EP3722730A1 - Absorptionsmaschine, die gepolsterte platten umfasst - Google Patents

Absorptionsmaschine, die gepolsterte platten umfasst Download PDF

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Publication number
EP3722730A1
EP3722730A1 EP20167406.6A EP20167406A EP3722730A1 EP 3722730 A1 EP3722730 A1 EP 3722730A1 EP 20167406 A EP20167406 A EP 20167406A EP 3722730 A1 EP3722730 A1 EP 3722730A1
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EP
European Patent Office
Prior art keywords
fluid
inlet
padded
plates
evaporator
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP20167406.6A
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English (en)
French (fr)
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EP3722730B1 (de
Inventor
Dominique Mailhot
Wael YAZBEK
Frédéric NUNES
Estelle MONORE
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CNIM Systemes Industriels SAS
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CNIM Groupe SA
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Publication of EP3722730A1 publication Critical patent/EP3722730A1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/12—Elements constructed in the shape of a hollow panel, e.g. with channels
    • F28F3/14—Elements constructed in the shape of a hollow panel, e.g. with channels by separating portions of a pair of joined sheets to form channels, e.g. by inflation
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/026—Evaporators specially adapted for sorption type systems

Definitions

  • the technical field of the invention is that of heat exchangers.
  • the present invention relates to an absorption machine comprising plate heat exchangers.
  • Absorption machines are thermal systems that generate cold or heat from hot sources. These systems are developing because they allow energy savings by recovering fatal heat at low temperature.
  • An absorption machine comprises at least four types of exchangers coupled two by two: an evaporator / absorber pair and a generator / condenser pair. These two couples are each placed in a vacuum chamber.
  • Such a machine is connected to three sources: the hot source which supplies thermal energy to the generator, the cold source connected to the evaporator, and the intermediate temperature cooling source, the fluid of which circulates in the absorber and the condenser. .
  • FIG. 1 schematically represents an absorption machine 10 according to the state of the art comprising an evaporator 11, an absorber 12, a generator 13 and a condenser 14, and being connected to the three sources mentioned above.
  • the absorbent 5 has the capacity to absorb vapor from the refrigerant 4, which feeds the operating cycle.
  • the couples of fluids most used in practice are water (H2O) as coolant 4 and lithium bromide (LiBr) as absorbent 5, or ammonia (NH3) as coolant 4 and water (H2O) as absorbent 5.
  • H2O water
  • NH3 ammonia
  • These torques are chosen so that absorbent 5 has a high affinity towards refrigerant 4 and that refrigerant 4 has a greater vaporization capacity than absorbent 5, in other words it must be much more volatile than absorbent 5.
  • the cold source (not shown) is connected to a bundle of tubes 1 of the evaporator 11.
  • the hot source (not shown) is connected to a bundle of tubes 3 of the generator 13.
  • the cooling source to intermediate temperature (not shown) is connected to a tube bundle 6 of the condenser and to a tube bundle 2 of the absorber.
  • each of the two refrigerant 4 and absorbent 5 fluids is as follows: At the level of the evaporator 11, the refrigerant 4 is distributed over the bundle of tubes 1 containing the fluid coming from the cold source. The pressure inside the evaporator 11 being very low, the refrigerant 4 will vaporize by subtracting heat from the fluid coming from the cold source which circulates in the tube bundle 1, which is thus cooled. Part of the refrigerant 4 does not vaporize and is recovered by a recuperator located in the bottom of the evaporator 11 to be distributed again over the bundle of tubes 1.
  • the absorbent 5 is distributed over the bundle of tubes 2 containing the fluid coming from the cooling source at intermediate temperature.
  • Absorbent 5 absorbs vapor from refrigerant 4 and dilutes. This action produces a vacuum which allows circulation of the refrigerant vapor 4 from the evaporator 11 to the absorber 12.
  • the absorption phenomenon also generates heat, which is recovered by the fluid coming from the cooling source to intermediate temperature.
  • the diluted distributed absorbent 5 is recovered by a recuperator located in the bottom of the absorber 12 and is then sent to the generator 13.
  • the absorbent 5 is distributed over the bundle of tubes 3 containing the fluid coming from the hot source.
  • the refrigerant 4 absorbed by the absorbent 5 then vaporizes and the absorbent 5 is recovered by a recuperator located in the bottom of the generator 13.
  • the undiluted absorbent 5 thus recovered is returned to be distributed within the absorber 12.
