EP2940416B1 - Dispositif caloduc en boucle pour transfert et régulation thermique - Google Patents

Dispositif caloduc en boucle pour transfert et régulation thermique Download PDF

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EP2940416B1
EP2940416B1 EP12832734.3A EP12832734A EP2940416B1 EP 2940416 B1 EP2940416 B1 EP 2940416B1 EP 12832734 A EP12832734 A EP 12832734A EP 2940416 B1 EP2940416 B1 EP 2940416B1
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Prior art keywords
compensation chamber
liquid
evaporator
stabilization
vapour
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German (de)
English (en)
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EP2940416A1 (fr
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Alejandro TORRES SEPÚLVEDA
Donatas Mishkinis
Andrei Kulakov
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Iberica del Espacio SA
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Iberica del Espacio SA
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    • 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
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/04—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure
    • F28D15/043—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure forming loops, e.g. capillary pumped loops
    • 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
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/04—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure

Definitions

  • the present invention relates to a heat transfer and thermal control device, in particular for use on a spacecraft, and more particularly the invention is directed to a heat transfer and thermal control device with two-phase capillary driven loops.
  • Spacecraft thermal control relies on the global spacecraft thermal balance: the heat loads must be rejected to deep space that works as a thermal sink. Since no matter links this sink and the spacecraft, this rejection is made by thermal radiation through dedicated radiators installed on the satellite external surfaces.
  • Spacecraft thermal loads come from the internal spacecraft equipment dissipation and, externally, from the sun and the earth or from the celestial bodies around which the spacecraft orbits.
  • the thermal systems used in spacecrafts must therefore be able to control equipment which operates at a specified range of temperatures and also discontinuously.
  • thermal devices for controlling thermal loads in spacecraft are two phase heat transfer loops which are also known in engineering practice as capillary driven and mechanically pumped loops or heat loops.
  • the purpose of these devices in a spacecraft is to transfer heat between a heat source (for instance, an electronic element) and a heat sink (typically, the space).
  • heat is transferred through an evaporation-condensation cycle of a working fluid kept inside a hermetically sealed container.
  • Capillary driven loops have a special porous structure, called capillary pump or wick, serving for working fluid continuous circulation in the system.
  • the wick is always located in the evaporator of the capillary driven loop.
  • the evaporator is attached to a heat source.
  • capillary driven loop technology has found a wide application for thermal control systems in many spacecraft applications, that usually use loops with a single evaporator.
  • many applications require thermal control of large thermal contact surface payloads or multiple remotely located heat sources.
  • LHPs loop heat pipes
  • CPLs capillary pumped loops
  • hybrid two-phase heat loops intend to create thermal control systems having the following characteristics: optimized functional layout, scalability, expandability, effective heat loads sharing, flexibility in components locations, thermal coupling between separate radiators and minimized mass and volume.
  • the LHP technology was initially invented in the Soviet Union, and this technology of a heat transfer apparatus is known as per US 4515209 , for example.
  • the first LHP systems were dedicated to terrestrial applications. Later, a capillary link (secondary wick) between the evaporator and the compensation chamber was introduced to provide liquid supply from the compensation chamber to the evaporator primary wick in zero gravity (0-g) conditions.
  • Every evaporator in the typical LHP system has its own compensation chamber, which can be directly connected to the compensation chambers of other evaporators or can have no direct connection with the compensation chambers of other evaporators in the system.
  • evaporators are rigidly connected with each other and are at a relatively close distance from each other.
  • each evaporator comprises a compensation chamber.
  • the compensation chamber volume increases rapidly when the number of evaporators increases. This leads to a limitation on the number of evaporators that can be used in these systems.
  • the key components for the LHP temperature control are the compensation chambers.
  • the LHP can operate at the desired temperature in most of the cases, as the LHP responds very well to rapid changes of heat load, sink temperature and set point temperature.
  • only one of the compensation chambers has a vapour-liquid two-phase condition during the operation regardless of how many are under temperature control.
