical Description . 111
9.4.2 External Geometries . 113
10 Cryogenic heat pipes . 116
10.1 General . 116
10.2 Working fluids . 116
10.3 Wicks . 118
10.3.1 Lab wicks . 120
10.3.2 Tunnel artery . 120
10.3.3 Graded-porosity wicks . 120
10.4 Operating limits . 121
10.4.1 Capillary heat transfer limit . 121
10.5 Transient operating characteristics . 127
10.5.1 Mathematical modelling of static transient . 127
10.5.2 Mathematical modelling of fluid dynamic transient. 128
10.6 Reduced gravity testing of cryogenic heat pipes . 129
10.7 Thermal diode cryogenic heat pipes . 131
10.7.2 Reversal requirements . 132
10.8 Superfluid heat pipes . 134
10.9 Existing systems . 138
Bibliography . 146
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Figures
1
Figure 5-1: Measured values of the inverse permeability, K , vs. mass flow rate per
unit area, m .> From Phillips & Hinderman (1969) [67]. . 27
1
Figure 5-2: Measured values of the inverse permeability, K , vs. mass flow rate per
unit area, m .> From Phillips & Hinderman (1969) [67]. . 27
Figure 6-1: Relevant physical properties of Ammonia as a function of temperature, T,
The labels correspond to experimental points. The expressions used to
calculate the tabulated values are given below. Calculated by the compiler. . 32
Figure 6-2: Relevant physical properties of Ethanol as a function of temperature, T, The
labels correspond to experimental points. The expressions used to
calculate the tabulated values are given below. Calculated by the compiler. . 34
Figure 6-3: Relevant physical properties of Freon 11 as a function of temperature, T,
The labels correspond to experimental points. The expressions used to
calculate the tabulated values are given below. Calculated by the compiler. . 36
Figure 6-4: Formulae Used for Calculating the Values of the Physical Properties. . 38
Figure 6-5: Relevant physical properties of Nitrogen as a function of temperature, T,
The labels correspond to experimental points. The expressions used to
calculate the tabulated values are given below. Calculated by the compiler. . 40
Figure 6-6: Relevant physical properties of Propane as a function of temperature, T,
The labels correspond to experimental points. The expressions used to
calculate the tabulated values are given below. Calculated by the compiler. . 42
Figure 6-7: Relevant physical properties of Water as a function of temperature, T, The
labels have been drawn to guide in the selection of the appropriate curve,
and do not correspond to experimental values. After Schmidt (1969) [82]. . 44
Figure 6-8: Figure of Merit, N, as a function of temperature, T, for several heat pipe
working fluids. For each curve, the range of temperature variation is
bounded between the largest and smallest operating pressures. Calculated
by the compiler. . 46
Figure 7-1: Sketch illustrating design variables in grooved heat pipes. From Frank et al.
(1967) [27], quoted by Winter & Barsch (1971) [96]. . 51
Figure 7-2: Relation between the dimensionless parameter 16/( / )F and the
v l
geometrical parameter, . From Frank et al. (1967) [27], quoted by Winter
& Barsch (1971) [96]. . 52
3
Figure 7-3: Optimum value of the dimensionless maximum heat transfer, Q /r , vs.
max w
the geometrical parameter, . From Frank et al. (1967) [27], quoted by
Winter & Barsch (1971) [96]. . 53
Figure 7-4: Graph for determining F. From Frank et al. (1967) [27], quoted by Winter &
Barsch (1971) [96]. . 53
Figure 7-5: Optimum value of the aspect ratio of the grooves, , vs. the geometrical
parameter, . From Frank et al. (1967) [27], quoted by Winter & Barsch
(1971) [96]. . 54
Figure 7-6: Maximum heat transfer, Q , based on sonic limit, vs. evaporator
max
temperature, T , for several values of the shear streets, , and of the
E
convective heat transfer, Q . Sodium heat pipe. A: = 0 and Q = 0; B:
conv conv
0 and Q 0; C: 0 and Q = 0; D: 0 and Q 0. In this case
conv conv conv
the heat pipe had an adiabatic length. In curves A, B, and C choking is
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reached at the evaporator, while in curve D choking is reached at the
adiabatic length end. From Levy (1972) [49]. . 55
Figure 7-7: Heat Transfer, Q , and Integral Heat Transport Factor, [Q.l ] , vs. wick
max eff max
thickness, , for several mesh sizes and two heat pipe diameters, D .