  • the refrigerant vapor 4 thus formed within the generator 13 is conducted towards the condenser 14.
  • the condenser 14 liquefies because the condenser 14 comprises a bundle of tubes 6 containing the fluid coming from the cooling source at intermediate temperature.
  • the refrigerant 4 in liquid form is then recovered by a recuperator located in the bottom of the condenser 14 and is returned to be distributed within the evaporator 11.
  • FIG. 2 shows an absorption machine comprising tube and shell type exchangers, with sprayed beam, as conventionally used in the state of the art.
  • absorber 12, and generator 13 sprinkling trays 21 allow uniform sprinkling of the bundles of tubes 22, in order to cover the bundles of tubes 22 with a film of refrigerant 4 or of absorbent 5 in depending on the type of exchanger.
  • Each of the exchangers 11, 12, 13 and 14 comprises a recuperator 23.
  • These exchangers are called “tube and calender” because a fluid circulates in the tube bundles 22 and at least one other fluid circulates between the tube bundles 22 and the tube. grille 24 of the exchanger.
  • plate heat exchangers in absorption machines instead of tube and calender heat exchangers as shown in the Figure 2 .
  • plate heat exchangers where a bundle of plates replaces the tube bundle of tube and shell exchangers, are less expensive to produce than tube and shell heat exchangers, and have a small footprint.
  • a first problem is the passage of steam. Indeed, the evaporator and the generator create low pressure steam which is very sensitive to pressure drops.
  • the ducts of the chevron-type exchangers being of very small diameter, they generate significant pressure drops which prevent the circulation of low pressure steam.
  • a second problem concerns the very integration of the plate heat exchangers within absorption machines.
  • absorption machines are designed specifically for each project.
  • the geometry of the exchangers can be very different, which does not present any difficulty for tube and calender exchangers.
  • chevron plate heat exchanger it is difficult to vary their geometry easily because they are made from stamped plates.
  • the investment cost for manufacturing a new pattern of plate heat exchanger plate rafters is very high, therefore making testing and industrialization very expensive.
  • the invention offers a solution to the problems mentioned above, by proposing an absorption machine comprising a first, a second, a third and a fourth plate exchanger, the first plate exchanger being an evaporator, the second plate exchanger being an absorber.
  • the third plate exchanger being a generator
  • the fourth plate exchanger being a condenser
  • each plate exchanger comprising a plurality of padded plates arranged successively and parallel to each other, each padded plate comprising two sheets and a plurality of connection points between the two sheets arranged in a plane, at least one sheet being curved between the connection points in order to form a fluid circulation space between the two sheets and the connection points of two adjacent padded plates included in the same exchanger being screwed -to-be.
  • the invention advantageously makes it possible to provide an absorption machine that is inexpensive to produce and easily adaptable according to requirements.
  • it is easy to vary the exchange surfaces by increasing the number of plates, without having to produce new patterns of suitable chevrons and therefore without new tests to be carried out.
  • the padded geometry of the plates ensures rigidity of the entire absorption machine by allowing the walls of the absorption machine to be held, thus limiting the need for other stiffeners.
  • the padded geometry of the plates also allows a turbulent flow of the fluid distributed over the plates and therefore improve the heat exchange coefficient.
  • connection points of two adjacent padded plates are opposite each other, in order to create a space for the passage of steam.
  • the curved shape of at least one sheet allows a larger exchange surface and a fluid circulation space inside the plates.
  • FIG. 3 shows a schematic representation of an evaporator / absorber module 300 of an absorption machine according to the first embodiment comprising at least two padded plate exchangers.
  • This module comprises a vacuum chamber 301 in order to ensure the operating conditions of the cycle of the evaporator 11 and of the absorber 12.
  • the coolant 4 and the absorbent 5 circulate outside the padded plates, for example by being distributed over bundles of padded plates or for example in the form of vapor. This distribution of the coolant 4 and of the absorbent 5 can for example be carried out by spraying.
  • the fluids coming from the cold, hot and intermediate temperature cooling sources circulate inside the padded plates.
  • padded plate is understood to mean an assembly of two sheets of metal, for example steel, welded together, for example by laser welding. This connection point then makes it possible to pressurize the assembly.
  • One of the sheets or both sheets are then pressurized in order to deform the pressurized sheet or sheets, and therefore to create a space between the two sheets allowing the passage of a fluid where the sheets have not been welded together.
  • the welding of the plates follows, for example, a pattern of “points”, distributed over the surface of the sheets so as to leave a space for the circulation of fluid between each point.
