EP3446054A1 - Procede pour refroidir ou chauffer un fluide dans une enceinte thermique au moyen d'un generateur thermique magnetocalorique et installation thermique mettant en oeuvre ledit procede - Google Patents
Procede pour refroidir ou chauffer un fluide dans une enceinte thermique au moyen d'un generateur thermique magnetocalorique et installation thermique mettant en oeuvre ledit procedeInfo
- Publication number
- EP3446054A1 EP3446054A1 EP17718029.6A EP17718029A EP3446054A1 EP 3446054 A1 EP3446054 A1 EP 3446054A1 EP 17718029 A EP17718029 A EP 17718029A EP 3446054 A1 EP3446054 A1 EP 3446054A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- thermal
- temperature
- secondary fluid
- fluid
- heat exchanger
- 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.)
- Withdrawn
Links
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
- F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
- F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2321/00—Details of machines, plants or systems, using electric or magnetic effects
- F25B2321/002—Details of machines, plants or systems, using electric or magnetic effects by using magneto-caloric effects
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
- F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
- F25D2317/065—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the air return
- F25D2317/0651—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the air return through the bottom
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
- F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
- F25D2317/066—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the air supply
- F25D2317/0665—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the air supply from the top
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
- F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
- F25D2317/067—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by air ducts
- F25D2317/0671—Inlet ducts
Definitions
- the present invention relates to a method for cooling or heating a fluid, said secondary fluid, in a thermal chamber by means of a magnetocaloric heat generator connected to said thermal enclosure by at least one heat exchanger in which a heat exchange takes place between a primary fluid circulating in said magnetocaloric heat generator and a secondary fluid circulating in said thermal chamber, the secondary fluid flowing in said thermal chamber between at least one injection port located in the thermal chamber and through which the secondary fluid leaves the heat exchanger by a secondary outlet for entering the thermal chamber at a first temperature, and at least one suction mouth located in the thermal chamber and through which the secondary fluid leaves said thermal chamber at a second temperature, different from the first temperature, to enter in the heat exchanger by a secondary entrance.
- the present invention also relates to a thermal installation implementing the method as defined above.
- Prior art :
- heat generators are traditionally used, in the form of heat pumps, compressors, or the like, which mainly use a primary phase-change fluid subjected to compression cycles. relaxation.
- the boiling and condensing temperature of the primary fluid is solely dependent on the working pressure, and totally independent of the ambient temperature or the temperature of the secondary fluid.
- the temperatures of the primary fluid of the hot side of the generator (after compression) and the cold side of the generator (after expansion) in this type of application are constant and independent of the temperature of the secondary fluid to be heated or cooled.
- This property generally leads to the configuration of the heat exchanger between the primary circuit and the secondary circuit so as to have the highest possible temperature difference between the inlet temperature of the primary and secondary fluids in said heat exchanger in order to maximize the temperature.
- heat exchange since the thermal power exchanged between the primary circuit and the secondary circuit is directly proportional to the temperature difference between the primary fluid and the secondary fluid.
- the secondary fluid when it is desired to cool a secondary fluid in a thermal chamber, the secondary fluid is commonly extracted in the zone of the thermal chamber where the temperature of the secondary fluid is the hottest, in accordance with the refrigerator described in the WO publication. 2016/036005 Al cited as an example.
- the secondary fluid is commonly extracted in the zone of the thermal enclosure where the temperature of the secondary fluid is the coldest.
- the publication US 2015/323237 A1 describes a deep freezer in which the cooling unit, consisting of a conventional compressor and an evaporator, is arranged in the lower part of the thermal chamber.
- the goal is to maintain a temperature in the thermal enclosure as uniform and stable as possible. There is therefore no colder zone than another, the temperature being exactly the same. There is even a heating device in the cold air supply duct to prevent the temperature from descending too quickly in the freezer.
- a thermal generator magnetocaloric effect as shown in the publications FR 2 861 455 and US 6,453,677, the traditional configuration mentioned above is not advantageous and even counterproductive.
- the magnetocaloric material undergoes a temperature variation ( ⁇ adiabatic temperature delta) which makes it possible to cool the primary fluid entering said generator on the warm side of the generator and to heat the primary fluid returning to the cold side of the generator . If the temperature difference between the incoming primary fluid and the primary fluid leaving said generator is substantially equal to or greater than the magnetocaloric effect of said material (adiabatic ⁇ ), the magnetocaloric heat generator no longer has the capacity to reset the temperature of the fluid. primary exiting at the same level as the previous magnetic cycle, resulting in degradation of the temperature gradient generated by the magnetocaloric heat generator.
- the temperature of the primary fluid leaving the generator is generally equal to the Curie temperature. If the temperature of the primary fluid entering said generator is significantly different from that of the primary fluid leaving said generator, the incoming primary fluid will place the active magnetocaloric material at a temperature away from its Curie temperature thereby decreasing the magnetocaloric effect that can generate said material.
- the cooling or heating dynamics intrinsically associated with the magnetocaloric effect, will be slower as the temperature difference between the outgoing primary fluid and the primary fluid entering said magnetocaloric heat generator will be high.
