CA2234403A1 - Capillary evaporator for diphasic loop of energy transfer between a hot source and a cold source - Google Patents
Capillary evaporator for diphasic loop of energy transfer between a hot source and a cold source Download PDFInfo
- Publication number
- CA2234403A1 CA2234403A1 CA002234403A CA2234403A CA2234403A1 CA 2234403 A1 CA2234403 A1 CA 2234403A1 CA 002234403 A CA002234403 A CA 002234403A CA 2234403 A CA2234403 A CA 2234403A CA 2234403 A1 CA2234403 A1 CA 2234403A1
- Authority
- CA
- Canada
- Prior art keywords
- enclosure
- evaporator
- tube
- heat
- chamber
- 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.)
- Abandoned
Links
- 239000007788 liquid Substances 0.000 claims abstract description 34
- 239000012530 fluid Substances 0.000 claims abstract description 24
- 239000011148 porous material Substances 0.000 claims abstract description 12
- 238000005192 partition Methods 0.000 claims description 17
- 239000000463 material Substances 0.000 claims description 7
- 230000005679 Peltier effect Effects 0.000 claims description 3
- 239000007787 solid Substances 0.000 claims description 3
- 239000004020 conductor Substances 0.000 claims description 2
- 238000007599 discharging Methods 0.000 claims description 2
- 239000007789 gas Substances 0.000 description 27
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 16
- 229910021529 ammonia Inorganic materials 0.000 description 8
- 230000008878 coupling Effects 0.000 description 4
- 238000010168 coupling process Methods 0.000 description 4
- 238000005859 coupling reaction Methods 0.000 description 4
- 238000001816 cooling Methods 0.000 description 3
- 230000005484 gravity Effects 0.000 description 3
- 229910052751 metal Inorganic materials 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 125000006850 spacer group Chemical group 0.000 description 3
- 239000007921 spray Substances 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000005507 spraying Methods 0.000 description 2
- 238000012360 testing method Methods 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 description 1
- 239000004698 Polyethylene Substances 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 229910010293 ceramic material Inorganic materials 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000001143 conditioned effect Effects 0.000 description 1
- 230000003750 conditioning effect Effects 0.000 description 1
- 238000000354 decomposition reaction Methods 0.000 description 1
- 238000003795 desorption Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 239000001257 hydrogen Substances 0.000 description 1
- 229910052739 hydrogen Inorganic materials 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 229920003023 plastic Polymers 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- -1 polyethylene Polymers 0.000 description 1
- 229920000573 polyethylene Polymers 0.000 description 1
- 230000037452 priming Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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
- F28D15/04—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
Abstract
The evaporator comprises a) a chamber (12) made of a porous material with an inlet for a heat exchanging fluid in liquid form, b) a shell (9) in which is located said chamber (12) to define around it, a chamber (15) for collecting said fluid in vapour form, said shell (9) having an outlet by which the vapour collected in said chamber (15) is evacuated. It further comprises a tube (22) which extends through the whole internal space of the chamber (12) with a porous wall, from one end (24) of the tube constituting the chamber (12) inlet for the heat exchanging fluid, said tube (22) being pierced over its whole length with holes (33) for injecting the heat exchanging liquid into the chamber (12) wall.
Description
' CAPILLARY EVAPORATOR FOR DIPHASIC LOOP OF ENERGY TRANSFER
BETWEEN A HOT SOURCE AND A COLD SOURCE.
The present invention concerns a capillary evaporator for a two-phase loop for transferring energy between a hot source and a cold source, of the typethat includes a) a porous material enclosure having an inlet for a heat-conducting fluid in the liquid state, and b) a jacket in which said enclosure is5 placed to define around the latter a chamber for collecting said fluid in the vapor state, said jacket having an outlet via which the vapor collected by said chamber is removed.
An evaporator of the above kind is known from French patent application No. 94 09459 filed 29 July 1994 by the applicant. Evaporators of 10 the above kind are part of two-phase loops such as that shown in figure 1 of the appended drawings, which is used to transfer thermal energy from a "hot source" area A to a "cold source" area B at a lower temperature. The loop takes the form of a closed circuit in which flows a heat-conducting fluid that can be water, ammonia, "Freon", etc, depending on the working temperatures. The 15 circuit includes "capillary" evaporators 1, 1', connected in parallel, condensers 2 also connected in parallel (or in series-parallel), a vapor flow pipe 3 and a liquid flow pipe 4. The direction of flow of the fluid is indicated by the arrows 5. An isolator 6 can be placed at the entry of each evaporator to preventaccidental return flow of vapor into the pipe 4. A supercooler 7 is placed on the pipe 4 to condense any vapor that is inadvertently not totally condensed at the outlet from the set of condensers 2 and to lower the temperature as a safetymeasure against the temperature locally reaching the saturation temperature leading to generation of bubbles of vapor on the upstream side of the evaporators.
The working temperature of the loop is controlled by a two-phase pressurizer storage container 8 mounted on the pipe 4. This storage container is controlled thermally (by means that are not shown) to control the evaporationtemperature.
With this type of loop it is possible in most cases to control the set point temperature for the hot source A to an accuracy better than 1~, regardlessof the power variations that the loop undergoes at the evaporators or condensers. The hot source can be equipment generating heat and installed on 5 a spacecraft or on the ground, for example, the loop maintaining the temperature of the equipment at a value compatible with its correct operation.
The maximal power that can be conveyed is conditioned by the maximum pressure rise that the capillary evaporators can produce and by the total head losses of the circuit for the maximal power in question. As described10 in the aforementioned French patent application, with ammonia pressure rises in the order of 5 000 Pa can be achieved.
- Figures 2 and 3 show an evaporator 1 suitable for use in the loop from figure 1. It is described in the document "Capillary pumped loop technology development" by J. Kroliczek and R. Mclntosh, ICES conference, LONG BEACH
15 (California), 1987. Evaporators of the above type are sold by the American company OAO.
The evaporator 1 includes a metal tubular jacket 9 that is a good conductor of heat with an inlet 10 at one end and an outlet 11 at the opposite end. A cylindrical enclosure 12 with porous material walls is held coaxially 20 inside the jacket 9 by spacers 13 (see figure 3).
The porous material, known as the "capillary wick", can be any material having substantially homogeneous pores of appropriate size, for example sintered metallic or plastics (polyethylene) or ceramic materials.
As explained in the aforementioned French patent application, to which 25 reference should be had for more detailed information, in normal operation the space 14 inside the enclosure 12 is filled with the heat-conducting fluid in theliquid state and the annular chamber 15 collects the vapor of this liquid which forms in the chamber due to the effect of the heat generated by the hot source A. The pressure of the vapor is higher than the pressure of the liquid, which 30 enables flow of the heat-conducting fluid in the loop and removal of the heat , conveyed towards the cold source B. The power of the installation is increased by disposing a plurality of evaporators in parallel, as shown in figure 1.
