EP1724535B1 - Echangeur de chaleur intermédiaire - Google Patents

Echangeur de chaleur intermédiaire Download PDF

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Publication number
EP1724535B1
EP1724535B1 EP06007927A EP06007927A EP1724535B1 EP 1724535 B1 EP1724535 B1 EP 1724535B1 EP 06007927 A EP06007927 A EP 06007927A EP 06007927 A EP06007927 A EP 06007927A EP 1724535 B1 EP1724535 B1 EP 1724535B1
Authority
EP
European Patent Office
Prior art keywords
vessel
chamber tube
chamber
heat
approximately
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.)
Not-in-force
Application number
EP06007927A
Other languages
German (de)
English (en)
Other versions
EP1724535A3 (fr
EP1724535A2 (fr
Inventor
Hubertus R. Dipl.-Ing. Kamsma
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Modine Manufacturing Co
Original Assignee
Modine Manufacturing Co
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Modine Manufacturing Co filed Critical Modine Manufacturing Co
Publication of EP1724535A2 publication Critical patent/EP1724535A2/fr
Publication of EP1724535A3 publication Critical patent/EP1724535A3/fr
Application granted granted Critical
Publication of EP1724535B1 publication Critical patent/EP1724535B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F28D7/1692—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/005—Other auxiliary members within casings, e.g. internal filling means or sealing means
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • 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
    • F25B9/008—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 carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
    • F28F2009/224—Longitudinal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/16—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes extruded