- This phenomenon is particularly noticeable at the start of a thermal installation when a large temperature differential exists between the primary fluid of the magnetocaloric heat generator and the secondary fluid to be cooled or heated contained in a thermal enclosure. This large difference in temperature induces a return temperature of the primary fluid to the magnetocaloric heat generator significantly different from its outlet temperature.
- the temperature of the primary fluid entering the magnetocaloric heat generator is closely dependent on the temperature of the secondary fluid leaving the thermal chamber and entering the heat exchanger in which it will transfer its calories or frigories to the primary fluid by conduction. Therefore, if it is desired to minimize the temperature difference between the primary fluid entering the generator and the primary fluid leaving the generator, it is imperative to minimize the temperature difference between the secondary fluid leaving the thermal chamber and the secondary fluid entering the thermal chamber, which amounts to limiting the temperature difference between the primary and secondary fluids entering the heat exchanger.
- the present invention aims to overcome these drawbacks by proposing a method and a thermal installation using a magnetocaloric heat generator to achieve satisfactory thermal performance to cool or heat the fluid of a thermal chamber, whatever the secondary fluid used in said thermal enclosure and the type of thermal enclosure concerned, minimizing the temperature difference between the secondary fluid leaving the thermal chamber and the secondary fluid entering the thermal chamber to minimize the temperature difference between the fluid primary input into the generator and the primary fluid exiting said generator, thereby reducing the time of establishment of the temperature gradient of said magnetocaloric heat generator at startup and maintain this temperature gradient at an optimum level throughout its operation, said method and said installation requiring few modifications to achieve said result, simply, efficiently, reliably and cheaply.
- the invention relates to a method of the kind indicated in the preamble, characterized in that it identifies a sampling zone inside the thermal chamber in which the temperature of the secondary fluid is coldest when it is desired to cool said secondary fluid, or in which the temperature of the secondary fluid is the hottest when it is desired to heat said secondary fluid, and said at least one suction mouth is positioned in said sampling zone to withdraw said fluid secondary to a second temperature as close as possible to the first temperature of the secondary fluid in order to limit the difference in temperature between the secondary fluid entering the heat exchanger with respect to the secondary fluid leaving said heat exchanger, and consequently limiting the temperature difference between the primary fluid entering the magnetocaloric heat generator and the fluid primary output of said magnetocaloric heat generator.
- the process according to the invention goes against a prejudice according to which, in order to achieve the most optimal thermal exchange possible, preference is given to the largest possible temperature difference between a primary fluid circulating in a heat generator and a fluid.
- secondary circulating in a thermal chamber necessarily involving taking the secondary fluid inside the enclosure thermal in a sampling zone where the temperature of the secondary fluid is the hottest when one wants to cool the secondary fluid, or the coldest when one wants to heat the secondary fluid.
- the sampling zone can be identified inside said thermal enclosure by using the natural phenomenon of thermal stratification in which the temperature of the secondary fluid is the coldest in the lower part. the thermal enclosure and the hottest in the upper part of the thermal enclosure.
- a development phase of said method it is possible to identify the sampling zone inside said thermal enclosure by instrumenting said thermal chamber with temperature sensors.
- this development phase of said method it is also possible to determine the position of said at least one injection port and said at least one suction port in the thermal chamber to optimize the circulation of the secondary fluid to the inside said thermal enclosure.
- this part of the deflected flow may be between 5 and 40%, and preferably between 5 and 20%, of the incoming flow of the secondary fluid at the first temperature.
- the invention relates to an installation of the kind indicated in the preamble, characterized in that the suction mouth is disposed inside said thermal chamber in a sampling zone in which the temperature of the secondary fluid is the colder when said thermal plant is used to cool a said secondary fluid, or in which the temperature of the secondary fluid is the hottest when said thermal plant is used to heat a said secondary fluid, to withdraw the secondary fluid at a second temperature the as close as possible to the first temperature of the secondary fluid, in order to limit the temperature difference between the secondary fluid entering the heat exchanger and the secondary fluid leaving said heat exchanger, and consequently to limit the difference in temperature between the primary fluid entering the said generator magnetocaloric material and the primary fluid exiting said magnetocaloric heat generator.
- said at least one suction mouth is disposed in a lower part of said thermal chamber given the natural phenomenon of thermal stratification.
- said at least one suction mouth is disposed in a portion high of said thermal chamber given the natural phenomenon of thermal stratification.
- the thermal enclosure may comprise at least one bypass duct extending between said secondary outlet and said secondary inlet of said heat exchanger and arranged to directly deflect a portion of the incoming flow of the secondary fluid at the first temperature and reinject it at the secondary inlet of said heat exchanger.
- the thermal enclosure may alternatively comprise at least one bypass orifice disposed in the thermal enclosure at the secondary outlet of said heat exchanger and arranged to indirectly deflect a portion of the incoming flow of the secondary fluid at the first temperature and reinject it at the inlet secondary of said heat exchanger.
