EP1767887A2 - Innerer Wärmetauscher für Klimaanlage-Kühlmittelkreislauf - Google Patents

Innerer Wärmetauscher für Klimaanlage-Kühlmittelkreislauf Download PDF

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Publication number
EP1767887A2
EP1767887A2 EP06120440A EP06120440A EP1767887A2 EP 1767887 A2 EP1767887 A2 EP 1767887A2 EP 06120440 A EP06120440 A EP 06120440A EP 06120440 A EP06120440 A EP 06120440A EP 1767887 A2 EP1767887 A2 EP 1767887A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
internal heat
tubes
distribution chamber
peripheral wall
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.)
Withdrawn
Application number
EP06120440A
Other languages
English (en)
French (fr)
Other versions
EP1767887A3 (de
Inventor
Roland Haussmann
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.)
Valeo Klimasysteme GmbH
Original Assignee
Valeo Klimasysteme GmbH
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 Valeo Klimasysteme GmbH filed Critical Valeo Klimasysteme GmbH
Publication of EP1767887A2 publication Critical patent/EP1767887A2/de
Publication of EP1767887A3 publication Critical patent/EP1767887A3/de
Withdrawn legal-status Critical Current

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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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0461—Combination of different types of heat exchanger, e.g. radiator combined with tube-and-shell heat exchanger; Arrangement of conduits for heat exchange between at least two media and for heat exchange between at least one medium and the large body of fluid
    • 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
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0025—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F28F9/0224—Header boxes formed by sealing end plates into covers
    • 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
    • F28F9/0243—Header boxes having a circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0073—Gas coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing

