EP2671032A2 - Heat exchanger - Google Patents

Heat exchanger

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Publication number
EP2671032A2
EP2671032A2 EP12703096.3A EP12703096A EP2671032A2 EP 2671032 A2 EP2671032 A2 EP 2671032A2 EP 12703096 A EP12703096 A EP 12703096A EP 2671032 A2 EP2671032 A2 EP 2671032A2
Authority
EP
European Patent Office
Prior art keywords
unit
heat exchanger
evaporator
distribution
distribution unit
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP12703096.3A
Other languages
German (de)
French (fr)
Other versions
EP2671032B1 (en
Inventor
Andreas Freund
Wolfgang Seewald
Michael Sickelmann
Bernd Schäfer
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
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Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP2671032A2 publication Critical patent/EP2671032A2/en
Application granted granted Critical
Publication of EP2671032B1 publication Critical patent/EP2671032B1/en
Revoked legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • 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
    • F25B39/028—Evaporators having distributing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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

Definitions

  • the invention relates to a heat exchanger according to the patent claim 1.
  • Evaporators are known in which the two-phase refrigerant is distributed from an inflow channel to a flow-through device, preferably tubes, in particular flat tubes. After flowing through the flat tubes, the vaporous refrigerant exits the evaporator via an outflow channel.
  • the uniform distribution of the liquid refrigerant in the entire length of the inflow channel presents difficulties.
  • the reason for this is, inter alia, the formation of different flow forms as a function of the operating state.
  • the segregation of the homogeneous two-phase refrigerant mixture at the entry of the evaporator also plays a special role over the length of the inflow channel. Individual pipes are thus supplied exclusively with refrigerant vapor, whereby the evaporator performance deteriorates.
  • the refrigerant is only distributed to a small proportion (typically 1/3, 1/4 or 1/8) of the flat tubes and further deflected in several blocks and thus passed through the evaporator.
  • the refrigerant in the individual collectors is intermixed by internals such as partitions, diaphragms, so that higher pressure losses occur are to be expected in the evaporator unit.
  • the ratio of the pressure differences in the distribution unit (injection pipe + distribution unit for the 1st block) and the entire block (flat tubes + deflections between the blocks) is in the range of less than 3.
  • the invention has for its object to provide an improved heat exchanger, which in particular in the heat-transmitting part of the evaporator - the evaporation section or, evaporator unit - realized low refrigerant side pressure losses, This object is achieved by a heat exchanger with the features of claim 1.
  • the heat exchanger in particular for a heating or air conditioning in a motor vehicle, with a via a distribution unit with a refrigerant medium fed and flowed through by this and after only one deflection (two-block design) formed in the depth in a deflection unit around evaporator unit, wherein the distribution unit is designed in the sense of a uniform distribution of the refrigerant medium over the entire evaporator width. Due to the additional internals in the distribution unit, the two-phase refrigerant is thus distributed evenly over the entire evaporator width on the flat tubes and deflected only once.
  • a design of the distribution unit in terms of a ratio V of the pressure difference between the pressure difference in the distribution unit on the one hand and the pressure difference in the evaporator unit on the other hand, which is greater than 3.
  • An increase in the ratio of the pressure differences is necessary for a homogeneous distribution of the refrigerant in the distribution unit and thus leads to an increase in the specific cooling capacity due to a better temperature profile.
  • a design of the distribution unit in the sense of a ratio of the pressure difference between the pressure difference in the distribution unit on the one hand and the pressure difference in the evaporator unit on the other hand be provided in the range between 3 and 70.
  • a design of the distribution unit in the sense of a ratio of the pressure difference between the pressure difference in the Distribution unit on the one hand and the pressure difference in the evaporator unit on the other hand be provided, which in a range of 3 to 30 at a refrigerant edium mass flow of 30 kg / h on the one hand and 30-70 at a refrigerant medium mass flow of 250 kg / h lies.
  • FIG. 2 and 3 also show a pressure-enthalpy diagram schematically illustrated a refrigerant circuit of an air conditioner, wherein essential points of the refrigerant circuit were provided with digits, which were shown according to the pressure-enthalpy diagram.
  • An embodiment of the invention provides in particular for a deflection unit free of any intermediate mixing means.
  • a further embodiment provides a pressure distribution element in the distribution unit in the sense of a distribution of the refrigerant medium in parallel to all through-flow or flow around tubes, in particular flat tubes, the evaporator unit.
  • a pressure distribution element for example, the installation of an additional pressure loss element at the evaporator inlet (before evaporation) for the distribution of the refrigerant can be applied in parallel to all flat tubes via the Velvet width of the evaporator may be provided so that all flat tubes are supplied evenly with liquid and gaseous refrigerant (this pressure loss element has no effect on the cooling capacity). This results in a large ratio of pressure loss in the refrigerant distribution at the evaporator inlet to the pressure loss in the evaporator network (evaporator section).

