EP0805942B1 - Appareil de transfert de chaleur a l'aide d'air - Google Patents

Appareil de transfert de chaleur a l'aide d'air Download PDF

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Publication number
EP0805942B1
EP0805942B1 EP96902509A EP96902509A EP0805942B1 EP 0805942 B1 EP0805942 B1 EP 0805942B1 EP 96902509 A EP96902509 A EP 96902509A EP 96902509 A EP96902509 A EP 96902509A EP 0805942 B1 EP0805942 B1 EP 0805942B1
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EP
European Patent Office
Prior art keywords
air
heat
heat exchanger
particulate material
target room
Prior art date
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EP96902509A
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German (de)
English (en)
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EP0805942A2 (fr
Inventor
René Jean Marie VAN GERWEN
Bartel Jan Cornelis Van Der Wekken
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Nederlandse Organisatie voor Toegepast Natuurwetenschappelijk Onderzoek TNO
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Nederlandse Organisatie voor Toegepast Natuurwetenschappelijk Onderzoek TNO
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/1411—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant
    • F24F3/1423—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant with a moving bed of solid desiccants, e.g. a rotary wheel supporting solid desiccants
    • 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
    • F25B30/00—Heat pumps
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/004—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being air
    • 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
    • F28D17/00—Regenerative heat-exchange apparatus in which a stationary intermediate heat-transfer medium or body is contacted successively by each heat-exchange medium, e.g. using granular particles
    • F28D17/005—Regenerative heat-exchange apparatus in which a stationary intermediate heat-transfer medium or body is contacted successively by each heat-exchange medium, e.g. using granular particles using granular particles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2203/00—Devices or apparatus used for air treatment
    • F24F2203/10—Rotary wheel
    • F24F2203/1032—Desiccant wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2203/00—Devices or apparatus used for air treatment
    • F24F2203/10—Rotary wheel
    • F24F2203/104—Heat exchanger wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2203/00—Devices or apparatus used for air treatment
    • F24F2203/10—Rotary wheel
    • F24F2203/1068—Rotary wheel comprising one rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2203/00—Devices or apparatus used for air treatment
    • F24F2203/10—Rotary wheel
    • F24F2203/1084—Rotary wheel comprising two flow rotor segments
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size

