EP2956729A1 - Heat transport device with diphasic fluid - Google Patents

Heat transport device with diphasic fluid

Info

Publication number
EP2956729A1
EP2956729A1 EP14704781.5A EP14704781A EP2956729A1 EP 2956729 A1 EP2956729 A1 EP 2956729A1 EP 14704781 A EP14704781 A EP 14704781A EP 2956729 A1 EP2956729 A1 EP 2956729A1
Authority
EP
European Patent Office
Prior art keywords
evaporator
liquid
volume
inlet
gas
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.)
Granted
Application number
EP14704781.5A
Other languages
German (de)
French (fr)
Other versions
EP2956729B1 (en
Inventor
Vincent Dupont
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.)
Euro Heat Pipes SA
Original Assignee
Euro Heat Pipes 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 Euro Heat Pipes SA filed Critical Euro Heat Pipes SA
Publication of EP2956729A1 publication Critical patent/EP2956729A1/en
Application granted granted Critical
Publication of EP2956729B1 publication Critical patent/EP2956729B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • F28D15/0266—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 separate evaporating and condensing chambers connected by at least one conduit; Loop-type heat pipes; with multiple or common evaporating or condensing chambers
    • 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
    • F28D15/025—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 having non-capillary condensate return means
    • 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
    • F28D15/06—Control arrangements therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/12—Safety or protection arrangements; Arrangements for preventing malfunction for preventing overpressure

Definitions

  • the present invention relates to two-phase fluid heat transport devices, in particular passive devices with a two-phase fluid loop with capillary pumping or using gravity.
  • the subject of the invention is a thermal transfer device, devoid of active regulation, adapted to extract heat from a hot source and to restore this heat to a cold source by means of a two-phase working fluid contained in a closed general circuit, comprising an evaporator, having an inlet and an outlet, a condenser, distinct and at a distance from the evaporator, a reservoir having an interior volume, with a liquid portion and a gas portion and at least one orifice an inlet / outlet arranged at the level of the liquid portion, the volume of the liquid portion being able to vary between a minimum volume Vmin and a maximum volume Vmax, a first communication circuit for working fluid essentially in the vapor phase, connecting the outlet of the evaporator to an inlet of the condenser,
  • a second communication circuit for working fluid essentially in the liquid phase, connecting an outlet of the condenser to the tank and to the inlet of the evaporator,
  • the gas portion of the reservoir comprises the vapor phase of the working fluid with a first partial pressure PI (pressure determined by the temperature of the reservoir) and a non-condensable auxiliary gas with a second partial pressure P2, the latter being adjusted to allow to obtain a total pressure greater than or equal to a predetermined minimum operating pressure required when the liquid portion in the entirety of the closed general circuit is at a minimum total volume.
  • PI pressure determined by the temperature of the reservoir
  • P2 non-condensable auxiliary gas
  • a minimum pressure is ensured in the tank due to the presence of the non-condensable auxiliary gas in the gas portion of the tank, even when the liquid portion is at its minimum. or that the device is completely cold, without adding heat to the evaporator for a long time.
  • the minimum pressure linked to the presence of the non-condensable auxiliary gas in the tank makes it possible to obtain a high saturation temperature in the second communication circuit (the gas pipe), which makes it possible to obtain a minimum density of the vapor phase of the Working fluid, and since the heat transfer capacity of the loop is proportional to the density of the vapor phase, an improved heat transport capability can be obtained instantaneously upon cold start of the loop.
  • a gas which remains in the gaseous state over the entire range of temperature / pressure to which the device is subjected is preferably chosen; in addition, a gas with a low diffusion coefficient in the liquids is chosen as the auxiliary gas.
  • the non-condensable auxiliary gas may be helium; whereby the physicochemical properties of helium are perfectly suitable and this gas has a good industrial availability;
  • the working fluid may be methanol; this fluid to work in a satisfactory temperature range and has a satisfactory capillary performance.
  • the second partial pressure P2 may be at least several times greater than the first partial pressure P1 when the liquid portion is at its minimum volume; so that the minimum pressure is high enough to allow instant start without preparation under high thermal load;
  • the volume of the reservoir can be between 1.3 and 2.5 times the maximum volume of the liquid portion; so that when the volume of the liquid portion is at a maximum, the pressure and temperature in the reservoir and in the loop remain limited and remain compatible with efficient removal of calories at the evaporator; the device can be mainly subjected to Earth's gravity, the inlet / outlet orifice being arranged at at least one low point of the tank; whereby the auxiliary gas is prevented from being sucked towards the evaporator;
  • the device can be mainly subjected to microgravity, the reservoir comprising a porous mass arranged at least in the vicinity of the inlet orifice; whereby a liquid barrier is formed in the porous mass and the auxiliary gas is prevented from being sucked towards the evaporator;
  • the evaporator may comprise a microporous mass adapted to ensure capillary pumping of fluid in the liquid phase; a maintenance-free passive system is thus obtained;
  • the evaporator without capillary structure can be placed below the condenser and the reservoir, so that the gravity is used to move the liquid towards the evaporator; which represents a very simple and particularly robust and reliable solution;
  • a non-return valve can be arranged at the inlet of the evaporator; it is thus possible to prevent a return of liquid in the opposite direction to the direction of normal circulation, and thus prevent drying of the evaporator at startup under heavy load;
  • the system is devoid of active regulation; which provides a particularly reliable solution.
  • FIG. 1 shows a general view of a device according to one embodiment of the invention
  • FIG. 2 illustrates the fluids in a general pressure-temperature diagram
  • FIGS. 3A and 3B show the reservoir with a respective minimum and maximum liquid portion
  • FIG. 4 shows a second embodiment of the device
  • FIGS. 5A and 5B illustrate diagrams of pressure and saturation temperature as a function of the ambient temperature.
  • Figure 1 shows a two-phase fluid loop heat transport device.
  • the device comprises an evaporator 1 having an inlet 1a and an outlet 1b, and a microporous mass 10 adapted to provide capillary pumping.
  • the microporous mass 10 surrounds a blind central longitudinal recess 15 in communication with the inlet 1a to receive working fluid in the liquid state from a fluid line in the liquid phase.
  • the evaporator 1 is thermally coupled to a hot source 11, such as an assembly comprising electronic power components or any other element generating heat, for example by joule effect, or by any other process.
  • a hot source 11 such as an assembly comprising electronic power components or any other element generating heat, for example by joule effect, or by any other process.
  • the temperature of the working fluid is lowered below its liquid-vapor equilibrium temperature, which is also called sub-cooling ('sub cooling' in English) so that the fluid can not return to the steam state without any heat input.
  • the vapor pressure pushes the liquid towards the outlet 2b of the condenser 2, which opens onto a second communication circuit 5, connected to the inlet 1a of the evaporator 1.
  • the second communication circuit 5 is also connected to a reservoir 3.
