EP1909054B1 - Caloporteur en plaques, en particulier évaporateur pour une climatisation de véhicule automobile - Google Patents

Caloporteur en plaques, en particulier évaporateur pour une climatisation de véhicule automobile Download PDF

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Publication number
EP1909054B1
EP1909054B1 EP20070018044 EP07018044A EP1909054B1 EP 1909054 B1 EP1909054 B1 EP 1909054B1 EP 20070018044 EP20070018044 EP 20070018044 EP 07018044 A EP07018044 A EP 07018044A EP 1909054 B1 EP1909054 B1 EP 1909054B1
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EP
European Patent Office
Prior art keywords
heat exchanger
accordance
deflection
distribution means
equal distribution
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
EP20070018044
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German (de)
English (en)
Other versions
EP1909054A2 (fr
EP1909054A3 (fr
Inventor
Karl-Heinz Staffa (Dipl.-Ing.)
Wolfgang Seewald (Dipl.-Ing.)
Gottfried Dürr (Dipl.-Ing.)
Boris Kerler (Dr.-Ing.)
Jie Zhang
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 EP1909054A2 publication Critical patent/EP1909054A2/fr
Publication of EP1909054A3 publication Critical patent/EP1909054A3/fr
Application granted granted Critical
Publication of EP1909054B1 publication Critical patent/EP1909054B1/fr
Expired - Fee Related 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
    • 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
    • F25B39/022—Evaporators with plate-like or laminated elements
    • 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
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements
    • 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
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • 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
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
    • 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
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0085—Evaporators

