WO2014140133A1 - Ensemble condensateur pour fluide frigorigène - Google Patents

Ensemble condensateur pour fluide frigorigène Download PDF

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Publication number
WO2014140133A1
WO2014140133A1 PCT/EP2014/054891 EP2014054891W WO2014140133A1 WO 2014140133 A1 WO2014140133 A1 WO 2014140133A1 EP 2014054891 W EP2014054891 W EP 2014054891W WO 2014140133 A1 WO2014140133 A1 WO 2014140133A1
Authority
WO
WIPO (PCT)
Prior art keywords
region
percentage
heat exchanger
capacitor assembly
refrigerant
Prior art date
Application number
PCT/EP2014/054891
Other languages
German (de)
English (en)
Inventor
Uwe FÖRSTER
David Guillaume
Andreas Kemle
Matthias Jung
Christoph Walter
Ottokar Kunberger
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 BR112015020809-6A priority Critical patent/BR112015020809B1/pt
Priority to CN201480015182.8A priority patent/CN105143806B/zh
Priority to EP14709946.9A priority patent/EP2972040B1/fr
Publication of WO2014140133A1 publication Critical patent/WO2014140133A1/fr
Priority to US14/851,299 priority patent/US20160069597A1/en

Links

Classifications

    • 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
    • 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
    • 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
    • F28D1/05375—Assemblies of conduits connected to common headers, e.g. core type radiators with particular pattern of flow, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • F25B2339/0441—Condensers with an integrated receiver containing a drier or a filter
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F28D2021/0084—Condensers