  • This reservoir serves as an expansion vessel for the working fluid, and contains working fluid both in the liquid phase and in the gas phase.
  • Said tank forms, together with the first and second communication circuits 4,5, together with the evaporator 1 and the condenser 2, a generally enclosed closed circuit.
  • the reservoir 3 has at least one inlet / outlet port 31, and a certain interior volume 30 generally attached to the design for a given application. This volume may possibly be adjustable by a mechanical device operated manually or automatically.
  • the reservoir also comprises a filling orifice 36 which allows an initial filling of the circuit, this filling orifice being closed the rest of the time. It should be noted that the reservoir 3 may have any shape, and in particular parallelepipedal, cylindrical, or other.
  • the heat transfer device is designed to operate within a certain range of ambient temperature; in the illustrated example, this temperature range can be: [-50 ° C, + 50 ° C]. Furthermore, it is desirable that the hot source 11 does not exceed a certain predetermined maximum temperature, regardless of the heat flow to be evacuated. This predetermined maximum temperature may be for example 100 ° C. Of course, these temperatures may depend on the intended application type, space applications in microgravity, terrestrial applications on board a vehicle or in a fixed location.
  • the working fluid of the loop is chosen to be always potentially two-phase in the range of fluid temperatures and pressures of the two-phase loop, depending on the above-mentioned temperature range (see reference 14 in Fig. 2).
  • the working fluid can be chosen from a list comprising in particular ammonia, acetone, methanol, water, dielectric fluids of the type HFE7200 or any other suitable fluid.
  • methanol will preferably be chosen.
  • a liquid portion 6 essentially comprising working fluid (in this case methanol) in the liquid phase and a gas portion 7 comprising fluid in the vapor phase, but also, as will be seen in more detail.
  • a non-condensable auxiliary gas 8 (denoted y NCG 'of the English Non-Condensible Gas) remains confined in the gas portion of the tank without directly participating in the heat exchanges; it has the effect of creating a minimum pressure in this gas portion.
  • the partial pressure of this non-condensable auxiliary gas 8 is denoted P2. Over the range of temperatures and pressures of the application, this non-condensable auxiliary gas remains in the gaseous state as shown in Figure 2, in the right part.
  • the gas portion 7 is located above the liquid portion 6 and a liquid-vapor interface 19 generally horizontal separates the two phases (free surface of the liquid in the tank).
  • the temperature of the liquid portion, the gas portion and the shell of the reservoir are relatively homogeneous; there is little temperature gradient inside the tank.
  • the temperature of the tank is also not far from the ambient temperature in which it is located.
  • the inlet / outlet orifice 31 is arranged at the level of the liquid portion, so that the gas portion is never directly in communication with the liquid communication circuit 5.
  • configuration of the capillary link between the reservoir and the porous mass may be like that described in patent EP0832411.
  • a porous mass 9 arranged in the vicinity of the inlet / outlet orifice 31, of which the function is to retain liquid, and therefore to form a barrier preventing components of the gas phase to be sucked towards the liquid communication circuit 5.
  • the inlet / outlet port 31 is arranged at a low point of the tank. It should be noted that there may be several low points in the tank.
  • the volume of the liquid portion 6 in the reservoir may vary between minimum volume ('Vrnin') represented in FIG. 3A which corresponds to a minimum total volume of liquid in the entirety of the general circuit, and a maximum volume ('Vmax') shown in Figure 3B which corresponds to a maximum total volume of liquid in the entirety of the general circuit.
  • Vmax and Vmin are at least equal to the sum of 2 volumes which are respectively called the expansion volume VOc and the purge volume Vpurge which respectively represent, on the one hand, the thermal expansion of the liquid and, on the other hand, the evacuation of the liquid driven by the presence of steam in the steam pipe 4 and a portion of the condenser 2 of the loop.
  • the pressure which prevails in the gas portion is essentially due to the presence of the auxiliary gas 8 (pressure P2) and not to the partial pressure P1 of the fluid of work that is very weak.
  • Still without caloric ratio on one evaporator (zero heat flow, Q 0), but with a maximum ambient temperature, there is a liquid dilation which gives a volume of liquid portion noted VOc, greater than Vmin.
  • This situation is represented in FIGS. 5A-5B by points 62.
  • the second pressure P2 is such that it makes it possible to obtain a total pressure in the tank greater than or equal to a predetermined minimum operating pressure required (shown at 0.7 bar in Figure 5B in a non-limiting manner, indeed this minimum value can be determined depending on the application considered).
  • the second partial pressure P2 may be several times, for example 5 times or 10 times greater than the first partial pressure P1 (cf. ).
  • the total volume of the tank is between 1.3 and 2.5 times the maximum volume Vmax of the liquid portion (case of the maximum total volume of liquid phase).
  • the saturation temperature Tsat for an ambient temperature of 50.degree. C. and a maximum flow Qmax, remains below 90.degree. this allows to continue to take calories at the hot spring 11.
  • this gas must remain in the vapor phase throughout the operating range of the loop and in particular the pressure and temperature conditions in the tank, it must have a very low boiling point; moreover, its diffusion coefficient inside the liquids and its Oswald coefficient must also be low in order to prevent this auxiliary gas from seeping inside the liquid portion 6 of the reservoir and in the rest of the loop.
  • helium can be chosen as an auxiliary gas. Helium is chemically neutral and its industrial availability is satisfactory. However, it is not excluded to use other gases such as nitrogen, argon or neon.
  • FIG. 4 illustrates a second embodiment of the thermosiphon type, in which the condenser 2 is placed above the evaporator 1 so that the gravity naturally leads the liquid towards the evaporator; under these conditions, the role of the porous material in the evaporator is to promote heat exchange and vaporization rather than perform the actual capillary pumping function.
  • the condenser 2 is placed above the evaporator 1 so that the gravity naturally leads the liquid towards the evaporator; under these conditions, the role of the porous material in the evaporator is to promote heat exchange and vaporization rather than perform the actual capillary pumping function.
  • everything else and in particular the operating principle is identical to the first mode described above, and will not be repeated.
  • the device is devoid of any mechanical pump although the invention does not exclude the presence of a mechanical booster pump.
  • the first and second fluid communication circuits 4,5 are preferably tubular conduits, but could be other types of fluid communication conduits or channels (rectangular conduits, flexible, etc.) - Similarly, the inlet / outlet port 31 could be a separate inlet and outlet.
  • the two-phase loop may advantageously be equipped with a non-return valve 18 located at the inlet of each evaporator so as to increase the maximum starting power. Indeed, the non-return valve 18 prevents a return of liquid in the opposite direction to the normal flow direction, and thus prevents drying of the evaporator at startup under heavy load.
  • the non-return valve may be formed by a floating element recalled by the buoyancy thrust against a bearing to close the passage and thus prevent a return of liquid.
  • the two-phase fluid system presented here is fully self-adaptive, it requires no control law, no sensor.
  • the result is a particularly simple design, particularly simple manufacturing, no need for maintenance, and incomparable reliability.