Definitions

  • the present invention relates to an apparatus for the transfer of heat with the aid of air according to the preamble of Claim 1.
  • US-A-4.665.715 Such an apparatus has been disclosed by US-A-4.665.715, corresponding to EP-A-0.192.501.
  • This US-A-4.665.715 discloses the following process and apparatus for it: by means of a suction line outside air is drawn in by means of a compressor, which delivers the air via a line to a heat exchanger. From this exchanger the air is delivered via a line to a water extractor. From the water extractor it goes to an expansion turbine and from the expansion turbine it goes to the enclosure room. From the disclosure the air is discharged via a line to heat exchanger 23. From this heat exchanger 23 it is discharged to the outside.
  • US-A-4.769.051 An other apparatus for the transfer of heat with the aid of air is disclosed by US-A-4.769.051.
  • air is taken in from the environment by means of an engine and supplied to a compressor via a primary heat exchanger. After the compressor, the air is supplied to a regenerative heat exchanger via a secondary heat exchanger 24. After the regenerative heat exchanger, the air passes through a water collector, through a filter and a unit before reaching a turbine. From the turbine the air passes through a load heat exchanger and afterwards through the regenerative heat exchanger to exit the cycle via the unit into the environment. The extraction of heat from the air within the closed environment, the target room, takes place by means of the load heat exchanger. The second air cycle is not in fluid connection with the first air cycle.
  • JP-A-57.174.692 discloses the use of balls of glass, steel or the like as heating medium in a regenerative heat exchanger.
  • a still further apparatus for the transfer of heat with the aid of air is disclosed by journal 'VMT VOEDINGSMIDDELTECHNOLOGIE', vol. 25, no. 21, 8 October 1992 (NL) Zeist, pp. 75-77 'Koelproces zonder CFK's: de air cycle [Cooling process without CFCs: the air cycle]' by R.J.M. van Gerwen and S.M. van der Sluis.
  • the apparatus described therein is configured as a refrigerating plant, that is to say the first means comprise a compressor and the second means comprise an expander, the first part of the regenerator is designed to take up heat from the air and the second part of the regenerator is designed to give up heat to the air.
  • the outlet of the second part of the regenerator is connected to the inlet of the first means, or compressor, via a heat exchanger of conventional design.
  • a heat exchanger of conventional design.
  • Such an apparatus has the disadvantage that, at cooling temperatures below 0°C, the regenerator freezes up, as a result of which defrosting agents have to be added.
  • the gas used such as air
  • the gas or air is passed through the target room or cold-storage room.
  • the aim of the present invention is to provide an improved apparatus wherein said freezing and the additional defrosting agents resulting therefrom can be dispensed with, wherein the energy efficiency of the apparatus is increased, wherein the thermal efficiency of the regenerator is increased, wherein the quality of the frozen products is better maintained and which can be implemented more simply and more cost-effectively.
  • the apparatus By omitting the heat exchanger between the outlet of the regenerator and the inlet of the first means for changing the pressure of the air, that is to say by drawing in the air into said first means directly from the surroundings and blowing off the air from the outlet of the regenerator directly into the surroundings, the temperature difference across this heat exchanger which is no longer present is prevented, as a result of which the apparatus can operate with a higher energy efficiency.
  • the heat exchanger which is no longer present is prevented from freezing up, as a result of which the heat pump can continue to operate even at outside temperatures below 0°C.
  • the equivalent diameter D of the particles of the particulate material is between 1 and 25 mm.
  • the change in state in the regenerator now preferably takes place in the regenerative heat exchanger, the particulate material satisfying the requirements as described in Claims 4-8. Tests have shown that with such materials no blockage of the bed takes place, while on the other hand optimum regenerative properties are achieved. More particularly, it is particularly advantageous according to the invention if the ratio of the volume of particulate material to the volume occupied by the bed is between 0.2 and 0.8. With such a ratio, it is possible to realize a good flow through the bed and, at the same time, a good exchange of sensible and latent heat and vapour.
  • particulate material comprises one or more of the following materials: ceramic material, glass, and/or hygroscopic material.
  • the particles can per se be composed of one or more of these materials, but it is also conceivable to construct the bed from a mixture of various particles, for example a mixture of glass particles and ceramic particles.
  • the regenerative heat exchanger comprises changeover means in order to be able to incorporate one compartment alternately in one or the other duct system
  • the regenerative heat exchanger comprises two compartments, which can simultaneously be incorporated in one or the other duct system, respectively.
  • Such a regenerative heat exchanger can be operated essentially continuously, the particulate material taking up heat from the passing flow of fluid in one compartment, while in the other compartment heat is given up to the flow of fluid passing through there by the particulate material.
  • the particulate material has taken up sufficient sensible and latent heat in one compartment and the particulate material has surrendered its sensible and latent heat in the other compartment
  • the two flows of fluid and the two compartments can be switched over with respect to one another. This alternating process can then be continually repeated.
  • the apparatus comprises further compression means, the outlet of which is connected to the inlet of the first compression means, optionally via a heat exchanger exchanging heat with the surroundings.
  • the compression means and the expansion means in this case each comprise a rotor, it being possible to drive the two rotors by means of a common shaft.