Definitions

  • the invention relates to a device for intermediate cooling of the refrigerant circulating in an air conditioning circuit and having the further features of the preamble of claims 1 and 2.
  • a device for intermediate cooling of the refrigerant circulating in an air conditioning circuit and having the further features of the preamble of claims 1 and 2.
  • Such a device is out of the JP 2003-314927 A known.
  • the JP publication has a tube stack of multi-chamber tubes with interposed heat exchange ribs.
  • a device of this kind which is often referred to as an internal heat exchanger in trans-critical air conditioning circuits, is from the DE 196 35 454A1 known. This can be regarded as progressive with regard to the achievable heat exchange rate.
  • the production of this - lying in the installation space of the motor vehicle - device seems to be quite expensive, inter alia, because the flat multi-chamber tubes are deformed as spirals and the insertion of the heat-conducting ribs between the turns of the spirals is also complicated.
  • the object of the invention is to propose with other design features comparable in terms of compactness and functionality device that can be produced cheaper.
  • the first solution according to the invention results in the device according to the preamble of claim 1 by the features in its characterizing part.
  • a second solution according to the invention is the subject of claim 2.
  • the container is an approximately round, slender, pressure-stable container, which is formed substantially over its entire length as a heat exchanger.
  • the multi-chamber tube is occupied with heat exchange ribs, which are the remaining cross section of the container or at least the cross section of a department of Fill container approximately.
  • the multi-chamber tube extends straight through the container, which is why, among other things, the ease of production is expected.
  • the multi-chamber tube and the container are preferably parts produced by extrusion. Since the container is designed over its entire length as a heat exchanger, good results with regard to the heat exchange efficiency can be expected.
  • the container or the intermediate heat exchanger has a decidedly slim appearance and is therefore particularly suitable for applications in which narrow spaces are present. For the purposes of the present invention, containers with a length / diameter ratio of at least 3: 1 or greater are to be regarded as slim containers.
  • the multi-chamber tube or the longitudinal wall divides the container into compartments, the multi-chamber tube extending longitudinally through at least one compartment.
  • the intermediate heat exchanger according to the invention is also particularly favorable to produce because of the continuous use of the extrusion process for the container and for the multi-chamber tube.
  • the multi-chamber tube extends substantially straight through the compartment, i. H. it does not have to be reshaped.
  • the heat exchange fin fills the remaining section cross-section approximately completely, which is why good results are to be expected in terms of heat exchange efficiency.
  • the already mentioned extrusion process for the production of the round container makes it possible to form the departmental cross-section, for example, rectangular, which is why there heat exchange ribs without substantial pinch are very cheap and while doing, as mentioned, the departmental cross-section about complete.
  • Approximately rectangular or square section cross sections are achieved either by the wall thickness of the container is partially increased, or in that in the longitudinal direction of the container extending gradations of the otherwise round container are made. Both options can be implemented by means of the forming process extrusion or extrusion. Therefore, the extrusion process for producing the container is particularly preferred.
  • the multi-chamber tube could also be a brazed or welded tube with an interior insert forming the chambers.
  • the heat exchanger rib can made extremely thin sheet metal, since it is not exposed to significant compressive stresses.
  • Fig. 1 and 2 forms a round tube produced by extrusion process the container 20.
  • the tube has two longitudinal walls 21 and 22 , which divide the tube into three compartments 23, 24 and 25 .
  • a flat, extruded multi-chamber tube 10 over approximately the entire length of the tube.
  • Each multi-chamber tube 10 has two rows of passages 12 in this embodiment .
  • the diameter of the passages 12 is about 1.20 mm or less.
  • Each multi-chamber tube 10 is provided with a heat-conducting rib 30 which fills the cross-section of the corresponding compartment as completely as possible so that the refrigerant flowing there does not have to flow through large, free cross-sectional spaces.
  • the high-pressure side refrigerant flows (arrows in Fig. 1 ) above through the central connection opening in the flat and larger multi-chamber tube 10 , flows down, there is distributed to the other two smaller multi-chamber tubes 10, in this back up and over the two outflow further to the expansion device, not shown, and continue through the evaporator stream.
  • the low-pressure side refrigerant flows above the associated inflow opening 60 either into the middle compartment 23 or into all three compartments, flows through the local heat exchange fins 30 down and distributed to the other two departments, or it flows in the second case there from the intermediate heat exchanger off and on to the compressor, not shown in the circulation.
  • the tube has a suitable cover 50 at the top and at the bottom, which complete the container 20 . As can be seen, flow channels for the high-pressure side refrigerant are formed in the cover 50 .
  • the preferred material is aluminum. The mentioned parts are joined together and connected by soldering.
  • the Fig. 3 shows the inflow and outflow of the high pressure side and the low pressure side refrigerant in an embodiment already briefly mentioned above.
  • the reference numerals 60 to 63 represent the low-pressure side refrigerant. At 60 , this refrigerant flows into the middle compartment 23 , or it exits there from this department.
  • the reference numeral 63 stands for a terminal block having channels and belonging to the mentioned soldered parts.
  • Reference numerals 61 and 62 designate two further inflow or outflow openings or the mentioned channels which communicate with the other two compartments 24 and 25 .
  • Reference numerals 70-74 denote the flow channels and connections for the high-pressure side refrigerant, which are formed in the upper cover 50 and communicating with the multi-chamber tubes 10 likewise already mentioned.
  • the middle section 24 was occupied by the multi-chamber tube 10 and the heat exchanger rib 30 .
  • the low-pressure side refrigerant may flow or may not flow. It should be emphasized that the longitudinal walls 26 much thinner than in the Fig. 4 can be performed to see, as in the departments 23, 24, 25 is about the same pressure.
  • the Fig. 5 shows a schematic representation of a modified embodiment, which has a container 20 with a slightly lower degree of slimming.
  • the multi-chamber pipe 10 has a reverse bend 11.
  • HP stands for the high-pressure section
  • LP correspondingly for the low-pressure section.
  • the lower lid 50 is curved and the longitudinal wall 21 terminates so that the low-pressure side refrigerant can flow there from the department 23 over to the other department 24 .
  • the remaining cross section of both compartments 23 and 24 is filled by heat exchange fins 30 .
  • Fig. 6 and 7 show examples that facilitate the insertion of the heat exchange fins 30 with the multi-chamber tube 10 , since the corresponding section cross section of the compartments 23 and 25 in the container 20 has been designed with a suitable adapted shape.
  • the wall thickness of the container 20 was partially increased somewhat, which was illustrated by the reference numeral 27 .
  • the Fig. 7 paragraphs were introduced into the wall of the container 20 by the reference numeral 28 .
  • Such embodiments are easy to produce by the extrusion process.
  • the heat exchange fins 30 common corrugated fins may be used, the spirally wound around the corresponding multi-chamber pipe 10 and then can be used together in the compartment 23, 24, 25 with the tube. This is not clear from the illustrations and should therefore be emphasized.
  • the Fig. 8 shows the simplest embodiment of the device according to the invention.
  • the multi-chamber tube 10 extends straight and lying on the central longitudinal plane of the container 20 through the same therethrough.
  • the semicircular cross sections of the created by the multi-chamber tube 10 sections 23 of the container 20 are filled by heat fins 30 .
  • the heat-conducting fins 30 have for this purpose adapted to the round shape of the container 20 fin height.
  • the Fig. 9 shows a further cross section through a particularly production-friendly device.
  • the container 20 longitudinal walls 21, 22 are provided.
  • the longitudinal walls 21, 22 are equipped with bent longitudinal edges 40 which bear against the inside of the container wall.
  • the longitudinal edges 40 have a certain elasticity.
  • the multi-chamber tube 10, the heat-conducting fins 30 and the two longitudinal walls 21, 22 are folded into a package and pushed together into the container 20 .
  • the longitudinal edges 40 nestle against the container wall. This also enables or supports perfect solder joints.
  • Department 23 is going through Heat-conducting fins 30 filled, which have a uniform rib height and therefore are inexpensive to produce.
  • the efficiency of the heat exchange and the small space requirement because of the very slim shape of the container 20 are further advantageous effects.
  • the slenderness of the container 20, expressed by the ratio of length L / diameter D, is at least 3: 1. Preferably, however, 6: 1 or even slimmer. ( Fig. 1 )