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)

Abstract

The invention relates to a heat transport device with a diphasic working fluid contained in a general closed circuit, including an evaporator (1) having a microporous body (10) suitable for providing capillary pumping of liquid phase fluid; a condenser (2); a tank (3) having an inner space (30), with a liquid portion (6) and a gas portion (7); and an inlet/outlet (31) arranged at the liquid portion, wherein the volume of the liquid portion can vary between a minimum volume (Vmin) and a maximum volume (Vmax), characterized in that the gas portion (7) of the tank contains the vapor phase of the working fluid, at a first partial pressure (P1), and a non-condensable auxiliary gas (8) at a second partial pressure (P2), wherein the second partial pressure is greater than the first partial pressure, at least when the liquid portion (6) is at the minimum volume thereof.

Description

Dispositif de transport de chaleur à fluide diphasique  Two-phase fluid heat transport device
La présente invention est relative aux dispositifs de transport de chaleur à fluide diphasique, en particulier les dispositifs passifs à boucle fluide diphasique à pompage capillaire ou utilisant la gravité. The present invention relates to two-phase fluid heat transport devices, in particular passive devices with a two-phase fluid loop with capillary pumping or using gravity.
Il est connu du document FR-A-2949642 un exemple d'un tel dispositif utilisé comme moyen de refroidissement pour convertisseur de puissance électrotechnique.  It is known from FR-A-2949642 an example of such a device used as a cooling means for electrotechnical power converter.
En conditions de fonctionnement établies, ces dispositifs donnent pleine satisfaction. Cependant, il est apparu que les phases de démarrage à partir d'un état ' à froid' (Température ambiante minimale et flux thermique nul) pouvaient être particulièrement délicates pour des puissances thermiques importantes, et pouvaient nécessiter une étape préalable de mise en condition, par exemple par un réchauffement préalable du réservoir. Sans cette mise en condition, la pression dans le circuit peut s'avérer insuffisante pour assurer un transfert de chaleur suffisant.  In established operating conditions, these devices give full satisfaction. However, it appeared that the starting phases from a 'cold' state (minimum ambient temperature and zero heat flux) could be particularly delicate for large thermal powers, and could require a preliminary conditioning step, for example by preheating the tank. Without this conditioning, the pressure in the circuit may be insufficient to ensure sufficient heat transfer.
Il est donc apparu un besoin d'améliorer la disponibilité du démarrage concernant de telles boucles diphasiques .  It has therefore appeared a need to improve the availability of start-up for such two-phase loops.
A cet effet, l'invention a pour objet un dispositif de transfert thermique, dépourvu de régulation active, adapté pour extraire de la chaleur depuis une source chaude et pour restituer cette chaleur à une source froide au moyen d'un fluide de travail diphasique contenu dans un circuit général clos, comprenant un évaporateur, ayant une entrée et une sortie, un condenseur, distinct et à distance de 1 ' évaporateur , un réservoir ayant un volume intérieur, avec une portion liquide et une portion gaz et au moins un orifice d'entrée/sortie agencé au niveau de la portion liquide, le volume de la portion liquide pouvant varier entre un volume minimum Vmin et un volume maximum Vmax, - un premier circuit de communication, pour du fluide de travail essentiellement en phase vapeur, reliant la sortie de 1 ' évaporateur à une entrée du condenseur, For this purpose, the subject of the invention is a thermal transfer device, devoid of active regulation, adapted to extract heat from a hot source and to restore this heat to a cold source by means of a two-phase working fluid contained in a closed general circuit, comprising an evaporator, having an inlet and an outlet, a condenser, distinct and at a distance from the evaporator, a reservoir having an interior volume, with a liquid portion and a gas portion and at least one orifice an inlet / outlet arranged at the level of the liquid portion, the volume of the liquid portion being able to vary between a minimum volume Vmin and a maximum volume Vmax, a first communication circuit for working fluid essentially in the vapor phase, connecting the outlet of the evaporator to an inlet of the condenser,
- un deuxième circuit de communication, pour du fluide de travail essentiellement en phase liquide, reliant une sortie du condenseur au réservoir et à l'entrée de 1 'évaporateur,  a second communication circuit, for working fluid essentially in the liquid phase, connecting an outlet of the condenser to the tank and to the inlet of the evaporator,
caractérisé en ce que la portion gaz du réservoir comprend de la phase vapeur du fluide de travail avec une première pression partielle PI (pression déterminée par la température du réservoir) et un gaz auxiliaire non condensable avec une deuxième pression partielle P2, cette dernière étant ajustée pour permettre d'obtenir une pression totale supérieure ou égale à une pression minimale de fonctionnement prédéterminée requise lorsque la portion liquide dans l'entièreté du circuit général clos est à un volume total minimum. characterized in that the gas portion of the reservoir comprises the vapor phase of the working fluid with a first partial pressure PI (pressure determined by the temperature of the reservoir) and a non-condensable auxiliary gas with a second partial pressure P2, the latter being adjusted to allow to obtain a total pressure greater than or equal to a predetermined minimum operating pressure required when the liquid portion in the entirety of the closed general circuit is at a minimum total volume.
Grâce à ces dispositions, en particulier grâce à la deuxième pression partielle P2, on assure une pression minimale dans le réservoir du fait de la présence du gaz auxiliaire non condensable dans la portion gaz du réservoir, même lorsque la portion de liquide est à son minimum, ou que le dispositif est complètement à froid, sans apport de chaleur sur 1 ' évaporateur depuis assez longtemps. La pression minimale liée à la présence du gaz auxiliaire non condensable dans le réservoir permet d'obtenir une température de saturation élevée dans le deuxième circuit de communication (la conduite gaz), ce qui permet d'obtenir une densité minimale de la phase vapeur du fluide de travail, et étant donné que la capacité de transport de chaleur de la boucle est proportionnelle à la densité de la phase vapeur, on peut obtenir instantanément dès le démarrage à froid de la boucle une capacité de transport de chaleur améliorée.  Thanks to these arrangements, in particular thanks to the second partial pressure P2, a minimum pressure is ensured in the tank due to the presence of the non-condensable auxiliary gas in the gas portion of the tank, even when the liquid portion is at its minimum. or that the device is completely cold, without adding heat to the evaporator for a long time. The minimum pressure linked to the presence of the non-condensable auxiliary gas in the tank makes it possible to obtain a high saturation temperature in the second communication circuit (the gas pipe), which makes it possible to obtain a minimum density of the vapor phase of the Working fluid, and since the heat transfer capacity of the loop is proportional to the density of the vapor phase, an improved heat transport capability can be obtained instantaneously upon cold start of the loop.
De plus, grâce à ces dispositions, on obtient une régulation passive sans besoin de système de commande actif, ce qui accroît la fiabilité de ce genre de dispositif. Un tel système, sans pompage actif et sans système de commande actif, ne nécessite aucun entretien et présente une fiabilité très élevée ; et sa consommation énergétique est très faible voire nulle. Moreover, thanks to these provisions, we obtain a passive regulation without the need for an active control system, which increases the reliability of this kind of device. Such a system, without active pumping and without active control system, requires no maintenance and has a very high reliability; and its energy consumption is very low or even zero.
De préférence on choisit, comme gaz auxiliaire non condensable, un gaz qui reste à l'état gazeux sur toute la plage de température/pression auquel est soumis le dispositif ; de plus on choisit comme gaz auxiliaire un gaz avec un faible coefficient de diffusion dans les liquides.  As a non-condensable auxiliary gas, a gas which remains in the gaseous state over the entire range of temperature / pressure to which the device is subjected is preferably chosen; in addition, a gas with a low diffusion coefficient in the liquids is chosen as the auxiliary gas.
Dans divers modes de réalisation de l'invention, on peut éventuellement avoir recours en outre à l'une et/ou à l'autre des dispositions suivantes :  In various embodiments of the invention, one or more of the following provisions may also be used:
- le gaz auxiliaire non condensable peut être de l'hélium ; moyennant quoi les propriétés physico-chimiques de l'hélium conviennent parfaitement et ce gaz présente une bonne disponibilité industrielle ; the non-condensable auxiliary gas may be helium; whereby the physicochemical properties of helium are perfectly suitable and this gas has a good industrial availability;
