WO2014095594A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2014095594A1
WO2014095594A1 PCT/EP2013/076449 EP2013076449W WO2014095594A1 WO 2014095594 A1 WO2014095594 A1 WO 2014095594A1 EP 2013076449 W EP2013076449 W EP 2013076449W WO 2014095594 A1 WO2014095594 A1 WO 2014095594A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
flow
flow channel
refrigerant
tubes
Prior art date
Application number
PCT/EP2013/076449
Other languages
German (de)
English (en)
Inventor
Gottfried DÜRR
Herbert Hofmann
Christoph Walter
Uwe FÖRSTER
Original Assignee
Behr Gmbh & Co. Kg
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 Behr Gmbh & Co. Kg filed Critical Behr Gmbh & Co. Kg
Priority to EP13814488.6A priority Critical patent/EP2936030A1/fr
Publication of WO2014095594A1 publication Critical patent/WO2014095594A1/fr

Links

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
    • F28D7/0008—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 for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0025—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 for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
    • 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
    • F25B39/04—Condensers
    • 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
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • 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
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0073—Gas coolers

Definitions

  • the invention relates to a heat exchanger with a first flow channel for a refrigerant, wherein the refrigerant is or contains CO 2 , and with a second flow channel for a liquid coolant, wherein at least a portion of the first flow channel with a portion of the second flow channel in thermal Contact is, wherein the refrigerant and the coolant in their flow channels in the DC and / or counterflow to each other are flowable, wherein the first flow channel is configured such that it withstands internal pressures of 100 bar and more, wherein the first flow channel of a plurality of first flow paths is formed, which are in fluid communication with a first manifold, wherein the second flow channel is formed of a plurality of second flow paths, which are in fluid communication with a second manifold.
  • condensers are used to cool a refrigerant to the condensation temperature and then condense the refrigerant.
  • a refrigerant come in solutions
  • different fluids are used. Both liquid and gaseous refrigerants are used for this purpose. Partly takes place in the Fluids idstrom of the refrigerant, a phase transition between a liquid and a gaseous phase instead.
  • capacitors are known in which the refrigerant undergoes no phase transition. These capacitors regularly have only one cooling section, in which the refrigerant is brought into thermal contact with a coolant.
  • refrigerants used are R-134a, R-1234yf or CO 2 (R744). While the refrigerants R-134a and R-1234yf have relatively low pressures on the refrigerant side, relatively high pressure prevails in systems using CO 2 as the refrigerant. This can be significantly greater than 100 bar.
  • a disadvantage of the devices known from the prior art is in particular that when using CO 2 (R744) as refrigerant high pressures within the refrigerant circuit occur, which burden the previously known heat exchanger beyond their load limits.
  • the object of the present invention is achieved by a heat exchanger with the features of claim 1.
  • An embodiment of the invention relates to a heat exchanger with a first flow channel for a refrigerant, wherein the refrigerant is or contains CO 2 , and with a second flow channel for a liquid coolant, wherein at least a portion of the first flow channel with a portion of the second flow channel in thermal Contact is, wherein the refrigerant and the coolant in their flow channels in the DC and / or counterflow to each other are flowable, wherein the first flow channel is configured such that it withstands internal pressures of 100 bar and more, wherein the first flow channel of a plurality of first flow paths is formed, which are in fluid communication with a first manifold, wherein the second flow channel is formed of a plurality of second flow paths, which are in fluid communication with a second manifold route, wherein the ratio of the hydrauli - See diameter of the second flow channel and the hydraulic diameter of the first flow channel is greater than 2: 1.
  • the ratio is greater than 5: 1 and furthermore it is preferred if the ratio is in the range between 5: 1 and 10: 1.
  • the hydraulic diameter of the second flow path in the range indicated above leads to a particularly advantageous ratio of possible heat transfer and pressure drop within the second flow path.
  • the hydraulic diameter of a first flow path is in a range between 0 mm and 1, 0 mm, preferably between 0.3 mm and 1, 0 mm.
  • a hydraulic diameter of the first flow path as described above makes it possible to realize a sufficiently high heat transfer, while at the same time achieving a sufficiently high pressure resistance of the first flow paths.