However, the heat-conducting fluid that flows in the loop is virtually never pure and often contains gases that cannot be condensed in the loop, such as 5 hydrogen. This gas can result from decomposition of the heat-conducting fluid when the latter is ammonia, for example. It can also result from chemical reactions between the ammonia and metallic parts of the loop made of aluminum, for example. In conditions of very low gravity, this incondensible gas can collect in a pocket 16 at the bottom of the enclosure 12, as shown in figure 2.
lo The space 14 inside the enclosure 12 can also contain bubbles 17 of uncondensed vapor of the heat-conducting fluid. This can cause local blocking of the flow of this fluid and therefore thermal runaway of the loop. If a portion of the capillary material constituting the wall of the enclosure 12, subject to the heat flow from the hot source A, is no longer directly supplied with the liquid from the interior of the enclosure, because of a pocket 16 of uncondensed or incondensible vapor or gas, the liquid contained in this portion of the capillary material evaporates quickly. A "punch-through" 18 appears in the enclosure 12 and the pressurized vapor then instantaneously fills the space 14 inside the enclosure 12, which blocks the flow of the heat-conducting fluid.
Figure 4 is a schematic representation of a different type of evaporator, as described in the document "Method of increase the evaporation reliability forloop heat pipes and capillary pumped loops" by E.Yu. Kotliarov, G.P. Serov, ICES conference, Colorado Springs, USA, 1994. Evaporators of the above type are sold by the Russian company Lavotchkin.
In figure 4 and subsequent figures of the appended drawings reference numbers identical to references used in figures 1 through 3 indicate members or units that are identical or similar.
The figure 4 evaporator differs from that of figures 2 and 3 in that it incorporates a buffer storage container 19 at the entry of the evaporator proper, which includes a jacket 9 and a porous material enclosure 12 similar to those of the evaporator from figure 2. The evaporator further includes a solid wall tube 20 passing axially through the pressurizer storage container 19 and the enclosure 12, this tube discharging at a point near the bottom of the enclosure.If the heat-conducting fluid arriving via the inlet 10 of the tube contains 5 incondensible bubbles 17 of gas or 17' of vapor, the bubbles pass through the tube 20 and return "countercurrentwise" into the storage container 19 without disrupting the operation of the porous wall of the enclosure 12, which is then not subject to any loss of priming.
On the other hand, because the evaporator from figure 4 incorporates lo its own pressurizer storage container 19, it becomes virtually impossible to dispose a plurality of such parallel evaporators in a loop like that of figure 1, any pressure imbalance between two reservoirs emptying one to fill the other.
Because of this the power that can be conveyed by the loop remains limited.
Figure 5 is a schematic representation of another type of evaporator as 15 described in the document "Test results of reliable and very high capillary multi-evaporation condensers loops" by S. Van 0st, M. Dubois and G.
Beckaert, ICES conference, San Diego, California, USA, 1995. Evaporators of the above type are sold by the Belgian company SABCA.
The evaporator is placed in one branch of a circuit that includes one 20 evaporator per branch, a common pressurizer storage container 8 feeding all the branches. Like the previous ones, the evaporator includes a jacket 9 and a porous wall enclosure 12. The reservoir 8 and the evaporator are connected by a tubular pipe lined with a "capillary coupling" 21 consisting of a woven metal tube. In normal operation the heat-conducting liquid reaching the condenser 2 25 passes through the pressurizer storage container 8 and fills all of the pipe 3 and the space inside the enclosure 12.
With incondensible gas in the loop but with no generation of vapor in the heart of the evaporator, a situation characteristic of operation at high thermal power (typically greater than 50 W for ammonia), the incondensible gas 30 accumulates in the enclosure 12 of the evaporator inside the capillary coupling , 21 only. The porous material of the enclosure 12 then continues to be supplied with the heat-conducting liquid, which assures operation of the evaporator.
In the presence of incondensible gas and with generation of vapor in the enclosure 12, a situation characteristic of operation at low thermal power, 5 the vapor that forms in the enclosure can, if the generating pressure is sufficiently high, return into the pressurizer storage container 8, as shown diagrammatically in figure 5, and entrain the incondensible gas. The liquid flows at the periphery of the capillary coupling 21 and feeds the porous material of the enclosure, which assures the operation of the evaporator.
It is then possible to place a plurality of evaporators in parallel and the resulting loop is highly resistant to the presence of incondensible gas or vaporin the porous enclosure 12 of the evaporators.
On the other hand, the capillary coupling 21 present in the evaporator feed pipes 3 make the latter rigid and bulky (diameter in the order of 10 mm), drawbacks which can become unacceptable when the loop must be disposed in a restricted space of complex shape, as is often the case in spacecraft, for example.
An aim of the present invention is therefore to provide an evaporator for a capillary pumped two-phase loop that tolerates the presence of incondensible vapor or gas inside its porous enclosure.
Another aim of the present invention is to provide an evaporator of this kind adapted to be integrated into a two-phase loop containing a plurality of such evaporators connected in parallel, the geometry of the loop being adaptable for installation in a space that is small and/or of complex shape.
These aims of the invention, and others that will become apparent on reading the following description, are achieved with an evaporator of the type described in the preamble to this description that is remarkable in that it includes a tube that extends throughout the space inside the porous wall enclosure from one end of the tube constituting the heat-conducting liquid inletof the enclosure, said tube having throughout its length holes for injecting theheat-conducting liquid into the wall of the enclosure.
As described in more detail below, in all circumstances this tube feeds all of the porous wall enclosure with heat-conducting liquid, which assures the necessary generation of vapor by the evaporator, even in the presence of uncondensed or incondensible vapor or gas in said enclosure.
Other features and advantages of the present invention will become apparent from a reading of the following description and an examination of the appended drawings, in which:
- figure 1 is a schematic representation of a two-phase energy transfer loop comprising capillary evaporators described in the preamble to this 1 0 description, - figures 2 through 5 represent prior art capillary evaporators also described in the preamble to this description, - figure 6 is a diagrammatic representation of a two-phase loop including at least one capillary evaporator in accordance with the present invention (shown in axial section), and - figures 7 through 9 are diagrammatic representations of the capillary evaporator of the invention similar to that of figure 6 and used to describe howit works.
Figure 6 of the appended drawings repeats the essential parts of the two-phase loop from figure 1, namely, in addition to one or more capillary evaporators 1, 1', 1", ... of the invention, gas and vapor pipes 3, 4, a condenser 2 and a pressurizer storage container 8.