- le fluide de travail peut être du méthanol ; ce fluide permettant de travailler dans une gamme de température satisfaisante et présente une performance capillaire satisfaisante .  the working fluid may be methanol; this fluid to work in a satisfactory temperature range and has a satisfactory capillary performance.
la deuxième pression partielle P2 peut être au moins plusieurs fois supérieure à la première pression partielle PI lorsque la portion liquide est à son volume minimum ; de sorte que la pression minimale est assez élevée pour autoriser un démarrage instantané sans préparation sous charge thermique importante ;  the second partial pressure P2 may be at least several times greater than the first partial pressure P1 when the liquid portion is at its minimum volume; so that the minimum pressure is high enough to allow instant start without preparation under high thermal load;
- le volume du réservoir peut être compris entre 1,3 et 2,5 fois le volume maximum de la portion liquide ; de sorte que lorsque le volume de la portion liquide est maximal, la pression et la température dans le réservoir et dans la boucle restent limitées et restent compatible avec un prélèvement efficace des calories au niveau de 1 ' évaporateur ; le dispositif peut être principalement soumis à la gravité terrestre, l'orifice d'entrée/sortie étant agencé au niveau d'au moins un point bas du réservoir ; moyennant quoi on évite que le gaz auxiliaire ne soit aspiré en direction de 1 ' évaporateur ; the volume of the reservoir can be between 1.3 and 2.5 times the maximum volume of the liquid portion; so that when the volume of the liquid portion is at a maximum, the pressure and temperature in the reservoir and in the loop remain limited and remain compatible with efficient removal of calories at the evaporator; the device can be mainly subjected to Earth's gravity, the inlet / outlet orifice being arranged at at least one low point of the tank; whereby the auxiliary gas is prevented from being sucked towards the evaporator;
le dispositif peut être principalement soumis à une microgravité, le réservoir comprenant une masse poreuse agencée au moins au voisinage de l'orifice d'entrée ; moyennant quoi une barrière de liquide est formée dans la masse poreuse et on évite que le gaz auxiliaire ne soit aspiré en direction de 1 ' évaporateur ;  the device can be mainly subjected to microgravity, the reservoir comprising a porous mass arranged at least in the vicinity of the inlet orifice; whereby a liquid barrier is formed in the porous mass and the auxiliary gas is prevented from being sucked towards the evaporator;
- 1 ' évaporateur peut comprendre une masse microporeuse adaptée pour assurer un pompage capillaire de fluide en phase liquide ; on obtient ainsi un système passif sans entretien ;  The evaporator may comprise a microporous mass adapted to ensure capillary pumping of fluid in the liquid phase; a maintenance-free passive system is thus obtained;
- dans le cas où le dispositif est principalement soumis à la gravité, 1 ' évaporateur sans structure capillaire peut être placé en dessous du condenseur et du réservoir, de sorte que la gravité est utilisée pour déplacer le liquide vers 1 ' évaporateur ; ce qui représente une solution très simple et particulièrement robuste et fiable ;  in the case where the device is mainly subjected to gravity, the evaporator without capillary structure can be placed below the condenser and the reservoir, so that the gravity is used to move the liquid towards the evaporator; which represents a very simple and particularly robust and reliable solution;
- un clapet anti-retour peut être agencé à l'entrée de 1 ' évaporateur ; on peut ainsi empêcher un retour de liquide en direction inverse au sens de circulation normal, et empêcher ainsi un assèchement de 1 ' évaporateur au démarrage sous forte charge ;  a non-return valve can be arranged at the inlet of the evaporator; it is thus possible to prevent a return of liquid in the opposite direction to the direction of normal circulation, and thus prevent drying of the evaporator at startup under heavy load;
avantageusement selon l'invention, le système est dépourvu de régulation active ; ce qui fournit une solution particulièrement fiable.  advantageously according to the invention, the system is devoid of active regulation; which provides a particularly reliable solution.
D'autres aspects, buts et avantages de l'invention apparaîtront à la lecture de la description suivante de deux modes de réalisation de l'invention, donnés à titre d'exemples non limitatifs, en regard des dessins joints sur lesquels :  Other aspects, objects and advantages of the invention will appear on reading the following description of two embodiments of the invention, given by way of non-limiting examples, with reference to the accompanying drawings, in which:
- la figure 1 montre une vue générale d'un dispositif selon un mode de réalisation de l'invention, - Figure 1 shows a general view of a device according to one embodiment of the invention,
- la figure 2 illustre les fluides dans un diagramme pression-température général,  FIG. 2 illustrates the fluids in a general pressure-temperature diagram,
- les figures 3A et 3B montrent le réservoir avec une portion liquide respectivement minimale et maximale,  FIGS. 3A and 3B show the reservoir with a respective minimum and maximum liquid portion,
- la figure 4 montre un second mode de réalisation du dispositif,  FIG. 4 shows a second embodiment of the device,
- les figures 5A et 5B illustrent des diagrammes de pression et température de saturation en fonction de la température ambiante.  FIGS. 5A and 5B illustrate diagrams of pressure and saturation temperature as a function of the ambient temperature.
Sur les différentes figures, les mêmes références désignent des éléments identiques ou similaires.  In the different figures, the same references designate identical or similar elements.
La figure 1 montre un dispositif de transport de chaleur à boucle fluide diphasique. Dans le cas de premier mode, le pompage est assuré en tirant partie du phénomène de capillarité. Le dispositif comprend un évaporateur 1, ayant une entrée la et une sortie lb, et une masse microporeuse 10 adaptée pour assurer le pompage capillaire. A cet effet, la masse microporeuse 10 entoure un évidement longitudinal central borgne 15 en communication avec l'entrée la pour recevoir du fluide de travail à l'état liquide depuis une conduite de fluide en phase liquide.  Figure 1 shows a two-phase fluid loop heat transport device. In the case of the first mode, the pumping is ensured by taking advantage of the capillarity phenomenon. The device comprises an evaporator 1 having an inlet 1a and an outlet 1b, and a microporous mass 10 adapted to provide capillary pumping. For this purpose, the microporous mass 10 surrounds a blind central longitudinal recess 15 in communication with the inlet 1a to receive working fluid in the liquid state from a fluid line in the liquid phase.
L ' évaporateur 1 est thermiquement couplé à une source chaude 11, comme par exemple un ensemble comprenant des composants électroniques de puissance ou tout autre élément générant de la chaleur, par exemple par effet joule, ou par tout autre processus.  The evaporator 1 is thermally coupled to a hot source 11, such as an assembly comprising electronic power components or any other element generating heat, for example by joule effect, or by any other process.
Sous l'effet de l'apport de calories au contact 16 de la masse microporeuse emplie de liquide, du fluide passe de l'état liquide à l'état vapeur et s'évacue par la chambre de transfert 17 et par un premier circuit de communication 4 qui achemine ladite vapeur vers un condenseur 2 ayant une entrée 2a et une sortie 2b ; le condenseur 2 étant distinct et non adjacent par rapport à 1 ' évaporateur 1. Dans 1 ' évaporateur 1, les cavités libérées par la vapeur évacuée sont comblées par du liquide aspiré par la masse microporeuse 10 à partir de l'évidement central 15 susmentionné ; il s'agit du phénomène de pompage capillaire bien connu en soi. Le flux de chaleur Q prélevé sur la source chaude correspond au débit multiplié par la chaleur latente L de vaporisation du fluide de travail (Q = L.dM/dt) . Under the effect of the supply of calories to the contact 16 of the microporous mass filled with liquid, fluid passes from the liquid state to the vapor state and is evacuated by the transfer chamber 17 and by a first circuit. communication 4 which conveys said vapor to a condenser 2 having an inlet 2a and an outlet 2b; the condenser 2 being distinct and not adjacent to the evaporator 1. In the evaporator 1, the cavities released by the evacuated vapor are filled with liquid sucked by the microporous mass 10 from the above-mentioned central recess; it is the phenomenon of capillary pumping well known in itself. The heat flux Q taken from the hot source corresponds to the flow rate multiplied by the latent heat L of vaporization of the working fluid (Q = L.dM / dt).
A l'intérieur du condenseur 2, de la chaleur est cédée par le fluide en phase vapeur à une source froide 12, ce qui provoque un refroidissement du fluide en phase vapeur et son changement de phase vers la phase liquide, autrement dit sa condensation.  Inside the condenser 2, heat is transferred by the fluid in the vapor phase to a cold source 12, which causes cooling of the fluid in the vapor phase and its phase change to the liquid phase, ie its condensation.
