EP4109012A1 - Mechanisch gepumpter zweiphasiger fluidkreislauf mit vorrichtung zur passiven steuerung des durchsatzes - Google Patents

Mechanisch gepumpter zweiphasiger fluidkreislauf mit vorrichtung zur passiven steuerung des durchsatzes Download PDF

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Publication number
EP4109012A1
EP4109012A1 EP22180768.8A EP22180768A EP4109012A1 EP 4109012 A1 EP4109012 A1 EP 4109012A1 EP 22180768 A EP22180768 A EP 22180768A EP 4109012 A1 EP4109012 A1 EP 4109012A1
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EP
European Patent Office
Prior art keywords
fluid
condenser
evaporator
inlet
heat transfer
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP22180768.8A
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English (en)
French (fr)
Inventor
Anthony DELMAS
Remi DOMPNIER
Giacomo SACCONE
Alain Chaix
Julien Hugon
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Thales SA
Original Assignee
Thales SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Thales SA filed Critical Thales SA
Publication of EP4109012A1 publication Critical patent/EP4109012A1/de
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B23/00—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect
    • F25B23/006—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect boiling cooling systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/09—Improving heat transfers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/007—Condensers

Definitions

  • the present invention is in the field of thermal control of sets of dissipative equipment.
  • the invention relates to a device and method for passive control of the flow rate of a fluid in a two-phase fluid loop with mechanical pumping.
  • This mechanically pumped fluid loop ensures the circulation of the fluid either by means of a fluid circulation device which can be a pump or a compressor.
  • the invention is described in the field of spacecraft of the satellite type but it applies to any two-phase fluid loop system with mechanical pumping. For the sake of synthesis, only the fluid loop application using a pump for circulating the fluid is described, but it applies similarly to the case with a compressor.
  • a mechanically pumped two-phase fluid loop comprises a closed circuit in which a heat transfer fluid circulates, an evaporator, through which the fluid circulates in liquid form at the inlet of the evaporator, the evaporator being configured to transform the fluid into liquid into fluid in partially gaseous form (totally gaseous in the case of circulation by a compressor), a condenser, through which the fluid in partially gaseous form circulates at the inlet of the condenser, the condenser being configured to transform the phase gaseous fluid into fluid in liquid form, a pump, arranged between the outlet of the condenser and the inlet of the evaporator, intended to move the fluid in the closed circuit from the evaporator to the condenser in partially gaseous form and from the condenser to the evaporator in liquid form, a fluid reservoir connected to the closed circuit, intended to compensate for the variations fluid volume ations in the closed circuit.
  • the two-phase fluid loop involves thermo-hydraulics at the level of the condensers several radiators of the satellite (that is to say the external faces of the satellite whose radiative environments are not symmetrical.
  • these are the faces traditionally called East/West or North/South/East/West) for the rejection of power dissipated at the satellite equipment levels.
  • the East and West faces of the satellite are subjected to very significant daily variations in external heat fluxes due to exposure to the sun. To maximize the power rejection, it is therefore necessary to adjust the flow according to the external environment of each wall.
  • the fluid loop In order to reject the harvested power at the dissipative equipment, the fluid loop must interface with the walls/radiators of the spacecraft. To maximize the effective radiative surface of the spacecraft, the East/West walls of the spacecraft are used and interested thermo-hydraulically by the two-phase fluid loop. In order to maximize the rejection of these walls, a system making it possible to adjust the flow to the external environment of the walls must be put in place. If none regulation system is put in place, the flow affecting each wall is similar and significantly de-optimizes the subsystem.
  • the invention aims to alleviate all or part of the problems cited above by proposing passive control of the flow rate of a diphasic fluid loop with mechanical pumping, in particular for a space application making it possible to couple several radiators around the supporting structure (satellite box ) and to passively optimize the flow requirement (and therefore the rejection) at the slightest environmental difference between the walls. Furthermore, the invention makes it possible to optimize the two-phase and single-phase exchange coefficient by maximizing the flow velocity for a given flow rate.
  • the invention allows a passive coupling of the various walls of the satellite via the two-phase loop: the design of the condenser generates a variable hydraulic resistance according to the capacity of the wall in question to reject the heat. Moreover, the diphasic and monophasic exchange coefficients are maximized with the proposed design.
  • the passage channel of the condenser can comprise a passage section lower than the inlet section of the condenser.
  • the condenser comprises a flow adjustment device comprising a central three-dimensional piece around which extends a thread defining the flow path in the form of a helical spiral.
  • the condenser may include a porous medium through which fluid flows.