  • Such a combined compression-expansion unit (a so-called turbo charger) generally operates optimally at rotational speeds at which it is hardly possible to supply the work required directly to the common shaft. This extra work required can be supplied by means of the further compression means.
  • the apparatus according to the invention can be used very advantageously in a refrigerating plant or heat pump for cooling or heating, respectively, a target room, the target room preferably being in open communication with the refrigerating plant or heat pump, respectively.
  • a refrigerating plant 30 according to the invention which is open on both sides is shown diagrammatically.
  • a heat pump 20 which is open on both sides is shown.
  • the refrigerating plant 30 and the heat pump 20 operate in accordance with the Joule-Brayton process, which in its simplest form consists of an adiabatic compression step, an isobaric heat exchange step and an adiabatic expansion step.
  • the refrigerating plant 30 which is open on both sides according to Fig, 1a operates as follows:
  • Air drawn in from the surroundings is passed to a compressor 32 via inlet 51.
  • the air is compressed in the compressor 32, during which process the pressure and temperature of the air increase.
  • the compressed air is fed via an intermediate conduct system 6, 7, in which a regenerative heat exchanger which will be described with reference to Fig. 3 is incorporated, to an expander 31 (expansion device). Expansion of the air takes place in the expander 31, during which process the pressure and temperature of the air decrease.
  • the expanded, cooled air is fed via conduct 46 to the target room 34 which is to be cooled.
  • This target room 34 which is to be cooled can be an essentially closed room, such as a cold store or a freezer store.
  • the cooled air flows from conduct 46 freely into the cold-storage room 34.
  • Air from the target room 34 which is still relatively cold or cool is discharged from the target room 34 via return conduct system 4, 5. Before this air which is still relatively cold or cool flows freely out into the surroundings, it is passed through the regenerative heat exchanger for the exchange of heat and moisture with the flow of air which is to be fed to the target room 34. During this process, the air discharged from the target room via the return conduct system 4, 5 takes up heat and moisture from the air which is to be fed to the target room 34.
  • a so-called heat pump according to the invention is shown diagrammatically. Briefly, the operation of this heat pump is as follows:
  • Air is drawn in from the surroundings via conduct 25. This air is expanded in an expander 22. During this process, the pressure and temperature of the air decrease. Then the air is fed via intermediate conduct system 6, 7, in which a regenerative heat exchanger which will be described with reference to Fig. 3 is incorporated, to a compression device 23. In the regenerative heat exchanger, the temperature of the air is increased, while the pressure will remain essentially the same. Once it arrives in the compressor 23, the air is compressed, during which process the pressure and temperature increase. The warm air is then fed via conduct 24 to the target room 21 which is to be heated. The heated air flows essentially freely into the target room 21, as a result of which a uniform and efficient heating of the room is made possible.
  • Air is discharged from this target room 21 via a return conduct system 4, 5, which air, before flowing to the outside air via conduct 5, is passed through the regenerative heat exchanger 1 in order to preheat the air which is to be fed to the target room 21 via the intermediate conduct system 6, 7.
  • Fig. 2a shows another embodiment of a refrigerating plant according to the invention.
  • This refrigerating plant 40 according to Fig. 2a generally corresponds to the refrigerating plant 30 according to Fig. 1a.
  • the difference is substantially that in the refrigerating plant 40 according to Fig. 2a, the compression takes place in two stages. There is a first compression stage, which takes place in the further compression means 41, and a second compression stage, which takes place in the first compression means 33.
  • intermediate cooling takes place between the two stages by means of a heat exchanger 43, which is incorporated in the conduct system 42, 44 between the two compressors 41 and 33.
  • the air which has been passed through the conduct system 42, 44 is cooled with the aid of ambient air, which is fed to the heat exchanger 43 via conduct 49, and is discharged again from the heat exchanger 43 to the surroundings via conduct 57.
  • the compressor 33 and the expander 31 here form a so-called turbo charger, which is driven by a common shaft 45.
  • Such turbo chargers generally operate optimally at rotational speeds of 50,000 to 150,000 rpm.
  • the extra compressor 41 here makes it possible to supply sufficient work.
  • Leakage flows can be counteracted by keeping the pressure in the room which is to be cooled essentially identical to the ambient pressure.
  • This can be realized by incorporating compression means in the air flow leaving the target room.
  • these compression means are located in conduct 5.
  • the control for these compression means can be based on the pressure difference between the surroundings and the target room or on the volume flow rates in the conduct systems 4, 5 and 51, 42, 44, 6, 7, 46.
  • the cooling temperature or cooling capacity of a refrigerating plant 40 according to Fig. 2a can advantageously be controlled by controlling the rotational rate of the compressor 41, for example by means of a speed regulator for a rotor.
  • Fig. 2b shows another embodiment of a heat pump according to the invention.
  • This heat pump 29 according to Fig. 2b largely corresponds to the heat pump 20 according to Fig. 1b.
  • the difference is essentially that in the heat pump 29 according to Fig. 2b the compression takes place in two stages. There is a first compression stage, which takes place in the further compression means 26, and a second compression stage, which takes place in the first compression means 23. Intermediate cooling or heating between the compression stages, such as in the refrigerating plant according to Fig. 2a, is not necessary in the heat pump 29 according to Fig 2b.