  • This high pressure resistance is particularly necessary when using CO 2 as a refrigerant, since internal pressures of more than 100 bar may occur.
  • the first distribution route has a flow cross-sectional area of 14 mm 2 to 50 mm 2 or has a flow cross-sectional area of 14 mm 2 to 40 mm 2.
  • a flow cross-sectional area in the range indicated above is particularly advantageous when the heat exchanger is used in a motor vehicle. In particular with regard to the mass flows occurring there.
  • the first distribution route has a flow cross-sectional area which is 5% to 50% of the flow cross-sectional area of the second distribution route, preferably a Strömungsquerschn 'rttsflä- which is 10% to 30% of the flow cross-sectional area of the second distribution line.
  • the second flow channel at least partially has a structured surface in its interior and / or has turbulence inserts.
  • a structured surface or turbulence inserts increase overall the heat transfer area of the second flow channel, which increases the overall efficiency of the heat exchanger.
  • a preferred embodiment is characterized in that the first flow channel has at least partially elliptical and / or circular inner diameter.
  • An elliptical or even circular inner diameter is particularly advantageous, in particular with regard to the necessary compressive strength.
  • the heat exchanger is formed in a stacked disk construction, wherein the heat exchanger consists of a plurality of stacked disk elements, between which channels are formed, wherein a first number of channels is associated with the first flow channel and a second number of channels is associated with the second flow channel.
  • a heat exchanger in stacking disc design is characterized by a particularly compact design. This facilitates the placement of the heat exchanger inside a motor vehicle.
  • a manufactured in stacking disk construction heat exchanger is particularly low to produce, since a large number of identical parts can be used.
  • the heat exchanger is a flat tube turbulence heat exchanger, wherein the first flow channel is formed by a number or plurality of first tubes, which are enclosed by a housing, wherein the second flow channel between the housing and the number or plurality of first tubes is formed.
  • a heat exchanger in which a medium flows in a first tube can be realized in a particularly simple manner, wherein the medium flows around the tube.
  • the second flow channel is formed by a housing which encloses the tubes of the first flow channel.
  • the heat exchanger is designed as a tube-tube heat exchanger, wherein the first flow channel is formed by a number or plurality of second tubes, and the second flow channel of a single or plurality of third tubes is formed, wherein the second tubes and the third tubes at least portion Werse are in thermal contact with each other.
  • the construction of a tube-tube heat exchanger is particularly advantageous because the structure is very simple.
  • the tubes of the two fluids are particularly easy to bring into thermal contact with each other.
  • the tubes for the heat exchanger are particularly simple and inexpensive to produce. A scaling of the heat exchanger is possible in a simple manner.
  • FIG. 1 shows a sectional view through a heat exchanger in Stapelaminbauwei- se, wherein in the left portion of the figure, the refrigerant flows into the heat exchanger and in the right part of the figure, the coolant flows out of the heat exchanger,
  • FIG. 2 is a sectional view of a tube-tube heat exchanger, wherein the first flow channel is formed by a plurality of circular flow paths and the second flow channel is formed by a plurality of flat tubes,
  • FIG 3 is a sectional view through a flat tube turbulence insert heat exchanger wherein the first flow channel is formed by a plurality of circular flow paths and the second flow channel is formed by a gap formed between the first flow paths and a housing surrounding the first flow paths .
  • FIG. 4 shows a sectional view through a flat-tube turbulence-insert heat exchanger, wherein additionally a supply line stub and a discharge stub are depicted
  • FIG. 5 shows a perspective view of a flat-tube turbulence insert heat transfer.
  • the heat exchanger 1 shows a sectional view through a heat exchanger 1.
  • the heat exchanger 1 is constructed in a stacked disk design. In this case, a multiplicity of disk elements 5 are stacked on one another such that 5 channels 8, 9 result between the disk elements.
  • the disk stack is closed at the top and at the bottom by a cover disk element 4.
  • the disk elements 5, which form the stack mainly, are largely identical and differ only by the alignment zueinan-.
  • the inflow region of the refrigerant is shown.
  • the refrigerant flows along the arrow 2 in the heat exchanger 1 a.
  • the disk elements 5 have openings which are arranged in such a way that a distribution line 6 results.