Definitions

  • the present invention relates to an internal heat exchanger for a cooling agent circuit of an air conditioning device, with a plurality of heat exchanger tubes arranged in parallel and traversed by the refrigerant, each with a dispensing head surrounding the ends. heat exchanger tubes forming at least one distribution chamber for the coolant.
  • the coolant CO 2 is preferably used under high pressure, however any other coolant is also conceivable.
  • the heat exchanger has a plurality of flat tubes that serve as heat exchanger tubes, which are stacked on top of one another in two bundles of tubes.
  • the beams are arranged laterally next to one another with a space between them and are surrounded on their respective ends by a common distribution head.
  • the dispensing head is composed of a cylindrical housing, the peripheral wall of which has two recesses in which the bundles of tubes are introduced and brazed laterally with the housing.
  • the present invention creates an internal heat exchanger of the type mentioned in the introduction, which is characterized by a simplified manufacturing process and therefore cheaper.
  • the dispensing head comprises a peripheral wall having the shape of an open profile tube.
  • a profiled tube of this category is, compared to the case known from the state of the art, much simpler to manufacture and therefore much cheaper.
  • the open profiled tube preferably has open longitudinal edges, on which are formed sections which extend parallel to each other, on the inner surfaces of which are fixed the sides of the heat exchanger tubes. These sections of the peripheral wall extending parallel to each other, which extend from the rest also parallel to the bundle of heat exchanger tubes, greatly facilitate a solder connection between the heat exchanger tubes and the head. of distribution. Even the durability of the solder joint is improved because of the significantly larger contact areas compared to the state of the art.
  • the dispensing head preferably has two end walls parallel to each other, which are manufactured as parts of separate constructions and are connected to the peripheral wall only during assembly.
  • the peripheral wall is preferably manufactured by profiled cylinders made of aluminum sheet, while the end walls are formed for example by milling, extrusion or stamping, each with numerical control for example. Since the individual parts are not yet connected to each other, the profiled tube which forms the peripheral wall may be slightly bent in an elastic manner during the assembly of the bundle of heat exchanger tubes (before the assembly of the tubes). walls end), which facilitates the placement of the beam in the profiled tube. In addition, this provides a better seal between the open longitudinal edges of the profiled tube and the beam.
  • Another advantage of the dispensing head composed of separate pieces of construction is that the distance between the two end walls, which are preferably arranged parallel to the flat side of the heat exchanger tubes, can be modified during the mounting within certain limits, so as to compress more or less strongly the heat exchanger tube bundle. In this way, it makes it possible to compensate the tolerances determined at the factory at the thickness of the tubes, which tolerances can be of ⁇ 1.2 mm maximum for a bundle of 15 tubes.
  • the peripheral wall and the separated end walls are first interconnected by crimping.
  • a dispensing head is used with an integral end wall which is welded before mounting the heat exchanger tubes to the peripheral wall (already soldered at this time -the).
  • the coating material diffuses locally locally into the base material, which increases the risk of electrochemical corrosion in a distribution head for a heat exchanger internal according to the state of the art.
  • the peripheral wall and the end walls are connected to each other by crimping, it is however possible without problem to provide an aluminum profile. profile laminated as peripheral wall, already provided before rolling a solder coating on both sides, preferably AlSi 5 to AlSi 12.5 . We then do without a welding process when closing the dispensing head.
  • a plurality of connectors integrally configured with the end walls are provided, which are formed directly with, in particular, during the manufacture of the end walls.
  • a partition wall may be provided, which divides the inner space of the dispensing head according to the flow into a first and a second distribution chamber, a portion of the heat exchanger tubes extending through the first distribution chamber in the second distribution chamber.
  • This partition wall is for example installed in corresponding grooves, which are provided in the peripheral wall as in the two end walls. It is particularly advantageous, in the case of separate end walls, that the grooves in the end walls are deeper than necessary to achieve the mounting position of the end walls. In this way it is possible to eliminate, as already mentioned, the thickness tolerance problems of the heat exchanger tubes during assembly.
  • the configuration according to the invention appears with a single bundle of flat tubes, which which makes it possible to reduce the depth of construction of the internal heat exchanger.
  • the first distribution chamber which together each time connects the shorter ends of the flat tubes respectively, has flow openings for the coolant on both sides of the bundle.
  • the internal heat exchanger heretofore described as part of an assembly is advantageous for a refrigerant circuit, in particular a vehicle air-conditioning device, which further comprises a gas cooler grouped with the heat exchanger in a set. This reduces the installation space required in the vehicle as well as the weight compared to the individual components. In addition, this saves pressure-resistant connection lines, which are particularly necessary for operation under high pressure.
  • the assembly preferably further comprises a low pressure side manifold.
  • FIG. 1 represents a CO 2 refrigerant circuit under high pressure of a vehicle air conditioning device according to the state of the art, as is known from the document DE 199 18 617 A1 .
  • the refrigerant is fed to a gas cooler 18 by a compressor 12 through a high pressure line 14 and a connector 16.
  • the high pressure side of an internal heat exchanger 20 is connected to the gas cooler 18, which exchanger forms an integrated assembly 10 with the gas cooler 18.
  • the coolant thus passes through the high pressure side of the heat exchanger 20 and leaves the assembly 10 by a connection 22.
  • Another high pressure line 24 brings the refrigerant of an expansion device 26, which relaxes the coolant and the conduit through a low pressure line 28 to an evaporator 30.
  • the evaporator 30 converts the coolant liquid to less partially in the gas phase.
  • the coolant flows to a fitting 34 of a low pressure side manifold 36.
  • the manifold 36 is also configured as an integrated component to the assembly 10, which thus includes the gas cooler 18 the heat exchanger 20 and the collector 36. After having passed through the collector 36 as well as the low pressure side connected thereto of the internal heat exchanger 20, the gaseous phase of the refrigerant comes out of the assembly 10 via a connector 38 and is returned to the compressor inlet 12 via a low-pressure suction line 40.