The evaporator of the invention comprises, like the previous ones, a tubular jacket 9 and a porous wall enclosure 12 supported in the jacket 9 and spaced from the jacket by spacers such as the spacers 13 shown in figure 3 or by grooves formed on the inside face of the jacket 9, so as to define between the jacket and the enclosure a chamber 15 for collecting the vapor formed in the evaporator. The evaporator includes an inlet 10 for the heat-conducting fluid in the liquid state and an outlet 11 for the vapor of this fluid.
In accordance with one feature of the evaporator of the invention, the evaporator includes (see figure 6) a tube 22, of helical shape, for example, extending axially throughout the interior space of the enclosure 12, as far as the bottom of the latter. The tube 22 is closed at its end 22' near the bottom but has holes 23 in it throughout its length, for example regularly spaced holes.
The helical tube 22 is a substantial fit to the inside diameter of the enclosure 12 so that it closely follows the porous wall of the enclosure. The holes 23 face this wall so that heat-conducting liquid injected into the space 14 inside the enclosure 12 sprays this wall continuously, as explained below.
The open end 24 of the tube 22 passes through and is supported by an impermeable material partition 25 mounted transversely in a chamber 26 lo interposed in accordance with the invention between the inlet 10 of the evaporator and the combination of the jacket 9 and the enclosure 12. The partition 25 divides the chamber 26 into a first compartment (261, 262)/ see figure 7, and a second compartment 263 one of which (261, 262) contains a partition 27 of a porous material similar to that constituting the wall of the 15 enclosure 12. The partition 27 is transverse to the axis X of the evaporator and is therefore substantially parallel to the impermeable partition 26. It divides the first compartment (261, 262) into two sub-compartments 261 and 262.
In accordance with another feature of the present invention, means 28 for cooling the chamber 26 are mounted on the latter. As described below, the 20 means 28 are used to condense the heat-conducting fluid in the vapor state present in the chamber 26 in some modes of operation of the evaporator. To give an illustrative and non-limiting example, the means 28 can be a Peltier effect cold source. In this case a heat sink 29 can be disposed between the means 28 and the metal jacket 9.
The evaporator of the invention then operates as follows.
In the absence of incondensible gas and vapor in the enclosure or at the inlet of the evaporator, an ideal situation shown in figure 6, the heat-conducting liquid returning from the condenser 2 passes through the porous partition 27 and is then obliged to enter the perforated tube 22 extending into the heart of 30 the evaporator. The liquid sprays out of the holes 23 in the tube, injecting the heat-conducting liquid into the porous wall of the enclosure facing the holes.
The enclosure 12 of the evaporator is full of liquid and its porous wall is always supplied with liquid. The condenser means 28 are then of no utility and therefore inactive. The evaporator operates normally.
The operation of the evaporator in accordance with the invention with 5 incondensible gas bubbles 30 in the loop and with no vapor formed in the enclosure 12 will now be explained with reference to figure 7. This situation arises in high power operation of the evaporator (typically greater than 50 W for ammonia). In this case the incondensible gas bubbles 30 are stopped by the porous partition 27 at the inlet of the evaporator, as- shown in the figure.
10 However, in conditions of very low gravity, for example, a quantity of incondensible gas can accumulate in a portion 31 of the enclosure 12 by desorption of the gas dissolved in the liquid. Nevertheless, because of the perforated tube 22, the porous wall of the enclosure 12 continues to be wetted by the liquid, even in this portion 31 of the enclosure in which the 15 incondensible gas has accumulated. In this case the cold source 28 can remain inactive and the performance of the evaporator remains nominal.
The operation of the evaporator of the invention with incondensible gas bubbles 30 in the loop and with formation of vapor bubbles 32 in the enclosure 12 will now be described with reference to figure 8. This situation arises in operation 20 at low thermal power (typically less than 50 W for ammonia). In this case theporous partition 27 stops the incondensible gas 30 and the vapor 32 that enter the evaporator due to the effect of the flow of heat-conducting fluid. A quantity ofincondensible gas can nevertheless accumulate at 31 in the enclosure 12 as in the previous situation and the enclosure is assumed to contain also the vapor 32 that 25 forms therein, assumed to be in small quantities. Nevertheless, because of the perforated tube 22, the porous wall of the enclosure 12 continues to be wetted by the heat-conducting liquid, even in the portion 31 in which the incondensible gas and the vapor has accumulated. To prevent the vapor accumulating on the upstream side of the porous partition 27 covering all of the surface of the partition 30 and so preventing operation of the evaporator, the invention activates the Peltier effect cold source 28 to condense this vapor. Its cooling capacity must evidently be .
compatible with the power (which is nevertheless very low) needed to condense the total mass flowrate of vapor generated in the enclosure 12 of the evaporator and reaching the inlet of the latter. The typical cooling capacity required for an ammonia evaporator is in the order of a few watts, for example.
Figure 9 is a schematic representation of extreme operation of the evaporator of the invention when the enclosure 12 is filled with incondensible gas and vapor, only the perforated tube 22 remaining filled with the heat-conducting liquid for spraying onto the inside face of the porous wall of the enclosure 12, to assure operation of the evaporator. In this extreme case the lo power delivered by the cold source 28 is exactly equal to that needed to condense all of the uncondensed vapor impinging on the porous partition 27.
It is now apparent that the invention achieves the stated objectives, namely providing an evaporator that can be disposed in parallel with others in atwo-phase thermal energy transfer loop, unlike the prior art evaporator shown infigure 4. The evaporator of the invention is furthermore robust in the sense of tolerating generation of incondensible gas and vapor in the porous wall enclosure of the evaporator, unlike the evaporator shown in figures 2 and 3.
The connection of its inlet to a two-phase loop requires a simple flexible and non-rigid pipe, unlike the prior art evaporator shown in figure 5, which facilitates the integration of a loop of this kind into spaces that are small and/or of complex shape, as encountered in equipment of spacecraft.
Of course, the invention is not limited to the embodiments described and shown which have been given by way of example only. Thus the invention is not limited to applications in the thermal conditioning circuits of equipment for spacecraft and has applications in equipment operating on the ground. Further, the evaporator of the invention can be integrated into any type of capillary pumped two-phase loop, regardless of the level of the temperature to be regulated.
Equally, the evaporator of the invention can be modified to facilitate testing it on the ground. Under these conditions, if the evaporator is disposed vertically with its outlet at the top, gravity causes the liquid to collect at the bottom and the gas to collect at the top, both in the enclosure 12 and in the tube 22, the upper end of which is no longer supplied with heat-conducting liquid, the latter then no longer spraying the upper part of the enclosure 12. To avoid this problem, a straight solid wall tubè 33 can be placed in the enclosure12 (as shown in chain-dotted outline in figure 6) to allow the liquid entering the 5 enclosure to enter the helical tube through the end of the tube near the bottom of the enclosure. In this case, it is evidently the other end of the tube 22, near the partition 25, that is closed. Thus the heat-conducting liquid entering the tube 22 sprays the wall of the enclosure, including any pocket of incondensible ~ gas such as that shown at 31 in figure 7.