Definitions

  • the invention relates to a capacitor assembly according to the preamble of claim 1.
  • refrigerant R1234yf instead of the previous refrigerant R134a results in non-negligible power reductions in the area of the refrigerant circuit in order to increase the capacity of the refrigerant circuit.
  • greater undercooling of the already liquefied refrigerant is possible, ie the refrigerant is in a subcooling range cooled a temperature which is below the condensation temperature of the refrigerant.
  • a capacitor assembly of an automotive air conditioning system for refrigerants with such an approach to increase performance is known for example from DE 10 2010 039 51 1 A1.
  • This known capacitor assembly provides a header on a first longitudinal side of the refrigerant condenser assembly, two header tubes, heat transfer tubes in a transition region for cooling the vapor refrigerant, a condensing region for condensing the refrigerant, and a subcooling region in which the subcooling region is formed with three cooling sections, at least two heat exchanger tubes being parallelly fluidly supplied with the refrigerant as a first subcool parallel section , the refrigerant flowing out of the first sub-cooling parabolic section discharges into a first sub-cooling intermediate flow channel.
  • This first sub-cooling intermediate flow channel discharges into at least two heat exchanger tubes as a second sub-cooling parabolic section.
  • This second sub-cooling parabolic section opens into a second sub-cooling intermediate flow channel.
  • the second subcooling intermediate flow channel discharges into at least two heat exchanger tubes as the third subcooler parabolic section, wherein an outlet opening is arranged on a second longitudinal side of the refrigerant condenser subassembly. Due to the increased subcooling distance, formed by three areas shaded in series, results in - with comparable overall size of the capacitor assembly - a reduced condensation area, which increases the high pressure in the refrigerant circuit. Such a capacitor assembly can therefore still wishes with regard to the cooling capacity and efficiency open.
  • the percentage of the heat exchanger tubes of the first group results
  • Such a configuration is particularly applicable for capacitors with a subcooling region, which has three cooling sections, each with at least two tubes in each cooling section.
  • both R.134, R1234yf but also other refrigerants can be used, which have approximately comparable properties with R 134 or R1234yf.
  • the percentage is preferably given by
  • the condenser assembly has at least four regions connected in series, wherein the first region of the series-connected regions occupies said percentage of the total end surface.
  • the percentage of the series-connected regions in the normal flow direction of the refrigerant can decrease from the second region to the third region.
  • the percentage of the series-connected regions in the normal flow direction of the refrigerant decreases at the beginning of the series and is constant at the end of the series.
  • the percentage of the first region of six regions connected in series in the normal flow direction of the refrigerant is greater than the percentage of the second region, and the percentage of the third region is preferably the same as the percentage of the fourth Area, the fifth area and the sixth area.
  • the percentage of the first region of six regions connected in series in the normal flow direction of the refrigerant is preferably twice as large as the percentage of the second region, and the percentage of the third region is preferably the same as the percentage Proportion of the fourth region, the fifth region and the sixth region, wherein the sum of the percentages of the third, fourth, fifth and sixth region is preferably equal to the percentage of the second region, and the percentage of the first region preferably equal what is the sum of the percentages of the remaining areas.
  • the deflection regions are preferably arranged within manifolds, wherein the refrigerant-receiving volume of the manifolds in the normal flow direction of the refrigerant in a first deflection region between the first region and the second region is preferably greater than in a second deflection region between the second region and the third region a collecting container is preferably arranged after the third region.
  • the invention is particularly suitable for capacitor assemblies with three-flow subcooling, each with at least two Wirmeübertragerrohren, but can also be used for other capacitor assemblies, for example, with einflutigem subcooling and dreiflutigem condensation region,
  • FIG. 1 is a schematic representation of a capacitor assembly with three cooling sections according to the first embodiment
  • Fig. 2 is a fragmentary, schematic representation of
  • FIG. 3 is a schematic representation of a capacitor assembly with three cooling sections according to the second embodiment, and a diagram of the percentage of capitasted instincterroh a first area over the wirmeübertragenden face.
  • a condenser module 1 which is part of an automotive air conditioning system (not shown in more detail) with an evaporator and a compressor arranged in a refrigerant circuit, has laterally arranged first and second longitudinal sides L1 and L2.
  • the condenser module 1 is usually located in a motor vehicle
  • the depth of the capacitor assembly 1 extends in the x-direction, wherein the x-direction of the air flow direction through the capacitor assembly 1 corresponds, ie opposite to the normal direction of travel of the vehicle runs. Corresponding directions are used below to describe the capacitor assembly 1.
  • An inlet opening 2 is arranged on the first longitudinal side L1 at the top of the condenser module 1, through which refrigerant circulating in the refrigerant circuit, in the present case R1234yf, enters the condenser module 1.
  • a presently continuous collecting pipe 3 is arranged on each longitudinal side L1, L2 of the capacitor assembly 1.
  • the headers 3 are connected via heat exchanger tubes 4, formed by flat tubes, in a known manner with each other.
  • baffles are arranged to specify the flow path (indicated schematically by arrows in the drawing) of the refrigerant through the heat exchanger tubes 4 and separate individual deflection regions from each other.
  • corrugated fins 5 are in a known manner arranged, which are in thermal and mechanical connection with the heat exchanger tubes 4 and enlarge the heat transfer surface of the heat exchanger tubes 4 and thus the capacitor assembly 1.