  • Test results showed that when one of the evaporators has a very low heat load, a sudden vapour generation on the inner surface of the capillary pump was observed, stridently increasing the parasitic heat leak to the compensation chamber which results in a higher operational temperature of the loop. This causes a hysteresis control problem for the loop that is hard to predict or prevent. Also, it was found that situations when the liquid distributes itself among the compensation chambers (trying to occupy the lowest pressure spots) can lead to unstable operation of the system. Furthermore, a problem of controllability for multi-evaporator LHP systems arises when the amount of evaporators and compensation chambers increases.
  • CPL capillary driven loop
  • evaporators typically comprising one or more evaporators, one or more condensers, transport lines, one remote compensation chamber and a sub cooler.
  • Location of compensation chamber is the main distinguishing feature between CPL and LHP designs.
  • LHP compensation chamber(s) is always directly attached to evaporator(s) but CPL has one remote compensation chamber (also known as liquid reservoir), separated from evaporator(s) by small diameter (2-5 mm) connecting tube(s).
  • liquid from the condenser and from the remote compensation chamber flows through the sub cooler before reaching the evaporators.
  • the CPL comprising a remote reservoir loses ability for self-start up without special preconditioning.
  • vapour parasitic heat leak is a significant problem of reliable operability of the system.
  • the growing of a vapour bubble on the inner surface of the capillary pump leads to the pump dry out and, finally, to the failure of CPL operation.
  • the bubble In case of LHP, the bubble usually migrates into the compensation chamber (as soon as it is closely attached to the evaporator) and condenses in sub cooled liquid which is always presented in the LHP compensation chamber.
  • the two-port evaporator (one liquid inlet and one vapour exit) initially used in CPLs generally experienced dry-out due to the appearance of vapour in the liquid core during start-up and transient regimes.
  • a three-port capillary evaporator was introduced in the system connecting the remote reservoir line to the liquid core of the evaporator. This configuration allows vapour to expand along the evaporator core and to migrate into the remote reservoir, instead of accumulating in the evaporator core and interfering with liquid returning from the condenser.
  • three-port capillary pumps were used as starter pumps, and then like the main functional evaporator design.
  • a capillary device known as a capillary isolator, was introduced, located upstream of the evaporator inlet.
  • Back pressure regulators were also installed in many multiple evaporator CPLs to assist start up.
  • These capillary devices located in the vapour transport line, redirect vapour initially generated at one evaporator to other inoperative (without heat load) evaporators. This action forces liquid from the vapour lines and improves the chances for a successful start up for all evaporators in the system: it is also helping to promote heat load sharing among evaporators, for instance, when an inoperative evaporator acts as a condenser.
  • CPLs should be designed to be tolerant to non-condensable gases in one way or another.
  • One of the possible solutions is to implement special traps to collect the bubbles.
  • the traps are usually used for systems with parallel condensers and are placed at the condenser exit where they can also serve as capillary flow regulators (if the trap utilizes a capillary structure to separate gas from liquid). The capillary structure helps to prevent vapour from leaving the condenser. If one of the condensers becomes fully utilized, then this trap can serve to redirect the flow to the other condenser(s).
  • Another solution is to have several parallel evaporators connected to the same compensation chamber, located at the evaporating part of the loop, and including special long capillary links between the evaporators and the compensation chamber.
  • This system is known as Free Location LHP, as shown for example in document US 5944092 or Russian Patent 2120592 .
  • This system was successfully tested on the ground with a favourable gravitational bias of the evaporators relative to the compensation chamber, making it easy for the capillary links to distribute the fluid to each evaporator.
  • Orientation constraint in gravity field is due to limits imposed by the capillary link.
  • the capillary link connecting the evaporators to the compensation chamber limits the separation distance between the evaporators and the compensation chamber. This limitation is similar to the existing in conventional heat pipes.
  • the capillary link supplies all amount of liquid that is needed for the evaporator, which leads to significant limitations for rates of change of heat source power or/and heat sink temperature.
  • Other disadvantage of such approach is the low thermal conductance of evaporators due to the permanent presence of vapour phase in the evaporator core.