  • the refrigerant can flow through the individual disk elements 5 and spread there into the channels 8.
  • the coolant flows.
  • a thermal exchange between the refrigerant in the channels 8 and the coolant in the channels 9 takes place via the disk elements 5.
  • the region of the heat exchanger 1 is shown, in which the coolant flows out of the heat exchanger 1.
  • the flow direction of the coolant is shown by the arrow with the reference numeral 3.
  • the disk elements 5 form openings in the outflow region of the coolant from the heat exchanger 1, which allow the coolant to flow through the individual disk elements 5 along the distributor path 7.
  • the distribution path 7 is in direct fluid communication with the channels 9.
  • channels 8 are indicated, which lead the refrigerant. It can be seen that the flow cross section of the distributor section 6 of the refrigerant and the flow cross section of the distributor section 7 of the coolant deviate significantly from one another.
  • the flow cross-section of the distributor route 7 of the coolant is significantly larger than the flow cross-section of the distributor route 6.
  • the distributor route 6 of the refrigerant has, in a preferred embodiment, a flow cross-sectional area of 14 to 50 mm 2 .
  • the flow cross-sectional area of the distributor section 6 has a flow cross-sectional area of 14 to 40 mm 2 .
  • the relatively small flow cross-sectional area of the distributor route 6 is based, in particular, on the high pressures of the refrigerant and the low mass flows within the heat exchangers, in particular for use in motor vehicles.
  • the ratios of the flow cross-sectional area of the refrigerant manifolds 6 and the coolant manifold 7 should preferably be such that the flow area of the manifold 6 is about 5 to 50%, ideally 10 to 30%, of the flow area of the manifold 7 of the coolant.
  • the small diameters of the distributor route 6 contribute in particular to ensuring a better heat transfer from the refrigerant which flows through the heat exchanger 1 to the coolant. Since the refrigerant is preferably CO 2 , the refrigerant is substantially in a gaseous phase.
  • ratios of the hydraulic diameter of the coolant side to the coolant side of greater than 2: 1, more preferably greater than 5: 1, ideally in a range greater than 5: 1 and less than 10: 1 have been found .
  • the individual channels 8, 9 have different diameters between the disk elements 5. This can be realized in particular by changing the distances between the disk elements 5 relative to each other. Through a change in the diameter of the channels 8, 9, the total hydraulic diameter on the refrigerant side and on the coolant side can also be changed.
  • FIG. 2 shows a section through a so-called pipe-tube heat exchanger 10.
  • a plurality of tubes 12, 13 are alternately stacked. These tubes 12, 13 are arranged inside a housing 11. The heat transfer takes place between the fluids flowing in the tubes 12, 13.
  • the tubes 13 are formed, for example, by flat tubes which have partition walls 14 inside the tubes 13, which subdivide the tubes 13 into individual flow paths 16.
  • the tubes 12 have a plurality of circular flow paths 15.
  • the tubes 12 are used in particular to guide the refrigerant within the heat exchanger 10.
  • the tubes 13 serve to guide the coolant.
  • the hydraulic diameter of the refrigerant side is substantially smaller than the hydraulic diameter of the coolant side.
  • the flow paths 15, which are assigned to the refrigerant side are suitable by their circular configuration for the guidance of a fluid which is under high pressure.
  • the hydraulic diameter of the individual coolant channels, which are represented by the flow paths 16, is ideally in a range of 2 to 4 mm.
  • the hydraulic diameter of the channels of the refrigerant side, which are represented by the flow paths 15 should ideally be in a range between 0 and 1 mm, ideally in a range between 0.3 mm and 1 mm.
  • FIG. 3 shows a so-called flat-tube turbulence-insert heat exchanger 20.
  • a plurality of tubes 22 are arranged within a housing 21, between which turbulence inserts 24 are arranged, which space the tubes 22 from one another.
  • the tubes 22 are designed analogously to the embodiment already described in FIG. 2 such that they have a plurality of flow paths 23.
  • the tubes 22 and the flow paths 23 are also associated with the refrigerant. By created by the turbulence inserts 24 flow paths 25 between the tubes 22, the coolant flows.
  • the flow paths 23 are circular in order to withstand the high pressures of the refrigerant can.
  • the turbulence inserts 24 are formed like corrugated ribs. In addition to the illustration shown in Fig. 3, various other possible embodiments of the turbulence inserts 24 are providable. Core task of the turbulence inserts is the enlargement of the heat transfer surface of the flow paths 25 to the tubes 22 and the complaint of the tubes 22 from each other.
  • FIG. 4 shows a sectional view through a further flat-tube turbulence insert heat exchanger 30.