  • the heat exchanger 20 therefore comprises, as can be seen above all in FIG. 2, two bundles 42 formed identically by flat tubes 44 and / or 46, which have two different lengths. and are stacked in turn on each other.
  • the ends of the shorter flat tubes 44 open respectively into a first distribution chamber 48, which is configured inside a dispensing head 50 and is separated by a separating wall 52 from a second distribution chamber 54 as well. disposed in the dispensing head 50.
  • the long flat tubes 46 thus extend through the partition wall 52 to terminate in the second distribution chamber 54 as can also be seen in FIG.
  • the dispensing head 50 itself is formed by a circle-shaped peripheral wall 56 and a bottom end wall 58 integrally formed therewith as well as by a separate cover 60, knowing that the peripheral wall has openings rectangular beams for passing the beam 42. Between the two beams 42 arranged parallel to one another, a space 62 is provided, which serves as a passage opening inside the first distribution chamber 48, whereby the coolant can also reach the short flat tubes 44 disposed between the longer flat tubes 46.
  • the first distribution chamber 48 together with the short flat tubes 44 forms the high pressure side of the heat exchanger 20, while that the long flat tubes 46 together with the second distribution chamber 54 represent the low pressure side of the heat exchanger 20.
  • the heat exchanger described so far is known according to the state of the art, in particular according to the document DE 199 18 617 A1 .
  • FIGS. 3 and 4 show a heat exchanger 20 according to the invention, in which identical or identically identical spare parts carry identical references and only the differences with respect to the state of the art should be studied hereinafter. .
  • the peripheral wall 56 is formed by an open profiled tube, on the open longitudinal edges of which sections 64 extending parallel to each other. to each other are integrally formed (see Figure 3). Except for the parallel sections 64, the peripheral wall 56 has a particularly stable configuration at the pressure level, almost circular.
  • the profiled tube is manufactured by rolling from an aluminum sheet coated on both sides. As a coating, we use AlSi 5 to AlSi 12.5 , with a relative thickness of 5 to 10%.
  • the two end walls 58 and 60 of the dispensing head 50 are configured as separate pieces and are connected to the peripheral wall 56 only after mounting the heat exchanger tubes, preferably by crimping (FIG. ).
  • the heat exchanger tubes are configured as flat tubes 44, 46 of different lengths, a short flat tube 44 and a long flat tube 46 being stacked one above the other. the other and forming a beam 42.
  • the flat tubes 44, 46 are manufactured by extrusion or spinning and then coated with a flux and a solder (eg "Silflux").
  • the beam 42 is introduced into the opening configured between the parallel sections 64 inside the dispensing head 50 so that the wide sides of the flat tubes 44, 46 are parallel to the end walls 58, 60. this goal and since the end walls 58, 60 are not yet mounted, the peripheral wall 56 may be slightly curved to facilitate the introduction of the beam 42.
  • the sections 64 are then used for the creation of a brazing junction which is easy to manufacture and compared with the state of the art, which is much more resistant with the flat tubes 44, 46. If, in particular, FIGS. it can be seen that in the configuration according to the invention, according to FIG. 3, there is a substantially longer contact surface between the internal surfaces of the sections 64 and the sides of the flat tubes 44, 46.
  • the lateral flow openings 66 allow the coolant, which is introduced into the first distribution chamber 48 through a connector 68 configured integrally with the end wall 58, to laterally pass to the long flat tubes 46 by passing in front of the short flat tubes 44 located below the long flat tubes 46 seen in the direction of flow.
  • the partitioning of the internal space of the dispensing head 50 is again in the first distribution chamber and in the second distribution chamber 54 by means of a partition wall 52, disposed in grooves 70 of the peripheral wall. 56 and 60 are provided in the end walls 58 and 60. As a result, the grooves 72 are configured in the end walls 58 and 60 a little deeper than what corresponds to the mounting position of the end walls 58, 60 shown on FIG. 4. In this way it is possible to move the two end walls 58, 60 a little further inwards before the connection to the peripheral wall 56 and thus to compensate for any manufacturing tolerances at the level of the wall. thickness of the flat tubes 44, 46.
  • the ends of the longer flat tubes 46 are introduced through the slot provided in the partition wall 52 and connected thereto before the beam 42 and the partition wall 52 are put into place in the dispensing head 50 and or the peripheral wall 56 thereof.
  • FIG. 5 shows an assembly 10 according to the invention for a refrigerant circuit under high pressure of CO 2 , which comprises a gas cooler 18, the heat exchanger 20 shown in FIGS. low-side manifold side 36.
  • the assembly 10 is here substantially identical to the known assembly according to the state of the art from Figure 1, however the heat exchanger 20 according to the invention is installed in place of the known heat exchanger according to the state of the art.
  • the refrigerant under high pressure passes through, as indicated by the arrow in Figure 5, first the gas cooler 18, before reaching the first distribution chamber 48 through the connector 68.
  • the refrigerant under high pressure is distributed between the short flat tubes 44, through which it passes (in Figure 5) from right to left and leaves through a distribution head 50 mounted identically, turned of 180 ° in its position of mounting and / or the first distribution chamber 48 thereof and the connector 22.
  • the refrigerant is introduced into the low pressure side manifold 36, which is also a component of the assembly 10.
  • the gaseous phase of the coolant enters through a channel 74 and a connector 76 in the second distribution chamber 54 of the dispensing head 50 located on the left in the figure.
  • the coolant under low pressure then passes through the long flat tube 46 from left to right and leaves the heat exchanger 20 or the assembly 10 by the second distribution chamber 54 of the right distribution head 50 as well as the coupling 38.
  • a suction pipe 40 of a compressor 12 (see FIG. 1) is connected to the connection 38.
  • connection of the three heat exchanger components 20, gas cooler 18 and manifold 36 can be carried out by complete brazing in a single operation, a connection by welding or screwing is also possible alternatively. Sealing of the connections or connections is however necessary.
  • the heat exchanger 20 may also be disposed above the gas cooler 18 (relative to the mounting position in the vehicle) instead of being below as shown in FIG. Particularly restricted installation results from the arrangement in vertical alignment of the flat tubes 44, 46 of the heat exchanger 20 with the flat tubes of the gas cooler 18. It is in particular of the same category of tube (standard components) .