o
Circumferential screen wick. Solid lines: vapour laminar flow; dotted lines:
vapour turbulent flow. From Skrabek (1972) [88]. . 58
Figure 7-8: Heat Transfer, Q , and Integral Heat Transport Factor, [Q.l ] , vs. wick
max eff max
thickness, , for several mesh sizes and two heat pipe diameters, D .
o
Circumferential screen wick. Solid lines: vapour laminar flow; dotted lines:
vapour turbulent flow. From Skrabek (1972) [88]. . 59
Figure 7-9: Heat Transfer, Q , and Integral Heat Transport Factor, [Q.l ] , vs. wick
max eff max
thickness, , for several mesh sizes and two heat pipe diameters, D .
o
Circumferential screen wick. Solid lines: vapour laminar flow; dotted lines:
vapour turbulent flow. From Skrabek (1972) [88]. . 60
Figure 7-10: Heat Transfer, Q , and Integral Heat Transport Factor, [Q.l ] , vs. wick
max eff max
thickness, , for several mesh sizes and two heat pipe diameters, D .
o
Porous slab wick. Solid lines: vapour laminar flow; dotted lines: vapour
turbulent flow. From Skrabek (1972) [88]. . 61
Figure 7-11: Heat Transfer, Q , and Integral Heat Transport Factor, [Q.l ] , vs. wick
max eff max
thickness, , for several mesh sizes and two heat pipe diameters, D .
o
Porous slab wick. Solid lines: vapour laminar flow; dotted lines: vapour
turbulent flow. From Skrabek (1972) [88]. . 62
Figure 7-12: Heat Transfer, Q , and Integral Heat Transport Factor, [Q.l ] , vs. wick
max eff max
thickness, , for several mesh sizes and two heat pipe diameters, D .
o
Porous slab wick. Solid lines: vapour laminar flow; dotted lines: vapour
turbulent flow. From Skrabek (1972) [88]. . 63
Figure 7-13: Heat pipe conductance, C, vs. wick thickness, , for several wick
conductivities, k , and two heat pipe diameters, D . Circumferential screen
eff o
wick. From Skrabek (1972) [88]. . 64
Figure 7-14: Heat pipe conductance, C, vs. wick thickness, , for several wick
conductivities, k , and two heat pipe diameters, D . Circumferential screen
eff o
wick. From Skrabek (1972) [88]. . 65
Figure 7-15: Heat pipe conductance, C, vs. wick thickness, , for several wick
conductivities, k , and two heat pipe diameters, D . Circumferential screen
eff o
wick. From Skrabek (1972) [88]. . 66
Figure 7-16: Heat pipe conductance, C, vs. wick thickness, , for several values of the
heat transfer coefficient of the wick, h, and heat pipe diameters, D . Porous
o
slab wick. From Skrabek (1972) [88]. . 67
Figure 7-17: Heat pipe conductance, C, vs. wick thickness, , for several values of the
heat transfer coefficient of the wick, h, and heat pipe diameters, D . Porous
o
slab wick. From Skrabek (1972) [88]. . 68
Figure 7-18: Heat pipe conductance, C, vs. wick thickness, , for several values of the
heat transfer coefficient of the wick, h, and heat pipe diameters, D . Porous
o
slab wick. From Skrabek (1972) [88]. . 69
Figure 8-1: VCHP with cold reservoir. . 71
Figure 8-2: VCHP with hot reservoir. (a) Internal hot reservoir. (b) External hot
reservoir. . 72
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Figure 8-3: Vapor concentration at the reservoir, n(t), over its steady-state value, n(),
and control temperature range, T, as functions of time, t. From
Hinderman. Waters & Kaser (1972) [35]. . 73
Figure 8-4: Dimensionless pressure ratio, , vs. control temperature range, T T ,
r Emax Emin
for several working fluids. From Hinderman, Waters & Kaser (1972) [35]. . 74