BETWEEN A HOT SOURCE AND A COLD SOURCE.
The present invention concerns a capillary evaporator for a two-phase loop for transferring energy between a hot source and a cold source, of the typethat includes a) a porous material enclosure having an inlet for a heat-conducting fluid in the liquid state, and b) a jacket in which said enclosure is5 placed to define around the latter a chamber for collecting said fluid in the vapor state, said jacket having an outlet via which the vapor collected by said chamber is removed.
An evaporator of the above kind is known from French patent application No. 94 09459 filed 29 July 1994 by the applicant. Evaporators of 10 the above kind are part of two-phase loops such as that shown in figure 1 of the appended drawings, which is used to transfer thermal energy from a "hot source" area A to a "cold source" area B at a lower temperature. The loop takes the form of a closed circuit in which flows a heat-conducting fluid that can be water, ammonia, "Freon", etc, depending on the working temperatures. The 15 circuit includes "capillary" evaporators 1, 1', connected in parallel, condensers 2 also connected in parallel (or in series-parallel), a vapor flow pipe 3 and a liquid flow pipe 4. The direction of flow of the fluid is indicated by the arrows 5. An isolator 6 can be placed at the entry of each evaporator to preventaccidental return flow of vapor into the pipe 4. A supercooler 7 is placed on the pipe 4 to condense any vapor that is inadvertently not totally condensed at the outlet from the set of condensers 2 and to lower the temperature as a safetymeasure against the temperature locally reaching the saturation temperature leading to generation of bubbles of vapor on the upstream side of the evaporators.
The working temperature of the loop is controlled by a two-phase pressurizer storage container 8 mounted on the pipe 4. This storage container is controlled thermally (by means that are not shown) to control the evaporationtemperature.
With this type of loop it is possible in most cases to control the set point temperature for the hot source A to an accuracy better than 1~, regardlessof the power variations that the loop undergoes at the evaporators or condensers. The hot source can be equipment generating heat and installed on 5 a spacecraft or on the ground, for example, the loop maintaining the temperature of the equipment at a value compatible with its correct operation.
The maximal power that can be conveyed is conditioned by the maximum pressure rise that the capillary evaporators can produce and by the total head losses of the circuit for the maximal power in question. As described10 in the aforementioned French patent application, with ammonia pressure rises in the order of 5 000 Pa can be achieved.
- Figures 2 and 3 show an evaporator 1 suitable for use in the loop from figure 1. It is described in the document "Capillary pumped loop technology development" by J. Kroliczek and R. Mclntosh, ICES conference, LONG BEACH
15 (California), 1987. Evaporators of the above type are sold by the American company OAO.
The evaporator 1 includes a metal tubular jacket 9 that is a good conductor of heat with an inlet 10 at one end and an outlet 11 at the opposite end. A cylindrical enclosure 12 with porous material walls is held coaxially 20 inside the jacket 9 by spacers 13 (see figure 3).
The porous material, known as the "capillary wick", can be any material having substantially homogeneous pores of appropriate size, for example sintered metallic or plastics (polyethylene) or ceramic materials.
As explained in the aforementioned French patent application, to which 25 reference should be had for more detailed information, in normal operation the space 14 inside the enclosure 12 is filled with the heat-conducting fluid in theliquid state and the annular chamber 15 collects the vapor of this liquid which forms in the chamber due to the effect of the heat generated by the hot source A. The pressure of the vapor is higher than the pressure of the liquid, which 30 enables flow of the heat-conducting fluid in the loop and removal of the heat , conveyed towards the cold source B. The power of the installation is increased by disposing a plurality of evaporators in parallel, as shown in figure 1.
However, the heat-conducting fluid that flows in the loop is virtually never pure and often contains gases that cannot be condensed in the loop, such as 5 hydrogen. This gas can result from decomposition of the heat-conducting fluid when the latter is ammonia, for example. It can also result from chemical reactions between the ammonia and metallic parts of the loop made of aluminum, for example. In conditions of very low gravity, this incondensible gas can collect in a pocket 16 at the bottom of the enclosure 12, as shown in figure 2.
lo The space 14 inside the enclosure 12 can also contain bubbles 17 of uncondensed vapor of the heat-conducting fluid. This can cause local blocking of the flow of this fluid and therefore thermal runaway of the loop. If a portion of the capillary material constituting the wall of the enclosure 12, subject to the heat flow from the hot source A, is no longer directly supplied with the liquid from the interior of the enclosure, because of a pocket 16 of uncondensed or incondensible vapor or gas, the liquid contained in this portion of the capillary material evaporates quickly. A "punch-through" 18 appears in the enclosure 12 and the pressurized vapor then instantaneously fills the space 14 inside the enclosure 12, which blocks the flow of the heat-conducting fluid.
Figure 4 is a schematic representation of a different type of evaporator, as described in the document "Method of increase the evaporation reliability forloop heat pipes and capillary pumped loops" by E.Yu. Kotliarov, G.P. Serov, ICES conference, Colorado Springs, USA, 1994. Evaporators of the above type are sold by the Russian company Lavotchkin.
In figure 4 and subsequent figures of the appended drawings reference numbers identical to references used in figures 1 through 3 indicate members or units that are identical or similar.
The figure 4 evaporator differs from that of figures 2 and 3 in that it incorporates a buffer storage container 19 at the entry of the evaporator proper, which includes a jacket 9 and a porous material enclosure 12 similar to those of the evaporator from figure 2. The evaporator further includes a solid wall tube 20 passing axially through the pressurizer storage container 19 and the enclosure 12, this tube discharging at a point near the bottom of the enclosure.If the heat-conducting fluid arriving via the inlet 10 of the tube contains 5 incondensible bubbles 17 of gas or 17' of vapor, the bubbles pass through the tube 20 and return "countercurrentwise" into the storage container 19 without disrupting the operation of the porous wall of the enclosure 12, which is then not subject to any loss of priming.
On the other hand, because the evaporator from figure 4 incorporates lo its own pressurizer storage container 19, it becomes virtually impossible to dispose a plurality of such parallel evaporators in a loop like that of figure 1, any pressure imbalance between two reservoirs emptying one to fill the other.
Because of this the power that can be conveyed by the loop remains limited.
Figure 5 is a schematic representation of another type of evaporator as 15 described in the document "Test results of reliable and very high capillary multi-evaporation condensers loops" by S. Van 0st, M. Dubois and G.
Beckaert, ICES conference, San Diego, California, USA, 1995. Evaporators of the above type are sold by the Belgian company SABCA.