- Said at least one bypass duct or said at least one bypass orifice may be arranged to deflect a portion of between 5 and 40%, and preferably between 5 and 20%, of the incoming flow of the secondary fluid at the first temperature.
- FIGS. 1A and 1B are diagrammatic axial sectional views of a first thermal installation according to the invention for an application for cooling a secondary fluid gas in a thermal enclosure, using thermal gravity and direct bypass respectively, and thermal gravity only, the heat exchanger being located in the upper part of the thermal enclosure to be cooled,
- FIGS. 2A, 2B and 2C are diagrammatic axial sectional views of a second thermal installation for an application for heating a secondary fluid gas in a thermal enclosure, using thermal gravity and a direct bypass respectively, thermal gravity and an indirect bypass, and thermal gravity alone, the heat exchanger being located in the upper part of the thermal enclosure to be heated,
- FIGS. 3A and 3B are diagrammatic axial sectional views of a third thermal installation according to the invention for an application for heating a secondary fluid gas in a thermal enclosure, using thermal gravity and a direct bypass respectively, and the thermal gravity alone, the heat exchanger being located in the lower part of the thermal enclosure to be heated,
- FIGS. 4A, 4B and 4C are diagrammatic axial section views of a fourth thermal installation for an application for cooling a secondary fluid gas in a thermal enclosure, using thermal gravity and a direct bypass respectively, thermal gravity, and an indirect bypass, and the thermal gravity alone, the heat exchanger being situated in the lower part of the thermal enclosure to be cooled,
- FIGS. 5A and 5B are diagrammatic axial section views of a fifth thermal installation according to the invention for an application of cooling a secondary fluid gas in a thermal enclosure, using thermal gravity and a direct bypass respectively, and the thermal gravity alone, the heat exchanger being located on one side of the thermal enclosure to be cooled,
- FIGS. 6A and 6B are diagrammatic axial section views of a sixth thermal installation according to the invention for an application for heating a secondary fluid gas in a thermal chamber, using gravity respectively. thermal and a direct bypass, and thermal gravity alone, the heat exchanger being located on one side of the thermal chamber to be heated,
- FIGS. 7A and 7B are diagrammatic axial sectional views of a seventh thermal installation according to the invention for an application of cooling a liquid secondary fluid in a thermal enclosure, using thermal gravity and a direct bypass respectively, and thermal gravity alone, the heat exchanger being located laterally to the thermal enclosure to be cooled, and
- FIGS. 8A and 8B are diagrammatic axial section views of an eighth thermal installation according to the invention for an application for heating a secondary fluid gas in a thermal enclosure, using thermal gravity and a direct bypass respectively, and thermal gravity alone, the heat exchanger being located laterally to the thermal chamber to be heated. Illustrations of the invention and different ways of making it:
- the invention relates to a method and a thermal installation 10-80 for cooling or heating a fluid in a thermal chamber 11-81, called secondary fluid FS.
- the thermal installation 10-80 implements a magnetocaloric thermal generator 1 arranged to produce thermal energy, such as for example that described in the publication WO 2015/079313 A1.
- a magnetocaloric thermal generator 1 arranged to produce thermal energy, such as for example that described in the publication WO 2015/079313 A1.
- This example is of course not limiting. and any other magnetocaloric heat generator 1 may be suitable.
- the magnetocaloric heat generator 1 will not be described in detail in the present application.
- it comprises in known manner at least one thermal stage comprising magnetocaloric materials arranged on a support, a magnetic arrangement arranged to subject said magnetocaloric materials to a magnetic field variation, and at least one coolant circuit, called primary fluid.
- the primary fluid FP is preferably a liquid such as water, mixed or not with one or more additives depending on the applications and the working temperature.
- the magnetocaloric effect (EMC) of magnetocaloric materials consists of a variation of their temperature when they are subjected to a magnetic field variation.
- This magnetocaloric effect therefore depends on the magnetocaloric material and therefore on its Curie temperature, the magnetic field applied to said material and the working temperature of said material. It is thus sufficient to subject these magnetocaloric materials to a succession of magnetic cycles comprising alternating phases. magnetization and demagnetization phases, and to achieve a heat exchange with a heat transfer fluid passing through said materials from one side to achieve the widest possible temperature variation between the hot and cold ends of said materials.
- the temperature difference between the cold end and the hot end of the magnetocaloric materials, or between the cold side and the hot side of the generator, is commonly referred to as the "temperature gradient" of the magnetocaloric heat generator.
- the magnetic cycle is repeated up to frequencies of several Hertz. The efficiency of such a cycle of refrigeration or magnetic heating surpasses by about 30% that of a conventional refrigeration or heating cycle.
- the thermal installation 10-80 implements two heat exchangers 2, 3, one connected to the cold side and the other connected to the hot side of the magnetocaloric heat generator 1.
- one of the heat exchangers 2 is a cold or hot exchanger connecting the cold or hot side of the magnetocaloric heat generator 1 to the thermal enclosure 11-81 to cool or heat it
- the other heat exchanger 3 is a hot or cold heat exchanger connecting the other hot or cold side of the magnetocaloric heat generator 1 to the atmosphere or another environment.