Abstract

A heat exchanger, in particular for a heating or air-conditioning system in a motor vehicle, having an evaporator unit to which a refrigerant medium can be supplied via a distribution unit and through which said refrigerant medium flows and around which said refrigerant medium flows after only one diversion (two-block design) at the bottom in a diversion unit, wherein the distribution unit is designed to effect a uniform distribution of the refrigerant medium over the hill width of the evaporator.

Description

Wärmeübertrager  Heat exchanger
Die Erfindung betrifft einen Wärmeübertrager gemäß dem Patentanspruch 1. The invention relates to a heat exchanger according to the patent claim 1.
Es sind Verdampfer bekannt, bei denen das zweiphasige Kältemittel aus einem Einströmkanal auf eine Durchflusseinrichtung, vorzugsweise Rohre, insbesondere Flachrohre, verteilt wird. Nach Durchströmung der Flachrohre tritt das dampfförmige Kältemittel über einen Ausströmkanal aus dem Verdampfer aus. Evaporators are known in which the two-phase refrigerant is distributed from an inflow channel to a flow-through device, preferably tubes, in particular flat tubes. After flowing through the flat tubes, the vaporous refrigerant exits the evaporator via an outflow channel.
Dabei bereitet die gleichmäßige Verteilung des flüssigen Kältemittels in der gesamten Länge des Einströmkanals Schwierigkeiten. Grund dafür ist unter anderem die Ausbildung unterschiedlicher Strömungsformen in Abhängigkeit vom Betriebszustand, Des Weiteren spielt auch die Entmischung des bei Verdampfereintritt homogenen zweiphasigen Kältemittelgemisches über die Länge des Einströmkanals eine besondere Rolle. Einzelne Rohre werden somit ausschließlich mit Kältemitteldampf versorgt, wodurch sich die Verdampferleistung verschlechtert. Um das Kältemittel optimal auf alle Flachrohre zu verteilen, wird das Kältemittel nur auf einen kleinen Anteil {typischerweise 1/3, 1/4 oder 1/8) der Flachrohre verteilt und in mehreren Blöcken weiter umgelenkt und so durch den Verdampfer geleitet. In diesen Umlenkungen werden häufig zusätzliche Einbauten zur gleichmäßigen Vermischung der flüssigen und gasförmigen Phase vorgesehen. Die aktuelle Beaufschlagung des Kältemittels auf nur einen Teil des Blockes und vorhandene Einbauten führen dabei zu einem deutlich erhöhten Druckverlust des Kältemittels im gesamten Block bzw. der Verdampfungsstrecke. In this case, the uniform distribution of the liquid refrigerant in the entire length of the inflow channel presents difficulties. The reason for this is, inter alia, the formation of different flow forms as a function of the operating state. Furthermore, the segregation of the homogeneous two-phase refrigerant mixture at the entry of the evaporator also plays a special role over the length of the inflow channel. Individual pipes are thus supplied exclusively with refrigerant vapor, whereby the evaporator performance deteriorates. To distribute the refrigerant optimally to all flat tubes, the refrigerant is only distributed to a small proportion (typically 1/3, 1/4 or 1/8) of the flat tubes and further deflected in several blocks and thus passed through the evaporator. In these deflections additional fittings for uniform mixing of the liquid and gaseous phase are often provided. The current admission of the refrigerant to only a portion of the block and existing internals lead to a significantly increased pressure drop of the refrigerant in the entire block or the evaporation section.