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (13)

  1. Echangeur de chaleur intermédiaire du réfrigérant qui circule dans un circuit de climatisation et traverse ainsi un côté haute pression et un côté basse pression dans lesquels le réfrigérant est à différentes températures, l'échangeur comprenant un tubage à plusieurs chambres (10) plat disposé dans un réservoir (20), sachant que le réservoir est formé essentiellement sur toute sa longueur comme un échangeur de chaleur et que le tubage à plusieurs chambres (10) est occupé par des nervures d'échange de chaleur (30), caractérisé en ce que le réservoir (20) est un réservoir (20) sensiblement rond, mince et à pression stable et que dans le réservoir (20), des sections (23) sont formées par l'agencement du tubage à plusieurs chambres plat et essentiellement droit sur le plan longitudinal médian de celui-ci, les sections transversales sensiblement semi-circulaires desquelles sections (23) étant sensiblement comblées par les nervures d'échange de chaleur (30).
  2. Echangeur de chaleur intermédiaire du réfrigérant qui circule dans un circuit de climatisation et traverse ainsi un côté haute pression et un côté basse pression dans lesquels le réfrigérant est à différentes températures, l'échangeur comprenant un tubage à plusieurs chambres (10) plat disposé
    dans un réservoir (20), sachant que le réservoir est formé essentiellement sur toute sa longueur comme un échangeur de chaleur et que le tubage à plusieurs chambres (10) est occupé par des nervures d'échange de chaleur (30), caractérisé en ce que le réservoir (20) est un réservoir (20) sensiblement rond, mince et à pression stable et qu'au moins une paroi longitudinale (21) est prévue qui divise le réservoir en sections (23, 24) et que le tubage à plusieurs chambres (10) s'étend dans le sens longitudinal et essentiellement non déformé à travers au moins une section (23), sachant que la section transversale restante de la section (23) est sensiblement comblée par les nervures d'échange de chaleur (30).
  3. Echangeur selon la revendication 1 ou 2, caractérisé en ce que les nervures d'échange de chaleur (30) ne sont soumises pratiquement à aucune compression.
  4. Echangeur selon l'une des revendications précédentes, caractérisé en ce que le réservoir (20) est complété par deux couvercles (50).
  5. Echangeur selon l'une des revendications 2 à 4, caractérisé en ce qu'une pluralité de parois longitudinales (21, 22) est prévue dans le réservoir (20), lesquelles sont parallèles entre elles.
  6. Echangeur selon l'une des revendications 2 à 5, caractérisé en ce que la forme de section transversale des sections (23, 24, 25) est adaptée pour recevoir le tubage à plusieurs chambres (10) avec des nervures d'échange de chaleur (30), qu'elle est rectangulaire par exemple.
  7. Echangeur selon l'une des revendications 2 à 6, caractérisé en ce que le tubage à plusieurs chambres (10) plat présente un arc d'inversion (11) et s'étend pour le reste en ligne droite à travers deux sections parallèles (23, 24) qui sont formées au moyen de la paroi longitudinale (21).
  8. Echangeur selon l'une des revendications 2 à 6, caractérisé en ce que chaque tubage à plusieurs chambres (10) plat s'étend à travers une section (23, 24, 25) associée, sachant que le réfrigérant est amené à un côté par exemple par l'un des tubages à plusieurs chambres (10) et est évacué par deux autres tubages à plusieurs chambres (10), ou inversement.
  9. Echangeur selon la revendication 8, caractérisé en ce qu'un des tubages à plusieurs chambres (10) présente une section transversale plus grande que les autres tubages à plusieurs chambres.
  10. Echangeur selon les revendications 8 et 9, caractérisé en ce que le tubage à plusieurs chambres (10) le plus grand est disposé sensiblement sur le plan médian du réservoir (20) sensiblement rond.
  11. Echangeur selon l'une des revendications précédentes, caractérisé en ce que les chambres (12) dans le tubage à plusieurs chambres (10) plat ont un diamètre de 1,20 mm ou moins.
  12. Echangeur selon l'une des revendications précédentes, caractérisé en ce que le rapport longueur/diamètre (L/D) du réservoir (20) est d'au moins 3 : 1.
  13. Echangeur selon l'une des revendications précédentes, caractérisé en ce que tant le réservoir (20) que le tubage à plusieurs chambres (10) peuvent être fabriqués au moyen d'un procédé par extrusion.
EP06007927A 2005-05-10 2006-04-15 Echangeur de chaleur intermédiaire Not-in-force EP1724535B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005021464A DE102005021464A1 (de) 2005-05-10 2005-05-10 Vorrichtung zur Zwischenkühlung