  • the basic structure of the central heat exchanger core corresponds to that of FIG. 3.
  • the tubes 32 have a large number flow paths 33, which have a circular cross-section. Between the tubes 32 turbulence inserts 34 are arranged, which form flow paths 35 and the tubes 32 to each other.
  • the flow paths 33 are substantially smaller in relation to the flow paths 35 which guide the coolant.
  • connecting pieces 36 and 37 which are arranged on the housing 31 on the outside, are now also shown. Via the connecting pieces 36, 37, a fluid can flow into the heat exchanger 30. In FIG. 4, the coolant, which is distributed along the flow paths 35 between the tubes 32, preferably flows in and out via the connecting pieces 36, 37.
  • FIG. 5 shows a further perspective view of a flat-tube turbulence-insert heat exchanger 40.
  • the heat exchanger 40 has a housing 41, in which, similar to FIGS. 3 and 4 above, turbulence inserts 46 are arranged, which space and space tubes between one another Form the tubes flow paths for a coolant.
  • a refrigerant in particular CO 2 flows .
  • the coolant is supplied to the heat exchanger 40 and discharged.
  • the refrigerant is discharged into the heat exchanger 40 or.
  • the inner structure corresponds to the flat tube turbulence heat exchangers of FIGS. 3 and 4.
  • All embodiments of the heat exchangers of FIGS. 1 to 5 shown have in common that the hydraulic diameter of the coolant side is greater in relation to the hydraulic diameter of the refrigerant side.
  • the hydraulic diameter of the coolant side is in particular greater than a ratio of 2: 1, preferably greater than a ratio of 5: 1, ideally even greater than a ratio of 5: 1 and less than a ratio of 10: 1. Due to the smaller hydraulic diameter on the refrigerant side, a more efficient cooling of the gas stream can be achieved by a better heat transfer between the refrigerant and the coolant is generated.
  • the hydraulic diameter of the coolant side must be selected larger in order to keep the pressure drop on the coolant side as low as possible. The ratio described has proven to be particularly suitable for applications in motor vehicles.
  • the coolant channels which are represented by the different flow paths of the coolant side, should have a hydraulic diameter of approximately 2 to 4 mm.
  • the channels of the refrigerant side which are represented by the corresponding flow paths, should have a hydraulic diameter smaller than 1 mm.
  • the hydraulic diameter of the refrigerant side should be between 0.3 and 1 mm.
  • the distribution channels of the individual heat exchangers which distribute the respective fluids to the individual flow channels, should be designed such that the flow cross section, in particular of the distribution channel of the refrigerant side, has an area of approximately 14 to 50 mm 2 , preferably an area of 14 to 40 mm 2 is particularly due to the high pressures that the refrigerant may have within the heat exchanger.
  • the flow cross-sectional areas of the refrigerant side distribution channels should be started such that the flow cross-sectional area of the refrigerant side distribution channels is approximately 5 to 50%, more preferably 10 to 30% of the flow cross-sectional area of the distribution channels of the refrigerant side.
  • the flow cross-sectional areas of the refrigerant side must each be as low as possible, in particular due to the high pressure of the refrigerant.
  • the flow channels on the coolant side can advantageously have a structured surface. This structured surface allows the heat transfer tion surface of the coolant side can be significantly increased.
  • one or more turbulence inserts can be used on the coolant side.
  • the refrigerant selt should have no roughened surfaces and no turbulence inserts. The smoothest possible surface is to be preferred on the refrigerant side.
  • the channels for the refrigerant are ideally equipped with an elliptical or even a circular inner diameter. This is particularly advantageous in terms of the necessary pressure resistance. All the heat exchangers shown may ideally have one or more deflections in their interior, whereby the refrigerant side and / or the coolant side is deflected in its main flow direction. It is particularly preferable if the refrigerant and the coolant flow at least partially in countercurrent to each other.
  • the refrigerant and the coolant flow countercurrently over the entire flow path within the heat exchanger. It is particularly advantageous if the refrigerant flows in countercurrent with the coolant at least in the last section of the heat exchanger before the refrigerant exit.
  • FIGS. 1 to 5 are merely exemplary embodiments and for their part have no limiting character for the design of the individual heat exchangers.
  • the individual flow paths and channels can be formed in other embodiments by other shape or other tube designs.
  • the design of the connection piece and the housing is merely exemplary.