Ferner wird auch bei dem in der US 2008/0223566 A1 offenbarten und in Zweiblockverschaltung ausgeführten Wärmeübertrager, insbesondere für eine Heizungs- oder Klimaanlage für Kraftfahrzeuge, das Kältemittel in den einzelnen Sammlern durch Einbauten, wie Zwischenwände, Blenden etc. zwischenvermischt, so dass höhere Druckverluste in der Verdampfereinheit zu erwarten sind. Das Verhältnis der Druckdifferenzen in der Verteilungseinheit (Einspritzrohr + Verteileinheit für den 1. Block) und dem gesamten Block (Flachrohre + Umlenkungen zwischen den Blöcken) liegt dabei im Bereich von kleiner 3. Furthermore, even in the case of the heat exchanger disclosed in US 2008/0223566 A1 and constructed in two-block connection, in particular for a heating or air conditioning system for motor vehicles, the refrigerant in the individual collectors is intermixed by internals such as partitions, diaphragms, so that higher pressure losses occur are to be expected in the evaporator unit. The ratio of the pressure differences in the distribution unit (injection pipe + distribution unit for the 1st block) and the entire block (flat tubes + deflections between the blocks) is in the range of less than 3.
Die aus dem Stand der Technik bekannten Wärmeübertrager in Zwei- und auch Mehrblockverschaltung lassen jedoch insbesondere im Hinblick auf ihre konstruktive Ausgestaltung (aufwändiger Fertigungsprozess) sowie dem vergleichsweise hohen kältemittelseitigen Druckabfall in der Verdampfungsstre- cke noch Wünsche offen. However, the known from the prior art heat exchangers in two- and multi-block interconnection still leave something to be desired, in particular with regard to their structural design (complex manufacturing process) and the relatively high refrigerant side pressure drop in the evaporation path.
Der Erfindung liegt die Aufgabe zugrunde, einen verbesserten Wärmeübertrager zu schaffen, welcher insbesondere im wärmeübertragenden Teil des Verdampfers - der Verdampfungsstrecke bzw, Verdampfereinheit- geringe kältemittelseitige Druckverluste realisiert, Diese Aufgabe wird gelöst durch einen Wärmeübertrager mit den Merkmalen des Anspruchs 1. Vorteilhafte Ausgestaltungen sind Gegenstand der Unteransprüche, Erfindungsgemäß ist der Wärmeübertrager, insbesondere für eine Heizungsoder Klimaanlage in einem Kraftfahrzeug, mit über eine Verteilungseinheit rnit einem Kältemittel-Medium beschickbaren und von diesem durchströmten und nach nur einer Umlenkung (Zweiblock-Bauweise) in der Tiefe in einer Umlenkeinheit umströmten Verdampfereinheit ausgebildet, wobei die Vertei- lungseinheit im Sinne einer gleichmäßigen Verteilung des Kältemittel- Mediums über die gesamte Verdampfer-Breite ausgelegt ist. Aufgrund der zusätzlichen Einbauten in der Verteilereinheit wird das zweiphasige Kältemittel also gleichmäßig über die gesamte Verdampfer-Breite auf die Flachrohre verteilt und nur einmal umgelenkt. Ein weiterer Vorteil liegt in der Tatsache, dass aufgrund der gleichmäßigen Beaufschlagung aller Flachrohre das Kältemittel in der Umlenkung nicht zwischenvermischt wird.Vorzugsweise kann eine Auslegung der Verteilungseinheit im Sinne eines Verhältnisses V der Druckdifferenz zwischen der Druckdifferenz in der Verteilungseinheit einerseits und der Druckdifferenz in der Verdampfereinheit andererseits vorgese- hen sein, welche größer 3 ist. Eine Erhöhung des Verhältnisses der Druckdifferenzen ist dabei notwendig für eine homogene Verteilung des Kältemittels in der Verteilungseinheit und führt somit in weiterer Folge zu