- heat exchangers 2, 3 allow a thermal exchange between a primary fluid FP on the one hand flowing in the magnetocaloric heat generator 1, and a secondary fluid FS on the other hand flowing in the thermal chamber 11-81 to heat or cool the interior volume of said enclosure or to exchange with the atmosphere.
- the heat exchanger 2, 3 can be a liquid / liquid exchanger when the two fluids FP, FS in the presence are liquids or a liquid / gas exchanger when the primary fluid FP is a liquid and the secondary fluid FS is a gaseous medium. This type of heat exchanger 2, 3 is well known and will not be described in detail in the present application.
- the two primary fluids FP and secondary FS are preferably circulated forcibly inside the heat exchanger 2, 3.
- the primary fluid FP can be forced to circulation in the primary circuit CP of the heat exchanger 2.
- the thermal enclosure 11-81 contains a secondary fluid FS in a volume that can be sealed or not, open totally or partially, depending on the purpose of the thermal enclosure 11 -81 and the nature of the secondary fluid FS.
- the secondary fluid FS is intended to be cooled or heated, depending on whether it is a cooling or heating application.
- This secondary fluid FS may be different depending on the application considered. It may consist of a gaseous medium, such as for example air, when the thermal enclosure 11-61 is a living room, a vehicle, a chamber of growth, a cold room such as a refrigerator, a refrigerated cabinet, a food distributor, a wine cellar, etc. or any other gas used in an industrial process, for example in the case of a storage application in a tank at a temperature different from the ambient temperature. It may also consist of a liquid, such as water when the thermal enclosure 71-81 is a water heater, a tank or a tank of liquid food such as milk, beer, etc.
- a gaseous medium such as for example air
- the secondary fluid FS contained in the thermal chamber 11-81 naturally organizes itself in vertically superposed layers according to its temperature ranging between a lower layer in which its lowest temperature is located in the lower part of the chamber. the thermal enclosure 11-81 and an upper layer in which its temperature is the highest located in the upper part of the thermal chamber 11-81.
- This natural phenomenon is due to the density of a fluid which varies with its temperature and which generates a thermal stratification corresponding to a vertical distribution of the temperature in a fluid, implying because of the gravity that the hot fluid is found elsewhere. above the cold fluid.
- the method and thermal installation 10-80 according to the invention will exploit at least in part this natural phenomenon.
- thermal enclosures (not shown) in which the thermal stratification is not applicable since these thermal enclosures comprise internal brewing or ventilation means and / or obstacles in the useful volume such as drawers, shelves , or the charges themselves, etc.
- the method and the thermal installation according to the invention remain however applicable in these complex installations as explained below.
- the thermal installation 10 is intended for a cooling application. It comprises for this purpose a closed thermal enclosure 11 containing a secondary fluid FS to be cooled, which in this example is a gas mixture such as air.
- a secondary fluid FS to be cooled
- the magnetocaloric heat generator 1 and the heat exchanger 2 are arranged in the upper part of the thermal enclosure 11.
- the heat exchanger 2 is a liquid / gas exchanger and is located inside the heat exchanger.
- thermal enclosure 11 while the magnetocaloric generator 1 is disposed outside the thermal enclosure 11.
- any other configuration may be suitable, in which the magnetocaloric generator 1 and the heat exchanger 2 are both arranged at the outside or inside the thermal enclosure 11.
- the fluidic connections provided respectively between the magnetocaloric heat generator 1 and the heat exchanger 2, and between the heat exchanger 2 and the thermal enclosure 11 are carried out either by pipes and fittings, either by direct connections without pipe depending on the configuration of the thermal installation 10.
- the primary circuit CP in which the primary fluid FP is circulated, is represented in the form of a fluid loop which leaves the magnetocaloric heat generator 1, to enter the heat exchanger 2 via a primary inlet EP, then into spring through a primary output SP to get back into the magnetocaloric heat generator 1.
- the secondary circuit CS in which the secondary fluid FS is circulated by a fan 4, is represented in the form of a fluidic loop, illustrated by arrows, which leaves the heat exchanger 2 through a secondary output SS, to return to a first temperature Tl in the thermal chamber 11 by an injection port 12, then leaves at a second temperature T2 by a suction port 13 to enter the heat exchanger again 2 by a secondary entrance ES.
- the first temperature T1 is necessarily lower than the second temperature T2.
- the thermal enclosure 11 has internal walls 14 arranged to delimit the useful volume of the thermal enclosure 11 relative to the secondary circuit CS.
- the inner walls 14 have for this purpose openings for placing this useful volume in communication with the secondary circuit CS, namely the injection port 12 in the thermal chamber 11 and the secondary outlet SS of the heat exchanger 2 which are in this example combined and located in the upper part of the thermal chamber 11, and the suction mouth 13 located in the lower part of the thermal chamber 11 and the secondary inlet ES of the heat exchanger 2 located in the upper part of the thermal enclosure 11 which are in this example connected by a suction pipe 15 substantially vertical delimited by a portion of the inner walls 14.
