EP1643202B1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
EP1643202B1
EP1643202B1 EP05021623A EP05021623A EP1643202B1 EP 1643202 B1 EP1643202 B1 EP 1643202B1 EP 05021623 A EP05021623 A EP 05021623A EP 05021623 A EP05021623 A EP 05021623A EP 1643202 B1 EP1643202 B1 EP 1643202B1
Authority
EP
European Patent Office
Prior art keywords
longitudinal
chamber
flow
partition
heat exchanger
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
EP05021623A
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German (de)
English (en)
Other versions
EP1643202A1 (fr
Inventor
Gottfried DÜRR
Wolfgang Seewald
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.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and 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 and Co KG filed Critical Behr GmbH and Co KG
Publication of EP1643202A1 publication Critical patent/EP1643202A1/fr
Application granted granted Critical
Publication of EP1643202B1 publication Critical patent/EP1643202B1/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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • 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
    • F28D2021/0071—Evaporators

Definitions

  • the invention relates to a heat exchanger, in particular an evaporator, with one of an inner medium to be tempered, in particular a refrigerant,
  • a heat exchanger in particular an evaporator, with one of an inner medium to be tempered, in particular a refrigerant,
  • an inner medium to be tempered in particular a refrigerant
  • Two headers having an inlet opening, an outlet opening and in each case at least one Longitudinal dividing wall are provided, are provided in the transfer openings and through which the headers are divided into longitudinal chambers, which communicate with each other through the transfer openings, and with outside of the flow channels with an external medium, in particular air, acted upon guide elements, in particular ribs, wherein a flood Flow channels each extending between two LGarskammem that belong to different collection boxes and are referred to as Lekscropartner.
  • Heat exchangers are described with at least two rows in flow passages through heat exchanger blocks. These known heat exchangers each have a collecting box with a longitudinal dividing wall, in which a plurality of transfer openings are provided.
  • an evaporator for performing a heat exchange between refrigerant flowing therethrough and an external fluid flowing outside the evaporator is known.
  • the known evaporator includes a plurality of tubes through which the refrigerant flows.
  • the tubes are arranged in multiple rows in the flow direction of the outer fluid.
  • a container is arranged in each case.
  • a partition wall element is provided for dividing the container into a plurality of container areas.
  • the container has an inlet and an outlet for the refrigerant or refrigerant.
  • several holes are provided, which have different openings with each other. The surfaces of the holes gradually narrow in the width direction.
  • the object of the invention is a heat exchanger, in particular an evaporator, with a to be tempered by an inner medium, in particular a refrigerant,
  • an inner medium in particular a refrigerant
  • the object is in a heat exchanger, in particular an evaporator, with one of an inner medium to be tempered, in particular a refrigerant,
  • a heat exchanger in particular an evaporator
  • one of an inner medium to be tempered in particular a refrigerant
  • the inlet opening can be provided laterally, that is to say in a narrow side, or in a longitudinal side of the longitudinal chamber.
  • a preferred embodiment of the heat exchanger is characterized in that the longitudinal chamber partner of the longitudinal chamber, in which the inlet opening is arranged, is delimited by a longitudinal dividing wall which has smaller transfer openings in the longitudinal section opposite the inlet opening than in the remaining region of the longitudinal dividing wall.
  • the size of the passage cross section of the transfer openings, the temperature profile on the outlet side of the outer medium can be adjusted to a predetermined temperature profile.
  • a further preferred exemplary embodiment of the heat exchanger is characterized in that the longitudinal chamber partner of the longitudinal chamber in which the inlet opening is arranged is delimited by a longitudinal dividing wall which has no transfer openings in the longitudinal section opposite the inlet opening.
  • the object is achieved with a heat exchanger described above in that the longitudinal chamber partner of the longitudinal chamber, in which the outlet opening is arranged, is delimited by a longitudinal dividing wall which has fewer crossing openings in a longitudinal section opposite the outlet opening than in the remaining region of the longitudinal dividing wall.
  • the outlet opening can be provided laterally, that is to say in a narrow side, or in a longitudinal side of the longitudinal chamber.
  • a further preferred exemplary embodiment of the heat exchanger is characterized in that the longitudinal chamber partner of the longitudinal chamber in which the outlet opening is arranged is delimited by a longitudinal dividing wall which has smaller transfer openings in the longitudinal section opposite the outlet opening than in the remaining region of the longitudinal dividing wall.
  • the size of the passage cross section of the transfer openings, the temperature profile on the outlet side of the outer medium can be adjusted to a predetermined temperature profile.
  • Another preferred exemplary embodiment of the heat exchanger is characterized in that the longitudinal chamber partner of the longitudinal chamber in which the outlet opening is arranged is delimited by a longitudinal dividing wall which has no transfer openings in the longitudinal section opposite the outlet opening.