einer Erhöhung der spezifischen Kälteleistung aufgrund eines besseren Temperaturprofils. Beispielsweise kann eine Auslegung der Verteilungseinheit im Sinne eines Verhältnisses der Druckdifferenz zwischen der Druckdifferenz in der Verteilungseinheit einerseits und der Druckdifferenz in der Verdampfereinheit andererseits im Bereich zwischen 3 und 70 vorgesehen sein. Diese Werte haben sich im Rahmen getätigter Versuche als besonders vorteilhaft erwiesen. The invention has for its object to provide an improved heat exchanger, which in particular in the heat-transmitting part of the evaporator - the evaporation section or, evaporator unit - realized low refrigerant side pressure losses, This object is achieved by a heat exchanger with the features of claim 1. Advantageous embodiments are the subject of the dependent claims, according to the invention, the heat exchanger, in particular for a heating or air conditioning in a motor vehicle, with a via a distribution unit with a refrigerant medium fed and flowed through by this and after only one deflection (two-block design) formed in the depth in a deflection unit around evaporator unit, wherein the distribution unit is designed in the sense of a uniform distribution of the refrigerant medium over the entire evaporator width. Due to the additional internals in the distribution unit, the two-phase refrigerant is thus distributed evenly over the entire evaporator width on the flat tubes and deflected only once. Another advantage lies in the fact that due to the uniform loading of all flat tubes, the refrigerant is not mixed in the deflection. Preferably, a design of the distribution unit in terms of a ratio V of the pressure difference between the pressure difference in the distribution unit on the one hand and the pressure difference in the evaporator unit on the other hand, which is greater than 3. An increase in the ratio of the pressure differences is necessary for a homogeneous distribution of the refrigerant in the distribution unit and thus leads to an increase in the specific cooling capacity due to a better temperature profile. For example, a design of the distribution unit in the sense of a ratio of the pressure difference between the pressure difference in the distribution unit on the one hand and the pressure difference in the evaporator unit on the other hand be provided in the range between 3 and 70. These values have proven to be particularly advantageous in the context of experiments.
Dabei kann insbesondere eine Auslegung der Verteilungseinheit im Sinne eines Verhältnisses der Druckdifferenz zwischen der Druckdifferenz in der Verteilungseinheit einerseits und der Druckdifferenz in der Verdampfereinheit andererseits vorgesehen sein, welche in einem Bereich von 3 bis 30 bei einem Kältemittel- edium-Massenstrom von 30 kg/h einerseits und von 30-70 bei einem Kältemittel-Medium-Massenstrom von 250 kg/h liegt. In particular, a design of the distribution unit in the sense of a ratio of the pressure difference between the pressure difference in the Distribution unit on the one hand and the pressure difference in the evaporator unit on the other hand be provided, which in a range of 3 to 30 at a refrigerant edium mass flow of 30 kg / h on the one hand and 30-70 at a refrigerant medium mass flow of 250 kg / h lies.