The evaporator is placed in one branch of a circuit that includes one 20 evaporator per branch, a common pressurizer storage container 8 feeding all the branches. Like the previous ones, the evaporator includes a jacket 9 and a porous wall enclosure 12. The reservoir 8 and the evaporator are connected by a tubular pipe lined with a "capillary coupling" 21 consisting of a woven metal tube. In normal operation the heat-conducting liquid reaching the condenser 2 25 passes through the pressurizer storage container 8 and fills all of the pipe 3 and the space inside the enclosure 12.
With incondensible gas in the loop but with no generation of vapor in the heart of the evaporator, a situation characteristic of operation at high thermal power (typically greater than 50 W for ammonia), the incondensible gas 30 accumulates in the enclosure 12 of the evaporator inside the capillary coupling , 21 only. The porous material of the enclosure 12 then continues to be supplied with the heat-conducting liquid, which assures operation of the evaporator.
In the presence of incondensible gas and with generation of vapor in the enclosure 12, a situation characteristic of operation at low thermal power, 5 the vapor that forms in the enclosure can, if the generating pressure is sufficiently high, return into the pressurizer storage container 8, as shown diagrammatically in figure 5, and entrain the incondensible gas. The liquid flows at the periphery of the capillary coupling 21 and feeds the porous material of the enclosure, which assures the operation of the evaporator.
It is then possible to place a plurality of evaporators in parallel and the resulting loop is highly resistant to the presence of incondensible gas or vaporin the porous enclosure 12 of the evaporators.
On the other hand, the capillary coupling 21 present in the evaporator feed pipes 3 make the latter rigid and bulky (diameter in the order of 10 mm), drawbacks which can become unacceptable when the loop must be disposed in a restricted space of complex shape, as is often the case in spacecraft, for example.
An aim of the present invention is therefore to provide an evaporator for a capillary pumped two-phase loop that tolerates the presence of incondensible vapor or gas inside its porous enclosure.
Another aim of the present invention is to provide an evaporator of this kind adapted to be integrated into a two-phase loop containing a plurality of such evaporators connected in parallel, the geometry of the loop being adaptable for installation in a space that is small and/or of complex shape.
These aims of the invention, and others that will become apparent on reading the following description, are achieved with an evaporator of the type described in the preamble to this description that is remarkable in that it includes a tube that extends throughout the space inside the porous wall enclosure from one end of the tube constituting the heat-conducting liquid inletof the enclosure, said tube having throughout its length holes for injecting theheat-conducting liquid into the wall of the enclosure.
As described in more detail below, in all circumstances this tube feeds all of the porous wall enclosure with heat-conducting liquid, which assures the necessary generation of vapor by the evaporator, even in the presence of uncondensed or incondensible vapor or gas in said enclosure.
Other features and advantages of the present invention will become apparent from a reading of the following description and an examination of the appended drawings, in which:
- figure 1 is a schematic representation of a two-phase energy transfer loop comprising capillary evaporators described in the preamble to this 1 0 description, - figures 2 through 5 represent prior art capillary evaporators also described in the preamble to this description, - figure 6 is a diagrammatic representation of a two-phase loop including at least one capillary evaporator in accordance with the present invention (shown in axial section), and - figures 7 through 9 are diagrammatic representations of the capillary evaporator of the invention similar to that of figure 6 and used to describe howit works.
Figure 6 of the appended drawings repeats the essential parts of the two-phase loop from figure 1, namely, in addition to one or more capillary evaporators 1, 1', 1", ... of the invention, gas and vapor pipes 3, 4, a condenser 2 and a pressurizer storage container 8.
The evaporator of the invention comprises, like the previous ones, a tubular jacket 9 and a porous wall enclosure 12 supported in the jacket 9 and spaced from the jacket by spacers such as the spacers 13 shown in figure 3 or by grooves formed on the inside face of the jacket 9, so as to define between the jacket and the enclosure a chamber 15 for collecting the vapor formed in the evaporator. The evaporator includes an inlet 10 for the heat-conducting fluid in the liquid state and an outlet 11 for the vapor of this fluid.
In accordance with one feature of the evaporator of the invention, the evaporator includes (see figure 6) a tube 22, of helical shape, for example, extending axially throughout the interior space of the enclosure 12, as far as the bottom of the latter. The tube 22 is closed at its end 22' near the bottom but has holes 23 in it throughout its length, for example regularly spaced holes.
The helical tube 22 is a substantial fit to the inside diameter of the enclosure 12 so that it closely follows the porous wall of the enclosure. The holes 23 face this wall so that heat-conducting liquid injected into the space 14 inside the enclosure 12 sprays this wall continuously, as explained below.
The open end 24 of the tube 22 passes through and is supported by an impermeable material partition 25 mounted transversely in a chamber 26 lo interposed in accordance with the invention between the inlet 10 of the evaporator and the combination of the jacket 9 and the enclosure 12. The partition 25 divides the chamber 26 into a first compartment (261, 262)/ see figure 7, and a second compartment 263 one of which (261, 262) contains a partition 27 of a porous material similar to that constituting the wall of the 15 enclosure 12. The partition 27 is transverse to the axis X of the evaporator and is therefore substantially parallel to the impermeable partition 26. It divides the first compartment (261, 262) into two sub-compartments 261 and 262.
In accordance with another feature of the present invention, means 28 for cooling the chamber 26 are mounted on the latter. As described below, the 20 means 28 are used to condense the heat-conducting fluid in the vapor state present in the chamber 26 in some modes of operation of the evaporator. To give an illustrative and non-limiting example, the means 28 can be a Peltier effect cold source. In this case a heat sink 29 can be disposed between the means 28 and the metal jacket 9.
The evaporator of the invention then operates as follows.
In the absence of incondensible gas and vapor in the enclosure or at the inlet of the evaporator, an ideal situation shown in figure 6, the heat-conducting liquid returning from the condenser 2 passes through the porous partition 27 and is then obliged to enter the perforated tube 22 extending into the heart of 30 the evaporator. The liquid sprays out of the holes 23 in the tube, injecting the heat-conducting liquid into the porous wall of the enclosure facing the holes.
The enclosure 12 of the evaporator is full of liquid and its porous wall is always supplied with liquid. The condenser means 28 are then of no utility and therefore inactive. The evaporator operates normally.
The operation of the evaporator in accordance with the invention with 5 incondensible gas bubbles 30 in the loop and with no vapor formed in the enclosure 12 will now be explained with reference to figure 7. This situation arises in high power operation of the evaporator (typically greater than 50 W for ammonia). In this case the incondensible gas bubbles 30 are stopped by the porous partition 27 at the inlet of the evaporator, as- shown in the figure.