Au niveau du condenseur 2, la température du fluide de travail est abaissée en dessous de sa température d'équilibre liquide-vapeur, ce qui est aussi appelé sous- refroidissement ( ' sub cooling' en anglais) de sorte que le fluide ne peut pas repasser à l'état vapeur sans apport conséquent de chaleur.  At the condenser 2, the temperature of the working fluid is lowered below its liquid-vapor equilibrium temperature, which is also called sub-cooling ('sub cooling' in English) so that the fluid can not return to the steam state without any heat input.
La pression de vapeur pousse le liquide en direction de la sortie 2b du condenseur 2 qui débouche sur un deuxième circuit de communication 5, relié à l'entrée la de 1 ' évaporateur 1. On obtient ainsi une boucle de circulation du fluide diphasique capable d'extraire de la chaleur depuis la source chaude 11 pour restituer cette chaleur à une source froide 12.  The vapor pressure pushes the liquid towards the outlet 2b of the condenser 2, which opens onto a second communication circuit 5, connected to the inlet 1a of the evaporator 1. This gives a circulation loop of the two-phase fluid capable of extracting heat from the hot source 11 to return this heat to a cold source 12.
La chaleur transportée par la phase vapeur dans le premier circuit de communication peut s'écrire Q=pVS, avec p représentant la densité de la phase vapeur, V la vitesse de déplacement de la phase vapeur et S la section du circuit de communication.  The heat transported by the vapor phase in the first communication circuit can be written as Q = pVS, where p is the density of the vapor phase, V is the displacement velocity of the vapor phase and S is the section of the communication circuit.
Le deuxième circuit de communication 5 est relié par ailleurs à un réservoir 3. Ce réservoir sert de vase d'expansion pour le fluide de travail, et contient du fluide de travail à la fois en phase liquide et en phase gazeuse. Ledit réservoir forme, avec les premier et second circuits de communication 4,5, ensemble avec 1 ' évaporateur 1 et le condenseur 2, un circuit général clos autrement dit hermétique. The second communication circuit 5 is also connected to a reservoir 3. This reservoir serves as an expansion vessel for the working fluid, and contains working fluid both in the liquid phase and in the gas phase. Said tank forms, together with the first and second communication circuits 4,5, together with the evaporator 1 and the condenser 2, a generally enclosed closed circuit.
Le réservoir 3 présente au moins un orifice d'entrée/sortie 31, et un certain volume intérieur 30 généralement fixé à la conception pour une application considérée. Ce volume peut-être éventuellement ajustable par un dispositif mécanique manœuvré manuellement ou automatiquement. Le réservoir comporte également un orifice de remplissage 36 qui permet un remplissage initial du circuit, cet orifice de remplissage étant fermé le reste du temps. Il est à noter que le réservoir 3 peut avoir une forme quelconque, et en particulier parallélépipédique, cylindrique, ou autre.  The reservoir 3 has at least one inlet / outlet port 31, and a certain interior volume 30 generally attached to the design for a given application. This volume may possibly be adjustable by a mechanical device operated manually or automatically. The reservoir also comprises a filling orifice 36 which allows an initial filling of the circuit, this filling orifice being closed the rest of the time. It should be noted that the reservoir 3 may have any shape, and in particular parallelepipedal, cylindrical, or other.
Le dispositif de transfert de chaleur est conçu pour pouvoir fonctionner dans une certaine gamme de température ambiante ; dans l'exemple illustré cette gamme de température peut être : [-50°C, +50°C] . Par ailleurs, il est souhaitable que la source chaude 11 ne dépasse pas une certaine température maximale prédéterminée, quel que soit le flux de chaleur à évacuer. Cette température maximale prédéterminée peut être par exemple 100°C. Bien sûr, ces températures peuvent dépendre du type d'application visée, applications spatiales en microgravité, applications terrestres à bord d'un véhicule ou dans un emplacement fixe .  The heat transfer device is designed to operate within a certain range of ambient temperature; in the illustrated example, this temperature range can be: [-50 ° C, + 50 ° C]. Furthermore, it is desirable that the hot source 11 does not exceed a certain predetermined maximum temperature, regardless of the heat flow to be evacuated. This predetermined maximum temperature may be for example 100 ° C. Of course, these temperatures may depend on the intended application type, space applications in microgravity, terrestrial applications on board a vehicle or in a fixed location.
Le fluide de travail de la boucle est choisi pour être toujours potentiellement diphasique dans la plage de températures et pressions du fluide de la boucle diphasique, en fonction de la gamme de température susmentionnée (voir référence 14 sur Fig. 2) .  The working fluid of the loop is chosen to be always potentially two-phase in the range of fluid temperatures and pressures of the two-phase loop, depending on the above-mentioned temperature range (see reference 14 in Fig. 2).
Ainsi le fluide de travail peut être choisi parmi une liste comprenant notamment l'ammoniac, l'acétone, le méthanol, l'eau, des fluides diélectriques du type HFE7200 ou tout autre fluide approprié. Dans l'exemple détaillé ci- après, on choisira préfèrentiellement du méthanol. Thus, the working fluid can be chosen from a list comprising in particular ammonia, acetone, methanol, water, dielectric fluids of the type HFE7200 or any other suitable fluid. In the detailed example below, methanol will preferably be chosen.
À l'intérieur du réservoir 3, on trouve une portion liquide 6 comprenant essentiellement du fluide de travail (ici du méthanol) en phase liquide et une portion gaz 7 comprenant du fluide en phase vapeur, mais aussi, comme il sera vu en détail plus loin, un gaz auxiliaire non condensable 8. Le gaz auxiliaire non condensable 8 (noté yNCG' de l'anglais Non Condensible Gas) reste confiné dans la portion gaz du réservoir sans participer directement aux échanges thermiques ; il a pour effet de créer une pression minimale dans cette portion gaz. La pression partielle de ce gaz auxiliaire non condensable 8 est notée P2. Sur la gamme de températures et pressions de l'application, ce gaz auxiliaire non condensable reste à l'état gazeux comme ceci apparaît à la figure 2, en partie droite. Inside the tank 3, there is a liquid portion 6 essentially comprising working fluid (in this case methanol) in the liquid phase and a gas portion 7 comprising fluid in the vapor phase, but also, as will be seen in more detail. a non-condensable auxiliary gas 8. The non-condensable auxiliary gas 8 (denoted y NCG 'of the English Non-Condensible Gas) remains confined in the gas portion of the tank without directly participating in the heat exchanges; it has the effect of creating a minimum pressure in this gas portion. The partial pressure of this non-condensable auxiliary gas 8 is denoted P2. Over the range of temperatures and pressures of the application, this non-condensable auxiliary gas remains in the gaseous state as shown in Figure 2, in the right part.
Il faut remarquer ici que selon l'art connu antérieurement, la présence de gaz non condensable dans le circuit de travail est indésirable car si des bulles de gaz non condensable parviennent dans la zone de 1 ' évaporateur capillaire, cela diminue les performances thermiques de vaporisation et cela peut même aller jusqu'à un désamorçage de 1 ' évaporateur capillaire, ce qui dans certaines applications critiques peut être catastrophique.  It should be noted here that according to the prior art, the presence of non-condensable gas in the working circuit is undesirable because if non-condensable gas bubbles reach the area of the capillary evaporator, this reduces the thermal performance of vaporization and this can even go as far as defusing the capillary evaporator, which in some critical applications can be catastrophic.
Dans un environnement où une gravité s'exerce, la portion gaz 7 se situe au-dessus de portion liquide 6 et une interface liquide-vapeur 19 généralement horizontale sépare les deux phases (surface libre du liquide dans le réservoir ) .  In an environment where gravity is exerted, the gas portion 7 is located above the liquid portion 6 and a liquid-vapor interface 19 generally horizontal separates the two phases (free surface of the liquid in the tank).
Dans un environnement où une microgravité s'exerce (en apesanteur) , la portion liquide est contenue dans du matériau poreux et la portion gaz occupe le reste du volume du réservoir ; il y a aussi dans ce cas de figure une interface liquide-vapeur 19, mais elle n'est pas plane. La température de cette surface de séparation 19 est reliée de façon univoque à la pression partielle Pl de fluide de travail dans la portion gaz, cette pression correspond à la pression de saturation Psat du fluide à la température Tsat prévalant à la surface de séparation 19, comme ceci apparaît à la figure 2, en partie gauche. In an environment where microgravity is exerted (in weightlessness), the liquid portion is contained in porous material and the gas portion occupies the rest of the volume of the reservoir; there is also in this case a liquid-vapor interface 19, but it is not flat. The temperature of this separation surface 19 is uniquely connected to the partial pressure P1 of working fluid in the gas portion, this pressure corresponds to the saturation pressure Psat of the fluid at the temperature Tsat prevailing at the separation surface 19, as shown in Figure 2, on the left.