- the thermal enclosure 11 further comprises a bypass duct 16 situated at the top of the thermal enclosure 11, delimited by another part of the interior walls 14, extending substantially horizontally between the secondary output SS and the secondary input ES of the heat exchanger 2 to deflect part of the incoming flow of the secondary fluid FS to reinject it directly into the heat exchanger 2.
- the section of the bypass duct 16 is defined to deflect a portion of the incoming flow of the secondary fluid FS of the order of 5 to 40% and preferably 5 to 20%. These values are not data only as an indication and are not restrictive.
- the thermal enclosure 11 does not have a bypass duct 16.
- the operation of the thermal installation 10 according to FIGS. 1A and 1B consists in cooling the secondary fluid FS contained in the thermal enclosure 11 by circulating it through the heat exchanger 2 so that it exchanges thermally with the primary fluid FP circulating in the magnetocaloric heat generator 1, between the secondary inlet ES through which it enters the heat exchanger 2 at a second temperature T2, and the secondary outlet SS through which it leaves the heat exchanger 2 after have been cooled to a first temperature T1, lower than the second temperature T2.
- sampling zone ZP where the temperature of the secondary fluid FS is the colder, at a second temperature T2 higher but close to the first temperature Tl, in accordance with Figure 1B, and unlike the methods of the state of the art.
- This sampling zone ZP is in this example located in the lower part of the thermal enclosure 11 in which is positioned the suction mouth 13 which communicates with the secondary inlet ES of the heat exchanger 2 by the suction duct 15.
- the interest of taking the secondary fluid FS has a second temperature T2 as cold as possible in the thermal chamber 11 and therefore as close as possible to the first temperature T1 to which it is injected into said thermal chamber 11, lies in limiting the difference between temperature between the secondary fluid FS entering the heat exchanger 2 at the second temperature T2 and the secondary fluid FS leaving said heat exchanger at the first temperature Tl, and consequently limiting the temperature difference between the primary fluid FP entering the magnetocaloric heat generator 1 and the primary fluid FP exiting said generator.
- the temperature difference between the secondary fluid FS entering the heat exchanger 2 relative to the secondary fluid exiting said heat exchanger) [Mi] is less than or equal to about 30 % of the magnetocaloric effect of the magnetocaloric heat generator 1, which makes, by way of example, for a magnetocaloric effect of 2.5K, a maximum temperature difference of 0.75K at the level of the secondary fluid FS.
- a temperature difference is obtained between the primary fluid FP entering the magnetocaloric heat generator 1 with respect to the primary fluid FP exiting said magnetocaloric heat generator of the order of 30 to 60% of the magnetocaloric effect of the generator.
- the magnetocaloric thermal 1 which makes, for example, for a magnetocaloric effect of 2.5K a maximum temperature difference 0.75K to 1.5K between the two fluids FP and FS entering into said heat exchanger 2.
- the primary fluid FP which enters the magnetocaloric heat generator 1, after having exchanged with the secondary fluid FS in said heat exchanger 2 has a temperature difference with the primary fluid FP coming out of said thermal generator less than a value of the order of 30 to 60% of the magnetocaloric effect and a temperature remaining close to the Curie temperature of the material at Curie temperature colder so that the magnetocaloric heat generator 1 has the ability to bring this primary fluid FP, emerging in the next half cycle, at the same temperature as the previous cycle.
- the magnetocaloric materials can thus work at their optimum Curie temperature, making it possible to preserve the temperature gradient of the magnetocaloric heat generator 1 and to accelerate the cooling of the secondary fluid FS.
- the advantage of this method is even more important in the startup phase of the thermal installation 10 when the secondary fluid FS contained in the enclosure thermal 11 may be at an initial temperature T2 much higher than its temperature T2 in steady state.
- the thermal installation 20 is intended for a heating application and comprises a closed thermal enclosure 21 containing a secondary fluid FS to be heated, which is, as in the previous example, a mixture gas such as air. Parts and components identical to the previous example have the same reference number.
- the positioning of the magnetocaloric heat generator 1 and the heat exchangers 2, 3 with respect to the thermal enclosure 21 is identical to the thermal installation 10 of FIGS. 1A and 1B.
- the thermal enclosure 21 has internal walls 24 which delimit the useful volume of the thermal enclosure 21 relative to the secondary circuit CS.
- the inner walls 24 have for this purpose openings for communicating this useful volume with the secondary circuit CS, namely several injection ports 22 located at different levels in the thermal chamber 21 and the secondary outlet SS of the exchanger thermal 2 located in the upper part of the thermal chamber 21 which are in this example connected by a substantially vertical injection conduit 27 defined by a portion of the inner walls 24, and a suction mouth 23 and the secondary entrance ES of the heat exchanger 2 located in the upper part of the thermal enclosure 11 which are in this example combined.
- the thermal enclosure 21 further comprises a branch duct 26 situated at the top of the thermal enclosure 21, delimited by another part of the interior walls 24, extending substantially horizontally between the secondary output SS and the secondary input ES of the heat exchanger 2 to deflect part of the incoming flow of the secondary fluid FS to reinject it directly into the heat exchanger 2.