10 However, in conditions of very low gravity, for example, a quantity of incondensible gas can accumulate in a portion 31 of the enclosure 12 by desorption of the gas dissolved in the liquid. Nevertheless, because of the perforated tube 22, the porous wall of the enclosure 12 continues to be wetted by the liquid, even in this portion 31 of the enclosure in which the 15 incondensible gas has accumulated. In this case the cold source 28 can remain inactive and the performance of the evaporator remains nominal.
The operation of the evaporator of the invention with incondensible gas bubbles 30 in the loop and with formation of vapor bubbles 32 in the enclosure 12 will now be described with reference to figure 8. This situation arises in operation 20 at low thermal power (typically less than 50 W for ammonia). In this case theporous partition 27 stops the incondensible gas 30 and the vapor 32 that enter the evaporator due to the effect of the flow of heat-conducting fluid. A quantity ofincondensible gas can nevertheless accumulate at 31 in the enclosure 12 as in the previous situation and the enclosure is assumed to contain also the vapor 32 that 25 forms therein, assumed to be in small quantities. Nevertheless, because of the perforated tube 22, the porous wall of the enclosure 12 continues to be wetted by the heat-conducting liquid, even in the portion 31 in which the incondensible gas and the vapor has accumulated. To prevent the vapor accumulating on the upstream side of the porous partition 27 covering all of the surface of the partition 30 and so preventing operation of the evaporator, the invention activates the Peltier effect cold source 28 to condense this vapor. Its cooling capacity must evidently be .
compatible with the power (which is nevertheless very low) needed to condense the total mass flowrate of vapor generated in the enclosure 12 of the evaporator and reaching the inlet of the latter. The typical cooling capacity required for an ammonia evaporator is in the order of a few watts, for example.
Figure 9 is a schematic representation of extreme operation of the evaporator of the invention when the enclosure 12 is filled with incondensible gas and vapor, only the perforated tube 22 remaining filled with the heat-conducting liquid for spraying onto the inside face of the porous wall of the enclosure 12, to assure operation of the evaporator. In this extreme case the lo power delivered by the cold source 28 is exactly equal to that needed to condense all of the uncondensed vapor impinging on the porous partition 27.
It is now apparent that the invention achieves the stated objectives, namely providing an evaporator that can be disposed in parallel with others in atwo-phase thermal energy transfer loop, unlike the prior art evaporator shown infigure 4. The evaporator of the invention is furthermore robust in the sense of tolerating generation of incondensible gas and vapor in the porous wall enclosure of the evaporator, unlike the evaporator shown in figures 2 and 3.
The connection of its inlet to a two-phase loop requires a simple flexible and non-rigid pipe, unlike the prior art evaporator shown in figure 5, which facilitates the integration of a loop of this kind into spaces that are small and/or of complex shape, as encountered in equipment of spacecraft.
Of course, the invention is not limited to the embodiments described and shown which have been given by way of example only. Thus the invention is not limited to applications in the thermal conditioning circuits of equipment for spacecraft and has applications in equipment operating on the ground. Further, the evaporator of the invention can be integrated into any type of capillary pumped two-phase loop, regardless of the level of the temperature to be regulated.
Equally, the evaporator of the invention can be modified to facilitate testing it on the ground. Under these conditions, if the evaporator is disposed vertically with its outlet at the top, gravity causes the liquid to collect at the bottom and the gas to collect at the top, both in the enclosure 12 and in the tube 22, the upper end of which is no longer supplied with heat-conducting liquid, the latter then no longer spraying the upper part of the enclosure 12. To avoid this problem, a straight solid wall tubè 33 can be placed in the enclosure12 (as shown in chain-dotted outline in figure 6) to allow the liquid entering the 5 enclosure to enter the helical tube through the end of the tube near the bottom of the enclosure. In this case, it is evidently the other end of the tube 22, near the partition 25, that is closed. Thus the heat-conducting liquid entering the tube 22 sprays the wall of the enclosure, including any pocket of incondensible ~ gas such as that shown at 31 in figure 7.
Claims (9)
1. A capillary evaporator for two-phase loops for transferring energy between a hot source (A) and a cold source (B) of the type that includes a) a porous material enclosure (12) having an inlet for a heat-conducting fluid in the liquid state and b) a jacket (9) in which said enclosure (12) is placed to define, around the latter, a chamber (15) for collecting said fluid in the vapor state, said jacket (9) having an outlet through which the vapor collected by said chamber (15) is removed, characterized in that it includes a tube (22) that extends throughout the space (14) inside the porous wall enclosure (12) from one end (24) of the tube constituting the heat-conducting liquid inlet of the enclosure (12), said tube (22) having throughout its length holes (33) for injecting the heat-conducting liquid into the wall of the enclosure (12).
2. An evaporator according to claim 1 characterized in that it comprises a chamber (26) at the inlet of the porous wall enclosure (12), the chamber being divided into first (26 1, 26 2) and second (26 3) compartments by an impermeable material partition (25), the heat-conducting fluid entering the first compartment (26 1, 26 2) in the liquid state and entering the enclosure (12) via the inlet (24) of the perforated tube (22) that passes through said partition (25) and the second compartment (26 3).
3. An evaporator according to claim 2 characterized in that said first compartment (26 1, 26 2) is divided into first (26 1) and second (26 2) sub-compartments by a porous material partition (27) substantially parallel to the impermeable material partition (25), the inlets (10) of the first compartment and of the perforated tube (22) being on respective opposite sides of said porous material partition (27).
4. An evaporator according to claim 3 characterized in that it comprises means (28) for condensing any vapor of the heat-conducting fluid present in the first sub-compartment (26 1).
5. An evaporator according to claim 3 characterized in that said condenser means (28) are of the Peltier effect type.
6. An evaporator according to claim 5 characterized in that it comprises a heat sink (29) between said condenser means (28) and the jacket (9) of the evaporator, the jacket (9) being made of a material that is a good conductor of heat.
7. An evaporator according to any one of the preceding claims characterized in that the perforated tube (22) is helical in shape and is disposed near a cylindrical inside face of the porous wall of the enclosure (12), the holes (23) in said tube (22) discharging towards said wall and the end of the tube (22) opposite its fluid inlet end being closed.
8. An evaporator according to any one of claims 2 to 7 characterized in that the liquid entering the enclosure (12) passes first through a solid wall tube (33) connected at the other end to the perforated tube (22) near the bottom of the enclosure (12).