En pratique, la température de la portion liquide, de la portion gaz et de l'enveloppe du réservoir sont relativement homogènes ; il y a peu de gradient de température à l'intérieur du réservoir. La température du réservoir est par ailleurs peu éloignée de la température ambiante dans laquelle il se situe.  In practice, the temperature of the liquid portion, the gas portion and the shell of the reservoir are relatively homogeneous; there is little temperature gradient inside the tank. The temperature of the tank is also not far from the ambient temperature in which it is located.
Selon un aspect avantageux de la présente invention, l'orifice d'entrée/sortie 31 est agencé au niveau de la portion liquide, de manière à ce que la portion gaz ne soit jamais directement en communication avec le circuit de communication liquide 5. La configuration du lien capillaire entre le réservoir et la masse poreuse peut-être comme celle décrit dans le brevet EP0832411.  According to an advantageous aspect of the present invention, the inlet / outlet orifice 31 is arranged at the level of the liquid portion, so that the gas portion is never directly in communication with the liquid communication circuit 5. configuration of the capillary link between the reservoir and the porous mass may be like that described in patent EP0832411.
Selon un aspect particulier, notamment dans les cas d'utilisation en microgravité (cas de figure non représenté sur les dessins) mais non exclusivement, on peut prévoir une masse poreuse 9 agencée au voisinage de l'orifice d'entrée/sortie 31, dont la fonction est de retenir du liquide, et par conséquent de former une barrière empêchant des composants de la phase gaz d'être aspirés en direction du circuit de communication liquide 5.  According to a particular aspect, especially in the case of use in microgravity (a case not shown in the drawings) but not exclusively, there can be provided a porous mass 9 arranged in the vicinity of the inlet / outlet orifice 31, of which the function is to retain liquid, and therefore to form a barrier preventing components of the gas phase to be sucked towards the liquid communication circuit 5.
Dans les applications terrestres la gravité s'exerce, l'orifice d'entrée/sortie 31 est agencé au niveau d'un point bas du réservoir. Il faut remarquer qu'il peut y avoir plusieurs points bas dans le réservoir.  In terrestrial applications gravity is exerted, the inlet / outlet port 31 is arranged at a low point of the tank. It should be noted that there may be several low points in the tank.
Le volume de la portion liquide 6 dans le réservoir peut varier entre volume minimum ( 'Vrnin' ) représenté à la figure 3A qui correspond à un volume total minimum de liquide dans l'entièreté du circuit général, et un volume maximum ( 'Vmax' ) représenté à la figure 3B qui correspond à un volume total maximum de liquide dans l'entièreté du circuit général . The volume of the liquid portion 6 in the reservoir may vary between minimum volume ('Vrnin') represented in FIG. 3A which corresponds to a minimum total volume of liquid in the entirety of the general circuit, and a maximum volume ('Vmax') shown in Figure 3B which corresponds to a maximum total volume of liquid in the entirety of the general circuit.
La différence entre Vmax et Vmin est au moins égale à la somme de 2 volumes que l'on appelle respectivement, volume de dilation VOc et volume de purge Vpurge qui représentent respectivement d'une part l'expansion thermique du liquide et, d'autre part l'évacuation du liquide chassé par la présence de vapeur dans la conduite vapeur 4 et d'une partie du condenseur 2 de la boucle. Autrement dit, lorsque la boucle diphasique est au repos depuis un certain temps, il n'y a plus de vapeur dans la boucle et le liquide occupe tout le volume intérieur de la boucle, ce qui donne un petit volume de portion liquide dans le réservoir ; à l'inverse lorsque le flux thermique est maximal (Q=Qmax) , le premier circuit de communication 4 est entièrement occupé par de la vapeur ainsi qu'une partie du circuit du condenseur 2, et de par le fait, le liquide est repoussé dans le réservoir où il occupe un grand volume. Le volume de portion liquide est aussi influencé par la température ambiante, ce qui conduit au volume de dilation VOc.  The difference between Vmax and Vmin is at least equal to the sum of 2 volumes which are respectively called the expansion volume VOc and the purge volume Vpurge which respectively represent, on the one hand, the thermal expansion of the liquid and, on the other hand, the evacuation of the liquid driven by the presence of steam in the steam pipe 4 and a portion of the condenser 2 of the loop. In other words, when the two-phase loop has been at rest for some time, there is no more steam in the loop and the liquid occupies the entire inner volume of the loop, which gives a small volume of liquid portion in the reservoir ; conversely, when the heat flow is maximum (Q = Qmax), the first communication circuit 4 is entirely occupied by steam and a part of the condenser circuit 2, and therefore the liquid is pushed back in the tank where it occupies a large volume. The volume of liquid portion is also influenced by the ambient temperature, which leads to the expansion volume VOc.
Plus précisément, le volume minimum Vmin correspond à une température ambiante minimale et un flux thermique nul (Q=0) sur 1 ' évaporateur ; cette situation est représentée dans les figures 5A-5B par les points 61. On remarque que la pression qui règne dans la portion gaz est essentiellement due à la présence gaz auxiliaire 8 (pression P2) et non pas à la pression partielle Pl du fluide de travail qui est très faible. La pression totale qui règne dans le réservoir vaut Près = Pl +P2 ; c'est aussi sensiblement la pression qui règne partout ailleurs dans la boucle diphasique. Toujours sans rapport de calories sur 1 ' évaporateur (flux thermique nul, Q=0), mais avec une température ambiante maximale, on constate une dilatation de liquide qui donne un volume de portion liquide noté VOc, supérieur à Vmin. Cette situation est représentée dans les figures 5A-5B par les points 62. More specifically, the minimum volume Vmin corresponds to a minimum ambient temperature and a zero heat flux (Q = 0) on one evaporator; this situation is represented in FIGS. 5A-5B by the points 61. It is noted that the pressure which prevails in the gas portion is essentially due to the presence of the auxiliary gas 8 (pressure P2) and not to the partial pressure P1 of the fluid of work that is very weak. The total pressure in the reservoir is Near = Pl + P2; it is also substantially the pressure that prevails everywhere else in the two-phase loop. Still without caloric ratio on one evaporator (zero heat flow, Q = 0), but with a maximum ambient temperature, there is a liquid dilation which gives a volume of liquid portion noted VOc, greater than Vmin. This situation is represented in FIGS. 5A-5B by points 62.
Dans les circonstances où la température ambiante est maximale et le flux thermique est lui aussi maximal Q=Qmax, le volume de la portion liquide est augmenté du volume correspondant à la purge Vpurge, ce qui conduit au cas illustré figure 3B. Cette situation est représentée dans les figures 5A-5B par les points 64.  In the circumstances where the ambient temperature is maximum and the heat flow is also maximum Q = Qmax, the volume of the liquid portion is increased by the volume corresponding to purge Vpurge, which leads to the case illustrated in Figure 3B. This situation is represented in FIGS. 5A-5B by points 64.
On constate donc que, lorsque la portion liquide 6 est à son volume minimum (Vmin) ce qui correspond à un volume total minimum de liquide dans l'entièreté du circuit général, la deuxième pression P2 est telle qu'elle permet d'obtenir une pression totale dans le réservoir supérieure ou égale à une pression minimale de fonctionnement prédéterminée requise (illustré à 0,7 bar dans la figure 5B à titre non limitatif, en effet cette valeur minimale peut être déterminée en fonction de l'application considérée).  It can therefore be seen that when the liquid portion 6 is at its minimum volume (Vmin), which corresponds to a minimum total volume of liquid in the entire general circuit, the second pressure P2 is such that it makes it possible to obtain a total pressure in the tank greater than or equal to a predetermined minimum operating pressure required (shown at 0.7 bar in Figure 5B in a non-limiting manner, indeed this minimum value can be determined depending on the application considered).
On peut aussi constater que, dans un exemple illustratif, lorsque la portion liquide 6 est à son volume minimum (Vmin) , la deuxième pression partielle P2 (NCG) est supérieure à la première pression partielle Pl. Cette condition reste vérifiée sur une majeure partie de la plage de température ambiante à Q=0 et même lorsque Q=Qmax sur la zone des températures froides.  It can also be noted that, in an illustrative example, when the liquid portion 6 is at its minimum volume (Vmin), the second partial pressure P2 (NCG) is greater than the first partial pressure P1. This condition remains verified over a major part from the ambient temperature range to Q = 0 and even when Q = Qmax in the cold temperature zone.