- the section of the bypass duct 26 is defined according to the percentage of the secondary fluid FS to be deflected.
- the thermal enclosure 21 comprises not a bypass duct 26 but at least one bypass orifice 28 located at the secondary outlet SS of the heat exchanger 2 and associated with a deflector 29 to deflect part of the incoming flow of the secondary fluid FS in order to be sucked and reinjected indirectly into the heat exchanger 2.
- the thermal enclosure 21 does not comprise bypass duct 26 or bypass orifice 28.
- the operation of the thermal installation 20 according to FIGS. 2A to 2C consists in heating the secondary fluid FS contained in the thermal enclosure 21 by circulating it through the heat exchanger 2 so that it exchanges thermally with the primary fluid FP circulating in the magnetocaloric heat generator 1, between the secondary inlet ES through which it enters the heat exchanger 2 at a second temperature T2, and the secondary outlet SS through which it leaves the heat exchanger 2 after have been heated to a first temperature T1, higher than the second temperature T2.
- sampling zone ZP where the temperature of the secondary fluid FS is the more hot at a second temperature T2 lower but close to the first temperature Tl, according to Figure 2B, and in contrast to the methods of the state of the art.
- This sampling zone ZP is in this example located in the upper part of the thermal enclosure 21 in which is positioned the suction mouth 23 which communicates with the secondary inlet ES of the heat exchanger 2. It can also be used.
- the objective is the same as that mentioned above, namely to limit the temperature difference between the secondary fluid FS entering the heat exchanger 2 at the second temperature T2 and the secondary fluid FS leaving said heat exchanger at the first temperature T1, and consequently to limit the temperature difference between the primary fluid FP entering the magnetocaloric heat generator 1 and the primary fluid FP coming out of said generator, to preserve the temperature gradient of the magnetocaloric heat generator. 1 and accelerate the heating of the secondary fluid FS.
- the thermal installation 30 according to the invention is intended for a heating application.
- the magnetocaloric heat generator 1 and the heat exchangers 2, 3 are arranged in the lower part of the thermal enclosure 31, one of the heat exchangers 2 being located inside the thermal enclosure 31 and the magnetocaloric generator 1 and the other heat exchanger 3 being located outside.
- the thermal enclosure 31 has internal walls 34 provided with openings to put its useful volume in communication with the secondary circuit CS, namely an injection port 32 and the secondary outlet SS of the heat exchanger 2 located at the bottom of the thermal enclosure 31 which are in this example combined, and a suction mouth 33 located in the upper part of the thermal chamber 31, in a sampling zone ZP where the temperature of the secondary fluid is the hottest, and the secondary input ES of the heat exchanger 2 located in the lower part of the enclosure 11, which are in this example connected a substantially vertical suction duct delimited by a portion of the inner walls 34.
- the thermal enclosure 31 further comprises a bypass duct 36, located in the lower part of the thermal enclosure 31, delimited by another part of the inner walls 34, extending substantially horizontally between the secondary output SS and the secondary input ES of the heat exchanger 2 in order to deflect part of the incoming flow of the secondary fluid FS to the first temperature T1 to reinject it directly into the heat exchanger 2 mixed with the outgoing flow secondary fluid FS at the second temperature T2.
- the thermal enclosure 31 has no bypass duct 36 and uses only the thermal stratification that makes it possible to inject into the heat exchanger 2 the flow exiting the secondary fluid FS at the second temperature T2. close to the first temperature T1 of the incoming flow.
- the thermal installation 40 according to the invention is intended for a cooling application.
- the positioning of the magnetocaloric heat generator 1 and the heat exchangers 2, 3 with respect to the thermal enclosure 41 is identical to the thermal installation 30 of FIGS. 3A and 3B.
- the thermal enclosure 41 has inner walls 44 provided with openings for communicating its useful volume with the secondary circuit CS, namely several injection ports 42 located at different levels in the thermal chamber 41 and the secondary outlet SS the heat exchanger 2 located in the lower part of the thermal chamber 41 which are in this example connected by a substantially vertical injection conduit 47 delimited by a portion of the inner walls 44, and a suction mouth 43 and the secondary inlet ES of the heat exchanger 2 combined and located in the lower part of the thermal enclosure 41, in a sampling zone ZP where the temperature of the secondary fluid is the coldest.
- the thermal enclosure 41 further comprises a bypass duct 46 situated at the bottom of the thermal enclosure 41, delimited by another part of the interior walls 44, extending substantially horizontally between the secondary output SS and the secondary input ES of the heat exchanger 2 to deflect part of the incoming flow of the secondary fluid FS to the first temperature Tl to reinject it directly into the heat exchanger 2, mixed with the outgoing flow secondary fluid FS at the second temperature T2.
- a bypass duct 46 situated at the bottom of the thermal enclosure 41, delimited by another part of the interior walls 44, extending substantially horizontally between the secondary output SS and the secondary input ES of the heat exchanger 2 to deflect part of the incoming flow of the secondary fluid FS to the first temperature Tl to reinject it directly into the heat exchanger 2, mixed with the outgoing flow secondary fluid FS at the second temperature T2.
