EP1448938B1 - Wärmetauscher - Google Patents

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Publication number
EP1448938B1
EP1448938B1 EP02785582A EP02785582A EP1448938B1 EP 1448938 B1 EP1448938 B1 EP 1448938B1 EP 02785582 A EP02785582 A EP 02785582A EP 02785582 A EP02785582 A EP 02785582A EP 1448938 B1 EP1448938 B1 EP 1448938B1
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EP
European Patent Office
Prior art keywords
cavity
wall
cooling
exchanger
cooling device
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.)
Expired - Lifetime
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EP02785582A
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English (en)
French (fr)
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EP1448938A1 (de
Inventor
Pierre Jeuch
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Thermagen SA
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Thermagen SA
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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
    • F25B17/00—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type
    • F25B17/08—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type the absorbent or adsorbent being a solid, e.g. salt
    • 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
    • F25D31/00—Other cooling or freezing apparatus
    • F25D31/006—Other cooling or freezing apparatus specially adapted for cooling receptacles, e.g. tanks
    • F25D31/007—Bottles or cans
    • 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
    • F25D2331/00—Details or arrangements of other cooling or freezing apparatus not provided for in other groups of this subclass
    • F25D2331/80—Type of cooled receptacles
    • F25D2331/805—Cans

Definitions

  • the present invention relates to a device for cooling a liquid by a method of evaporation and adsorption.
  • the principle of such a cooling method consists in evaporating a liquid under the effect of a depression maintained by pumping the vapors of said liquid.
  • the heat exchanger according to the invention is intended for use in a container in the form of a refrigerant plunger or incorporated in a self-cooling beverage package.
  • the object of the present invention is thus to allow the consumption of a drink at an ideal temperature in any place and at any time.
  • US Pat. No. 4,928,495 an illustration of which is given in FIG. 1, describes a self-refrigerating packing configuration (presented as a can) comprising a heat exchanger 16 of flattened rectangular shape immersed in a beverage to be cooled and connected to an adsorption device 22.
  • This patent describes a schematic diagram without specifying the means of making such a device taking into account the economic constraints related to an application to disposable packaging.
  • the exchanger 30 as described has several disadvantages. Indeed, the efficiency of the heat exchange between the evaporator and the beverage to be cooled, which conditions the cooling rate of the beverage, depends mainly on the geometry of the exchanger. However, to obtain a satisfactory cooling efficiency, these patent applications propose to increase the size of the exchanger 30 to the maximum that it is possible to insert into the can, namely a diameter of 50 mm for a height of 100mm. The volume of the resulting exchanger is 80ml for a consumable drink volume of 300ml, which represents more than 25%.
  • Document FR 2 011 939 also discloses a self-cooling device for beverage packaging comprising a conical exchanger containing a fluid under pressure such as liquefied freon.
  • a conical exchanger containing a fluid under pressure such as liquefied freon.
  • the expansion of the gas to the outside atmosphere causes the cooling of the beverage in contact with the exchanger.
  • the adiabatic expansion of gas under pressure causes a very large drop in temperature which allows efficient cooling of the drink despite a reduced contact surface with the beverage to be cooled.
  • this method of cooling is not compatible with industrial manufacturing techniques, the pressurized gas being delicate handling. This method is also contrary to certain environmental protection standards aimed at reducing the emission of gases into the atmosphere.
  • the objective of the present invention is to solve the disadvantages of the prior art.
  • the present invention provides a heat exchanger whose geometry and arrangement allows to promote the cooling rate of a beverage on the principle of evaporation of a refrigerant liquid at reduced pressure.
  • the geometry of the exchanger favors the establishment of large convection currents in the beverage to ensure rapid cooling.
  • This geometry also makes it possible to ensure a maximum heat exchange surface with the beverage for a minimum space requirement of the exchanger.
  • Another object of the invention is to generalize the principle of refrigeration by evaporation under the effect of a vacuum to any refrigeration device of a liquid by the use of a heat exchanger according to the invention, for example used as a diver in a container containing the beverage to be cooled.
  • the invention relates to a cooling device according to claim 1.
  • the first wall of the cavity has a ribbed structure.
  • At least a portion of the ribs of the first wall have a zero width inside the cavity.
  • the first wall of the cavity has a section whose cross-sectional area is constant or the cross-sectional area of the first wall decreases progressively from the base to the top.
  • the conical cavity has a rounded or flattened top.