On peut aussi constater que lorsque la portion liquide 6 est à son volume minimum (Vmin) , la deuxième pression partielle P2 (NCG) peut être plusieurs fois, par exemple 5 fois ou 10 fois supérieure à la première pression partielle Pl (cf points 61) .  It can also be noted that when the liquid portion 6 is at its minimum volume (Vmin), the second partial pressure P2 (NCG) may be several times, for example 5 times or 10 times greater than the first partial pressure P1 (cf. ).
La pression minimale liée à la présence du gaz auxiliaire non condensable dans le réservoir (0,7 bar sur l'exemple la figure 5B) permet d'obtenir une température de saturation élevée dans le deuxième circuit de communication (50°C sur l'exemple la figure 5A) , ce qui permet d'obtenir une densité p minimale de la phase vapeur du fluide de travail, et étant donné que la capacité de transport de chaleur de la boucle est proportionnelle à la densité de la phase vapeur (Q=pVS) , on peut obtenir instantanément dès le démarrage à froid de la boucle une capacité de transport de chaleur suffisante pour éviter un désamorçage de l 'évaporateur et obtenir et un bon rendement de boucle. The minimum pressure related to the presence of gas non-condensable auxiliary in the tank (0.7 bar in the example Figure 5B) provides a high saturation temperature in the second communication circuit (50 ° C in the example Figure 5A), which allows to obtain a minimum density p of the vapor phase of the working fluid, and since the heat transport capacity of the loop is proportional to the density of the vapor phase (Q = pVS), it is possible to obtain instantaneously from the cold start of the loop a sufficient heat transport capacity to avoid a defusing of the evaporator and obtain and a good loop efficiency.
Pour conserver une performance d'évacuation thermique satisfaisante dans le cas thermique le plus contraint (température ambiante maximale et flux thermique maximale) , illustré par les points 64, il est nécessaire de prévoir un volume de la portion de gaz 7 suffisant au-dessus du volume de portion liquide Vmax.  To maintain a satisfactory thermal evacuation performance in the most constrained thermal case (maximum ambient temperature and maximum heat flow), illustrated by the points 64, it is necessary to provide a sufficient volume of the gas portion 7 over the volume of liquid portion Vmax.
De manière avantageuse, on pourra prévoir que le volume total 30 du réservoir est compris entre 1,3 et 2,5 fois ledit volume maximum Vmax de la portion liquide (cas du volume total maximum de phase liquide) . Ainsi la température de saturation Tsat, pour une température ambiante de 50 °C et un flux maximum Qmax, reste inférieure à 90°C ; ceci permet de continuer à prélever des calories à la source chaude 11.  Advantageously, it can be provided that the total volume of the tank is between 1.3 and 2.5 times the maximum volume Vmax of the liquid portion (case of the maximum total volume of liquid phase). Thus, the saturation temperature Tsat, for an ambient temperature of 50.degree. C. and a maximum flow Qmax, remains below 90.degree. this allows to continue to take calories at the hot spring 11.
S 'agissant du choix du gaz auxiliaire non condensable 8, ce gaz doit rester en phase vapeur dans toute la plage de fonctionnement de la boucle et notamment des conditions pression et température dans le réservoir, il doit avoir un point d'ébullition très bas ; de plus son coefficient de diffusion à l'intérieur des liquides et son coefficient d'Oswald doivent être également bas pour éviter que ce gaz auxiliaire ne s'infiltre à l'intérieur de la portion liquide 6 du réservoir et dans le reste de la boucle. Avantageusement, on pourra choisir l'hélium comme gaz auxiliaire. L'hélium est chimiquement neutre et sa disponibilité industrielle est satisfaisante. Cependant, il n'est pas exclu d'utiliser d'autres gaz comme l'azote, l'argon ou le néon. With regard to the choice of non-condensable auxiliary gas 8, this gas must remain in the vapor phase throughout the operating range of the loop and in particular the pressure and temperature conditions in the tank, it must have a very low boiling point; moreover, its diffusion coefficient inside the liquids and its Oswald coefficient must also be low in order to prevent this auxiliary gas from seeping inside the liquid portion 6 of the reservoir and in the rest of the loop. . Advantageously, helium can be chosen as an auxiliary gas. Helium is chemically neutral and its industrial availability is satisfactory. However, it is not excluded to use other gases such as nitrogen, argon or neon.
La figure 4 illustre un deuxième mode de réalisation de type thermosiphon, dans lequel on place le condenseur 2 au-dessus de 1 ' évaporateur 1 de manière à ce que la gravité conduise naturellement le liquide en direction de 1 ' évaporateur ; dans ces conditions le rôle du matériau poreux dans 1 ' évaporateur est de favoriser les échanges thermiques et la vaporisation plutôt que de réaliser la fonction de pompage capillaire proprement dit. Hormis la source du mouvement de liquide et la position relative des éléments qui diffèrent, tout le reste et notamment le principe de fonctionnement est identique au premier mode décrit plus haut, et ne sera donc pas répété.  FIG. 4 illustrates a second embodiment of the thermosiphon type, in which the condenser 2 is placed above the evaporator 1 so that the gravity naturally leads the liquid towards the evaporator; under these conditions, the role of the porous material in the evaporator is to promote heat exchange and vaporization rather than perform the actual capillary pumping function. Apart from the source of the liquid movement and the relative position of the elements that differ, everything else and in particular the operating principle is identical to the first mode described above, and will not be repeated.
Grâce à la pressurisation exercée par la présence du gaz auxiliaire 8, il est possible de s'affranchir de la présence d'un élément chauffant pour mettre en condition la boucle diphasique avant le démarrage thermique effectif.  Due to the pressurization exerted by the presence of the auxiliary gas 8, it is possible to overcome the presence of a heating element to condition the two-phase loop before the actual thermal start.
Il faut aussi remarquer qu'une telle boucle diphasique peut être dépourvue de régulation active, ce qui est un avantage déterminant en matière de fiabilité.  It should also be noted that such a two-phase loop can be devoid of active regulation, which is a decisive advantage in terms of reliability.
Avantageusement selon l'invention, le dispositif est dépourvu d'une quelconque pompe mécanique bien que l'invention n'exclut pas la présence d'une pompe mécanique d ' appoint .  Advantageously according to the invention, the device is devoid of any mechanical pump although the invention does not exclude the presence of a mechanical booster pump.
Il faut bien noter que les proportions des éléments sur les dessins ne sont pas forcément représentatives des proportions ou dimensions relatives des différents organes.  It should be noted that the proportions of the elements in the drawings are not necessarily representative of the proportions or relative dimensions of the various organs.
Les premier et second circuits de communication fluide 4,5 sont de préférence des conduites tubulaires, mais il pourrait s'agir d'autres types de conduites ou de canaux de communication fluides (conduites rectangulaires, flexibles, etc.)- De même, l'orifice d'entrée/sortie 31 pourrait se présenter comme une entrée et une sortie distinctes . The first and second fluid communication circuits 4,5 are preferably tubular conduits, but could be other types of fluid communication conduits or channels (rectangular conduits, flexible, etc.) - Similarly, the inlet / outlet port 31 could be a separate inlet and outlet.
La boucle diphasique peut être équipée avantageusement d'un clapet anti-retour 18 situé à l'entrée de chaque évaporateur de manière à accroître la puissance maximale de démarrage. En effet, le clapet anti-retour 18 empêche un retour de liquide en direction inverse au sens de circulation normal, et empêche ainsi un assèchement de 1 ' évaporateur au démarrage sous forte charge.  The two-phase loop may advantageously be equipped with a non-return valve 18 located at the inlet of each evaporator so as to increase the maximum starting power. Indeed, the non-return valve 18 prevents a return of liquid in the opposite direction to the normal flow direction, and thus prevents drying of the evaporator at startup under heavy load.
Dans une application soumise à la gravité, le clapet anti-retour peut être formé par un élément flottant rappelé par la poussée de flottaison contre une portée pour fermer le passage et ainsi empêcher un retour de liquide.  In an application subjected to gravity, the non-return valve may be formed by a floating element recalled by the buoyancy thrust against a bearing to close the passage and thus prevent a return of liquid.
On remarque que, avantageusement selon l'invention, le système à fluide diphasique présenté ici est entièrement auto adaptatif, il ne nécessite aucune loi de commande, aucun capteur. Il en résulte une conception particulièrement simple, une fabrication particulièrement simple, une absence de besoin de maintenance, et une fiabilité incomparable.  Note that, advantageously according to the invention, the two-phase fluid system presented here is fully self-adaptive, it requires no control law, no sensor. The result is a particularly simple design, particularly simple manufacturing, no need for maintenance, and incomparable reliability.