  • the above object is achieved in a heat exchanger described above with a longitudinal chamber which is delimited in the longitudinal direction by a transverse partition in which a passage opening is provided, characterized in that the Lssenshuntpartner the longitudinal chamber in which the passage opening is arranged delimited by a longitudinal partition is, which has in one of the passage opening opposite longitudinal section fewer transfer openings than in the remaining region of the longitudinal partition wall.
  • the passage opening may be provided laterally, that is to say in a narrow side, or in a longitudinal side of the longitudinal chamber.
  • the passage opening in the transverse partition wall can also be given in the context of the present invention in that the transverse partition completely eliminated, in which case preferably the Lekscropartner of a transverse partition on the level - seen in the longitudinal direction - the omitted transverse partition is limited.
  • a further preferred exemplary embodiment of the heat exchanger is characterized in that the longitudinal chamber partner of the longitudinal chamber in which the passage opening is arranged is delimited by a longitudinal dividing wall which has smaller transfer openings in the longitudinal section opposite the passage opening than in the remaining region of the longitudinal dividing wall.
  • the size of the passage cross section of the transfer openings, the temperature profile on the outlet side of the outer medium can be adjusted to a predetermined temperature profile.
  • a further preferred exemplary embodiment of the heat exchanger is characterized in that the longitudinal chamber partner of the longitudinal chamber in which the passage opening is arranged is delimited by a longitudinal dividing wall which has no transfer openings in the longitudinal section opposite the passage opening.
  • the transfer openings are arranged distributed uniformly in the longitudinal partition wall.
  • the distribution according to the invention of the transfer openings in the longitudinal dividing wall ensures that the tide having the inlet opening, the outlet opening or the passage opening in the direction of flow is sufficiently and evenly supplied with refrigerant.
  • FIG. 1 shows a flat tube evaporator 1 in a schematic, perspective view.
  • the flat tube evaporator 1 comprises an evaporator block 3, which has a multiplicity of flat tubes (not shown), between which corrugated ribs are arranged.
  • the structure and function of such a flat tube evaporator are assumed to be known and are for example in the German patent application DE 103 12 780 A1 described.
  • the evaporator block 3 is bounded above and below by collecting tanks 5, 6, each in L Lucasskammem 8, 9; 11,12 are divided.
  • the evaporator block 3 is laterally closed by side parts 15, 16, which form the one side, such as the narrow sides.
  • the others Pages, such as the long sides, are in FIG. 1 denoted by 18 and 19.
  • the longitudinal side 18 corresponds to the air inlet side.
  • the parts of the evaporator block 3 and the manifolds 5 and 6 are preferably made of aluminum or an aluminum alloy and are preferably soldered together, the ends of the flat tubes are sealed or sealed in openings in the manifolds 5, 6 are added.
  • the ribs arranged between the flat tubes are overflowed by air in the direction of flow indicated by arrows 21 to 23.
  • the longitudinal chamber 8 extends over the entire width of the heat exchanger 1.
  • the longitudinal chamber 9 is divided by a transverse partition 25 in two Lssenskammem 26 and 27.
  • an inlet opening 29 is provided, through which a refrigerant, for example R134a, enters the evaporator 1.
  • an outlet opening 30 is provided through which the refrigerant exits the heat exchanger 1.
  • the longitudinal chamber 11 opposite the longitudinal chamber 8 is divided by a transverse dividing wall 32 into two longitudinal chambers 34 and 35.
  • the longitudinal chamber 12 opposite the longitudinal chamber 12 is divided by a transverse partition wall 37 into two longitudinal chambers 39, 40.
  • the refrigerant is, as indicated by an arrow 41, the front, that is windward longitudinal chamber 26 fed through a (not shown) pressure line.
  • the refrigerant can also be supplied to the windward longitudinal chamber 27 and the leeward longitudinal chamber 8.
  • the refrigerant in an expansion valve (not shown) is reduced to the evaporator pressure, that is, the refrigerant enters the longitudinal chamber 26 as the refrigerant wet steam.
  • the refrigerant After flowing through the evaporator 1, which is explained in more detail below, the refrigerant is sucked off via a suction line (not shown).
  • an (not shown) expansion valve is arranged in the air flow direction 21 to 23 in front of the evaporator 1 and the evaporator block 3.
  • the arrows 42, 44, 46, 48 each provide a flood of flow channels
  • the heat exchanger 1 is therefore also referred to as tardflutig.
  • the arrow 43 represents a passage between the LCodeskammem 39 and 34 in the collecting box 6.
  • the arrow 47 represents a transition between the LCodeskammem 35 and 40 in the collecting box 6.
  • the Studentstrritte 43 and 47 are made possible by transfer openings in a partition are provided, through which the LHarskammem 34 and 39 and 35 and 40 are separated from each other.
  • FIGS. 2 to 4 is in each case the view of a section through the collecting box 6 FIG. 1 shown.
  • a longitudinal partition wall 51 which is arranged in the longitudinal direction between the longitudinal chamber 34 and the longitudinal chamber 39 in the collecting box 6.
  • a longitudinal partition wall 52 which is arranged between the longitudinal chambers 35 and 40.
  • the longitudinal partition walls 51, 52 are preferably integrally connected to each other.