Definitions

  • the invention relates to a plate-type heat exchanger, in particular evaporator, with at least one collector, which has at least two adjacent to each other, in particular brazed together sheets.
  • a heat exchanger according to the preamble of claim 1 is made DE 102 60 107 A1 known.
  • a CO 2 heat exchanger Particularly suitable as a CO 2 heat exchanger are so-called plate evaporator, wherein the refrigerant passes through an injection pipe in a collector, which usually by three large area soldered to each other, just formed plates, namely a connecting plate, a distributor or baffle and a bottom plate formed is.
  • a collector which usually by three large area soldered to each other, just formed plates, namely a connecting plate, a distributor or baffle and a bottom plate formed is.
  • the refrigerant is distributed with the help of the appropriately designed baffle on the individual projecting into the bottom plate with their ends flat tubes and possibly also repeatedly deflected in width and / or depth.
  • one or two collectors may be provided, in the case of a collector, the flat tubes are bent usually U-shaped and in the case of two collectors, the flat tubes usually straight, so that in normal installation position in a motor vehicle, a collector above and Collector is arranged below.
  • the refrigerant leaves the collector via a suction pipe and is forwarded in the refrigerant circuit.
  • a plate evaporator is for example in the DE 102 60 107 A1 whose disclosure content with respect to the refrigerant flow through the evaporator, in particular as in the Figures 3 . 6 . 8th and 9 illustrated and described with reference to these figures, is expressly incorporated.
  • a corresponding plate evaporator is also in the post-published German patent application 10 2005 020 499.6 discloses, whose disclosure content is also expressly included with respect to the refrigerant guide.
  • An example of known in H-shaped deflection openings in the baffle is in Fig. 12 shown.
  • a plate-type heat exchanger in particular an evaporator, is provided with the features of claim 1.
  • the flat tubes are preferably arranged parallel to each other, i. the broadsides are opposite each other.
  • the arrival or possibly the outflow takes place here preferably by an inflow or outflow hole in a connecting plate.
  • the flat tubes can also be arranged in a plane with opposite narrow sides.
  • the flat tubes can also be designed such that one or more channels of the same are not flowed through, so that in principle there are two flat tubes, which are, however, integrally connected to one another.
  • the deflection openings are rounded rectangular, formed with wedge-shaped sides. Also, the long sides can be pulled slightly inward, but only up to the opening of the flat tubes. If necessary, the wedge angle can also be rounded, but a sharp-edged configuration is advantageous.
  • the tubes are preferably multi-chamber flat tubes with multiple channels. This more uniform distribution also results in a more uniform temperature distribution over the entire heat exchanger.
  • the configuration of the deflection openings can be provided both in inflow and outflow.
  • the sides of the rectangle with wedge-shaped inwardly drawn pages are the narrow sides of the rectangle.
  • a wedge shape is preferably an acute-angled wedge, the tip being directed inwardly in the direction of the central longitudinal axis of the inflow bore through which the refrigerant enters the deflection opening.
  • the wedge angle is particularly preferably in the range of 180 ° - 2 x arctan [0.5 x flat tube depth / 0.5 x base wedge] to 180 °, the length of the base of the wedge corresponds to the distance of the center planes of the flat tubes (see illustration of Fig. 5 ).
  • At least one metal sheet which is arranged adjacent to the plate with the deflection, ie in particular formed on the bottom plate or on the connection plate, in the deflector formed in the Umlenkö Stammen protruding projections, ribs, knobs, mandrels or attached, which in addition to the homogenization of the refrigerant distribution on the channels of the flat tubes serve.
  • at least one projection per deflection opening is preferably provided.
  • ribs or nubs also several projections per deflection opening may be provided, which are particularly preferably distributed around the central longitudinal axis of the inflow bore around. The distribution is particularly preferably elliptical or possibly also circular.
  • the rib or nub lengths are preferably adapted to the distance to the inlet opening in the flat tube.
  • the arrangement density of projections, in particular of ribs, is preferably in the central region, ie the region near the flat tube, denser than in the remaining region.
  • a single projection in the central longitudinal axis of the inflow bore may be provided on or attached to the opposite plate.
  • an inflow bore is arranged in the connection plate with respect to the associated inflow deflection opening.
  • the central arrangement ensures a uniform distribution.
  • a projection or mandrel serving as a direct distribution means can also serve as a direct distribution means by means of an inserted pin, preferably with a tip, in particular preferably with a pyramidal or conical tip, which is arranged in a channel of a flat tube which is not or only partly used, in particular preferably in FIG Center of the flat tube, be formed.
  • opposite surface and / or the side surfaces can be achieved in a simple manner equalize the distribution of the medium on individual channels of a flat tube, even with I-shaped deflection or deflection, where three or more flat tubes end ,
  • Leg the pipes are preferably flat tubes, particularly preferably multi-chamber flat tubes with multiple channels. If two flat tubes arranged parallel to one another are provided with a plurality of channels, at least one of the internally arranged channels, in particular preferably the middle channel, is unused. It is preferably covered by the floor panel. Alternatively, two times with its narrow sides adjacent, arranged parallel to each other flat tubes can be provided for an overflow.
  • the free flow cross-section of the supply line in particular of the injection tube or optionally also of an overflow pipe, preferably decreases in the flow direction, so that a uniform distribution of refrigerant takes place on all overflow openings and not only on the pipes assigned to an overflow opening.
  • the free flow cross-section of at least one deflection opening in a second, lower collector in an area in extension of the tubes, through which the refrigerant flows out of the collector, so that even the air upstream arranged tubes, especially with a plurality of channels, evenly with refrigerant be charged.
  • influx deflection openings are also possible following an overflow tube, which serves as an injection tube with respect to the subsequent part of the heat exchanger.
  • a corresponding configuration may be provided for the reverse flow, i. For example, for outflow deflection and outflow holes.
  • Such heat exchangers are particularly suitable for CO 2 , but any other refrigerant, for example R134a, can also be used.
  • a plate-type heat exchanger in this case an evaporator of a motor vehicle air-conditioning system in which CO 2 is used as the refrigerant in the present case, which is thus exposed to relatively high pressures, has, as in Fig. 7 represented, an inlet pipe E, via which the refrigerant is supplied to the evaporator, a collector 1, formed by a connecting plate 2, a baffle 3 and a bottom plate 4, a plurality of mutually parallel multi-chamber flat tubes F, with their ends in the in Bottom plate 4 provided slots 5 protrude, and a suction pipe S, via which the refrigerant passes from the evaporator on.