  • the main loop is basically a traditional CPL with same as for CPL configuration and operational principles, whose function is to transport the waste heat and reject it to a heat sink via the primary condenser.
  • the auxiliary loop is used to remove vapour bubbles from the core of the CPL evaporators and move them to the compensation chamber.
  • the auxiliary loop contains only one LHP-type evaporator with the attached large compensation chamber.
  • the chamber is only one and it is common for all evaporators: the CPL evaporators in the main loop and the LHP evaporator in the auxiliary loop.
  • the auxiliary loop is also used to ease the start-up process. In this manner, the auxiliary loop functionally replaces the secondary wick of a conventional LHP.
  • the feasibility of this design was however only achieved when the evaporators were connected in series. This means that liquid consequently goes through the evaporators: flow leaving the first evaporator enters the second one, etc.
  • the multi-evaporator hybrid LHP included three evaporators, one of which was a standard LHP evaporator directly attached to the common system's compensation chamber, and two traditional three-port CPL evaporators. Tests indicated that the system was not very reliable during power cycling. The sensitivity to power cycle was attributed to the expansion of vapour bubbles in the evaporator core. Heat conduction through the wall of the evaporator capillary pump made it relatively easy to nucleate vapour in the evaporator core. In case of steady state operation, these bubbles were swept from the core of functional evaporators by forward flow of the liquid to the capillary pump.
  • the internal design of the evaporators was modified to include a special phase separation wick, designed to provide better control of the two phases vapour/liquid distribution in the core of the pumps.
  • the design modifications were intended to extend the phase control provided by the secondary wick in the traditional LHP evaporator to the CPL evaporators.
  • the operation was verified in relatively limited conditions: mostly in horizontal orientation, evaporators were located close to each other, and therefore with similar hydraulic resistance of lines. Therefore, such configuration was not representative of the conditions of potential spacecraft thermal control application when evaporators and remote reservoir are spatially separated, and the rate of evaporators response on variations of the input power and heat sink conditions depend on the length of the lines connecting these elements. Therefore, the ability for temperature control was not properly verified.
  • hybrid cooling loop technology As those shown for example in documents US6990816 and US6948556 , which combine the active liquid pumping with the passive capillary liquid management in the wick structure of the evaporator and its liquid/vapour separation.
  • the hybrid cooling loop consists of an evaporator, a condenser, a liquid compensation chamber and a pump as the simplest design. Because of the active amplificatory pumping system, the hybrid loop system could manage different multiple evaporator designs.
  • the necessity of the supplementary loop circulation means can be considered as a drawback because of the active character of critical design components which reduces the reliability and life time of the system.
  • LHP is a LHP with two evaporators: main (functional) and secondary (auxiliary) evaporators, as per document US6810946 B2 , for example, incorporating a secondary evaporator to the conventional LHP design.
  • the secondary evaporator is located in a cold-biased environment to ensure that its capillary pump is always primed. Electrical heaters are attached to this evaporator to provide the necessary thermal power for its functioning. With the secondary pump operating, it actively removes the vapour that is accumulated in the compensation chamber by the parasitic heat leaks to the compensation chamber of the main evaporator and to the liquid line.
  • This design considers only a single main evaporator LHP.
  • the main drawback of this approach is the existence of the additional evaporator and its active character. In fact, this solution is needed only for a LHP with not properly designed secondary pump.
  • an evaporator with attached compensation chamber was proposed to use in a capillary driven loop, known for example per documents US7061446 , US7268744 or US7841 392 .
  • the undivided large capillary wick is used in the evaporator portion and in the compensation chamber.
  • the wick has greater transverse size in the compensation chamber than in the evaporator portion. There are no means to guarantee vapour tolerance of the evaporators.
  • the present invention is therefore oriented towards these needs.
  • the present invention therefore provides a heat transfer and thermal control system, in particular, a two-phase capillary driven LHP system.
  • An object of the invention is to provide a two-phase capillary driven LHP system having reliable operation at a wide range of operation conditions, providing at the same time vapour parasitic heat leak tolerance means for the evaporator and design flexibility by implementation of remote compensation chamber.