9. A two-phase loop for transferring energy between a hot source and a cold source comprising at least one capillary evaporator according to any one ofthe preceding claims.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FR9610110A FR2752291B1 (en) | 1996-08-12 | 1996-08-12 | HAIR EVAPORATOR FOR DIPHASIC LOOP OF TRANSFER OF ENERGY BETWEEN A HOT SOURCE AND A COLD SOURCE |
| FR9610110 | 1996-08-12 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2234403A1 true CA2234403A1 (en) | 1998-02-19 |
Family
ID=9494993
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002234403A Abandoned CA2234403A1 (en) | 1996-08-12 | 1997-08-08 | Capillary evaporator for diphasic loop of energy transfer between a hot source and a cold source |
Country Status (8)
| Country | Link |
|---|---|
| US (1) | US6058711A (en) |
| EP (1) | EP0855013B1 (en) |
| JP (1) | JPH11514081A (en) |
| CA (1) | CA2234403A1 (en) |
| DE (1) | DE69704105T2 (en) |
| ES (1) | ES2156398T3 (en) |
| FR (1) | FR2752291B1 (en) |
| WO (1) | WO1998006992A1 (en) |
Families Citing this family (52)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3450148B2 (en) * | 1997-03-07 | 2003-09-22 | 三菱電機株式会社 | Loop type heat pipe |
| FR2783313A1 (en) * | 1998-09-15 | 2000-03-17 | Matra Marconi Space France | HEAT TRANSFER DEVICE |
| JP2000241089A (en) * | 1999-02-19 | 2000-09-08 | Mitsubishi Electric Corp | Evaporator, heat sink, and system and method for transporting heat |
| KR100294317B1 (en) * | 1999-06-04 | 2001-06-15 | 이정현 | Micro-cooling system |
| US6189333B1 (en) * | 1999-07-26 | 2001-02-20 | Delphi Technologies, Inc. | Refrigerant filter for use in an automotive air conditioning system |
| US8047268B1 (en) | 2002-10-02 | 2011-11-01 | Alliant Techsystems Inc. | Two-phase heat transfer system and evaporators and condensers for use in heat transfer systems |
| US7251889B2 (en) * | 2000-06-30 | 2007-08-07 | Swales & Associates, Inc. | Manufacture of a heat transfer system |
| US8136580B2 (en) | 2000-06-30 | 2012-03-20 | Alliant Techsystems Inc. | Evaporator for a heat transfer system |
| US7931072B1 (en) | 2002-10-02 | 2011-04-26 | Alliant Techsystems Inc. | High heat flux evaporator, heat transfer systems |
| WO2002002201A2 (en) * | 2000-06-30 | 2002-01-10 | Swales Aerospace | Phase control in the capillary evaporators |
| US8109325B2 (en) | 2000-06-30 | 2012-02-07 | Alliant Techsystems Inc. | Heat transfer system |
| US7549461B2 (en) | 2000-06-30 | 2009-06-23 | Alliant Techsystems Inc. | Thermal management system |
| US7004240B1 (en) * | 2002-06-24 | 2006-02-28 | Swales & Associates, Inc. | Heat transport system |
| US7708053B2 (en) * | 2000-06-30 | 2010-05-04 | Alliant Techsystems Inc. | Heat transfer system |
| US6843308B1 (en) | 2000-12-01 | 2005-01-18 | Atmostat Etudes Et Recherches | Heat exchanger device using a two-phase active fluid, and a method of manufacturing such a device |
| US7200161B2 (en) * | 2001-01-22 | 2007-04-03 | The Boeing Company | Side-pumped solid-state disk laser for high-average power |
| US6625193B2 (en) * | 2001-01-22 | 2003-09-23 | The Boeing Company | Side-pumped active mirror solid-state laser for high-average power |
| US6768751B2 (en) | 2002-06-17 | 2004-07-27 | The Boeing Company | Methods and apparatus for removing heat from a lasing medium of a solid-state laser assembly |
| BR0315812A (en) * | 2002-10-28 | 2005-09-13 | Swales & Associates Inc | Heat transfer system, thermodynamic system and method of using the systems |
| CN100449244C (en) * | 2002-10-28 | 2009-01-07 | 斯沃勒斯联合公司 | Heat transfer system |
| US6941761B2 (en) * | 2003-06-09 | 2005-09-13 | Tecumseh Products Company | Thermoelectric heat lifting application |
| TW592033B (en) * | 2003-10-20 | 2004-06-11 | Konglin Construction & Mfg Co | Heat transfer device and manufacturing method thereof |
| US6926072B2 (en) * | 2003-10-22 | 2005-08-09 | Thermal Corp. | Hybrid loop heat pipe |
| AU2004286255B2 (en) * | 2003-10-28 | 2010-04-08 | Northrop Grumman Systems Corporation | Manufacture of a heat transfer system |
| US6990816B1 (en) * | 2004-12-22 | 2006-01-31 | Advanced Cooling Technologies, Inc. | Hybrid capillary cooling apparatus |
| CN100344918C (en) * | 2005-05-26 | 2007-10-24 | 王双玲 | Dedicated evaporation cavity of semiconductor electronic refrigerator, and preparation method |
| JP2007107784A (en) * | 2005-10-12 | 2007-04-26 | Fujikura Ltd | Loop type heat pipe |
| US7661464B2 (en) * | 2005-12-09 | 2010-02-16 | Alliant Techsystems Inc. | Evaporator for use in a heat transfer system |
| US7748436B1 (en) | 2006-05-03 | 2010-07-06 | Advanced Cooling Technologies, Inc | Evaporator for capillary loop |
| JP2008008512A (en) * | 2006-06-27 | 2008-01-17 | Fujikura Ltd | Loop-type heat pipe |
| AT507187B1 (en) | 2008-10-23 | 2010-03-15 | Helmut Dr Buchberger | INHALER |
| JP5676205B2 (en) * | 2010-10-26 | 2015-02-25 | 株式会社 正和 | Loop heat pipe and manufacturing method thereof |
| CN102032821A (en) * | 2010-11-17 | 2011-04-27 | 上海彩耀新能源投资发展有限公司 | Loop heat pipe radiator |
| HUE026804T2 (en) | 2011-02-11 | 2016-07-28 | Batmark Ltd | Inhaler component |
| AT510837B1 (en) | 2011-07-27 | 2012-07-15 | Helmut Dr Buchberger | INHALATORKOMPONENTE |
| KR101953201B1 (en) | 2011-09-06 | 2019-02-28 | 브리티시 아메리칸 토바코 (인베스트먼츠) 리미티드 | Heating smokeable material |
| EP3892125A3 (en) | 2011-09-06 | 2022-01-05 | Nicoventures Trading Limited | Heating smokable material |
| FR2979981B1 (en) * | 2011-09-14 | 2016-09-09 | Euro Heat Pipes | CAPILLARY PUMP HEAT DELIVERY DEVICE |
| JP5741354B2 (en) * | 2011-09-29 | 2015-07-01 | 富士通株式会社 | Loop heat pipe and electronic equipment |
| GB201207039D0 (en) | 2012-04-23 | 2012-06-06 | British American Tobacco Co | Heating smokeable material |