Figure 8-5: Sketch of a variable conductance heat pipe. 1: Evaporator. 2: Adiabatic
Section. 3: Condenser. 4: Adiabatic Section. 5: Reservoir. . 75
Figure 8-6: Dimensionless reservoir to condenser volume ratio, V /V , vs. evaporator
R C
temperature variation, (T T ), for two different working fluids, and a
Emax Emin
given reservoir temperature variation, (T T ) = 28 K. From Edelstein
Rmax Rmin
& Hembach (1972) [23]. . 75
Figure 8-7: Dimensionless reservoir to condenser volume ratio, V /V , vs. reservoir
R C
temperature variation, (T T ), with fixed evaporator control
Rmax Rmin
temperature variation, (T T ) = 6 K. From Edelstein & Hembach
Emax Emin
(1972) [23]. . 76
Figure 8-8: Dimensionless reservoir to condenser volume ratio, V /V , vs. evaporator
R C
temperature variation, (T T ), for ammonia working fluid. From
Emax Emin
Edelstein & Hembach (1972) [23]. . 76
Figure 8-9: Dimensionless reservoir to condenser volume ratio, V /V , vs. evaporator
R C
temperature variation, (T T ). Solid lines: cold reservoir. Dashed
Emax Emin
lines: hot reservoir. (A) and (M) correspond to ammonia and methanol
respectively. T is the sink temperature; in one case the back of the radiator
s
is pained black (222 K < T < 254 K), and in the other it is aluminized (196 K
s
< T < 245 K). Evaporator temperature, T = (287 + (T T )/2) K. From
s E Emax Emin
Kirkpatrick & Marcus (1972) [42]. . 77
Figure 9-1: WR7 Heat Pipe Profile (Cryogenic Application) . 83
Figure 9-2: WR12 Heat Pipe Profile. 84
Figure 9-3: WR18 Heat Pipe Profile. 84
Figure 9-4: WR19 Heat Pipe Profile. 85
Figure 9-5: WR20 Heat Pipe Profile. 85
Figure 9-6: WR22 Heat Pipe Profile. 86
Figure 9-7: WR24 Heat Pipe Profile. 86
Figure 9-8: WR25 Heat Pipe Profile. 87
Figure 9-9: WR26 Heat Pipe Profile. 87
Figure 9-10: WR27 Heat Pipe Profile . 88
Figure 9-11: WR28 Heat Pipe Profile . 88
Figure 9-12: WR29 Heat Pipe Profile . 89
Figure 9-13: WR7 Heat Pipe used for SCIAMACHY on ENVISAT . 89
Figure 9-14: EADS ASTRIUM HP experience . 90
Figure 9-15: EHP: typical Aluminium extruded HP . 91
Figure 9-16: Heat transport capability – NH3 (Note: AG110 = size 11 mm in tens of
millimetres.) . 94
Figure 9-17: HP Profile Tolerances. 97
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Figure 9-18: HP Profile Tolerances (cont.). 98
Figure 9-19: HP Profile Tolerances (cont.). 99
Figure 9-20: ESA SMART 1 with HP . 100
Figure 9-21: ESA AEOLUS – ALADIN instrument with HP network . 100
Figure 9-22: Constant Conductance Heat Pipe . 101
Figure 9-23: Variable Conductance Heat Pipe . 101
Figure 9-24: Heat Pipe Profiles examples Table 9.2-3. Stainless Steel Heat Pipes
types. . 102
Figure 9-25: “Thank to 40 state-of-the art variable conductance heat pipes located in
the avionics bay the ATV is able to carry away the heat and release the
energy directly into space or, otherwise, to warm up other parts in a very
economic fashion” Astrium – ESA “Jules Verne goes hot and cold” –
Successful achievement of the Qualification Thermal Test campaign – 14
Dec 2006. . 104
Figure 9-26: Stainless Steel HP Performance curves . 105
Figure 9-27: Stainless Steel HP Performance curves (cont.) . 105
Figure 9-28: Axial Grooved HP profiles . 106
Figure 9-29: Axial Grooved HP profiles drawings . 107
Figure 9-30: Dependence of AGHP Heat Transfer Capacity on Working Fluid