  • Another object of the present invention is to provide a two-phase capillary driven LHP system that can be expanded, that is, that can vary the number of its evaporators and/or its condensers.
  • the system of the invention comprises at least one evaporator, comprising a thermal stabilization-compensation chamber attached to it, at least one condenser, liquid and vapour lines, and a single remote compensation chamber, the thermal stabilization-compensation chamber comprising two-phase and hydro accumulator reservoirs.
  • the remote compensation chamber is hydraulically connected with the two-phase and hydro accumulator reservoirs of the thermal stabilization-compensation chamber.
  • the evaporator comprises a primary capillary pump which serves to absorb heat from the equipment, which has to be cooled, and to provide fluid heat continuous circulation between the evaporator, which is connected to the heat source, and the condenser, which is connected to the heat sink.
  • a secondary capillary pump is located inside the primary wick and inside of the thermal stabilization-compensation chamber and serves to supply the primary wick with liquid, and to provide fluid/heat intermittent circulation in transient regimes of operation of the system, between the inner part of the primary wick and the thermally controlled remote compensation chamber.
  • the thermal stabilization-compensation chamber serves to remove internal heat leak through a primary capillary pump by convection and condensation on the heat exchanger surface, which separates the two-phase and hydro accumulator reservoirs in the thermal stabilization-compensation chamber.
  • the present invention relates to a LHP device 1 comprising evaporator 2 containing a stabilization-compensation chamber 10, a combination of a primary capillary pump 30 and a secondary capillary pump 40, together with the corresponding plumbing components of the LHP device 1.
  • the primary capillary pump 30 serves for pumping fluid in the LHP device 1, the evaporation of which absorbs heat from the system that has to be cooled.
  • the secondary capillary pump 40 serves for supplying liquid to the primary capillary pump 30 and, together with the stabilization-compensation chamber 10 and the remote compensation chamber 20, for providing means to remove the vapour that is formed by internal parasitic heat leak of the at least one evaporator 2.
  • the present invention relates to a LHP device 1, which can be of the type single evaporator-condenser or multiple evaporators (and /or condensers) embodiments, as shown in Figures 1a , 1b , 1c .
  • the LHP device 1 of the invention comprises the following components:
  • FIGS. 1a , 1b and 1c show different schemes of an embodiment of the invention, showing a LHP device 1 having an arrangement of a remote compensation chamber 20 and evaporators 2, such that:
  • the three presented cases illustrate different variants of the remote compensation chamber 20 designs and different ways of layout in the LHP device 1.
  • the two-phase port of the remote compensation chamber 20 is always connected via line 12 with the stabilization-compensation chamber 10.
  • liquid port(s) of the remote compensation chamber 20 can be connected to stabilization-compensation chamber 10 in 3 different manners: directly, through liquid line 24 in series and in parallel.
  • the maximum quantity of fluid ports for remote compensation chamber 20 can be calculated by multiplying the number of evaporators by two and adding the number of condensers: in this case every evaporator has two individual lines 12 and 13 joining the stabilization-compensation chamber 10 with remote compensation chamber 20 and the remote compensation chamber 20 has additional liquid lines 24 connected with the condenser. Different combinations between maximum and minimum amount of ports are possible and it also provides flexibility in the system design.
  • the evaporator 2 comprises a small stabilization-compensation chamber 10 containing a secondary capillary pump 40, designed in such a way that it efficiently manages the vapour flow due to the parasitic heat leak 18 into the central core of the primary capillary pump 30.
  • the evaporator 2 design comprises a primary capillary pump 30 with external vapour-removing channels 19 outside the primary capillary pump 30, a secondary capillary pump 40 and a stabilization-compensation chamber 10 which comprises two chambers, a two-phase reservoir 5 and a liquid accumulator reservoir 6.
  • the primary capillary pump 30 also comprises internal vapour-removing channels 16 in the evaporator 2 core, to remove the vapour that forms due to the heat leak through the primary capillary pump 30. These vapour-removing channels 16 are connected with the small two-phase reservoir 5 close to the vapour-removing channels 16 outlets.