| WO2014102402A1 (en) * | 2012-12-28 | 2014-07-03 | Ibérica Del Espacio, S.A. | Loop heat pipe apparatus for heat transfer and thermal control |
| GB201407426D0 (en) | 2014-04-28 | 2014-06-11 | Batmark Ltd | Aerosol forming component |
| GB2533135B (en) | 2014-12-11 | 2020-11-11 | Nicoventures Holdings Ltd | Aerosol provision systems |
| GB201511349D0 (en) | 2015-06-29 | 2015-08-12 | Nicoventures Holdings Ltd | Electronic aerosol provision systems |
| US20170055584A1 (en) | 2015-08-31 | 2017-03-02 | British American Tobacco (Investments) Limited | Article for use with apparatus for heating smokable material |
| US11924930B2 (en) | 2015-08-31 | 2024-03-05 | Nicoventures Trading Limited | Article for use with apparatus for heating smokable material |
| BR112018071824B1 (en) | 2016-04-27 | 2023-01-10 | Nicoventures Trading Limited | SUB-ASSEMBLY, SYSTEM, METHOD FOR MANUFACTURING A VAPORIZER AND ELECTRONIC STEAM DELIVERY DEVICE |
| US10948238B2 (en) * | 2017-11-29 | 2021-03-16 | Roccor, Llc | Two-phase thermal management devices, systems, and methods |
| CN108089618B (en) * | 2017-12-11 | 2019-06-18 | 北京空间机电研究所 | A kind of energy-saving temperature control loop circuit heat pipe device of space flight optical remote sensor |
| JP7390252B2 (en) | 2020-05-12 | 2023-12-01 | 新光電気工業株式会社 | loop heat pipe |
| WO2022183793A1 (en) * | 2021-03-01 | 2022-09-09 | 苏州圣荣元电子科技有限公司 | Thin plate type loop heat pipe |
| CN113446888B (en) * | 2021-06-30 | 2022-05-20 | 华中科技大学 | Multi-evaporator flat-plate loop heat pipe system suitable for long-distance heat transfer |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4352392A (en) * | 1980-12-24 | 1982-10-05 | Thermacore, Inc. | Mechanically assisted evaporator surface |
| US4467861A (en) * | 1982-10-04 | 1984-08-28 | Otdel Fiziko-Tekhnicheskikh Problem Energetiki Uralskogo Nauchnogo Tsentra Akademii Nauk Sssr | Heat-transporting device |
| DE3431240A1 (en) * | 1984-08-24 | 1986-03-06 | Michael 4150 Krefeld Laumen | REFRIGERATION MACHINE OR HEAT PUMP AND JET PUMP HERE |
| DE3526574C1 (en) * | 1985-07-25 | 1987-03-26 | Dornier System Gmbh | Capillary supported evaporator |
| US4791634A (en) * | 1987-09-29 | 1988-12-13 | Spectra-Physics, Inc. | Capillary heat pipe cooled diode pumped slab laser |
| DE3810128C1 (en) * | 1988-03-25 | 1989-09-07 | Erno Raumfahrttechnik Gmbh, 2800 Bremen, De | |
| US4869313A (en) * | 1988-07-15 | 1989-09-26 | General Electric Company | Low pressure drop condenser/evaporator pump heat exchanger |
| US4957157A (en) * | 1989-04-13 | 1990-09-18 | General Electric Co. | Two-phase thermal control system with a spherical wicked reservoir |
| FR2723187B1 (en) * | 1994-07-29 | 1996-09-27 | Centre Nat Etd Spatiales | ENERGY TRANSFER SYSTEM BETWEEN A HOT SOURCE AND A COLD SOURCE |
| US5725049A (en) * | 1995-10-31 | 1998-03-10 | The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration | Capillary pumped loop body heat exchanger |
-
1996
- 1996-08-12 FR FR9610110A patent/FR2752291B1/en not_active Expired - Fee Related
-
1997
- 1997-08-08 CA CA002234403A patent/CA2234403A1/en not_active Abandoned
- 1997-08-08 DE DE69704105T patent/DE69704105T2/en not_active Expired - Lifetime
- 1997-08-08 JP JP10509452A patent/JPH11514081A/en active Pending
- 1997-08-08 EP EP97936757A patent/EP0855013B1/en not_active Expired - Lifetime
- 1997-08-08 ES ES97936757T patent/ES2156398T3/en not_active Expired - Lifetime
- 1997-08-08 WO PCT/FR1997/001470 patent/WO1998006992A1/en active IP Right Grant
-
1998
- 1998-04-10 US US09/058,516 patent/US6058711A/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH11514081A (en) | 1999-11-30 |
| WO1998006992A1 (en) | 1998-02-19 |
| ES2156398T3 (en) | 2001-06-16 |
| EP0855013B1 (en) | 2001-02-21 |
| US6058711A (en) | 2000-05-09 |
| FR2752291B1 (en) | 1998-09-25 |
| DE69704105D1 (en) | 2001-03-29 |
| FR2752291A1 (en) | 1998-02-13 |
| DE69704105T2 (en) | 2001-08-02 |
| EP0855013A1 (en) | 1998-07-29 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US6058711A (en) | Capillary evaporator for diphasic loop of energy transfer between a hot source and a cold source | |
| US9273887B2 (en) | Evaporators for heat transfer systems | |
| US8109325B2 (en) | Heat transfer system | |
| US4934160A (en) | Evaporator, especially for discharging waste heat | |
| US4470450A (en) | Pump-assisted heat pipe | |
| US6810946B2 (en) | Loop heat pipe method and apparatus | |
| US4217765A (en) | Heat exchanger-accumulator | |
| EP1957925B1 (en) | Heat transfer system with evaporator | |
| US3661202A (en) | Heat transfer apparatus with improved heat transfer surface | |
| US4770238A (en) | Capillary heat transport and fluid management device | |
| JP4033699B2 (en) | Loop thermosyphon and Stirling refrigerator | |
| US20040206479A1 (en) | Heat transfer system | |
| US4576009A (en) | Heat transmission device | |
| CN104040280B (en) | Cooling device | |
| US4492266A (en) | Manifolded evaporator for pump-assisted heat pipe | |
| JPH10503580A (en) | Energy transfer system between hot and cold heat sources | |
| EP0806620A2 (en) | Capillary evaporator | |
| US3677336A (en) | Heat link, a heat transfer device with isolated fluid flow paths | |
| US4372126A (en) | Closed cycle system for generating usable energy from waste heat sources | |
| EP1549897B1 (en) | Evaporator for a heat transfer system | |
| WO2004040218A9 (en) | Heat transfer system | |
| JP5060785B2 (en) | Heat transfer system manufacturing | |
| JP2023536287A (en) | Thermal energy storage and recovery system and method | |
| CN107208980A (en) | Loop circuit heat pipe with satellite-type evaporator | |
| RU2755365C1 (en) | Vaporizer |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| FZDE | Discontinued |