  • the upper ends of the flat tubes F are divided centrally by a slot (see detail of Fig. 9 ).
  • the elongated holes 5 are divided centrally by a web which is positioned in the slot of the flat tubes F in the assembled state, so that in each case a flat tube provides two oppositely directed flow paths for the refrigerant formed by a plurality of chambers or channels ,
  • the refrigerant flow is divided into a plurality of partial flows, each flowing from the inflow deflection opening in one half of the flat tube F flowing through the evaporator downstream of the air.
  • the lower collector 1 ' which is also formed by three sheets, in this case by an externally arranged end plate 2', a baffle 3 'and a bottom plate 4', the partial flows in depth by depth deflection 10 'deflected, in this case without exchange between the individual flat tubes F, and flow through the other half of the flat tubes F arranged upstream of the air upstream to the upper collector 1.
  • the connecting plate 2, the baffle 3 and the bottom plate 4 of the upper header 1 as well as the end plate 2 ', the baffle 3' and the bottom plate 4 'of the lower collector 1' are each soldered flat, wherein the soldering in one operation with the Soldering of the entire evaporator takes place.
  • nubs (not shown) are formed on the connecting plate, which protrude upwards on the nub side and in correspondingly formed recesses or bores are received, which are provided in the tubes, so that a positionally accurate and simple (pre-) fixation in the context of assembly is possible
  • inflow holes 7 are also provided, via which the refrigerant from the injection tube E coming into the air downstream part of the upper header 1 can flow.
  • outflow bores 8 which are formed in the connecting plate 2 upstream of the air, the refrigerant passes from the collector 1 into the suction pipe S.
  • the depth deflection openings in the deflection plate 3 ' are presently formed by simple elongated holes, which are each associated with a flat tube F. H-shaped, wider, rectangular shapes, etc., to mix To allow adjacent refrigerant flows are also possible.
  • the inflow deflection openings arranged in alignment therewith in the deflection plate 3 are formed according to the embodiments described in more detail below with DC distribution means.
  • the basic configuration of the heat exchanger corresponds to the above description.
  • the inflow Umfenkö Stamm 10 as shown schematically in FIG Fig. 1 shown, formed substantially rectangular.
  • the longitudinal sides of the rectangle are slightly offset outward with respect to the alignment line of the outer edge of the flat tubes F, in this case by about the flat tube thickness.
  • the edges are rounded, whereby here too the radius of the rounding is larger by about a flat tube thickness than the radius of the narrow sides of the narrow-side round flat tubes F.
  • the or the central channels of the multi-chamber flat tube is covered by the baffle, so that no refrigerant flows through them.
  • the inflow deflection opening 10 is arranged only in front of a part of the channels of the flat tubes F, the outflow deflection in the baffle 3 of the upper header 1 are formed according to the present embodiment according to the inflow deflection openings 10.
  • another, for example, a greater length of the longitudinal sides of the Ausström Umklenkö Maschinenen would be possible, so that correspondingly fewer channels of the flat tubes for the guidance of the refrigerant to the lower collector 1 'as for the return to the upper collector 1 are available, ie the block depths of the heat exchanger differ.
  • the narrow sides of the deflection opening 10 according to the first embodiment are, as in Fig. 1 shown and in contrast to the representation of FIGS. 7 and 9 wedge-shaped pulled inwards, the wedge slightly acute angle, ie the angle is slightly smaller than 90 °, is formed.
  • the wedge tips lie in a line with the central longitudinal axis of the inflow bore 7, wherein the distance between the wedge tips to the central longitudinal axis is equal in each case.
  • the transition from the wedge to the rounded edges is such that the wedge tangentially abuts the circle of curvature.
  • a plurality of radially arranged around the central longitudinal axis of the inflow bore 7 ribs 11 are provided, in this case on the connecting plate 2.
  • ribs can also be provided on the bottom plate ,
  • Gleichverteilmittel according to the first embodiment thus serves the shape of the deflection opening 10 and the ribs 11 on the connection plate. 2
  • the shape of the inflow deflection opening 10 corresponds to that of the first embodiment.
  • ribs 11 are triangular knobs 12, manufactured, for example.
  • the tips of the dimples 12 point in the direction of the central longitudinal axis of the inflow bore 7.
  • Fig. 3 shows another way to distribute the refrigerant flow to the individual channels of the flat tubes F as evenly as possible.
  • a mandrel 13 is provided on the bottom plate 4 in the central longitudinal axis of the inflow bore 7, a mandrel 13, but placed here, but it can also be made by means of forming of the material of the bottom plate.
  • both the shape of the deflection opening 10 and the mandrel 13 serve as Gleichverteilstoff.
  • grooves or channels, winglets, nubs, bulges or the like be provided on the bottom plate and / or connecting plate as Gleichverteilstoff.
  • the deflection opening 10 corresponds to that of the first embodiment, ie the narrow sides are wedge-shaped pulled inwards.
  • the wedge angle ⁇ is about 80 °.
  • the base of the wedge is designated in the drawing by KS.
  • KS base side wedge
  • KS base side wedge
  • Fig. 5 shows an embodiment of the deflection opening 10, according to which the wedge angle ⁇ is reduced to about 45 °, ie the wedges protrude further to the central longitudinal axis of the inflow bore 7 than in the first embodiment.
  • Fig. 6 shows an example according to the prior art in which no wedges are provided, ie the narrow sides of the deflection opening 10 are straight running formed and the wedge angle ⁇ corresponds to 180 °, so that the deflection opening 10 is rounded rectangular.
  • FIG. 5 can of course be supplemented with the measures described in the embodiments 1, 2 and 3 and mentioned in this context.
  • each flat tube substantially the same proportion of liquid refrigerant can be supplied are possible.
  • the cross section i. the hydraulic diameter of the injection tube in the flow direction can be reduced, wherein a cross-sectional reduction in the range of 5 to 90% can be provided. It should be present over the entire length of the injection tube, the same flow shape, preferably a ring flow.
  • the cross section of the injection tube can be arbitrary, in particular round, D-shaped, oval or angular.
  • the cross-sectional area can be reduced by making the tube more compressed in the direction of flow.
  • variable injection pipe flow cross-section and the injection holes can be formed with different diameters or be varied by inserts the cross section.
  • a further improvement of the temperature distribution over the evaporator surface results from measures, ie the provision of direct distribution means, in the lower collector 1 '.
  • Modifications are possible.
  • the cross-sectional reduction can possibly also be done by inserts.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air-Conditioning For Vehicles (AREA)