  • a padded plate is also commonly called a “pillow plate” according to the Anglo-Saxon name.
  • padded plate will be understood to mean a plate comprising two sheets and a plurality of connection points between the two sheets arranged in a plane, at least one sheet being curved between the connection points in order to form a circulation space. of fluid between the two sheets.
  • a first padded plate heat exchanger is the evaporator 11. It comprises a bundle of padded plates 310 above which is positioned a coolant spraying system 311 4. This spraying system 311 allows uniform distribution of the coolant fluid. 4 on the bundle of plates 310.
  • the sprinkler system 311 comprises for example a tube and a perforated plate, the tube allowing a coarse distribution of the fluid on the perforated plate, and the perforated plate allowing a uniform distribution of the fluid on the whole surface of the plates.
  • the evaporator 11 further comprises at least two collectors.
  • a starting collector of the cold source 312, to which the cold source is connected, is connected to one of the fields of each of the padded plates forming the bundle of plates 310.
  • the starting collector of the cold source 312 can inject inside the padded plates the fluid coming from the cold source.
  • This connection of the collector 312 to one of the fields of each of the plates of the bundle 310 may for example be a weld.
  • An inlet manifold of the cold source 313 is also connected to one of the fields of each of the padded plates forming the bundle of plates 310.
  • the inlet manifold of the cold source 313 allows the recovery of the fluid coming from of the cold source injected inside the plates by the starting collector 312.
  • This connection of the collector 313 to one of the fields of each of the plates of the bundle 320 may for example be a weld.
  • the direction of flow of fluids in the plates can be reversed in order to operate against the current.
  • the cold source outlet manifold 312 and the intermediate temperature cooling source inlet manifold 323 are reversed.
  • this counter-current can be implemented for all the other exchangers.
  • a second padded plate heat exchanger included in the evaporator / absorber module 300 is the absorber 12. It comprises a bundle of padded plates 320 above which is positioned a sprinkler system 321 of absorbent fluid 5. This sprinkler system 321 allows a uniform distribution of the absorbent fluid 5 on the bundle of plates 320.
  • the sprinkler system 321 will be presented in more detail below.
  • the absorber 12 further comprises at least two collectors.
  • An intermediate temperature cooling source start manifold 322, to which the intermediate temperature cooling source is connected, is connected to one of the fields of each of the padded plates forming the plate bundle 320. In this way, the heat sink manifold. leaving the cooling source at intermediate temperature 322 allows the fluid coming from the intermediate temperature cooling source to be injected inside the padded plates.
  • An inlet manifold of the intermediate temperature cooling source 323 is also connected to one of the fields of each of the padded plates forming the bundle of plates 320. In this way, the inlet manifold of the temperature cooling source intermediate 323 allows the recovery of the fluid coming from the cooling source at intermediate temperature injected inside the plates by the starting manifold 322.
  • the connections of the collectors 322 and 323 to one of the fields of each of the plates respectively of the beams 320 and 330 can be for example a weld.
  • the coolant 4 sprinkling system 311 distributed over the bundle of plates 310 the coolant 4. This distribution can be achieved for example by spraying.
  • the refrigerant 4 thus distributed flows uniformly over the padded plates and vaporizes, cooling the surface of the padded plates. The cold fluid circulating inside the plates is thereby cooled.
  • the outer faces of the padded plates may have been covered with a hydrophilic surface treatment.
  • the geometry of the plates that is to say the fact that they are padded, makes it possible to create turbulence in the refrigerant film 4 and thus to improve the heat exchange coefficient with respect to the plates of the state of technique.
  • the absorbent fluid 5 is distributed over the bundle of padded plates 320 by the sprinkling system 321 of absorbent fluid 5. This distribution can be carried out for example by spraying.
  • the absorbent fluid 5 flows over the padded plates included in the padded sheet bundle 320, creating a film of absorbent fluid 5 in which turbulence is created due to the padding of the plates.
  • the film of absorbent fluid 5 absorbs the vapor of the refrigerant fluid 4 and is therefore diluted by the refrigerant fluid 4 coming from the evaporator 11. This action produces a vacuum which allows circulation of the vapor from the evaporator 11 to the absorber. 12. This action also produces heat, which is recovered by the coolant at intermediate temperature.
  • FIG. 4 schematically shows a sectional view along a transverse plane of the connection between the padded plates included in a bundle of padded plates and the vacuum chamber 301.