  • This two-phase reservoir 5 comprises a heat exchanger 15 (heat exchange surface) between the two-phase reservoir 5 and the liquid accumulator reservoir 6 of the stabilization-compensation chamber 10.
  • the liquid accumulator reservoir 6 and the two-phase reservoir 5 with the heat exchange surface 15 can be called as stabilization-compensation chamber 10.
  • the secondary capillary pump 40 is located inside of the primary capillary pump 30 and the stabilization-compensation chamber 10.
  • a porous wick 25 is installed inside of the remote compensation chamber 20 to manage fluid distribution in micro gravity conditions. The porous wick 25 prevents also vapour or non condensable gas bubbles penetration to the liquid line 13 as well as to the liquid accumulator reservoir 6.
  • Working fluid exists in three states inside of the LHP device 1 of the invention: vapour 29, liquid 14 and two-phase 31 states.
  • the heat evaporates working liquid. Vapour goes from the evaporator 2 to the condenser 27 through the vapour transport line 28, where it is condensed. After that, the working liquid returns to the stabilization-compensation chamber 10 and to the evaporator 2 through the liquid transport line 24, to be again evaporated in the primary capillary pump 30 of the evaporator 2.
  • the proposed LHP device 1 of the invention is controlled by the remote compensation chamber 20, as two-phases are always present in this chamber.
  • the link of the secondary capillary pump 40 and the stabilization-compensation chamber 10 provides the following functions:
  • the LHP device 1 can contain several evaporators 2 and several condensers 27 ( Figures 1 , 2 ). It is provided the opportunity that the evaporators 2 can collect the power from different heat sources, which could be located far one from the others thanks to the flexibility/adaptability provided by the LHP device 1 concept:
  • the main vapour / non-condensable gases tolerance means are located in maximum proximity to the evaporators 2. Moreover, not only the liquid flowing from the condenser 27 reaches the evaporator 2, but also liquid storage in the liquid accumulator reservoir 6 can be supplied to the evaporator 2 when required (mainly in transient regimes), providing additional reliability for the system. Besides, several additional redundant means can be considered: auxiliary LHP and / or thermal electrical cooler, for example.
  • Vapour generated by internal heat leak 18 in the evaporator core moving to the two-phase reservoir 5 is condensed by the heat exchanger 15 (nominal case operation). Therefore the two-phase line 12 connecting the two-phase reservoir 5 and the remote compensation chamber 20 is usually filled with liquid.
  • part of vapour 11 which could not be condensed completely on the heat exchange surface 15 in the stabilization-compensation chamber 10, can go to the remote compensation chamber 20 to condensate there.
  • the rest of heat leak (secondary leak penetrating to the liquid channel through the secondary capillary pump 40 will be compensated with condensation in the liquid accumulator reservoir 6 in the stabilization-compensation chamber 10 by sub-cooled liquid.
  • non-condensable gas is located in the compensation chamber 10 in proximity of the evaporator 2 and can penetrate to the evaporator core 16 and thus influence more significantly the evaporator 2 and therefore, the LHP operation.
  • non-condensable gas will move to the remote compensation chamber 20 and it will accumulate non-condensable gas preventing negative impact on LHP operation.
  • Such scheme guarantees vapour / non-condensable gases tolerance of the LHP device 1 and system reliability (especially in transient regimes) individually, passively and automatically for every evaporator 2 (of multiple evaporator option), without the necessity of having an active control.
  • This design is a simpler and more robust alternative to the active external "forced pumping" designs of known technical solutions in the prior art equipped with remote auxiliary capillary or mechanically pumped loops for the entire system.
  • the secondary capillary pump 40 is working as a capillary pump of the secondary loop with remote compensation chamber 20 as a condenser to absorb heat leak through the primary capillary pump 30.
  • the secondary capillary pump 40 has similar function as a remote auxiliary capillary or mechanically pumped loop in known designs.
  • a remote compensation chamber 20 (common for all evaporators 2 of multiple evaporator option) included in the proposed design serves to accumulate liquid and to compensate the liquid volume changes during the LHP device 1 operation.