Das Verhältnis der Differenzdrücke zum Kältemittel-Medium-Massenstrom, wie oben beschrieben, wird durch Fig. 1 veranschaulicht. Hierbei stellt die Differenz (pa- s) die Druckdifferenz in der Verteilungseinheit und die Diffe- renz (p3-p ) die Druckdifferenz in der Verdampfereinheit dar. Zur besseren Veranschaulichung sind ferner in den Fig. 2 und 3 ein Druck-Enthalpie Diagramm beziehungsweise schematisch ein Kältemittelkreislauf einer Klimaanlage dargestellt, wobei wesentliche Punkte des Kältemittelkreislaufes mit Ziffern versehen wurden, die entsprechend im Druck-Enthalpie Diagramm dar- gestellt wurden. The ratio of the differential pressures to the refrigerant-medium mass flow, as described above, is illustrated by FIG. In this case, the difference (pas) represents the pressure difference in the distribution unit and the difference (p 3 -p) the pressure difference in the evaporator unit. For better illustration, FIGS. 2 and 3 also show a pressure-enthalpy diagram schematically illustrated a refrigerant circuit of an air conditioner, wherein essential points of the refrigerant circuit were provided with digits, which were shown according to the pressure-enthalpy diagram.
Aufgrund der Verteilung über die Verteilungseinheit mit einem zusätzlichen Druckverlust des Kältemittels auf alle Flachrohre, und zwar über die gesamte Verdampferbreite, kann ein gleichmäßiges Temperaturprofil ohne zusätzli- che Einbauten im Netz bzw. in den Sammelkästen erzielt werden. Due to the distribution over the distribution unit with an additional pressure loss of the refrigerant to all flat tubes, and indeed over the entire evaporator width, a uniform temperature profile can be achieved without additional installations in the network or in the collection boxes.
Eine Ausführungsform der Erfindung sieht dabei insbesondere eine von jeglichen Zwischenvermischungsmitteln freie Umlenkeinheit vor. Eine weitere Ausführungsform sieht ein Druckverteilelement in der Verteilungseinheit im Sinne einer Verteilung des Kältemittel-Mediums parallel auf sämtliche durch- bzw. umströmten Rohre, insbesondere Flachrohre, der Verdampfereinheit vor. Im Sinne eines Druckverteilelements kann beispielsweise der Einbau eines zusätzlichen Druckverlustelements am Verdampfer-Eintritt (vor Verdampfung) zur Verteilung des Kältemittels parallel auf alle Flachrohre über die ge- samte Breite des Verdampfers vorgesehen sein, so dass alle Flachrohre gleichmäßig mit flüssigem und gasförmigem Kältemittel versorgt werden (dieses Druckverlustelement hat dabei keine Auswirkung auf die Kälteleistung). Daraus ergibt sich ein großes Verhältnis von Druckverlust bei der Käl- temittel-Verteilung am Verdampfer- Eintritt zum Druckverlust im Verdampfer- Netz (Verdampferstrecke). An embodiment of the invention provides in particular for a deflection unit free of any intermediate mixing means. A further embodiment provides a pressure distribution element in the distribution unit in the sense of a distribution of the refrigerant medium in parallel to all through-flow or flow around tubes, in particular flat tubes, the evaporator unit. In the sense of a pressure distribution element, for example, the installation of an additional pressure loss element at the evaporator inlet (before evaporation) for the distribution of the refrigerant can be applied in parallel to all flat tubes via the Velvet width of the evaporator may be provided so that all flat tubes are supplied evenly with liquid and gaseous refrigerant (this pressure loss element has no effect on the cooling capacity). This results in a large ratio of pressure loss in the refrigerant distribution at the evaporator inlet to the pressure loss in the evaporator network (evaporator section).