  • the volume of the cavity is less than 2/3 of the volume delimited by the surface of revolution enveloping said cavity.
  • the internal walls of the cavity are at least partially covered with a hydrophilic porous material.
  • the cooling liquid is water and / or water containing an additive having a saturation vapor pressure higher than that of water.
  • the cavity contains a liquid-gas state separator device.
  • At least the first wall of the cavity is composed of a thermally conductive material.
  • the associated pumping means are selected from the means consisting of an adsorbent material conditioned under vacuum, a mechanical vacuum pump, a cryogenic vacuum pump.
  • the invention also relates to a self-cooling beverage package according to claim 16.
  • the second cavity has a volume-to-surface ratio at least twice as small as the volume-to-surface ratio of the first cavity.
  • the first wall of the cavity of the heat exchanger is in contact with the beverage contained in the first cavity.
  • the first wall of the cavity of the heat exchanger is adjacent to a wall of the first cavity
  • the second wall of the cavity of the exchanger constitutes a wall of the third cavity and integrates the means for placing said second and third cavities into communication.
  • the exchanger is connected to the pumping means by a tube or the exchanger is integral with the pumping means, the second wall of the cavity of the exchanger being integrated with said pumping means.
  • the heat exchanger according to the invention comprises a cavity 2 containing a refrigerant liquid capable of evaporating under the effect of a depression maintained by pumping means.
  • the heat exchanger is intended to be immersed in a beverage to be cooled.
  • the heat exchanger according to the invention has at least a first wall 21 in contact with the beverage to be cooled and at least one second wall 22 which incorporates communication means 30 with pumping means 31. .
  • the wall 21 of the cavity 2 in contact with the liquid to be cooled is of substantially conical shape such that its sectional area decreases from base to top.
  • This particular geometry of the cavity 2 of the exchanger in fact favors the establishment of large convection currents in the beverage to ensure rapid cooling. It is important that the overall shape of the cavity is conical, in particular that its sectional area gradually decreases from base to top. Nevertheless, a cross-section which does not modify the cross-sectional area of the exchanger may possibly be carried out over part of the height of the exchanger without affecting its proper functioning.
  • the conical shapes covered by this definition may take several possible configurations. and concern both a pointed cone (3b) and a dome cylinder (3d).
  • FIGs 4a to 4d are sectional views from above of the cavity 2 of the exchanger according to the invention and the embodiments shown in these figures can be interchangeably combined with the embodiments shown in Figures 3a to 3d.
  • the wall 21 of the cavity 2 of the heat exchanger in contact with the beverage to be cooled may have a ribbed structure in order to increase the surface area of the heat exchange between the exchanger and the drink.
  • Figure 4c illustrates an embodiment in which the first wall 21 has no rib.
  • At least a portion of the ribs of the first wall 21 have a zero width inside the cavity 2 so as to create fins 23 on the cavity 2.
  • the first wall 21 of the exchanger may be defined as being included between two surfaces of internal and external revolution (referenced i and e in FIGS. 3a to 3d) merged at the base of the cone, that is to say at the junction line with the second wall 22 of the exchanger incorporating communication means 30 with pumping means.
  • These surfaces i and e may advantageously consist of an assembly of cones, cylinders, cores, spheres or any other more complex surface, made by stamping for example.
  • the vertex 24 of the cone is also defined as being the point of the wall 21 furthest from the base 22 situated substantially on the axis of revolutions of the previously described surfaces.
  • the top 24 of the cone 21 of the exchanger according to the invention may have a rounding without impairing the efficiency of the heat exchange. This rounding is motivated by a concern to avoid any incident when the empty packaging containing this exchanger is overwritten.
  • the exchanger according to the invention is oriented with the top of the cone downwards.
  • the lower heat exchange surface area than the known heat exchangers is largely compensated by an acceleration of the convection currents produced in the axis of revolution of the cone according to a so-called "inverted chimney” effect by which all the cooling water streams are cooled. contact of the wall of the exchanger flow towards the axis of the cone.
  • This column Cold liquid produced strengthens the pressure gradient and creates cold convection currents rising through an "inverted chimney” effect without being braked by the surface of the heat exchanger.
  • a heat exchange area of about 100cm 2 achieves equivalent performance to known heat exchangers having an exchange surface of more than 300 cm 2 with a planar geometry. Due to its geometry, the exchanger according to the invention allows the establishment of a strong axial convection current rather than the formation of cells of non-axial secondary convection currents.