- the thermal enclosure 41 comprises not a bypass duct 46 but at least one bypass orifice 48 located at the secondary outlet SS of the heat exchanger 2 and associated with a deflector 49 to divert a part of the incoming flow of the secondary fluid FS at the first temperature T1, so that it is sucked and reinjected indirectly into the heat exchanger 2, mixed with the flow leaving the secondary fluid FS at the second temperature T2.
- the thermal enclosure 41 has no bypass duct 46 or bypass orifice 48, and uses only the thermal stratification for injecting into the heat exchanger 2 the outgoing flow.
- secondary fluid FS at the second temperature T2 close to the first temperature T1 of the incoming flow.
- FIGS. 5A, 5B and 6A, 6B illustrate thermal installations 50 and 60 in which the magnetocaloric heat generator 1 and the heat exchangers 2, 3 are arranged laterally on one side of the thermal enclosure 51, 61, one of the heat exchangers 2 being located inside the thermal chamber 51, 61, and the other heat exchanger 3 with the magnetocaloric heat generator 1 being located outside.
- the thermal plant 50 of Figures 5A and 5B is for a cooling application.
- the thermal chamber 51 has inner walls 54 provided with openings for communicating its useful volume with the circuit secondary CS, namely an injection port 52 located in the upper part of the thermal enclosure 51 and the secondary outlet SS of the heat exchanger 2 located in the middle part which are in this example connected by an injection conduit 57, and a suction mouth 53 located in the lower part of the thermal chamber 51, in a sampling zone ZP where the temperature of the secondary fluid is the coldest, and the secondary inlet ES of the heat exchanger 2 located in the middle part which are in this example connected a suction pipe 55.
- the injection pipes 57 and suction 55 are substantially vertical, in the extension of one another and defined by a portion of the inner walls 54 .
- the thermal enclosure 51 further comprises a bypass duct 56 located in the middle part of the thermal enclosure 51, delimited by another part of the inner walls 54, extending substantially vertically between the secondary output SS and the secondary input ES of the heat exchanger 2 in order to deflect part of the incoming flow of the secondary fluid FS to the first temperature Tl to reinject it directly into the heat exchanger 2, mixed with the flow exiting the secondary fluid FS at the second temperature T2.
- the thermal enclosure 51 has no bypass duct 56 and uses only the thermal stratification for injecting into the heat exchanger 2 the flow leaving the secondary fluid FS at the second temperature T2 close to the first temperature T1 of the incoming flow.
- the thermal plant 60 of Figures 6A and 6B is for a heating application.
- the thermal chamber 61 has internal walls 64 provided with openings for communicating its useful volume with the secondary circuit CS, namely an injection port 62 situated in the lower part of the thermal chamber 61 and the secondary outlet SS of the heat exchanger 2 located in the middle part which are in this example connected by an injection conduit 67, and a suction mouth 63 located in the upper part of the thermal chamber 61, in a sampling zone ZP where the temperature of the secondary fluid is the hottest, and the secondary inlet ES of the heat exchanger 2 situated in the middle part which are in this example connected to a suction duct 65.
- the injection ducts 67 and suction ducts 65 are substantially vertical, in the extension one of the other and delimited by part of the inner walls 64.
- the thermal enclosure 61 further comprises a bypass duct 66 located in the middle part of the thermal enclosure 61, delimited by another part of the internal walls 64, extending substantially vertically between the secondary output SS and the secondary input ES of the heat exchanger 2 in order to deflect part of the incoming flow of the secondary fluid FS to the first temperature T1 to reinject it directly into the heat exchanger 2, mixed with the outgoing flow secondary fluid FS at the second temperature T2.
- the thermal enclosure 61 has no bypass duct 66 and uses only the thermal stratification for injecting into the heat exchanger 2 the flow leaving the secondary fluid FS at the second temperature T2 close to the first temperature T1 of the incoming flow.
- FIGS. 7A, 7B and 8A, 8B illustrate thermal installations 70 and 80 in which the thermal enclosure 71, 81 is hermetically sealed and contains a secondary fluid FS in the form of a liquid to be cooled in the thermal installation 70 of the FIGS. 7A, 7B or to be heated in the thermal installation 80 of FIGS. 8A, 8B.
- the magnetocaloric heat generator 1 and the heat exchangers 2, 3 are, in these examples, arranged laterally outside the thermal enclosure 71, 81.
- the heat exchanger 2 communicating with the thermal enclosure 71, 81 is this time a liquid / liquid exchanger, whose secondary circuit CS comprises a pump 5 circulating the secondary fluid FS through ducts 6 opening into the thermal chamber 71, 81 through an injection port 72, 82 and a mouth suction 73, 83.
- a liquid / liquid exchanger whose secondary circuit CS comprises a pump 5 circulating the secondary fluid FS through ducts 6 opening into the thermal chamber 71, 81 through an injection port 72, 82 and a mouth suction 73, 83.