  • the heat-transferring region of the capacitor assembly 1 is flowed through in a z-shaped manner in the significantly larger, upper region, the height and thus the number of parallel arranged, in a direction of refrigerant heat exchanger tubes 4 greatly reduced down before the refrigerant at the bottom End of this upper portion obliquely opposite to the inlet opening 2 in a parallel to the arranged on the second longitudinal side L2 collecting pipe 3 conventionally constructed collecting container 6, in which a dryer and filter ⁇ not shown) is arranged.
  • the upper group of the heat exchanger tubes 4, which flow in parallel in one direction, of this upper region as the first flow path (first region A), onto the middle group of the heat exchanger tubes 4, which flow through the upper region in parallel and opposite to the upper group, as the second flow path (second region B ) and the lower group of the heat exchanger tubes 4, which flow through this upper region in parallel and counter to the middle group, are referred to as the third flow path (third region C).
  • These individual regions AC are connected in series via said deflection regions. Due to the function, namely that the superheated, gaseous refrigerant is cooled to a saturation temperature in the corresponding upper region of the capacitor assembly 1, the first region A is also referred to as the overheating region.
  • the second and third regions B and C are referred to collectively as the condensation region, since in this region the refrigerant cooled to the saturation temperature condenses and then passes as liquid into the collection container 6.
  • a subcooling region 7 is provided as a smaller, lower region as a further part of the capacitor assembly 1, to which the refrigerant liquefied in the condensation region is supplied.
  • this subcooling region 7 is likewise flowed through in Z-shape, starting from the lower end region of the collecting container 6.
  • the subcooling region 7 is, according to DE 10 2010 039 51 1 A1, by three cooling sections, in each case by two heat exchanger tubes running parallel to one another, as well as deflecting regions arranged therebetween formed in the headers 3, wherein at the end the Kiltemittei passes over the arranged on the first longitudinal side L1 manifold 3 to an outlet opening 8.
  • these heat exchanger tubes are referred to as areas D, E and F in the order of the normal flow of refrigerant.
  • the deflection of the refrigerant in the subcooling 7 between the individual cooling sections is present in the headers 3 by baffles, corresponding to the deflection in the larger, upper area, but it can also be done in any other way, ie the headers 3, for example, above the supercooling ereichs 7 ends and the deflection can be done by separately formed deflection.
  • the manifolds 3, the heat exchanger tubes 2, the corrugated fins 5 and possibly the deflection areas are usually made of metal, in this case made of aluminum.
  • the individual components are presently materially connected as solder joints with each other, but also another Hersannon with a corresponding structure is conceivable.
  • all heat exchanger tubes 4 are formed with mutually corresponding and over the length of the Wirmeübertragerrohre 4 constant flow cross-sections, and all Wirmeübertragerrohre 4 are arranged equidistantly over the height of the capacitor assembly 1.
  • the entire flow path of the refrigerant within the heat transfer area AC and corresponding to the subcooling DE results due to the deflection respectively approximately 3 x Lh, wherein within the individual areas AF each have a plurality of parallel heat exchanger tubes 4 are provided, and the number of parallel heat exchanger tubes. 4 in the areas A, B, C respectively in the direction of the flow path decreases.
  • the number of parallel heat exchanger tubes 4 in the areas DE is present constant. It can also correspond to the number of heat exchanger tubes in the area C connected in parallel. In the present case, the number of heat exchanger tubes connected in parallel in the areas CF is two in each case.
  • FIGS. 1 and 3 correspond.
  • Essential for optimizing the cooling capacity of the condenser assembly 1 is the ratio of the heat exchanger tube number (and thus the area ratio with respect to the end face S) of the first region A, hereinafter referred to as nA, to the heat exchanger tube number nB of the second region B.
  • nA the heat exchanger tube number
  • nB the heat exchanger tube number
  • the influence of the third region C with nC heat exchanger tubes is of minor importance for performance
  • the condenser assembly 1, the heat exchanger tube number in the fourth to sixth range nD, nE, nF is also of minor importance.
  • Range A to the total number of heat exchanger tubes 4 of P nA / [100 x ( ⁇ + ⁇ + nC + nD + nE + nF)] in "square" design of the end face.
  • a capacitor module 1 with a ratio of Lh / Lv of 1.0 is shown in FIG. 1 as the first exemplary embodiment.
  • the percentage of the first region A is about 10% below.
  • the proportion of the heat exchanger tubes 4, which are associated with the first area, with respect to the total number of heat exchanger tubes 4 in percent, which to a good performance of an air conditioner with an inventively designed capacitor assembly 1 leads.
  • the abovementioned ratio is valid, in particular, for end faces S in the range from 10 to 30 dm a , in particular in the range from 15 to 25 dm 2 , the plurality of capacitors used in the vehicle area having a correspondingly large end face S.
  • the second area B is approximately the same size as the third to sixth areas CF together.
  • a corresponding ratio to the percentage design of the first region A with respect to the entire heat-transferring end face S can also be used if the subcooling region is not formed as described above but in three-flowed, two-flow or multiple flow, the number of flat tubes in the subcooling region totaling at least 6 to 16 is.
  • the o.g. Equation for P can also be used for nE and / or nF equal to zero, provided that the sum of the heat exchanger tubes in the subcooling range is in the range 6 to 16.
  • the headers 3 may also be formed by individual, separately formed deflection regions, in particular may reduce the flow cross-sectional area and / or volume in the flow direction of the refrigerant, as in DE 10th 2011 007 216 A1.
  • a corresponding flow cross-sectional area reduction is advantageous in particular between the first deflection region (region between region A and region B) and the second peripheral region (region between region B and region C), but may advantageously additionally be provided between the following regions.