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

Abstract

L'invention concerne un échangeur de chaleur (1, 10, 20, 30, 40) pourvu d'un premier canal d'écoulement pour un fluide frigorigène, le fluide frigorigène étant ou contenant en particulier du CO2, et pourvu d'un deuxième canal d'écoulement pour un réfrigérant liquide. Au moins une partie du premier canal d'écoulement est en contact thermique avec une partie du deuxième canal d'écoulement. Le fluide frigorigène et le réfrigérant peuvent circuler dans leurs canaux d'écoulement l'un par rapport à l'autre dans le même sens et/ou dans des sens contraires. Le premier canal d'écoulement est réalisé de telle manière qu'il résiste à des pressions intérieures supérieures ou égales à 100 bar. Le premier canal d'écoulement est constitué d'une pluralité de trajets d'écoulement (8, 15, 23, 33), lesquels sont en communication fluidique avec un premier parcours de distribution (6), le deuxième canal d'écoulement étant constitué d'une pluralité de deuxièmes trajets d'écoulement (9, 16, 25, 35), lesquels sont en communication fluidique avec un deuxième parcours de distribution (7). Le rapport entre le diamètre hydraulique du deuxième canal d'écoulement et le diamètre hydraulique du premier canal d'écoulement est supérieur à 2:1, de préférence supérieur à 5:1 et de préférence compris entre 5:1 et 10:1.
PCT/EP2013/076449 2012-12-21 2013-12-12 Échangeur de chaleur WO2014095594A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP13814488.6A EP2936030A1 (fr) 2012-12-21 2013-12-12 Échangeur de chaleur

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012224353.4A DE102012224353A1 (de) 2012-12-21 2012-12-21 Wärmeübertrager
DE102012224353.4 2012-12-21

Publications (1)

Publication Number Publication Date
WO2014095594A1 true WO2014095594A1 (fr) 2014-06-26

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EP (1) EP2936030A1 (fr)
DE (1) DE102012224353A1 (fr)
WO (1) WO2014095594A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2966391B1 (fr) * 2014-07-09 2017-03-08 MAHLE International GmbH Échangeur de chaleur
DE102014221168A1 (de) * 2014-10-17 2016-04-21 Mahle International Gmbh Wärmeübertrager
FR3037387B1 (fr) * 2015-06-12 2019-07-19 Valeo Systemes Thermiques Echangeur de chaleur pour vehicule automobile