Publications (3)

Publication Number Publication Date
EP1724535A2 EP1724535A2 (fr) 2006-11-22
EP1724535A3 EP1724535A3 (fr) 2008-07-02
EP1724535B1 true EP1724535B1 (fr) 2010-09-01

Family

ID=36889203

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06007927A Not-in-force EP1724535B1 (fr) 2005-05-10 2006-04-15 Echangeur de chaleur intermédiaire

Country Status (3)

Country Link
US (1) US20060254757A1 (fr)
EP (1) EP1724535B1 (fr)
DE (2) DE102005021464A1 (fr)

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DE102009024202A1 (de) * 2009-06-08 2010-12-09 Andreas Jahn Wärmetauscher für eine Kältemaschine und Verfahren zur Herstellung eines Wärmetauschers
DE102009047620C5 (de) * 2009-12-08 2023-01-19 Hanon Systems Wärmeübertrager mit Rohrbündel
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US9464847B2 (en) 2011-02-04 2016-10-11 Lockheed Martin Corporation Shell-and-tube heat exchangers with foam heat transfer units
US9951997B2 (en) 2011-02-04 2018-04-24 Lockheed Martin Corporation Staged graphite foam heat exchangers
CA2826141C (fr) * 2011-02-04 2019-02-26 Lockheed Martin Corporation Echangeur de chaleur a ailettes en mousse
WO2012106601A2 (fr) 2011-02-04 2012-08-09 Lockheed Martin Corporation Échangeur de chaleur à écoulement radial à ailettes d'échange de chaleur en mousse
DE102011012577A1 (de) * 2011-02-26 2012-08-30 Volkswagen Ag Wärmeaustauschvorrichtung
CN103635771A (zh) * 2011-06-27 2014-03-12 开利公司 微孔壳管式换热器
DE102012224353A1 (de) * 2012-12-21 2014-06-26 Behr Gmbh & Co. Kg Wärmeübertrager
DE102017216943A1 (de) * 2017-09-25 2019-03-28 BSH Hausgeräte GmbH Kältegerät mit Lagerkammer und Verdampferkammer
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DE102005021464A1 (de) 2006-11-16
EP1724535A3 (fr) 2008-07-02
EP1724535A2 (fr) 2006-11-22
US20060254757A1 (en) 2006-11-16
DE502006007755D1 (de) 2010-10-14

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