  • This large reservoir helps to avoid the obligation of designing a large volume compensation chamber for the individual evaporators in the multiple evaporator option (in ordinary LHPs with multiple evaporators their volumes depend strongly on the total number of evaporators 2 in the system). Therefore, this configuration allows having a scalable design which can be fitted easier to the required number of evaporators 2 and the specific requirements of each application, because evaporators 2 will have same design independently on the design and volume of the lines, condensers 27, total number of evaporators 2, etc. Only the volume of the remote compensation chamber 20 has to be adjusted for specific requirements.
  • the design and location of the remote compensation chamber 20 can be selected depending on the functional purposes and the geometrical constraints. However, it is recommendable to control the temperature of the remote compensation chamber 20. For these purposes, several options can be considered and the best solution can be selected depending on each application requirements:
  • the LHP device 1 of the invention can comprise several optional additional elements, such as:
  • the LHP device 1 of the invention may further comprise external auxiliary means such as cold bias links or thermal electric coolers for subcooling the liquid inside the liquid accumulator reservoirs 6 in the stabilization-compensation chambers 10.
  • external auxiliary means such as cold bias links or thermal electric coolers for subcooling the liquid inside the liquid accumulator reservoirs 6 in the stabilization-compensation chambers 10.

Claims (14)

  1. Dispositif formant caloduc en boucle (1) permettant un transfert de chaleur et une thermorégulation, utilisant un fluide diphasique comme milieu de travail et comprenant :
    - au moins un évaporateur (2) à raccorder à une source de chaleur et comprenant une chambre de stabilisation-compensation thermique (10) fixée sur le au moins un évaporateur (2) et une pompe capillaire secondaire (40) située à l'intérieur de la chambre de stabilisation-compensation thermique (10),
    - au moins un condenseur (27) à raccorder à un puits thermique,
    - des conduites de liquide (24) et des conduites de vapeur (28) raccordant le au moins un évaporateur (2) et le au moins un condenseur (27), et
    - une chambre de compensation distante (20),
    caractérisé en ce que la chambre de stabilisation-compensation thermique (10) comprend un réservoir diphasique (5) et un réservoir de collecte de liquide (6) séparés par une surface d'échange thermique (15), de sorte que la chambre de compensation distante (20) est raccordée de manière hydraulique au réservoir diphasique (5) et au réservoir de collecte de liquide (6).
  2. Dispositif formant caloduc en boucle (1) permettant un transfert de chaleur et une thermorégulation, selon la revendication 1, comprenant en outre une pompe capillaire primaire (30) comprenant des canaux de vapeur extérieurs (19) afin de collecter et extraire de la chaleur en provenance de la source de chaleur et des canaux de vapeur intérieurs (16) afin de collecter et extraire de la vapeur produite par une fuite de chaleur parasite s'infiltrant à travers la pompe capillaire primaire (30).
  3. Dispositif formant caloduc en boucle (1) permettant un transfert de chaleur et une thermorégulation, selon la revendication 2, dans lequel les canaux de vapeur intérieurs (16) sont reliés au réservoir diphasique (5) de la chambre de stabilisation-compensation (10) où la vapeur extraite générée du fait de la fuite de chaleur parasite est condensée sur la surface d'échange de chaleur (15) dédiée.
  4. Dispositif formant caloduc en boucle (1) permettant un transfert de chaleur et une thermorégulation, selon l'une quelconque des revendications précédentes, dans lequel la pompe capillaire secondaire (40) contient un canal de liquide intérieur (26) avec un tube à baïonnette (7) pour du liquide revenant du condenseur (27) et de la chambre de compensation distante (20).
  5. Dispositif formant caloduc en boucle (1) permettant un transfert de chaleur et une thermorégulation, selon l'une quelconque des revendications précédentes, dans lequel la chambre de compensation distante (20) présente une structure capillaire interne qui sépare une conduite de renvoi de liquide (13) par rapport à la totalité du volume de la chambre de compensation distante (20) afin d'empêcher une circulation de vapeur/des bulles de s'infiltrer dans la conduite de renvoi de liquide (13) et dans le réservoir de collecte de liquide (6) de la chambre de stabilisation-compensation (10).