  • the ribbed cone structure makes it possible in particular to obtain a significant heat exchange surface in a limited space, specifically a limited height, which allows an advantageous application to closed beverage packages.
  • the height of the ribbed cone exchanger may be limited to less than half the height of the package containing the beverage to be cooled.
  • the cavity of the exchanger is composed of a thermally conductive material, such as steel or aluminum, for example.
  • a thermally conductive material such as steel or aluminum, for example.
  • this structure allows good resistance to the external pressure exerted on the cavity of the exchanger by the beverage to be cooled.
  • the metal thickness constituting the cavity can therefore be reduced.
  • a thickness of the order of 0.2 to 0.4 mm may be sufficient.
  • the coolant contained in the cavity of the exchanger may be water, or preferably water containing an additive, for example methanol, having a high saturation vapor pressure to trigger the boiling of the coolant more quickly and reduce the projections of drops that may be violent at the beginning of the pumping process.
  • an additive for example methanol
  • the liquid only partially fills the cavity, for example halfway.
  • the cavity of the exchanger contains only the coolant and the vapors of said liquid, that is to say that the liquid has previously been degassed before being introduced into the cavity.
  • This degassing can be ensured, in particular, by boiling at atmospheric pressure followed by boiling by reducing pressure to a few millibars.
  • the coolant is then placed in the cavity of the vacuum exchanger.
  • the partial pressure, in the exchanger, of gases other than the vapor of the coolant, before it is put in communication with the pumping means is less than or equal to 1mb.
  • the internal walls of the cavity 2 of the exchanger are covered, at least partially, with a hydrophilic porous material, such as cellulose, a fabric or a polymer for example.
  • a hydrophilic porous material such as cellulose, a fabric or a polymer for example.
  • This porous layer can be glued for example.
  • the wall 21 of heat exchange is thus wetted on its inner surface which promotes better evaporation and therefore better cooling on the exchange surface.
  • a fabric with spaced meshes is used to promote the evaporation of the coolant in contact with the metal of the exchanger while allowing the vapor of said liquid to escape through the porous layer. This removes the thermal resistance of the porous layer.
  • the cavity 2 of the exchanger may contain a liquid-gas separation device 50.
  • This embodiment is possible due to the particular geometry of the cavity 2 constituting the exchanger according to the invention. Indeed, a large volume is available at the base of the cone, precisely near the second wall 22 incorporating the connection means 30 to the pumping means 31. It is thus possible to arrange the inside of the exchanger a liquid-gas separation device 50 near the opening of said connecting means 30. Such a device is described below and could not be easily implemented in a geometry exchanger known from the prior art.
  • the state separation device 50 disposed in the exchanger according to the invention occupies a volume of less than 20 cm 3 .
  • Such a liquid-gas state separator 50 makes it possible to separate the vapor molecules from the pumped refrigerant liquid from drops of said liquid entrained by the vapor of said liquid. Indeed, according to the physical principle of cooling carried out by evaporation, the refrigerant liquid evaporates under the effect of a vacuum initiated by a vacuum rupture and maintained by a pumping of the vapors of said liquid. However, the pumping force can be such that drops of liquid can be driven to the pump 31 and thus adversely affect its proper operation. It is therefore necessary to provide a liquid-gas state separator 50 which passes the vapors of the coolant to be pumped and which returns the drops of liquid in the cavity 2 of the heat exchanger.
  • Such a state separator comprises a vapor baffle which consists of at least one baffle wall 51 imposing one or more sudden changes of direction to the vapor flow.
  • the vapor molecules have a very low average free path, of the order of a micrometer, which means that they can change direction very quickly.
  • the drops of liquid have a mass such that they are driven by their inertia and thus separated from the gas flow. This mechanism advantageously allows a liquid-gas separation without significant slowdown of the vapor flow and therefore does not require the occupation of a large volume.
  • the state-separating device also comprises, in addition, a drops collector 60 making it possible to extend the drops of liquid separated from the vapor gas flow towards the bottom of the cavity of the evaporator 2.
  • the collector 60 comprises a funnel and at the less a tube of flow drops.
  • the funnel may advantageously contribute to forming the baffle 51 of the steam deflector.
  • the vapor deflector 51 is advantageously arranged around the communication means 30 with the pumping means 31 and the funnel of the drop collector 60 defines a solid angle which includes the said communication means 30 and the steam deflector 51.
  • the flow tube drops collector 60 has a length greater than or equal to the pressure drop of the steam in the baffle 51 to prevent the projection of drops through said flow tube.