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

Abstract

L'invention concerne un ensemble condensateur (1) comportant une pluralité de tubes de transmission de chaleur (4) disposés à équidistance sous une couche intermédiaire de nervures ondulées (5). Lesdits tubes de transmission de chaleur (4) débouchent de part et d'autre dans des zones de renvoi et présentent une longueur (Lh) libre servant à la transmission de chaleur. Ils forment, en combinaison avec les nervures ondulées (5), une surface frontale (S) présentant une largeur définie correspondant à la longueur (Lh) libre des tubes de transmission de chaleur (4) et une hauteur (Lv) de sorte que la surface frontale (S) est le résultat du produit de la largeur et de la hauteur. Les tubes de transmission de chaleur (4) sont branchés en parallèle dans des groupes et les divers groupes sont branchés en série. Les tubes de transmission de chaleur (4) des divers groupes sont disposés de manière adjacente, chaque groupe étant composé d'au moins deux tubes de transmission de chaleur (4). La part exprimée en pourcentage (P) des tubes de transmission de chaleur (4) du premier groupe est obtenue à partir de 26,162 In (S/dm2) - 40,746 ≤ P ≤ 25,49 In (S/dm2) - 27,842 pour une surface frontale (S) dont le rapport entre la largeur et la hauteur est situé dans la plage allant de 0,5 à 1,0, pour une surface frontale (S) dont la surface est comprise dans la plage allant de 10 à 30 dm², ladite surface de la surface frontale (S) étant exprimée en dm².
PCT/EP2014/054891 2013-03-12 2014-03-12 Ensemble condensateur pour fluide frigorigène WO2014140133A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
BR112015020809-6A BR112015020809B1 (pt) 2013-03-12 2014-03-12 módulo condensador para fluido refrigerante
CN201480015182.8A CN105143806B (zh) 2013-03-12 2014-03-12 用于冷却剂的冷凝器组件
EP14709946.9A EP2972040B1 (fr) 2013-03-12 2014-03-12 Ensemble condensateur pour fluide frigorigène
US14/851,299 US20160069597A1 (en) 2013-03-12 2015-09-11 Condenser assembly for refrigerant

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013204294.9 2013-03-12
DE102013204294.9A DE102013204294A1 (de) 2013-03-12 2013-03-12 Kondensatorbaugruppe für Kältemittel

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US14/851,299 Continuation US20160069597A1 (en) 2013-03-12 2015-09-11 Condenser assembly for refrigerant

Publications (1)

Publication Number Publication Date
WO2014140133A1 true WO2014140133A1 (fr) 2014-09-18

Family

ID=50277227

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2014/054891 WO2014140133A1 (fr) 2013-03-12 2014-03-12 Ensemble condensateur pour fluide frigorigène

Country Status (6)