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP06120440.0A 2005-09-23 2006-09-11 Innerer Wärmetauscher für Klimaanlage-Kühlmittelkreislauf Withdrawn EP1767887A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200510045539 DE102005045539A1 (de) 2005-09-23 2005-09-23 Innerer Wärmetauscher für einen Kältemittelkreislauf einer Klimaanlage

Publications (2)

Publication Number Publication Date
EP1767887A2 true EP1767887A2 (de) 2007-03-28
EP1767887A3 EP1767887A3 (de) 2013-10-02

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009068547A1 (fr) * 2007-11-29 2009-06-04 Valeo Systemes Thermiques Condenseur pour circuit de climatisation avec partie de sous-refroidissement
CN104344607A (zh) * 2013-08-08 2015-02-11 浙江盾安热工科技有限公司 一种换热器
CN111615615A (zh) * 2017-12-19 2020-09-01 法雷奥热系统公司 用于容纳在热交换器的集管中的制冷剂流体分配装置
EP3819579A1 (de) * 2019-11-07 2021-05-12 Valeo Systemes Thermiques-THS Wärmetauscher

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009057175A1 (de) * 2009-12-05 2011-06-09 Volkswagen Ag Wärmetauscher

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001023823A1 (en) * 1999-09-29 2001-04-05 Norsk Hydro Asa Heat exchanger
JP2002333221A (ja) * 2001-05-01 2002-11-22 Mitsubishi Heavy Ind Ltd ガスクーラ及び車載用空調装置
US6539746B1 (en) * 1999-04-23 2003-04-01 Valeo Klimatechnik Gmbh High pressure gas cooler for a refrigerant circuit of a motor-vehicle air-conditioning system
FR2890726A1 (fr) * 2005-09-13 2007-03-16 Valeo Systemes Thermiques Ensemble integre pour circuit de climatisation fonctionnant avec un fluide refrigerant supercritique

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Publication number Priority date Publication date Assignee Title
DE19543986A1 (de) * 1995-11-25 1997-05-28 Behr Gmbh & Co Wärmetauscher und ein Verfahren zur Herstellung eines Wärmetauschers
JP4727051B2 (ja) * 2001-02-14 2011-07-20 三菱重工業株式会社 インタークーラ及びｃｏ２冷媒車両用空調装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6539746B1 (en) * 1999-04-23 2003-04-01 Valeo Klimatechnik Gmbh High pressure gas cooler for a refrigerant circuit of a motor-vehicle air-conditioning system
WO2001023823A1 (en) * 1999-09-29 2001-04-05 Norsk Hydro Asa Heat exchanger
JP2002333221A (ja) * 2001-05-01 2002-11-22 Mitsubishi Heavy Ind Ltd ガスクーラ及び車載用空調装置
FR2890726A1 (fr) * 2005-09-13 2007-03-16 Valeo Systemes Thermiques Ensemble integre pour circuit de climatisation fonctionnant avec un fluide refrigerant supercritique

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009068547A1 (fr) * 2007-11-29 2009-06-04 Valeo Systemes Thermiques Condenseur pour circuit de climatisation avec partie de sous-refroidissement
FR2924490A1 (fr) * 2007-11-29 2009-06-05 Valeo Systemes Thermiques Condenseur pour circuit de climatisation avec partie de sous-refroidissement
CN104344607A (zh) * 2013-08-08 2015-02-11 浙江盾安热工科技有限公司 一种换热器
CN104344607B (zh) * 2013-08-08 2018-07-06 浙江盾安热工科技有限公司 一种换热器
CN111615615A (zh) * 2017-12-19 2020-09-01 法雷奥热系统公司 用于容纳在热交换器的集管中的制冷剂流体分配装置
CN111615615B (zh) * 2017-12-19 2022-04-19 法雷奥热系统公司 用于容纳在热交换器的集管中的制冷剂流体分配装置
EP3819579A1 (de) * 2019-11-07 2021-05-12 Valeo Systemes Thermiques-THS Wärmetauscher

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DE102005045539A1 (de) 2007-03-29

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