  • This pressure drop is advantageously measured in height of volume of water. If we consider, for example, a pressure drop of steam V of 1mb (corresponding to 1 cm of water column height) the tube will be at least 1 cm long.
  • the state-separating device further comprises a protection 55 for direct projections of drops which completes the steam deflector 51.
  • This protection 55 is arranged facing the communication means 30 in order to avoid pollution. direct pumping means 31 especially during the initiation of the adsorption reaction.
  • the pumping means 31 associated with the heat exchanger 2 according to the invention may consist of a mechanical vacuum pump, or cryogenic pumping means such as cold traps which condense the water vapor, or a vacuum cartridge containing reagents (desiccants) capable of triggering and maintaining the adsorption of the liquid.
  • cryogenic pumping means such as cold traps which condense the water vapor
  • reagents desiccants
  • the implementation of cooling is therefore initiated by an implementation communication 30 of the heat exchanger 2 according to the invention with pumping means 31.
  • it is the wall of the cavity forming the base 22 of the cone which comprises the connecting means Integrated in said wall 22.
  • the invention also relates to a beverage package containing a heat exchanger according to the invention as previously described.
  • Such a self-cooling beverage package 10 comprises a first cavity 1 containing a drinking beverage.
  • This first cavity 1 may have the shapes and dimensions of a standardized can.
  • a second cavity 2 is contiguous with the first cavity and constitutes a heat exchanger according to the forms and features already described of the invention.
  • the first conical wall 21 of the second cavity 2 is in contact with the beverage contained in the first cavity 1.
  • the first wall 21, conical, of the second cavity 2 is adjacent to a wall of the first cavity 1.
  • These walls are thus in close contact to ensure good heat transfer. They may nevertheless be made of different materials, for example the wall 21 of the cavity of the heat exchanger 2 is made of metal while the wall of the cavity 1 containing the beverage is PET plastic (Poly Ethylene Terephthalate).
  • PET plastic Poly Ethylene Terephthalate
  • the second cavity 2 forming the heat exchanger has a volume-to-surface ratio at least two times lower than the volume-to-surface ratio of the first cavity 1 containing the beverage to be cooled.
  • the cooling of the beverage contained in the first cavity 1 is obtained by evaporation of the coolant contained in the second cavity 2 (the heat exchanger).
  • This evaporation is initiated by a depression caused in the cavity 2 of the exchanger by actuating means for placing the cavity forming the heat exchanger in communication with pumping means 31, and this depression is maintained by pumping the vapors. said liquid.
  • the self-cooling beverage package according to the invention comprises a third cavity 3 containing pumping means 31, in this case a desiccant reservoir able to adsorb the vapors of the refrigerant liquid according to a known physical principle mentioned previously.
  • the conical wall 21 of the second cavity 2 forming the exchanger also constitutes a wall of the first cavity 1 containing the liquid to be cooled.
  • the wall forming the base 22 of the cone of the second cavity 2 forming the heat exchanger also constitutes a wall of the third cavity 3 containing the desiccants, this common wall 22 incorporating the communication means 30 of said second and third cavities.
  • the third cavity 3 may comprise actuating means 32 communication means 30 such as a rod triggering the opening of said communication means 30.
  • the heat exchanger according to the invention can be used in a cooling device of a beverage contained in an open container as a cooling plunger.
  • the cooling plunger comprises a heat exchanger according to the invention with a substantially conical cavity 2 connected to pumping means 31 by placing means 30. integrated in the wall 22 forming the base of the cavity 2.
  • the heat exchanger is then provided alone with its integrated communication means 30 and must be connected to adapted pumping means 31, such as a mechanical or cryogenic vacuum pump or vacuum cartridge containing air desiccants, by a flexible or rigid tube, fixed or removable.
  • the cooling plunger comprises a heat exchanger according to the invention with a substantially conical cavity 2 secured to pumping means by the wall 22 forming the base of the cavity 2.
  • the exchanger The thermal device is then provided with integrated communication means 30 and adapted pumping means 31, such as an air-vacuum cartridge containing desiccants.