  • transverse plane is understood to mean a section plane perpendicular to the largest dimension of a padded plate.
  • the wall of the vacuum vessel 301 is positioned adjacent to the plate bundle as shown. Figure 4 .
  • the padded plates are for example welded on a vertical field with the inner wall of the enclosure 301.
  • the fact that the plates are padded ensures good rigidity of the plate-enclosure assembly 301 and makes it possible to constitute this vacuum enclosure 301 of simple way. This rigidity due to the geometry of the plates makes it possible to dispense with a stiffener or to limit their use.
  • FIG. 5 schematically shows a sectional view along a transverse plane of part of the evaporator / absorber module 300 and of the fluid exchanges between the two exchangers included in this module.
  • each of the plates of the bundles of plates 310 and 320 are distributed respectively the refrigerant fluid 4 and the absorbent fluid 5, distributed by the sprinkling systems presented above.
  • This distribution can be achieved for example by spraying.
  • the cold fluid 401 coming from the cold source and injected by the starting manifold of the cold source 312 circulates inside the padded plates included in the bundle of padded plates 310 of the evaporator 11.
  • the intermediate fluid 402 coming from the cooling source at intermediate temperature and injected by the starting manifold of the intermediate temperature cooling source 322 circulates inside the padded plates included in the bundle of padded plates 320 of the absorber 12.
  • the refrigerant fluid 4 after vaporizing circulates between the padded plates included in the padded plate bundle 310 of the evaporator 11 to the padded plates included in the padded plate bundle 320 of the absorber 12.
  • the padded shape of the plates allows the low pressure vapor of refrigerant 4 to circulate from the evaporator 11 to the absorber 12 without pressure drops and to create turbulence in the films of refrigerant 4 and of absorbent 5, thus improving the heat exchange coefficient.
  • the pitch between the plates is calculated in order to allow the passage of the refrigerant vapor 4 from the evaporator 11 to the absorber 12. For example, a pitch between the plates can be chosen between 20mm and 50mm.
  • FIG. 6 represents a variant of the first embodiment.
  • an anti-drip mat 501 can be positioned between the evaporator 11 and the absorber 12 in order to avoid any pollution of the absorbent film 5 by refrigerant 4.
  • This anti-drip mat 501 allows the vapor of refrigerant 4 while blocking the refrigerant 4 in liquid form, since drops of refrigerant 4 may be carried away by the vapor.
  • An anti-drip mat 501 can also be placed between the generator 13 and the condenser 14, in the same way as for the evaporator 11 and the absorber 12.
  • this anti-drip mat 501 between the generator 13 and the condenser 14 is that it makes it possible to recover in the condenser a refrigerant 4 which is as little diluted as possible, that is to say as pure as possible, thus improving the exchange coefficient in the evaporator 11 where it will be conducted by the following.
  • FIG. 7 schematically shows a variant of the first embodiment in which the padded plates comprise passes.
  • the 700 quilted plate shown Figure 7 comprises linear welds called “passes” 701. If it is included in the evaporator 11, this padded plate can be connected, for example, to the inlet manifolds of the cold source 312 and the inlet of the cold source 313 presented previously, in order to that the cold source fluid circulates inside the plate 700.
  • the passes 701 allow a better distribution of the fluid circulating inside, in order to orient the path of the fluid and to force its contact with the entire surface of the plate.
  • the passes 701 also make it possible to increase the speed and agitation of the fluid, which has the effect of improving the heat exchange coefficient.
  • FIG. 8 shows a schematic representation of a generator / condenser module 800 of an absorption machine according to the first embodiment comprising at least two padded plate exchangers.
  • This module comprises a vacuum chamber 801 in order to ensure the operating conditions of the cycle of the generator 13 and of the condenser 14.
  • a padded plate heat exchanger included in module 800 is generator 13, comprising a padded plate bundle 810, a diluted absorbent fluid sprinkler system 811, a hot source outlet manifold 812, and an inlet manifold. 813 from the cold source.
  • the outlet 812 and inlet 813 collectors of the hot source are connected to one of the fields of each of the padded plates forming the bundle of plates 810 as shown in the Figure 8 .
  • This connection can be for example a solder.
  • Another padded plate heat exchanger included in the module 800 is the condenser 14, comprising a bundle of padded plates 820 and an inlet 822 and inlet 823 manifold of the intermediate temperature cooling source.
  • the two collectors 822 and 23 are connected to one of the fields of each of the padded plates forming the bundle of plates 820. This connection may for example be a weld.