Claims

REVENDICATIONS
1. Dispositif de transfert thermique, dépourvu de régulation active, adapté pour extraire de la chaleur depuis une source chaude (11) et pour restituer cette chaleur à une source froide (12) au moyen d'un fluide de travail diphasique contenu dans un circuit général clos, comprenant : 1. Thermal transfer device, without active regulation, adapted to extract heat from a hot source (11) and to return this heat to a cold source (12) by means of a two-phase working fluid contained in a circuit general enclosed, comprising:
- au moins un évaporateur (1), ayant une entrée et une sortie, at least one evaporator (1), having an inlet and an outlet,
- au moins un condenseur (2), distinct et à distance de l 'évaporateur,  at least one condenser (2), distinct and at a distance from the evaporator,
- un réservoir (3) ayant un volume intérieur (30), avec une portion liquide (6) et une portion gaz (7) et au moins un orifice d'entrée/sortie (31) agencé au niveau de la portion liquide, le volume de la portion liquide pouvant varier entre un volume minimum (Vmin) et un volume maximum (Vmax) , a reservoir (3) having an interior volume (30), with a liquid portion (6) and a gas portion (7) and at least one inlet / outlet orifice (31) arranged at the level of the liquid portion, the volume of the liquid portion that can vary between a minimum volume (Vmin) and a maximum volume (Vmax),
- un premier circuit de communication (4), pour du fluide de travail essentiellement en phase vapeur, reliant la sortie de 1 ' évaporateur à une entrée du condenseur, a first communication circuit (4) for working fluid essentially in vapor phase, connecting the output of the evaporator to an inlet of the condenser,
- un deuxième circuit de communication (5), pour du fluide de travail essentiellement en phase liquide, reliant une sortie du condenseur au réservoir et à l'entrée de l 'évaporateur ,  a second communication circuit (5) for working fluid essentially in the liquid phase, connecting an outlet of the condenser to the tank and to the inlet of the evaporator,
caractérisé en ce que la portion gaz (7) du réservoir comprend la phase vapeur du fluide de travail avec une première pression partielle (PI) et un gaz auxiliaire non condensable (8) avec une deuxième pression partielle (P2), cette dernière étant ajustée pour permettre d'obtenir une pression totale supérieure ou égale à une pression minimale de fonctionnement prédéterminée requise lorsque la portion liquide dans l'entièreté du circuit général clos est à un volume total minimum. characterized in that the gas portion (7) of the reservoir comprises the vapor phase of the working fluid with a first partial pressure (PI) and a non-condensable auxiliary gas (8) with a second partial pressure (P2), the latter being adjusted to allow to obtain a total pressure greater than or equal to a predetermined minimum operating pressure required when the liquid portion in the entirety of the closed general circuit is at a minimum total volume.
2. Dispositif selon la revendication 1, dans lequel le gaz auxiliaire non condensable est de l'hélium. 2. Device according to claim 1, wherein the gas Non-condensable auxiliary is helium.
3. Dispositif selon l'une des revendications 1 à 2, dans lequel le fluide de travail est du méthanol.  3. Device according to one of claims 1 to 2, wherein the working fluid is methanol.
4. Dispositif selon l'une des revendications 1 à 3, dans lequel le volume total (30) du réservoir est compris entre 4. Device according to one of claims 1 to 3, wherein the total volume (30) of the reservoir is between
1,3 et 2,5 fois le volume maximum (Vmax) de la portion liquide . 1.3 and 2.5 times the maximum volume (Vmax) of the liquid portion.
5. Dispositif selon l'une des revendications 1 à 4, principalement soumis à la gravité terrestre, dans lequel l'orifice d'entrée est agencé au niveau d'un point bas du réservoir .  5. Device according to one of claims 1 to 4, mainly subjected to Earth's gravity, wherein the inlet port is arranged at a low point of the tank.
6. Dispositif selon l'une des revendications 1 à 4, principalement soumis à une micro-gravité, dans lequel le réservoir comprend une masse poreuse (9) agencée au moins au voisinage de l'orifice d'entrée.  6. Device according to one of claims 1 to 4, mainly subjected to a micro-gravity, wherein the reservoir comprises a porous mass (9) arranged at least in the vicinity of the inlet port.
7. Dispositif selon l'une des revendications 1 à 6, dans lequel 1 ' évaporateur comprend une masse microporeuse (10) adaptée pour assurer un pompage capillaire de fluide en phase liquide.  7. Device according to one of claims 1 to 6, wherein 1 'evaporator comprises a microporous mass (10) adapted to provide capillary pumping fluid in the liquid phase.
8. Dispositif selon l'une des revendications 1 à 5, principalement soumis à la gravité, dans lequel 1 ' évaporateur est placé en dessous du condenseur et du réservoir, de sorte que la gravité est utilisée pour déplacer le liquide vers 1 ' évaporateur . 8. Device according to one of claims 1 to 5, mainly subjected to gravity, wherein the evaporator is placed below the condenser and the reservoir, so that the gravity is used to move the liquid to the evaporator.
9. Dispositif selon l'une des revendications 1 à 8, dans lequel un clapet anti-retour (18) est agencé à l'entrée de 1 ' évaporateur (1). 9. Device according to one of claims 1 to 8, wherein a non-return valve (18) is arranged at the inlet of 1 evaporator (1).
EP14704781.5A 2013-02-14 2014-02-14 Heat transport device with diphasic fluid Active EP2956729B1 (en)

Applications Claiming Priority (2)

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FR1351282A FR3002028B1 (en) 2013-02-14 2013-02-14 DEVICE FOR TRANSPORTING HEAT WITH DIPHASIC FLUID
PCT/EP2014/052896 WO2014125064A1 (en) 2013-02-14 2014-02-14 Heat transport device with diphasic fluid

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JP (1) JP6351632B2 (en)
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FR3002028A1 (en) 2014-08-15
WO2014125064A1 (en) 2014-08-21
US20150369541A1 (en) 2015-12-24
FR3002028B1 (en) 2017-06-02
CN105074373B (en) 2020-10-16
JP6351632B2 (en) 2018-07-04
JP2016507043A (en) 2016-03-07
EP2956729B1 (en) 2018-09-05
US10234213B2 (en) 2019-03-19
ES2690339T3 (en) 2018-11-20
CN105074373A (en) 2015-11-18

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