Country Link
US (1) US20160069597A1 (fr)
EP (1) EP2972040B1 (fr)
CN (1) CN105143806B (fr)
BR (1) BR112015020809B1 (fr)
DE (1) DE102013204294A1 (fr)
WO (1) WO2014140133A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA1334627C (fr) * 1988-09-14 1995-03-07 Hironaka Sasaki Condensateur
JP2001133077A (ja) * 1999-11-09 2001-05-18 Showa Alum Corp レシーバタンク付き熱交換器
EP1167910A2 (fr) * 2000-06-20 2002-01-02 Showa Denko Kabushiki Kaisha Condenseur
EP1365200A1 (fr) * 2002-05-24 2003-11-26 Halla Climate Control Corporation Condenseur à séparation multiétagée des phases gazeuses et liquides
FR2915793A1 (fr) * 2007-05-03 2008-11-07 Valeo Systemes Thermiques Echangeur de chaleur ameliore pour circuit de climatisation de vehicule automobile
DE102010039511A1 (de) 2010-08-19 2012-02-23 Behr Gmbh & Co. Kg Kältemittelkondensatorbaugruppe
DE102011007216A1 (de) 2011-04-12 2012-10-18 Behr Gmbh & Co. Kg Kältemittelkondensatorbaugruppe

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5682944A (en) * 1992-11-25 1997-11-04 Nippondenso Co., Ltd. Refrigerant condenser
FR2709344B1 (fr) * 1993-08-27 1995-10-13 Valeo Thermique Moteur Sa Condenseur pour installation de climatisation de véhicule automobile.
JP3316365B2 (ja) * 1996-02-16 2002-08-19 三菱重工業株式会社 レシーバ一体型熱交換器
JPH10300271A (ja) * 1997-04-30 1998-11-13 Nippon Light Metal Co Ltd ヒートポンプ式冷暖房機の室外用熱交換器
GB2346680A (en) * 1999-02-11 2000-08-16 Llanelli Radiators Ltd Condenser
DE10065205A1 (de) * 2000-12-23 2002-07-04 Behr Gmbh & Co Kältemittel-Kondensator
DE10155001A1 (de) * 2001-11-08 2003-05-22 Behr Gmbh & Co Kältemittelkondensator
DE102007009923A1 (de) * 2007-02-27 2008-08-28 Behr Gmbh & Co. Kg Kondensator für eine Klimaanlage, insbesondere eines Kraftfahrzeuges
CN101978229B (zh) * 2008-10-20 2013-03-27 株式会社京滨冷暖科技 冷凝器
JP5717474B2 (ja) * 2010-04-16 2015-05-13 株式会社ケーヒン・サーマル・テクノロジー コンデンサ
DE102010039518A1 (de) * 2010-08-19 2012-02-23 Behr Gmbh & Co. Kg Kältemittelkondensatorbaugruppe
JP5651431B2 (ja) * 2010-11-08 2015-01-14 株式会社ケーヒン・サーマル・テクノロジー コンデンサ

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA1334627C (fr) * 1988-09-14 1995-03-07 Hironaka Sasaki Condensateur
JP2001133077A (ja) * 1999-11-09 2001-05-18 Showa Alum Corp レシーバタンク付き熱交換器
EP1167910A2 (fr) * 2000-06-20 2002-01-02 Showa Denko Kabushiki Kaisha Condenseur
EP1365200A1 (fr) * 2002-05-24 2003-11-26 Halla Climate Control Corporation Condenseur à séparation multiétagée des phases gazeuses et liquides
FR2915793A1 (fr) * 2007-05-03 2008-11-07 Valeo Systemes Thermiques Echangeur de chaleur ameliore pour circuit de climatisation de vehicule automobile
DE102010039511A1 (de) 2010-08-19 2012-02-23 Behr Gmbh & Co. Kg Kältemittelkondensatorbaugruppe
DE102011007216A1 (de) 2011-04-12 2012-10-18 Behr Gmbh & Co. Kg Kältemittelkondensatorbaugruppe

Also Published As

Publication number Publication date
BR112015020809B1 (pt) 2020-12-22
EP2972040A1 (fr) 2016-01-20
EP2972040B1 (fr) 2018-10-31
DE102013204294A1 (de) 2014-10-02
BR112015020809A2 (pt) 2017-07-18
US20160069597A1 (en) 2016-03-10
CN105143806B (zh) 2018-04-03
CN105143806A (zh) 2015-12-09

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