  • the sprinkler system 811 of the generator 13 receives the absorbent 5 diluted with the refrigerant 4 and distributes it over each of the padded plates of the bundle of plates 820. This distribution can be carried out for example by spraying. Inside these plates circulates the fluid coming from the hot source, injected by the starting manifold 812. In contact with the hot padded plates, the refrigerant 4 will vaporize and the absorbent 5 will flow undiluted along the plates. to be recovered by a recuperator (not shown), then sent to the absorber 12 to be distributed.
  • the refrigerant 4 in the form of vapor in contact with the padded plates included in the bundle of plates 820 in which the intermediate temperature fluid injected by the starting manifold 822 circulates, will condense and then flow along the plates to be recovered by a recuperator (not shown), then sent to the evaporator 11 to be distributed.
  • FIG. 9 shows a schematic representation of an evaporator / absorber module 900 of an absorption machine according to the second embodiment comprising at least two padded plate exchangers.
  • the coolant 4 and the absorbent 5 are distributed over the interior surfaces of the padded plates and the fluids from the cold, hot and intermediate sources circulate outside the padded plates. This distribution can be achieved for example by spraying.
  • the evaporator 11 and the absorber 12 respectively comprise an enclosure 901 and 902 which is specific to them, allowing the circulation respectively of the fluid coming from the cold source and the fluid coming from the cooling source at intermediate temperature outside the plates. quilted.
  • the evaporator 11 comprises a starting collector 312 for refrigerant 4 and an arrival collector 313 for refrigerant 4. These collectors are connected to one of the fields of each of the plates included in the bundle of padded plates 310 so as to be able to distribute the heat. refrigerant fluid 4 on the inner walls of the padded plates. This distribution can be achieved for example by spraying. These connections can be welds, for example.
  • the refrigerant 4 thus circulating inside the plates vaporizes because the cold source fluid circulates outside the plates.
  • the refrigerant vapor 4 circulates inside the plates to the vapor manifold 903, which is connected to one of the fields of each of the plates included in the bundle of padded plates 310 and to one of the fields of each of the plates included in the bundle of padded plates 320. These connections may for example be welds. In this way, the refrigerant vapor 4 can reach the absorber 12 in which is distributed by the absorbent inlet manifold 322 the absorbent 5 on the inner walls of the padded plates included in the bundle of padded plates 320.
  • the size of the vapor collector 903 is calculated in order to avoid pressure drops and to allow the passage of vapor to the plates of the absorber.
  • the absorption of the refrigerant 4 by the absorbent 5 creates a vacuum, which creates a circulation of the vapor of refrigerant 4 between the evaporator 11 and the absorber 12 passing through the vapor collector 903.
  • FIG. 10 schematically shows a sectional view along a transverse plane of part of the evaporator / absorber module 800 and of the fluid exchanges between the two exchangers included in this module.
  • Two sheets 405 and 406 form a padded plate 314 and are connected at at least one connection point 403.
  • This connection point 403 may for example be a weld.
  • At least one of the two sheets is curved between two connection points 403 and 407 to form a fluid circulation space 408 between the two sheets 405 and 406.
  • the two sheets 405 and 406 are curved to have a larger exchange surface.
  • Two padded plates 314 and 315 are said to be "adjacent" when the padded plate 314 is adjacent to the padded plate 315 in the plate bundle 310, that is, there is no other padded plate. between the plates 314 and 315.
  • the connection points 403 and 404 of the two adjacent padded plates 314 and 315 are facing each other, in order to create a space for the circulation of steam.
  • the cold fluid 401 circulates outside the padded plates included in the bundle of padded plates 310 of the evaporator 11. It is for example injected inside the enclosure 901 by a cold source fluid outlet manifold. not shown, and recovered by a cold source fluid inlet manifold, not shown.
  • the intermediate temperature cooling fluid 402 circulates outside the padded plates included in the bundle of padded plates 320 of the absorber 12.
  • the refrigerant fluid 4 after being vaporized circulates inside the padded plates included in the padded plate bundle 310 of the evaporator 11 towards the interior of the padded plates included in the padded plate bundle 320 of the absorber 12 by the way by the vapor manifold 903.
  • the circulation of fluids 401 and 402 outside the padded plates allows easier cleaning than when they circulate inside the padded plates thanks to the space between the plates. This is particularly interesting when fouling fluids such as sea water or river water are used as fluid 401 and / or 402.