  • FIG.1 The figure 1 schematically represents a passive control device for distributing the flow of fluid to the condensers in a two-phase fluid loop with mechanical pumping according to the invention
  • FIG.2 The figure 2 schematically represents a preferred embodiment of a passive control device for distributing the flow of fluid to the condensers in a diphasic fluid loop with mechanical pumping according to the invention.
  • the figure 1 schematically represents a device 10 for controlling the flow of a heat transfer fluid to the condensers in a mechanically pumped two-phase fluid loop according to the invention.
  • the two-phase fluid loop with mechanical pumping comprises a closed circuit 11 in which a heat transfer fluid 20 circulates.
  • the loop comprises an evaporator 12 comprising an inlet 13 and an outlet 14, through which the fluid flows from the inlet 13 of the evaporator 12 in liquid form 20-liq to the outlet 14 of the evaporator 12, the evaporator 12 being configured to transform the fluid into liquid form 20 -liq in fluid in partially gaseous form 20-g.
  • the evaporator is configured to recover, to capture a certain quantity of thermal energy external to the loop, in particular coming from the dissipative equipment on the satellite.
  • the loop comprises on at least two radiators of the satellite a condenser 15 comprising an inlet 16 and an outlet 17 connected to the inlet 16 by a passage channel 35, through which the fluid in partially gaseous form 20-g circulates from the inlet 16 of condenser 15 to outlet 17 of condenser 15, condenser 15 being configured to transform the fluid in partially gaseous form 20-g into fluid in liquid form 20-liq.
  • the loop comprises at least two condensers 15 in parallel, each associated with a satellite radiator.
  • the condenser is configured to restore a certain amount of thermal energy to the outside of the loop, for example to the cold space around the satellite.
  • the transformation of the fluid into liquid form in the condenser can be partial or total. Nevertheless, the joining of the different branches of condensers ensures a 20-liq fluid in liquid form in the condenser, and leaves the joining (38) of the condensers in 20-liq liquid fluid form.
  • the loop comprises a pump 18, arranged between the outlet 17 of the condenser 15 and the inlet 13 of the evaporator 12, intended to move the fluid in the closed circuit 11 from the evaporator 12 to the condenser 15 in partially 20-g gas, and from the meeting (point 38) of the condensers 15 to the evaporator 12 in liquid form 20-liq.
  • the loop comprises a fluid reservoir 19 connected to the closed circuit 11, intended to compensate for the variations in volume of fluid in the closed circuit 11, in connection with the quantity of vapor, due to evaporation, present in the closed circuit.
  • a pump 18 generally applies to a fluid circulation device 18, which can also be a compressor, for example.
  • the passage channel 35 of the condenser 15 extends over a first length 31 and it comprises a flow path 32 for the fluid in partially gaseous form 20-g of length greater than the first length 31.
  • the path flow path is to be understood as the path that the fluid travels through the condenser 15 in the passage channel 35.
  • the length of the flow path is the linear evolute, that is to say the distance traveled by the fluid in the passage channel.
  • the flow path 32 is represented very schematically on the figure 1 for the purpose of illustrating the principle of the invention in a non-limiting manner.
  • the device of the invention allows an increase in the length of condensation. This results in a high and adaptive hydraulic resistance obtained thanks to the particular shape of the fluid passage channel in the condenser, as will appear more clearly below.
  • the picture 2 schematically represents a preferred embodiment of a passive control device for distributing the flow rate of a fluid to the condensers in a two-phase fluid loop with mechanical pumping according to the invention. More specifically, the picture 2 represents the passage channel 35 of the condenser. The flow path 32 is symbolized by the arrows representing the path of the fluid in the passage channel 35. The length of this path is greater than the length 31 of the passage channel.
  • passage channel 35 of condenser 15 comprises a passage section 33 lower than inlet section 34 16 of condenser 15.
  • the particular shape of the passage channel of the condenser according to the invention generates high hydraulic resistance in proportion to its capacity to condense.
  • this reduced passage section 33 generates a high flow rate for a given flow rate and makes it possible to maximize the two-phase and single-phase exchange coefficients of the fluid.
  • the increase in length of the flow path relative to the length of the passage channel can be achieved in a number of ways, one of them being presented below.
  • Another variant can be constituted by one or more channels close to the walls of the condenser, of section smaller than the inlet section of the condenser.
  • the condenser 15 comprises a flow adjustment device comprising a central three-dimensional part, preferably but not limited to a solid cylinder, (shown in the figure 2 ) around which extends a thread defining the flow path 32 in the form of a helical spiral.
  • the thread pitch 36 and the passage section 33 can be determined by a person skilled in the art according, in particular, to the fluid used, the pressure lifting capacity of the pump 18, in order to create the hydraulic resistance.
  • the flow adjustment device by means of the three-dimensional hydraulic part, by creating a hydraulic resistance, then makes it possible to optimize the management of the flow in the condenser 15.