  6. Dispositif formant caloduc en boucle (1) permettant un transfert de chaleur et une thermorégulation, selon la revendication 5, dans lequel la chambre de compensation distante (20) est raccordée au réservoir diphasique (5) de la chambre de stabilisation-compensation (10) grâce à une conduite diphasique (12) et au réservoir de collecte de liquide (6) de la chambre de stabilisation-compensation (10) directement grâce à la conduite de renvoi de liquide (13).
  7. Dispositif formant caloduc en boucle (1) permettant un transfert de chaleur et une thermorégulation, selon la revendication 5, dans lequel la chambre de compensation distante (20) est raccordée au réservoir diphasique (5) de la chambre de stabilisation-compensation (10) grâce à une conduite diphasique (12) et au réservoir de collecte de liquide (6) de la chambre de stabilisation-compensation (10) grâce à la conduite de renvoi de liquide (13) et à une conduite de transport de liquide (24).
  8. Dispositif formant caloduc en boucle (1) permettant un transfert de chaleur et une thermorégulation, selon la revendication 5, dans lequel la chambre de compensation distante (20) est raccordée au réservoir diphasique (5) de la chambre de stabilisation-compensation (10) grâce à une conduite diphasique (12) et au réservoir de collecte de liquide (6) de la chambre de stabilisation-compensation (10) grâce à la conduite de renvoi de liquide (13) qui possède deux fonctions : transporter du liquide en provenance du condenseur (27) via une conduite de transport de liquide (24) vers une entrée de tube à baïonnette (7) de l'évaporateur (2), et renvoyer du liquide en provenance de la chambre de compensation distante (20).
  9. Dispositif formant caloduc en boucle (1) permettant un transfert de chaleur et une thermorégulation, selon l'une quelconque des revendications précédentes, comprenant en outre plusieurs évaporateurs (2).
  10. Dispositif formant caloduc en boucle (1) permettant un transfert de chaleur et une thermorégulation, selon l'une quelconque des revendications précédentes, comprenant en outre plusieurs condenseurs (27).
  11. Dispositif formant caloduc en boucle (1) permettant un transfert de chaleur et une thermorégulation, selon la revendication 9 ou 10, comprenant un dispositif de blocage capillaire situé au sein d'une conduite de transport de liquide (24) dans l'entrée de liquide de chaque évaporateur (2).
  12. Dispositif formant caloduc en boucle (1) permettant un transfert de chaleur et une thermorégulation, selon la revendication 10, comprenant un dispositif de blocage capillaire situé dans la sortie de liquide de chaque condenseur (27).
  13. Dispositif formant caloduc en boucle (1) permettant un transfert de chaleur et une thermorégulation, selon l'une quelconque des revendications précédentes, comprenant en outre un moyen auxiliaire externe permettant de sous-refroidir du liquide à l'intérieur de réservoirs de collecte de liquide (6) de chambres de stabilisation-compensation (10).
  14. Dispositif formant caloduc en boucle (1) permettant un transfert de chaleur et une thermorégulation, selon la revendication 13, dans lequel les moyens auxiliaires externes permettant de sous-refroidir du liquide à l'intérieur de réservoirs de collecte de liquide (6) de chambres de stabilisation-compensation (10) sont des ponts thermiques ou des dispositifs de refroidissement électrique.
EP12832734.3A 2012-12-28 2012-12-28 Dispositif caloduc en boucle pour transfert et régulation thermique Active EP2940416B1 (fr)

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PCT/ES2012/070918 WO2014102402A1 (fr) 2012-12-28 2012-12-28 Système de boucle fluide diphasique de type lhp pour la transmission de chaleur et la régulation thermique

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ES2648877T3 (es) 2018-01-08
US20150338171A1 (en) 2015-11-26
WO2014102402A1 (fr) 2014-07-03
EP2940416A1 (fr) 2015-11-04

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