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003279138A (ja) * 2002-03-20 2003-10-02 Sanyo Electric Co Ltd 熱交換器及びそれを用いたヒートポンプ式給湯装置
FR2846733A1 (fr) * 2002-10-31 2004-05-07 Valeo Thermique Moteur Sa Condenseur, notamment pour un circuit de cimatisation de vehicule automobile, et circuit comprenant ce condenseur
US20040094291A1 (en) * 2002-11-19 2004-05-20 Memory Stephen B. High pressure heat exchanger
US20050155749A1 (en) * 2004-01-20 2005-07-21 Memory Stephen B. Brazed plate high pressure heat exchanger
EP1571407A2 (fr) * 2004-03-05 2005-09-07 Modine Manufacturing Company Echangeur de chaleur à plaques
FR2912811A1 (fr) * 2007-02-16 2008-08-22 Valeo Systemes Thermiques Echangeur de chaleur pour fluides a circulation en u
FR2939187A1 (fr) * 2008-12-01 2010-06-04 Valeo Systemes Thermiques Echangeur de chaleur a spires et dispositif de climatisation comprenant un tel echangeur de chaleur
WO2010108992A1 (fr) * 2009-03-26 2010-09-30 Valeo Systemes Thermiques Echangeur de chaleur, en particulier condenseur de climatisation
EP2410278A1 (fr) * 2009-03-18 2012-01-25 Mitsubishi Electric Corporation Échangeur thermique de type à plaques et dispositif de conditionnement d'air et de réfrigération

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19845336A1 (de) * 1998-10-01 2000-04-06 Behr Gmbh & Co Mehrkanal-Flachrohr
JP3945208B2 (ja) * 2001-10-09 2007-07-18 株式会社デンソー 熱交換用チューブ及び熱交換器
DE10160380A1 (de) * 2001-12-10 2003-06-18 Bosch Gmbh Robert Vorrichtung zur Wärmeübertragung
DE10346141B4 (de) * 2003-10-01 2006-04-13 Eaton Fluid Power Gmbh Wärmetauschereinheit
DE102005058153B4 (de) * 2005-04-22 2007-12-06 Visteon Global Technologies Inc., Van Buren Wärmeübertrager mit Mehrkanalflachrohren
DE102005021464A1 (de) * 2005-05-10 2006-11-16 Modine Manufacturing Co., Racine Vorrichtung zur Zwischenkühlung

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003279138A (ja) * 2002-03-20 2003-10-02 Sanyo Electric Co Ltd 熱交換器及びそれを用いたヒートポンプ式給湯装置
FR2846733A1 (fr) * 2002-10-31 2004-05-07 Valeo Thermique Moteur Sa Condenseur, notamment pour un circuit de cimatisation de vehicule automobile, et circuit comprenant ce condenseur
US20040094291A1 (en) * 2002-11-19 2004-05-20 Memory Stephen B. High pressure heat exchanger
US20050155749A1 (en) * 2004-01-20 2005-07-21 Memory Stephen B. Brazed plate high pressure heat exchanger
EP1571407A2 (fr) * 2004-03-05 2005-09-07 Modine Manufacturing Company Echangeur de chaleur à plaques
FR2912811A1 (fr) * 2007-02-16 2008-08-22 Valeo Systemes Thermiques Echangeur de chaleur pour fluides a circulation en u
FR2939187A1 (fr) * 2008-12-01 2010-06-04 Valeo Systemes Thermiques Echangeur de chaleur a spires et dispositif de climatisation comprenant un tel echangeur de chaleur
EP2410278A1 (fr) * 2009-03-18 2012-01-25 Mitsubishi Electric Corporation Échangeur thermique de type à plaques et dispositif de conditionnement d'air et de réfrigération
WO2010108992A1 (fr) * 2009-03-26 2010-09-30 Valeo Systemes Thermiques Echangeur de chaleur, en particulier condenseur de climatisation

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
HWANG Y ET AL: "THEORETICAL EVALUATION OF CARBON DIOXIDE REFRIGERATION CYCLE", HVAC&R RESEARCH, AMERICAN SOCIETY OF HEATING, REFRIGERATING AND AIR- CONDITIONING ENGINEERS, ATLANTA, GA; US, vol. 4, no. 3, 1 July 1998 (1998-07-01), pages 245 - 264, XP008041022, ISSN: 1078-9669 *

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