  • the compressor 23 and the expander 22 form, in a corresponding manner to the compressor 33 and the expander 31 of the refrigerating plant 40 according to Fig. 2a, a so-called turbo charger, which is driven by a common shaft 28. As has already been explained, such turbo chargers generally operate optimally at rotational speeds of 50,000 to 150,000 rpm.
  • the extra compressor 26 here makes it possible to supply sufficient work
  • leakage flows can be counteracted by keeping the pressure in the room 21 which is to be heated essentially identical to the ambient pressure.
  • This can be realized by incorporating compression means, such as a fan, in the flow of air leaving the target room 21.
  • these compression means are located in conduct 5.
  • the control for these compression means can be based on the pressure difference between the surroundings and the target room 21 or on the volume flow rates in the conduct systems 4, 5 and 25, 6, 7, 27, 24.
  • the heating temperature or the heating capacity of the heat pump 29 according to Fig. 2b can advantageously be controlled by controlling the air flow rate of the compressor 26, for example by means of a speed regulator for a rotor.
  • Fig. 3 shows an example of a regenerative heat exchanger 1 according to the invention.
  • This heat exchanger comprises two compartments 2 and 3, which are each provided with a packed bed of particulate material 10.
  • the particles 11 thereof are essentially spherical, but differently shaped, for example irregular, particles are also very conceivable.
  • Fluid such as air, which is to be fed to the target room 21, 34, is fed to the regenerative heat exchanger via conduct 6, passed by means of valve 9 to the left-hand compartment 3, passed through the packed bed located herein and fed through in the direction of the target room via valve 8 and conduct 7.
  • Fluid, such as air, which has been discharged from the target room is passed into the right-hand compartment 2 via conduct 4 and valve 8, passed through the packed bed of particulate material 10, and discharged from the regenerative heat exchanger 1 via valve 9 and conduct 5.
  • the effect is achieved that the flow of fluid which is going towards the target room is passed through the right-hand compartment (instead of through the left-hand compartment), and that the flow of fluid which is discharged from the target room is passed through the left-hand compartment (instead of through the right-hand compartment).
  • this rotation of the valves 8, 9 to take place with a regularity to be determined in more detail (which will be dependent on, inter alia, the process conditions, the physical properties of the particulate material, etc.)
  • the effect is achieved that alternately the bed is always taking up heat in one compartment while the bed is giving up heat in the other compartment.
  • the bed of such particulate material is also very able to bind to itself condensation or precipitation, such as deposition of moisture or ice, and then to give it up to the other flow of fluid.
  • condensation or precipitation such as deposition of moisture or ice
  • one of the flows of the fluid can be dehumidified.
  • the air which is to be fed to the refrigerating plant is hereby simultaneously cooled and dehumidified in the regenerative heat exchanger, it being possible to discharge the moisture through the flow of fluid discharged from the cold-storage room after the valves have been switched over, while the temperature of the particulate material is simultaneously lowered. In this way, the regenerative heat exchanger 1 is prevented from becoming blocked as a consequence of the deposition of moisture and/or ice.
  • a further advantage is that the flow of air which has been dehumidified in the regenerative heat exchanger 1 will not form any deposition of moisture or ice in further process steps in a refrigerating plant or heat pump either, so that here too the apparatus is prevented from becoming defective.
  • Fig. 4 shows a regenerative heat exchanger 70 according to the invention of the so-called rotary type.
  • This regenerative heat exchanger 70 consists essentially of a cylinder 74 which is subdivided into compartments extending in the longitudinal direction thereof.
  • the cylinder 74 shown in Fig. 4 comprises three compartments 71, 72 and 73, which are obtained by installing three partitions 75, 76 and 77 in the cylinder 74, which partitions are fixed to one another at the longitudinal centre axis of the cylinder 74.
  • Each compartment thus obtained is filled with a bed 10 of particulate material 11.
  • the cylinder 74 is arranged so as to be rotatable about axis 78.
  • Feed conducts 4, 6 and discharge conducts 5, 7 are arranged at the ends of the cylinder 74.
  • the conducts 4 and 5 here form part of one conduct system, while the conducts 6 and 7 form part of another conduct system.
  • fluid for example air
  • the effect is achieved that the various compartments are successively incorporated in one conduct system (for example 4, 5) or the other conduct system (for example 6, 7).
  • regenerative heat exchanger 70 The operation of the regenerative heat exchanger 70 is, as will be clear, otherwise in accordance with the operation as has been described with reference to Fig. 3 for regenerative heat exchanger 1. It will also be clear, then, that the regenerative heat exchanger 1 from Fig. 1a, 1b, 2a and 2b can readily be replaced by a regenerative heat exchanger 70 of the rotary type.
  • feed conduct 6 can be a discharge conduct, discharge conduct 7 then becoming a feed conduct. Accordingly, it is possible to reverse the direction of flow in the conducts 4 and 5.
  • valves 8, 9 many other changeover means for making one or the other flow of fluid flow through the respective compartments alternately are also conceivable.
  • the regenerative heat exchanger comprises one, preferably cylindrical, compartment which rotates about its axis. The particulate material in this compartment is then exposed in turn to one or the other flow of fluid.
  • heat exchangers, compressors, expanders, etc. can also be connected upstream, intermediately or downstream.
  • apparatuses should comprise at least one expansion device, at least one compression device, and at least one regenerative heat exchanger arranged between a compression device and expansion device.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Steam Or Hot-Water Central Heating Systems (AREA)