- This sampling zone ZP is, in this cooling application, located in the lower part of the thermal enclosure 71 in which is positioned the suction port 73 which communicates with the secondary inlet ES of the heat exchanger 2.
- the injection port 72 which communicates with the secondary outlet SS of the heat exchanger 2 is located in the upper part of the thermal chamber 71, from which the secondary fluid FS leaves the heat exchanger 2 at the first temperature T1 lower than the second temperature T2. The incoming flow of the secondary fluid FS then moves naturally inside the thermal enclosure 71 from top to bottom.
- bypass duct 76 is outside the thermal enclosure 81, extends between the secondary outlet SS and the secondary inlet ES of the heat exchanger 2, and its section is defined according to the percentage of the secondary fluid FS to be deflected.
- This sampling zone ZP is, in this cooling application, located in the upper part of the thermal chamber 81 in which is positioned the suction mouth 83 which communicates with the secondary inlet ES of the heat exchanger 2.
- the injection port 82 which communicates with the secondary outlet SS of the heat exchanger 2 is located in the lower part of the thermal chamber 81, from which the secondary fluid FS leaves the heat exchanger 2 at the first temperature Tl greater than the second temperature T2. The incoming flow of the secondary fluid FS then moves naturally inside the thermal enclosure 71 from bottom to top.
- bypass duct 86 is outside the thermal enclosure 81 and extends between the secondary outlet SS and the secondary inlet ES of the heat exchanger 2, and its section is defined according to the percentage of the secondary fluid FS to be deflected.
- the ZP sampling zone is identified inside the thermal enclosure by instrumenting the thermal chamber with temperature sensors in one phase.
- process development In this development phase, it is also possible to determine the position of the injection port and the suction mouth in the thermal chamber to optimize the circulation of the secondary fluid inside the thermal chamber.
- the examples of embodiment detailed above are not exhaustive, but allow to illustrate the different cases that can be encountered in heating or cooling applications, and in which it is possible to always apply the same process for modifying the temperature of a secondary fluid FS in a thermal chamber 11-81 by maximizing the performance of a magnetocaloric heat generator 1.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1653509A FR3050517B1 (fr) | 2016-04-20 | 2016-04-20 | Procede pour refroidir ou chauffer un fluide dans une enceinte thermique au moyen d'un generateur thermique magnetocalorique et installation thermique mettant en oeuvre ledit procede |
PCT/EP2017/058228 WO2017182285A1 (fr) | 2016-04-20 | 2017-04-06 | Procede pour refroidir ou chauffer un fluide dans une enceinte thermique au moyen d'un generateur thermique magnetocalorique et installation thermique mettant en oeuvre ledit procede |
Publications (1)
Publication Number | Publication Date |
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EP3446054A1 true EP3446054A1 (fr) | 2019-02-27 |
Family
ID=56411733
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP17718029.6A Withdrawn EP3446054A1 (fr) | 2016-04-20 | 2017-04-06 | Procede pour refroidir ou chauffer un fluide dans une enceinte thermique au moyen d'un generateur thermique magnetocalorique et installation thermique mettant en oeuvre ledit procede |
Country Status (3)
Country | Link |
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EP (1) | EP3446054A1 (fr) |
FR (1) | FR3050517B1 (fr) |
WO (1) | WO2017182285A1 (fr) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
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CN108566768B (zh) * | 2018-06-01 | 2021-03-23 | 深圳市研派科技有限公司 | 一种无管液冷散热系统 |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6453677B1 (en) | 2002-04-05 | 2002-09-24 | Praxair Technology, Inc. | Magnetic refrigeration cryogenic vessel system |
FR2861455B1 (fr) | 2003-10-23 | 2008-02-15 | Christian Muller | Enceinte thermique a circulation de fluide |
DE102009041915A1 (de) * | 2009-08-05 | 2011-02-10 | Liebherr-Hausgeräte Lienz Gmbh | Kühl- und/oder Gefriergerät |
KR101783031B1 (ko) * | 2012-06-28 | 2017-09-28 | 수퍼쿨러 주식회사 | 과냉각 냉동고 및 과냉각 냉동고 제어방법 |
US20140165594A1 (en) * | 2012-12-19 | 2014-06-19 | General Electric Company | Magneto caloric device with continuous pump |
FR3014178B1 (fr) | 2013-11-29 | 2015-11-20 | Cooltech Applications | Appareil thermique magnetocalorique |
WO2016036005A1 (fr) * | 2014-09-02 | 2016-03-10 | Samsung Electronics Co., Ltd. | Appareil réfrigérant |
-
2016
- 2016-04-20 FR FR1653509A patent/FR3050517B1/fr not_active Expired - Fee Related
-
2017
- 2017-04-06 WO PCT/EP2017/058228 patent/WO2017182285A1/fr active Application Filing
- 2017-04-06 EP EP17718029.6A patent/EP3446054A1/fr not_active Withdrawn
Also Published As
Publication number | Publication date |
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WO2017182285A1 (fr) | 2017-10-26 |
FR3050517B1 (fr) | 2018-04-27 |
FR3050517A1 (fr) | 2017-10-27 |
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