  • the plunger thus constitutes a disposable autonomous cooling device or possibly reusable after regeneration.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Power Steering Mechanism (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (21)

  1. Vorrichtung zur Kühlung einer Flüssigkeit, umfassend:
    - einen Wärmeaustauscher, umfassend einen Hohlraum (2), der eine Kühlflüssigkeit, die zum Verdampfen unter der Wirkung eines Unterdrucks geeignet ist, und die Dämpfe der Flüssigkeit bei einem Druck unterhalb des atmosphärischen Drucks enthält,
    - Pumpeinrichtungen (31), die zum Abpumpen der Dämpfe der Kühlflüssigkeit geeignet sind, so dass in dem Hohlraum (2) ein Unterdruck aufrechterhalten wird,
    wobei der Hohlraum (2) des Wärmeaustauschers mindestens eine erste Wand (21) von im Wesentlichen konischer Form, derart dass sich ihre Schnittfläche von der Basis bis zur Spitze verjüngt, und mindestens eine zweite Wand (22), die die Basis der konischen Form bildet, aufweist, wobei die erste konische Wand (21) zum Kontakt mit der zu kühlenden Flüssigkeit bestimmt ist und in der zweiten Wand (22) Einrichtungen (31) zum Kommunizieren mit den Pumpeinrichtungen (30) integriert sind.
  2. Kühlvorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass die erste Wand (21) des Hohlraums (2) eine Rippenstruktur aufweist.
  3. Kühlvorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass mindestens ein Teil der Rippen der ersten Wand keine Breite im Inneren des Hohlraums aufweist.
  4. Kühlvorrichtung nach Anspruch 1 bis 3, dadurch gekennzeichnet, dass die erste Wand (21) des Hohlraums (2) einen Abschnitt aufweist, dessen Schnittfläche konstant ist.
  5. Kühlvorrichtung nach Anspruch 1 bis 3, dadurch gekennzeichnet, dass sich die Schnittfläche der ersten Wand (21) des konischen Hohlraums (2) von der Basis (22) bis zur Spitze (21) fortschreitend verjüngt.
  6. Kühlvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der konische Hohlraum (2) eine abgerundete oder abgeflachte Spitze (24) aufweist.
  7. Kühlvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Volumen des Hohlraums (2) weniger als 2/3 des Volumens beträgt, das durch die umlaufende Fläche, die den Hohlraum umschließt, begrenzt wird.
  8. Kühlvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Innenwände des Hohlraums (2) mindestens teilweise mit einem hydrophilen porösen Material bedeckt sind.
  9. Kühlvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Kühlflüssigkeit Wasser und/oder Wasser, das einen Zusatzstoff mit einem Sättigungsdampfdruck enthält, der höher ist als derjenige des Wassers, ist.
  10. Kühlvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Hohlraum (2) eine Trennvorrichtung für den Flüssig-Gas-Zustand (50) enthält.
  11. Kühlvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass mindestens die erste Wand (21) des Hohlraums (2) aus einem wärmeleitenden Material besteht.
  12. Kühlvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die beigefügten Pumpeinrichtungen (31) aus den Mitteln ausgewählt sind, bestehend aus einem unter Vakuum konditionierten adsorbierenden Material, einer mechanischen Vakuumpumpe, einer Tiefsttemperatur-Vakuumpumpe.
  13. Kühlvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Hohlraum (2) des Wärmeaustauschers eine in die zu kühlende Flüssigkeit eingetauchte Tauchvorrichtung darstellt.
  14. Kühlvorrichtung nach Anspruch 13, dadurch gekennzeichnet, dass der Hohlraum (2) des Austauschers über ein Rohr mit der Pumpeinrichtung (31) verbunden ist.
  15. Kühlvorrichtung nach Anspruch 13, dadurch gekennzeichnet, dass der Hohlraum (2) des Austauschers mit der Pumpeinrichtung (31) aus einem Stück besteht, wobei die zweite Wand (22) des Hohlraums in die Pumpeinrichtung integriert ist.
  16. Selbstkühlende Getränkeverpackung (10), umfassend:
    - einen ersten Hohlraum (1), der ein trinkfertiges Getränk enthält,
    - einen zweiten Hohlraum (2), der aus einem Wärmeaustauscher besteht, der eine Kühlflüssigkeit, die zum Verdampfen unter der Wirkung eines Unterdrucks geeignet ist, und die Dämpfe der Flüssigkeit bei einem Druck unterhalb des atmosphärischen Drucks enthält,
    - einen dritten Hohlraum (3), der die Pumpeinrichtungen (31) enthält, die zur Adsorption der Dämpfe der Kühlflüssigkeit ausgelegt sind, so dass in dem zweiten Hohlraum (2) ein Unterdruck aufrechterhalten wird,
    wobei der Hohlraum (2) des Wärmeaustauschers mindestens eine erste Wand (21) von im Wesentlichen konischer Form, derart, dass sich ihre Schnittfläche von der Basis bis zur Spitze verjüngt, und mindestens eine zweite Wand (22), die die Basis der konischen Form bildet, aufweist, wobei die erste konische Wand (21) mit dem Getränk in Kontakt ist, das in dem ersten Hohlraum(1) enthalten ist, und in der zweiten Wand (22) mit den Pumpeinrichtungen (31) kommunizierende Mittel (30) integriert sind.