Claims (11)

  1. Appareil pour le transfert de chaleur avec de l'air, comprenant, successivement, dans la direction de l'écoulement d'air :
    des premiers moyens (22, 32) pour modifier la pression de l'air dans une première direction ;
    une première partie d'un échangeur (1) à récupération de chaleur pour l'échange de chaleur à partir de l'air dans une première direction ;
    des seconds moyens (31, 23) pour modifier la pression de l'air dans une seconde direction, laquelle seconde direction est opposée à la première direction ;
    une seconde partie dudit échangeur (1) à récupération de chaleur pour l'échange de chaleur à partir de l'air dans une seconde direction qui est opposée à ladite première direction ;
    lequel appareil comprend en outre une chambre cible (21, 34) dans laquelle de la chaleur doit être transférée, chambre cible qui est dotée d'une entrée d'air et d'une sortie d'air,
    où l'entrée d'air de la chambre cible (21, 34) est reliée aux seconds moyens (31, 23);
    où la sortie d'air de la chambre cible (21, 34) est reliée à la seconde partie de l'échangeur à récupération de chaleur ;
    où les premiers moyens sont dotés d'une entrée (51, 23) aspirant de l'air provenant exclusivement du milieu environnant ; et
    où la sortie (5) de la seconde partie de l'échangeur à récupération de chaleur est reliée exclusivement au milieu environnant,
    caractérisé
    en ce que les première et seconde parties de l'échangeur (1) à récupération de chaleur sont interchangeables en ce qui concerne leur fonction et comprennent un lit de matière particulaire pour l'échange de chaleur sensible, de chaleur latente et d'humidité ;
    en ce que le diamètre équivalent (D) des particules (11) de la matière particulaire est compris entre 1 mm et 25 mm, le diamètre équivalent (D) étant déterminé selon: D = 3 6V π où V est le volume d'une particule, et
    en ce que les propriétés physiques de la matière particulaire (10), le diamètre équivalent de la matière particulaire (10) et les dimensions de l'échangeur de chaleur sont conçus pour satisfaire la relation suivante: B = A D λ2m air CpL2 < 0,1 où
    A =
    surface totale d'échange de chaleur des particules dans un compartiment, en m2
    D =
    diamètre moyen équivalent des particules en m
    λ =
    coefficient de transfert de chaleur des particules en W/mK
    mair =
    écoulement massique d'air en kg/s
    Cp =
    chaleur massique d'air en J/kgK
    L =
    longueur du lit en m.
  2. Appareil selon la revendication 1, comprenant un système de refroidissement où le premier moyen (33) comprend un compresseur, le second moyen (31) comprenant un expanseur, où la première partie du récupérateur est conçue pour absorber de la chaleur sensible et latente de l'air, la seconde partie du récupérateur étant conçue pour fournir à l'air de la chaleur sensible et latente.
  3. Appareil selon la revendication 1, comprenant une pompe à chaleur où le premier moyen comprend un expanseur (22), où le second moyen comprend un compresseur (23), où la première partie du récupérateur est conçue pour fournir à l'air de la chaleur sensible et latente, la seconde partie du récupérateur étant conçue pour absorber la chaleur de l'air.
  4. Appareil selon l'une quelconque des revendications précédentes, dans lequel le rapport (∈) du volume de la matière particulaire dans le récupérateur, sur le volume occupé par le lit est compris entre 0,2 et 0,8.
  5. Appareil selon l'une quelconque des revendications précédentes, dans lequel les particules (11) de la matière particulaire sont essentiellement sphériques.
  6. Appareil selon l'une quelconque des revendications précédentes, dans lequel la matière particulaire comprend une matière céramique.
  7. Appareil selon l'une quelconque des revendications précédentes 1 à 5, dans lequel la matière particulaire comprend du verre.
  8. Appareil selon l'une quelconque des revendications précédentes, dans lequel la matière particulaire comprend une matière hygroscopique.
  9. Appareil selon l'une quelconque des revendications précédentes, comprenant en outre des moyens de compression (41 ; 26) dont la sortie (42 ; 27) est reliée à l'entrée (44 ; 27) des moyens de compression (33 ; 23), le cas échéant via un échangeur de chaleur (43) échangeant de la chaleur avec le milieu environnant.
  10. Appareil selon la revendication 9, dans lequel les moyens de compression (33 ; 23) et les moyens d'expansion (31 ; 22) comprennent chacun un rotor, et il est possible, pour les deux rotors, d'être entraínés au moyen d'un arbre commun (45 ; 28).
  11. Appareil selon la revendication 9 ou 10, comprenant en outre des moyens de compression, tels qu'un ventilateur, pour régler la différence de pression entre le milieu environnant et la chambre cible.
EP96902509A 1995-01-24 1996-01-24 Appareil de transfert de chaleur a l'aide d'air Expired - Lifetime EP0805942B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
NL9500130A NL9500130A (nl) 1995-01-24 1995-01-24 Regeneratieve warmtewisselaar; warmtepomp en koelinrichting voorzien van regeneratieve warmtewisselaar; werkwijze voor uitwisseling van warmte; werkwijze voor koelen; werkwijze voor verwarmen.
NL9500130 1995-01-24
PCT/NL1996/000042 WO1996023188A2 (fr) 1995-01-24 1996-01-24 Appareil et procede de transfert de chaleur a l'aide d'air