  • the in FIG. 2 illustrated collection box 6 has in one of the inlet opening (29 in FIG. 1 ) opposite region on a longitudinal portion 54 in which no transfer openings are provided. Between the longitudinal section 54 and the transverse partition walls 32, 37, four transfer openings 56 to 59 are recessed in the longitudinal partition wall 51, which have the shape of elongated holes.
  • a longitudinal portion 61 is provided in which no transfer openings are arranged. Between the longitudinal section 61 and the transverse partition walls 32, 37, two transfer openings 63 and 64 are recessed in the longitudinal partition 52. Between the longitudinal section 61 and the side wall of the Sammieikastens 6 52 three transfer openings 66 to 68 are recessed in the longitudinal partition wall.
  • the transfer opening 68 has a smaller passage cross-section than the transfer openings 66 and 67.
  • FIG. 3 illustrated embodiment of the inlet opening (29 in FIG. 1 ) opposite longitudinal portion 74 greater than in the FIG. 2 illustrated embodiment formed.
  • three transfer openings 77 to 79 are recessed in the longitudinal partition wall 51.
  • the outlet opening (30 in FIG. 1 ) opposite longitudinal portion 81 is in the in FIG. 3 illustrated embodiment also larger than in the FIG. 2 illustrated embodiment.
  • two transfer openings 86, 87 are recessed.
  • the longitudinal portion 94 is the same size as the longitudinal portion 54 in the in FIG. 2 illustrated embodiment.
  • the transfer openings 97 to 99 have a larger passage cross-section than the transfer openings in the preceding embodiments.
  • the longitudinal partition wall 52 has in the in FIG. 4 illustrated embodiment with respect to the outlet opening (30 in FIG. 1 ) has a longitudinal portion 101 which is larger than that in FIG. 2 illustrated embodiment, but smaller than in the FIG. 3 illustrated embodiment.
  • a transfer opening 103 is arranged, which has a larger passage cross-section than in the preceding embodiments.
  • two transfer openings 106, 107 are arranged, each having a larger passage cross-section than in the preceding embodiments.
  • FIG. 5 shows a flat tube evaporator 118 with a side refrigerant inlet 119 and a longitudinal port 120 for the outlet or the suction of the refrigerant.
  • This evaporator 118 is in principle the same as the evaporator 1 described above, but it is larger in the longitudinal extent and flows through five-flow, that is, in five passages I, II, III, IV, V, wherein after the passage III, a deflection in the Depth III / IV against the air flow direction L takes place. However, the deflection in depth can also take place in the air flow direction. This applies in general, also for the other embodiments.
  • the evaporator 118 has an upper header box 121 with two L Lucasskammem 121 a, 121 b and two transverse partitions 122, 123.
  • a lower header 124 has two longitudinal chambers 124a, 124b with a transverse partition 150.
  • the divider walls 122, 150 on the leeward side are staggered with respect to the longitudinal extent of the evaporator to ensure three-flow formation.
  • the partition wall 123 is arranged centrally of the evaporator. As a result, two equally distributed floods are generated on the windward side.
  • the refrigerant in the passages I, II and III on the leeward side of the evaporator 118 as wet steam with (constant) evaporation temperature, so that could result in a uniform temperature distribution on the air outlet side.
  • the refrigerant at outlet 120 should be in the form of superheated steam at a predetermined superheat temperature; therefore in the last passage V refrigerant with overheating temperature flows, possibly already in the penultimate passage IV -beide, however, are on the air inlet side. This results in a uniform temperature distribution on the air outlet side even for a five-flute evaporator.
  • the evaporator is divided into different areas on the lee side and the windward side, as in different floods. These areas are not the same size on the lee side and the windward side as shown.
  • the block interconnection is progressive, that is, the first row of tubes into which the refrigerant flows or is injected is divided into three areas and floods (I, II, III), while the second row of tubes, from which the one Refrigerant is sucked, divided into only two areas or floods (IV, V).
  • the block interconnection in a five-flute evaporator may also be degressive, that is, the first row of tubes into which the refrigerant flows or is injected divides into two zones (I, II), while the second row of tubes from which the refrigerant is sucked, divided into three areas or floods (III, IV, V).
  • the inlet for the refrigerant is arranged on a lower longitudinal chamber and the outlet on an upper connection.
  • the connections are arranged on the same side of the evaporator, viewed in the longitudinal direction.
  • the ports may also be arranged on opposite sides of the evaporator in the longitudinal direction.
  • a heat exchanger block which is bounded by transverse partition walls 122 and 123.
  • transverse partition walls 122, 123 for example, transverse dividing walls, not shown, are arranged with passage openings, which preferably, as in Fig. 5 shown, also completely eliminated, to ensure an overflow from or to an adjacent heat exchanger block.
  • Fig. 1 is formed by the first two flow path sections seen from the entry 41 from a heat exchanger block, which is bounded by the transverse partition 25.
  • the transverse partition wall 25 also eliminates a fictitious transverse partition, so that refrigerant can flow over to the other two Stömungspfadabitesen.
  • the size and / or distribution of the transfer openings in a longitudinal partition dividing the longitudinal partition 34 depends either on the position of the inlet 41 or on the position of the given by the attributable transverse partition overflow or both positions.