  17. Selbstkühlende Getränkeverpackung nach Anspruch 16, dadurch gekennzeichnet, dass die Spitze der konischen Form des zweiten Hohlraums (2) nach unten gerichtet ist, so dass bei der Adsorption des Dampfes der Kühlflüssigkeit mindestens eine Konvektionsströmung in der Achse des Konus in dem ersten Hohlraum (1) erzeugt wird.
  18. Selbstkühlende Getränkeverpackung nach einem der Ansprüche 16 bis 17, dadurch gekennzeichnet, dass der zweite Hohlraum (2) ein Verhältnis von Volumen zu Oberfläche aufweist, das mindestens zweimal geringer ist als das Verhältnis von Volumen zu Oberfläche des ersten Hohlraums (1).
  19. Selbstkühlende Getränkeverpackung nach einem der Ansprüche 16 bis 17, dadurch gekennzeichnet, dass die erste Wand (21) des Hohlraums (2) des Wärmeaustauschers mit dem in dem ersten Hohlraum (1) enthaltenen Getränk in Kontakt ist.
  20. Selbstkühlende Getränkeverpackung nach einem der Ansprüche 16 bis 18, dadurch gekennzeichnet, dass die erste Wand (21) des Hohlraums (2) des Wärmeaustauschers an eine Wand des ersten Hohlraums (1) angrenzt.
  21. Selbstkühlende Getränkeverpackung nach einem der Ansprüche 16 bis 20, dadurch gekennzeichnet, dass die zweite Wand (22) des Hohlraums (2) des Austauschers eine Wand des dritten Hohlraums (3) aufbaut und in sie die Einrichtungen (31) zum Kommunizieren des zweiten mit dem dritten Hohlraum (2, 3) integriert sind.
EP02785582A 2001-11-16 2002-11-04 Wärmetauscher Expired - Lifetime EP1448938B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR0114854 2001-11-16
FR0114854A FR2832495B1 (fr) 2001-11-16 2001-11-16 Echangeur thermique
PCT/FR2002/003772 WO2003042610A1 (fr) 2001-11-16 2002-11-04 Echangeur thermique

Publications (2)

Publication Number Publication Date
EP1448938A1 EP1448938A1 (de) 2004-08-25
EP1448938B1 true EP1448938B1 (de) 2006-04-05

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EP02785582A Expired - Lifetime EP1448938B1 (de) 2001-11-16 2002-11-04 Wärmetauscher

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Country Link
US (1) US7240507B2 (de)
EP (1) EP1448938B1 (de)
JP (1) JP4065430B2 (de)
CN (1) CN100467977C (de)
AT (1) ATE322657T1 (de)
AU (1) AU2002350872B2 (de)
CA (1) CA2466296A1 (de)
DE (1) DE60210496T2 (de)
FR (1) FR2832495B1 (de)
RU (1) RU2299382C2 (de)
WO (1) WO2003042610A1 (de)

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FR2875587B1 (fr) * 2004-09-20 2007-03-30 Thermagen Sa Emballage auto-refrigerant
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DE60210496T2 (de) 2006-11-23
CN100467977C (zh) 2009-03-11
ATE322657T1 (de) 2006-04-15
JP2005509830A (ja) 2005-04-14
FR2832495A1 (fr) 2003-05-23
WO2003042610A1 (fr) 2003-05-22
AU2002350872B2 (en) 2007-10-04
RU2299382C2 (ru) 2007-05-20
FR2832495B1 (fr) 2004-02-20
CN1615419A (zh) 2005-05-11
JP4065430B2 (ja) 2008-03-26
US7240507B2 (en) 2007-07-10
CA2466296A1 (fr) 2003-05-22
US20050039485A1 (en) 2005-02-24
EP1448938A1 (de) 2004-08-25
DE60210496D1 (de) 2006-05-18
RU2004118069A (ru) 2005-05-10

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