  • FIG. 11 shows a schematic representation of a generator / condenser module 1000 of an absorption machine according to the second embodiment comprising at least two padded plate exchangers.
  • the generator 13 and the condenser 14 respectively comprise an enclosure 904 and 905 which is specific to them, allowing the circulation respectively of the fluid coming from the hot source and the fluid coming from the cooling source at intermediate temperature outside the padded plates.
  • the generator 13 comprises a starting collector 812 for the refrigerant 4 and an incoming collector 813 for the absorbent 5. These collectors are connected to one of the fields of each of the plates included in the bundle of padded plates 810 so as to be able to distribute the absorbent fluid 5 diluted with the refrigerant fluid 4 on the inner walls of the padded plates. This connection can be for example a solder.
  • the undiluted absorbent fluid 5 is recovered by the inlet manifold 813 and the refrigerant 4, which has vaporized on contact with the hot padded plates 810, circulates in the form of vapor towards the condenser 14, passing through the vapor collector. 906.
  • the vapor collector 906 is connected to one of the fields of each of the plates included in the bundle of padded plates 810 and to one of the fields of each of the plates included in the bundle of padded plates 820. These connections may for example be welds. In this way, the refrigerant vapor 4 can reach the condenser 14 where it condenses. The refrigerant 4 in liquid form is recovered by an inlet manifold 823 to be sent to the evaporator 11.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP20167406.6A 2019-04-10 2020-03-31 Absorptionsmaschine, die gepolsterte platten umfasst Active EP3722730B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR1903846A FR3095035B1 (fr) 2019-04-10 2019-04-10 Machine a absorption comprenant des plaques matelassees

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Publication Number Publication Date
EP3722730A1 true EP3722730A1 (de) 2020-10-14
EP3722730B1 EP3722730B1 (de) 2022-04-20

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1093868A1 (de) * 1999-10-19 2001-04-25 Joh. Vaillant GmbH u. Co. Verfahren zur Herstellung eines Verdampfers/Kondensators
DE102005037708A1 (de) * 2005-08-10 2007-02-15 Albert-Ludwig-Universität Freiburg Anordnung von Wärmetauscherplatten, die in thermischem Kontakt mit einem Adsorbens stehen
WO2007125221A1 (fr) * 2006-05-02 2007-11-08 Peugeot Citroen Automobiles Sa Ensemble evaporateur/absorbeur, dispositif de refroidissement par absorption et vehicule automobile associes
WO2007125220A1 (fr) * 2006-05-02 2007-11-08 Peugeot Citroen Automobiles Sa Dispositif de refroidissement par absorption et vehicule automobile associe
EP2213963A1 (de) * 2009-01-30 2010-08-04 Peugeot Citroën Automobiles SA Klimagerät mit verbesserter Adsorption
FR2989767A1 (fr) * 2012-04-24 2013-10-25 Gaelle Anne Mathilde Duval Echangeur de chaleur a plaques souples
EP3382313A1 (de) * 2017-03-29 2018-10-03 Ostbayerische Technische Hochschule Regensburg Wärmetauscher

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1093868A1 (de) * 1999-10-19 2001-04-25 Joh. Vaillant GmbH u. Co. Verfahren zur Herstellung eines Verdampfers/Kondensators
DE102005037708A1 (de) * 2005-08-10 2007-02-15 Albert-Ludwig-Universität Freiburg Anordnung von Wärmetauscherplatten, die in thermischem Kontakt mit einem Adsorbens stehen
WO2007125221A1 (fr) * 2006-05-02 2007-11-08 Peugeot Citroen Automobiles Sa Ensemble evaporateur/absorbeur, dispositif de refroidissement par absorption et vehicule automobile associes
WO2007125220A1 (fr) * 2006-05-02 2007-11-08 Peugeot Citroen Automobiles Sa Dispositif de refroidissement par absorption et vehicule automobile associe
EP2213963A1 (de) * 2009-01-30 2010-08-04 Peugeot Citroën Automobiles SA Klimagerät mit verbesserter Adsorption
FR2989767A1 (fr) * 2012-04-24 2013-10-25 Gaelle Anne Mathilde Duval Echangeur de chaleur a plaques souples
EP3382313A1 (de) * 2017-03-29 2018-10-03 Ostbayerische Technische Hochschule Regensburg Wärmetauscher

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Publication number Publication date
EP3722730B1 (de) 2022-04-20
FR3095035B1 (fr) 2021-11-05
FR3095035A1 (fr) 2020-10-16

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