Claims (9)

  1. Echangeur de chaleur, en particulier évaporateur (1 ; 121), comprenant un bloc (3) de l'échangeur de chaleur pouvant être traversé par un milieu intérieur à tempérer, en particulier un fluide frigorigène, passant dans des conduits d'écoulement, en plusieurs flux, au moins sur deux rangées, bloc de l'échangeur de chaleur qui est délimité par un ou deux bacs collecteurs (5, 6 ; 121, 124) qui sont dotés d'une ouverture d'entrée (29), d'une ouverture de sortie (30), où au moins un bac collecteur est doté d'au moins une paroi de séparation longitudinale (51, 52) dans laquelle il est prévu une ou plusieurs ouvertures de trop-plein (56 - 59, 63, 64, 66 - 68 ; 77 - 79, 83, 86, 87 ; 97 - 99, 103, 106, 107) et par laquelle le bac collecteur (6) est divisé en chambres longitudinales (34, 39 ; 35, 40) qui communiquent entre elles par les ouvertures de trop-plein, et comprenant des éléments conducteurs, en particulier des ailettes pouvant être sollicitées, à l'extérieur des conduits d'écoulement, par un milieu extérieur, en particulier de l'air, où un flux des conduits d'écoulement s'étend à chaque fois entre deux chambres longitudinales qui font partie de différents bacs collecteurs (5, 6 ; 121, 124) et sont désignées comme des chambres longitudinales associées,
    caractérisé en ce que la chambre longitudinale (39), associée à la chambre longitudinale (26) dans laquelle est disposée l'ouverture d'entrée (29), est délimitée par une paroi de séparation longitudinale (51) qui, dans une partie longitudinale (54 ; 74 ; 94) faisant face à l'ouverture d'entrée (29), présente des ouvertures de trop-plein ayant une surface de section plus faible, ou bien présente moins d'ouvertures de trop-plein que dans une zone restante de la paroi de séparation longitudinale (51) délimitant la chambre longitudinale associée (39).
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que la chambre longitudinale (39), associée à la chambre longitudinale (26) dans laquelle est disposée l'ouverture d'entrée (29), est délimitée par une paroi de séparation longitudinale (51) qui, dans la partie longitudinale (54 ; 74 ; 94) faisant face à l'ouverture d'entrée, présente des ouvertures de trop-plein plus petites que dans la zone restante de la paroi de séparation longitudinale.
  3. Echangeur de chaleur selon l'une ou l'autre des revendications précédentes, caractérisé en ce que la chambre longitudinale (39), associée à la chambre longitudinale (26) dans laquelle est disposée l'ouverture d'entrée (29), est délimitée par une paroi de séparation longitudinale (51) qui, dans la partie longitudinale (54 ; 74 ; 94) faisant face à l'ouverture d'entrée, ne présente aucune ouverture de trop-plein.
  4. Echangeur de chaleur selon le préambule de la revendication 1, caractérisé en ce que la chambre longitudinale (40), associée à la chambre longitudinale (26) dans laquelle est disposée l'ouverture de sortie (30), est délimitée par une paroi de séparation longitudinale (52) qui, dans une partie longitudinale (61 ; 81 ; 101) faisant face à l'ouverture de sortie (30), présente des ouvertures de trop-plein ayant une surface de section plus petite que dans une zone restante de la paroi de séparation longitudinale (52) délimitant la chambre longitudinale associée (40).
  5. Echangeur de chaleur selon la revendication 4, caractérisé en ce que la chambre longitudinale (40), associée à la chambre longitudinale (26) dans laquelle est disposée l'ouverture de sortie (30), est délimitée par une paroi de séparation longitudinale (52) qui, dans la partie longitudinale (61 ; 81 ; 101) faisant face à l'ouverture de sortie (30), présente des ouvertures de trop-plein plus petites que dans la zone restante de la paroi de séparation longitudinale.
  6. Echangeur de chaleur selon la revendication 4 ou 5, caractérisé en ce que la chambre longitudinale (40), associée à la chambre longitudinale (26) dans laquelle est disposée l'ouverture de sortie (30), est délimitée par une paroi de séparation longitudinale (52) qui, dans la partie longitudinale (61 ; 81 ; 101) faisant face à l'ouverture de sortie (30), ne présente aucune ouverture de trop-plein.
  7. Echangeur de chaleur selon le préambule de la revendication 1, comprenant une chambre longitudinale qui, dans la direction longitudinale, est délimitée par une paroi de séparation transversale dans laquelle il est prévu une ouverture de passage, caractérisé en ce que la chambre longitudinale, associée à la chambre longitudinale dans laquelle est disposée l'ouverture de passage, est délimitée par une paroi de séparation longitudinale qui, dans une partie longitudinale faisant face à l'ouverture de passage, présente des ouvertures de trop-plein ayant une surface de section plus petite, ou bien présente moins d'ouvertures de trop-plein que dans une zone restante de la paroi de séparation longitudinale délimitant la chambre longitudinale associée.
  8. Echangeur de chaleur selon la revendication 7, caractérisé en ce que la chambre longitudinale, associée à la chambre longitudinale dans laquelle est disposée l'ouverture de passage, est délimitée par une paroi de séparation longitudinale qui, dans la partie longitudinale faisant face à l'ouverture de passage, présente des ouvertures de trop-plein plus petites que dans la zone restante de la paroi de séparation longitudinale.
  9. Echangeur de chaleur selon la revendication 7 ou 8, caractérisé en ce que la chambre longitudinale, associée à la chambre longitudinale dans laquelle est disposée l'ouverture de passage, est délimitée par une paroi de séparation longitudinale qui, dans la partie longitudinale faisant face à l'ouverture de passage, ne présente aucune ouverture de trop-plein.
EP05021623A 2004-10-04 2005-10-04 Echangeur de chaleur Not-in-force EP1643202B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004048569 2004-10-04
DE102004056790A DE102004056790A1 (de) 2004-10-04 2004-11-24 Wärmetauscher