Publications (2)

Publication Number Publication Date
EP0805942A2 EP0805942A2 (fr) 1997-11-12
EP0805942B1 true EP0805942B1 (fr) 2001-04-18

Family

ID=19865487

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96902509A Expired - Lifetime EP0805942B1 (fr) 1995-01-24 1996-01-24 Appareil de transfert de chaleur a l'aide d'air

Country Status (5)

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EP (1) EP0805942B1 (fr)
AU (1) AU4679296A (fr)
DE (1) DE69612546T2 (fr)
NL (1) NL9500130A (fr)
WO (1) WO1996023188A2 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2334094B (en) * 1998-02-05 2002-08-14 Howden Aircontrol Ltd Air environment control systems
JP2000257968A (ja) * 1999-03-05 2000-09-22 Daikin Ind Ltd 空気調和装置
JP4172088B2 (ja) * 1999-04-30 2008-10-29 ダイキン工業株式会社 冷凍装置
FR2793312B1 (fr) 1999-05-04 2001-07-13 Air Liquide Appareil d'echange thermique a contre-courant et son application aux installations de distillation d'air
US6631754B1 (en) * 2000-03-14 2003-10-14 L'air Liquide Societe Anonyme A Directoire Et Conseil De Surveillance Pour L'etude Et L'exploitation Des Procedes Georges Claude Regenerative heat exchanger and method for heating a gas therewith
GB2402736B (en) 2003-06-13 2007-04-11 Aircontrol Technologies Ltd Air environment control system
WO2006011297A1 (fr) * 2004-07-30 2006-02-02 Mitsubishi Heavy Industries, Ltd. Appareil de refroidissement de type réfrigérant à air

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1281125A (en) * 1969-02-20 1972-07-12 Kureha Chemical Ind Co Ltd Regenerative heat exchanger
US3868827A (en) * 1973-04-05 1975-03-04 Airco Inc Air cycle food freezing system and method
US4295518A (en) * 1979-06-01 1981-10-20 United Technologies Corporation Combined air cycle heat pump and refrigeration system
US4280416A (en) * 1980-01-17 1981-07-28 Philip Edgerton Rotary valve for a regenerative thermal reactor
JPS57174692A (en) * 1981-04-21 1982-10-27 Kawasaki Heavy Ind Ltd Regenerative heat exchanger
SU1101663A1 (ru) * 1983-02-24 1984-07-07 Проектный Институт "Авторемпромпроект" Гранула насадки регенеративного теплообменника
SE442777B (sv) * 1984-03-16 1986-01-27 Lennart Karlsson Anordning for luftforvermning och rening av gas, fremst rokgas
FR2576399B1 (fr) * 1985-01-18 1989-03-31 Abg Semca Procede de conditionnement d'atmosphere et climatiseur mettant en oeuvre le procede
US4769051A (en) * 1987-10-19 1988-09-06 United Technologies Corporation Filtered environmental control system
FI90284C (fi) * 1992-02-13 1994-01-10 Ahlstroem Oy Modernisoitu esilämmitin ilman esilämmittämiseksi esim. masuunilaitoksessa

Also Published As

Publication number Publication date
EP0805942A2 (fr) 1997-11-12
WO1996023188A2 (fr) 1996-08-01
WO1996023188A3 (fr) 1996-09-26
DE69612546T2 (de) 2001-10-18
AU4679296A (en) 1996-08-14
NL9500130A (nl) 1996-09-02
DE69612546D1 (de) 2001-05-23

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