  • the thread of the central three-dimensional part in the form of a helical spiral is defined according to a spiral section varying between 2 and 4 mm 2 and preferably 3 mm 2 and comprises a thread pitch 36 of between 1 mm and 15 mm .
  • the hydraulic resistance thus created makes it possible, depending on the efficiency of the condensation and therefore of the thermal environment of the condenser 15, to create a more or less strong flow asymmetry between the condensers in order to maximize the mass flow in the condensers whose thermal environment is favorable.
  • the table shows that the presence of the flow path 32 in the form of a spiral makes it possible on the one hand to increase the rejection, that is to say the quantity of energy rejected by the condensers 15 or quantity of Watts rejected, in the case of a symmetrical environment (+ ⁇ 33%) and on the other hand to accentuate the gain brought to the rejection via a redistribution of the flow in an asymmetrical configuration (+60%), that is- that is to say according to a configuration in which the presence of different operating conditions or not between the two condensers such as the interface temperature.
  • the flow adjustment device thus has the advantage, by means of the three-dimensional part, of being capable of managing the flow passing through the flow path 32 by generating a variable hydraulic resistance as a function of the parameters structures of the central three-dimensional part and a function of the rejection capacity of the condenser (and therefore of its operating conditions such as the interface temperature), namely the thread pitch 36 and the passage section 33 while increasing the surface of heat exchange also making it possible to improve the heat exchange specific to the condenser 15.
  • the presence of the central three-dimensional piece makes it possible to accentuate the mass flow towards the most favorable thermal environment.
  • the condenser 15 comprises a porous medium through which the fluid flows.
  • the local velocity field of the fluid is heterogeneous. Due to the porosity of the porous medium, the length of the flow path 32 is increased and the passage section 33 is smaller than the inlet section 34 .
  • the porous medium can be, by way of examples and without limitation, obtained by a sintered metal manufacturing process during which metal particles are compacted and the level of porosity is adjusted by changing the size of the metal particles. Or the porous medium can be obtained by additive manufacturing.
  • the device of the invention consists in significantly reducing the passage section while increasing the hydraulic condensation length. This can result, for example, in a helical flow of the fluid. This principle makes it possible to achieve, for a small footprint, both high hydraulic resistance and an exchange coefficient as well as a high exchange surface.
  • the invention is based, for a given length of condenser, on a significant increase in the hydraulic resistance at the level of the condenser in comparison with the hydraulic resistance in the tubing (reference 37 on the figure 1 ) distributing the flow to the condenser of each wall.
  • the hydraulic resistance depends on the amount of vapor of the partially gaseous fluid that enters the condenser and whether or not it decreases throughout the flow path 32. This results in a dynamic and passive adjustment of the fluid flow carrying the heat dissipation equipment according to the environment of each wall of the satellite.
  • the proposed solution allows the use of a single two-phase loop with effective coupling of the walls by adjusting the flow rates directed towards each of them.
  • This adjustment of the flow rates is achieved passively, by the hydraulic design of the condensers.
  • the design of the condensers is made in such a way as to generate a significant hydraulic resistance when there is presence of steam in the flow and proportional to the quantity of the latter.
  • the significant hydraulic resistance implies a reduction in the flow in this wall, naturally directing the flow towards a wall where the condensation is more effective (wall with a more favorable radiative environment).
  • the solution makes it possible to passively optimize the flow rate requirement (and therefore the rejection) at the slightest environmental difference between the walls. This is done passively without any active control (that is to say without additional adjustment or without intervention of a control law, or even measurement of physical quantity) of the flow rate or of the temperature at the level of the wall(s).
  • the design of the condensers generating high hydraulic resistance in proportion to its capacity to condense allows also to maximize the two-phase and single-phase exchange coefficients of the fluid
  • the invention consists in significantly reducing the passage section while increasing the hydraulic condensation length. This can result, for example, in a helical flow of the fluid. This principle makes it possible to achieve, for a small footprint, a high hydraulic resistance, and a high exchange coefficient as well as a high exchange surface.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Flow Control (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
EP22180768.8A 2021-06-24 2022-06-23 Mechanisch gepumpter zweiphasiger fluidkreislauf mit vorrichtung zur passiven steuerung des durchsatzes Pending EP4109012A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR2106763A FR3124585B1 (fr) 2021-06-24 2021-06-24 Dispositif et procédé de contrôle passif du débit d’un fluide dans une boucle fluide diphasique à pompage mécanique