Publications (2)

Publication Number Publication Date
EP1643202A1 EP1643202A1 (fr) 2006-04-05
EP1643202B1 true EP1643202B1 (fr) 2009-05-13

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EP05021623A Not-in-force EP1643202B1 (fr) 2004-10-04 2005-10-04 Echangeur de chaleur

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EP (1) EP1643202B1 (fr)
AT (1) ATE431535T1 (fr)
DE (2) DE102004056790A1 (fr)

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KR101291033B1 (ko) 2007-11-09 2013-08-01 한라비스테온공조 주식회사 열교환기
KR101462173B1 (ko) 2010-10-28 2014-12-04 삼성전자주식회사 열교환기
EP3120097B1 (fr) 2014-03-18 2020-06-24 Carrier Corporation Évaporateur d'échangeur de chaleur à micro-canaux
DE102015210184A1 (de) * 2015-06-02 2016-12-22 Volkswagen Aktiengesellschaft Kraftfahrzeug mit einem Klimagerät
WO2020123653A1 (fr) * 2018-12-14 2020-06-18 Modine Manufacturing Company Condenseur de fluide frigorigène
JP7399286B2 (ja) * 2020-06-04 2023-12-15 三菱電機株式会社 熱交換器および冷凍サイクル装置

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DE102004056790A1 (de) 2006-04-06
ATE431535T1 (de) 2009-05-15
EP1643202A1 (fr) 2006-04-05

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