Claims (13)

  1. Echangeur de chaleur du type à plaques, en particulier évaporateur, comprenant au moins un collecteur (1) qui présente au moins deux tôles (2, 3, 4) adjacentes l'une à l'autre, en particulier brasées l'une avec l'autre, et une pluralité de tubes plats (F) reliés au collecteur (1) et traversés par un milieu en circulation, où des ouvertures de retour de flux (10) sont configurées dans au moins une tôle (3), ouvertures de retour de flux qui sont disposées dans le prolongement à chaque fois d'au moins deux tubes (F), où il est prévu, dans la zone des ouvertures de retour de flux (10), au moins un moyen de répartition égale pour le milieu en circulation, moyen de répartition égale qui provoque, sur les tubes plats (F), une uniformisation de la répartition du flux du milieu en circulation, caractérisé en ce que les ouvertures de retour de flux (10), en tant que moyen de répartition égale, sont configurées en étant de forme rectangulaire arrondie et en ayant des côtés en forme de coin, ramenés vers l'intérieur.
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que les côtés du rectangle comportant des côtés en forme de coin, ramenés vers l'intérieur, sont les petits côtés.
  3. Echangeur de chaleur selon la revendication 1 ou 2, caractérisé en ce que l'angle de coin est un angle aigu et/ou se situe dans la plage comprise entre 180°- 2 x arctan [profondeur du tube plat/côté de base du coin] et 180°.
  4. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'il est prévu au moins une partie saillante servant de moyen de répartition égale, partie saillante suivant laquelle est orientée la direction de flux entrant du milieu en circulation.
  5. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que sur au moins une tôle (2, 4) servant de moyen de répartition égale, tôle qui est disposée en étant adjacente à la tôle (3) comportant les ouvertures de retour de flux (10), sont configurés ou placés des parties saillantes, des nervures (11), des ergots (12), des pointes (13) pénétrant dans les ouvertures de retour de flux (10).
  6. Echangeur de chaleur selon la revendication 4 ou 5, caractérisé en ce qu'il est prévu une pluralité de parties saillantes qui sont disposées en étant réparties tout autour de l'axe longitudinal médian d'un perçage associé (7) de flux entrant, et/ou en ce qu'il est prévu une seule partie saillante se trouvant dans l'axe longitudinal médian du perçage associé (7) de flux entrant.
  7. Echangeur de chaleur selon la revendication 6, caractérisé en ce que les parties saillantes sont disposées de façon radiale tout autour de l'axe longitudinal médian du perçage associé (7) de flux entrant.
  8. Echangeur de chaleur selon la revendication 7, caractérisé en ce que les extrémités intérieures des parties saillantes sont disposées de façon elliptique tout autour de l'axe longitudinal médian du perçage associé (7) de flux entrant.
  9. Echangeur de chaleur selon la revendication 4, caractérisé en ce qu'une partie saillante est disposée dans le prolongement d'un conduit central d'un tube plat non traversé ou traversé seulement partiellement par le milieu en circulation.
  10. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'une des deux tôles adjacentes l'une à l'autre est la tôle de raccordement (2), et à chaque fois un perçage (7) de flux entrant est disposé dans la tôle de raccordement, au milieu par rapport à l'ouverture de retour de flux associée (10).
  11. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que les tubes sont des tubes plats (F), où il est prévu, pour une ouverture de trop-plein (10), deux tubes plats (F) à chambres multiples, lesdits tubes plats comprenant un ou plusieurs conduits inutilisés et disposés intérieurement, ou bien deux fois deux tubes plats disposés en étant parallèles entre eux et adjacents les uns aux autres par leurs petits côtés.
  12. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que, en plus d'au moins un élément de répartition égale, la section d'écoulement libre de la conduite d'alimentation diminue dans la direction d'écoulement.
  13. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que la section d'écoulement libre d'au moins une ouverture de trop-plein (10') placée dans un deuxième collecteur inférieur (1') diminue dans une zone située dans le prolongement des tubes par lesquels s'écoule le fluide frigorigène sortant du collecteur (1').
EP20070018044 2006-09-29 2007-09-14 Caloporteur en plaques, en particulier évaporateur pour une climatisation de véhicule automobile Expired - Fee Related EP1909054B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006046671A DE102006046671A1 (de) 2006-09-29 2006-09-29 Wärmetauscher in Plattenbauweise, insbesondere Verdampfer für eine Kraftfahrzeug-Klimaanlage