Claims

P a t e n t a n s p r ü c h e P a n t a n s p r e c h e
1. Wärmeübertrager, insbesondere für eine Heizungs- oder Klimaanlage in einem Kraftfahrzeug, mit über eine Verteilungseinheit mit einem Kältemittel-Medium beschickbaren und von diesem durchströmten und nach nur einer Umlenkung (Zweiblock-Bauweise) in der Tiefe in einer Umlenkeinheit umströmten Verdampfereinheit, wobei die Verteilungseinheit im Sinne einer gleichmäßigen Verteilung des Kältemittel- Mediums über die gesamte Verdampfer- Breite ausgelegt ist, 1. Heat exchanger, in particular for a heating or air conditioning in a motor vehicle, via a distribution unit with a refrigerant medium can be fed and flowed through by this and after only one deflection (two-block design) in the flow around in a diverter evaporator unit, wherein the Distribution unit is designed in the sense of a uniform distribution of the refrigerant medium over the entire evaporator width,
2. Wärmeübertrager nach Anspruch 1 , gekennzeichnet durch eine Ausle- gung der Verteilungseinheit im Sinne eines Verhältnisses V der Druckdifferenzen zwischen der Verteilungseinheit (p2-p3) einerseits und der Verdampfereinheit (p3-p4) andererseits, das größer 3 ist. 2. Heat exchanger according to claim 1, characterized by a design of the distribution unit in terms of a ratio V of the pressure differences between the distribution unit (p 2 -p 3 ) on the one hand and the evaporator unit (p 3 -p 4 ) on the other hand, which is greater than 3.
3. Wärmeübertrager nach Anspruch 2, gekennzeichnet durch eine Ausle- gung der Verteilungseinheit im Sinne eines Verhältnisses der Druckdifferenzen zwischen der Verteilungseinheit einerseits und der3. Heat exchanger according to claim 2, characterized by a design of the distribution unit in terms of a ratio of the pressure differences between the distribution unit on the one hand and the
Verdampfereinheit andererseits im Bereich zwischen 3 und 70, Evaporator unit, on the other hand, in the range between 3 and 70,
4. Wärmeübertrager nach Anspruch 3, gekennzeichnet durch eine Ausle- gung der Verteilungseinheit im Sinne eines Verhältnisses der Druckdifferenz zwischen dem Druck in der Verteilungseinheit einerseits und dem Druck in der Verdampfereinheit andererseits in einem Bereich von 3 bis 30 bei einem Kältemittel-Medium-Massenstrom von 30 kg/h einerseits und von 30-70 bei einem Kältemittel-Medium-Massenstrom von 250 kg/h liegt. 4. Heat exchanger according to claim 3, characterized by a design of the distribution unit in terms of a ratio of the pressure difference between the pressure in the distribution unit on the one hand and the pressure in the evaporator unit on the other hand in a range of 3 to 30 at a refrigerant medium mass flow of 30 kg / h on the one hand and from 30-70 at a refrigerant medium mass flow of 250 kg / h.
5. Wärmeübertrager nach zumindest einem der Ansprüche 1 bis 4, gekennzeichnet durch eine von jeglichen Zwischenvermischungsmitteln freien Umlenkeinheit, 8. Wärmeübertrager nach zumindest einem der vorherigen Ansprüche, gekennzeichnet durch ein Druckverteilelement in der Verteilungseinheit im Sinne einer Verteilung des Kältemittel-Mediums parallel auf sämtliche durch- bzw. umströmten Rohre, insbesondere Flachrohre, der Verdampfereinheit. 5. Heat exchanger according to at least one of claims 1 to 4, characterized by a free of any intermediate mixing means deflecting unit, 8. Heat exchanger according to at least one of the preceding claims, characterized by a pressure distribution element in the distribution unit in the sense of a distribution of the refrigerant medium in parallel to all - or flowed around pipes, in particular flat tubes, the evaporator unit.
7. Wärmeübertrager nach zumindest einem der vorherigen Ansprüche, gekennzeichnet durch einen Dual-Flow-Verdampfer als Wärmeübertrager. 7. Heat exchanger according to at least one of the preceding claims, characterized by a dual-flow evaporator as a heat exchanger.
EP12703096.3A 2011-02-04 2012-02-06 Heat exchanger Revoked EP2671032B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011003649A DE102011003649A1 (en) 2011-02-04 2011-02-04 Heat exchanger
PCT/EP2012/051984 WO2012104438A2 (en) 2011-02-04 2012-02-06 Heat exchanger

Publications (2)

Publication Number Publication Date
EP2671032A2 true EP2671032A2 (en) 2013-12-11
EP2671032B1 EP2671032B1 (en) 2018-05-09

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EP12703096.3A Revoked EP2671032B1 (en) 2011-02-04 2012-02-06 Heat exchanger

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Country Link
US (1) US9599409B2 (en)
EP (1) EP2671032B1 (en)
DE (1) DE102011003649A1 (en)
WO (1) WO2012104438A2 (en)

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US9599409B2 (en) 2017-03-21
WO2012104438A3 (en) 2013-03-28
WO2012104438A2 (en) 2012-08-09
EP2671032B1 (en) 2018-05-09
US20140027096A1 (en) 2014-01-30
DE102011003649A1 (en) 2012-08-09

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