(Ammonia) . 108
Figure 9-31: Influence of tilt angle on AGHP maximum Heat Transfer Capacity at 20°C . 108
Figure 9-32: Thermal performance of Arterial HP with different working fluids . 109
Figure 9-33: Experimental data for Arterial HP with ammonia . 109
Figure 9-34: Arterial HP profile schematics . 110
Figure 9-35: Arterial HP typical configurations . 110
Figure 9-36: Arterial HP for rotator application. Length 2400 mm. Power 150 W. . 111
Figure 9-37: 0g guaranteed heat transport capability for ThalesAlenia Space Heat
Pipes . 112
Figure 9-38: Mono-core heat pipe profile . 113
Figure 9-39: Dual-core heat pipe profiles . 114
Figure 9-40: Minimal dimensions of straight parts for Ø 12.2 bent heat pipe . 115
Figure 10-1: Operating temperature range for cryogenic working fluids. Data from
ECSS-E-HB-31-01 Part 14, Table 8-1, clause 8.1.1. For fluorine: melting
point, T = 53,5 K, critical point, T = 144 K. . 117
Figure 10-2: Figure of Merit, N, as a function of temperature, T, for several cryogenic
working fluids. Compare with Figure 6-8, clause 6.3. Replotted after Chi &
Cygnarowicz (1970) [15]. . 118
Figure 10-3: Axial distribution of porosity, , and cross section of a graded-porosity
slab wick. From Groll, Pittman & Eninger (1976) [30]. . 121
Figure 10-4: Maximum heat transport factor, (Q.l ), for a homogeneous wick heat pipe
eff
as a function of inner diameter, D, for different gravity levels. a) Working
i
fluid is Nitrogen at 77 K. b) Oxygen at 77 K. From Joy (1970) [38]. . 124
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Figure 10-5: Maximum heat transport factor, (Q.l ), for an axially grooved heat pipe
eff
and for a homogeneous wick heat pipe vs. inner diameter of the pipe, D, for
i
different gravity levels. Working fluid is Oxygen at 77 K. From Joy (1970)
[38]. . 125
Figure 10-6: Axial temperature drop, T, for Oxygen heat pipes at 77 K vs. inner
diameter of the pipe, D. Also shown are data for an axially grooved heat
i
pipe and for aluminium rods of the same diameter. From Joy (1970) [38].
Calculation procedure is outlined in the text. . 126
Figure 10-7: Nodal points in the static transient model of a heat pipe. From Smirnov,
Barsookov & Mishchenko (1976) [89]. . 127
Figure 10-8: Schematic of the heat pipe considered by Chang & Colwell (1985) [13]. . 128
Figure 10-9: ERTS-C (Landsat III) cryogenic heat pipe experiment configuration. From
Brennan & Kroliczek (1975) [45]. . 130
Figure 10-10: Schematic of a blocking orifice thermal diode heat pipe. From Kosson,
Quadrini & Kirckpatrick (1974) [44] . 131
Figure 10-11: a) Axial temperature profiles during reverse mode tests of a cryogenic
heat pipe diode. No tilt. Tests performed in an insulated LN cooled
2
enclosure. At time 0 power (3 W) is removed from the evaporator, and the
reservoir heater is on. T is the ambient temperature within the enclosure.
o
b) Shut-down temperature response of evaporator and upstream end of
blocked transport section. From Quadrini & McCreight (1977) [66]. . 133
Figure 10-12: Axial temperature profiles during reverse mode tests. Tests performed as
in Figure 10-11a except 1 W heat load on the evaporator continuously fed
during the run. T is the ambient temperature within the enclosure. From
o
Quadrini & McCreight (1977) [66]. . 134
Figure 10-13: Cross sectio
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