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EP4109012A1 true EP4109012A1 (de) 2022-12-28

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EP22180768.8A Pending EP4109012A1 (de) 2021-06-24 2022-06-23 Mechanisch gepumpter zweiphasiger fluidkreislauf mit vorrichtung zur passiven steuerung des durchsatzes

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FR (1) FR3124585B1 (de)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015116661A1 (en) * 2014-01-28 2015-08-06 Phononic Devices, Inc. Mechanism for mitigating high heat-flux conditions in a thermosiphon evaporator or condenser
CN111442575A (zh) * 2020-03-17 2020-07-24 中国移动通信集团设计院有限公司 可调式制冷装置及制冷调节方法
CN211204518U (zh) * 2019-11-29 2020-08-07 刘慎念 一种制冷设备用壳管冷凝器

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Publication number Priority date Publication date Assignee Title
CN1065953C (zh) * 1995-12-04 2001-05-16 刘玉海 新型热管装置
WO2010057919A1 (de) * 2008-11-18 2010-05-27 Highterm Research Gmbh Vorrichtung zur erzeugung von brennbarem produktgas aus kohlenstoffhaltigen einsatzstoffen
WO2014147838A1 (ja) * 2013-03-22 2014-09-25 富士通株式会社 熱交換器、冷却システム、及び、電子機器
ES2625404T3 (es) * 2014-08-14 2017-07-19 Ibérica Del Espacio, S.A. Bucle de transferencia de calor de dos fases de control avanzado
EP3113590B1 (de) * 2015-06-30 2020-11-18 ABB Schweiz AG Kühlvorrichtung

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015116661A1 (en) * 2014-01-28 2015-08-06 Phononic Devices, Inc. Mechanism for mitigating high heat-flux conditions in a thermosiphon evaporator or condenser
CN211204518U (zh) * 2019-11-29 2020-08-07 刘慎念 一种制冷设备用壳管冷凝器
CN111442575A (zh) * 2020-03-17 2020-07-24 中国移动通信集团设计院有限公司 可调式制冷装置及制冷调节方法

Non-Patent Citations (2)

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VASILIEV LEONARD L ET AL: "Thermosyphons with innovative technologies", APPLIED THERMAL ENGINEERING, PERGAMON, OXFORD, GB, vol. 111, 12 August 2016 (2016-08-12), pages 1647 - 1654, XP029845069, ISSN: 1359-4311, DOI: 10.1016/J.APPLTHERMALENG.2016.07.101 *

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FR3124585B1 (fr) 2023-11-10
FR3124585A1 (fr) 2022-12-30

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