Publications (3)

Publication Number Publication Date
EP1909054A2 EP1909054A2 (fr) 2008-04-09
EP1909054A3 EP1909054A3 (fr) 2011-03-02
EP1909054B1 true EP1909054B1 (fr) 2014-03-19

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DE (1) DE102006046671A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008023055A1 (de) 2007-05-22 2008-11-27 Behr Gmbh & Co. Kg Wärmeübertrager
DE102014203038A1 (de) * 2014-02-19 2015-08-20 MAHLE Behr GmbH & Co. KG Wärmeübertrager
DE102014206955A1 (de) 2014-04-10 2015-10-15 Mahle International Gmbh Wärmeübertrager

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Publication number Priority date Publication date Assignee Title
US5205347A (en) * 1992-03-31 1993-04-27 Modine Manufacturing Co. High efficiency evaporator
JPH11351786A (ja) * 1998-06-04 1999-12-24 Calsonic Corp 熱交換器
DE10149507A1 (de) * 2001-10-06 2003-04-10 Behr Gmbh & Co Wärmetauscher, insbesondere Flachrohr-Wärmetauscher eines Kraftfahrzeugs
US7481266B2 (en) * 2001-12-21 2009-01-27 Behr Gmbh & Co. Kg Heat exchanger for a motor vehicle
DE20307881U1 (de) * 2003-05-21 2004-09-23 Autokühler GmbH & Co. KG Wärmeaustauscher, insbesondere Ladeluftkühler
DE10349150A1 (de) * 2003-10-17 2005-05-19 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere für Kraftfahrzeuge
FR2863044B1 (fr) * 2003-11-27 2006-01-13 Valeo Climatisation Module pour l'echange de chaleur entre fluides en circulation
DE102005020499A1 (de) * 2005-04-29 2006-11-09 Behr Gmbh & Co. Kg Verdampfer, insbesondere Heckverdampfer für ein Kraftfahrzeug
JP2007155268A (ja) * 2005-12-07 2007-06-21 Denso Corp 熱交換器および冷媒蒸発器
DE102005059919A1 (de) * 2005-12-13 2007-06-14 Behr Gmbh & Co. Kg Wärmetauscher, insbesondere Verdampfer

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Publication number Publication date
EP1909054A2 (fr) 2008-04-09
EP1909054A3 (fr) 2011-03-02
DE102006046671A1 (de) 2008-04-03

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