EP1813903A1 - Sammelkasten mit Deckel für ein Hochdruckmedium, Wärmetauscher mit dem Sammelkasten und Herstellungsverfahren - Google Patents

Sammelkasten mit Deckel für ein Hochdruckmedium, Wärmetauscher mit dem Sammelkasten und Herstellungsverfahren Download PDF

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Publication number
EP1813903A1
EP1813903A1 EP07001090A EP07001090A EP1813903A1 EP 1813903 A1 EP1813903 A1 EP 1813903A1 EP 07001090 A EP07001090 A EP 07001090A EP 07001090 A EP07001090 A EP 07001090A EP 1813903 A1 EP1813903 A1 EP 1813903A1
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EP
European Patent Office
Prior art keywords
channels
cover
metal bar
distribution
box according
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
EP07001090A
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English (en)
French (fr)
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EP1813903B1 (de
Inventor
Frédéric MESLIN
Yannig Travers
Claude Besombes
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 Systemes Thermiques SAS
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Valeo Systemes Thermiques SAS
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.)
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Application filed by Valeo Systemes Thermiques SAS filed Critical Valeo Systemes Thermiques SAS
Publication of EP1813903A1 publication Critical patent/EP1813903A1/de
Application granted granted Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0214—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—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
    • F28F9/026—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2225/00—Reinforcing means
    • F28F2225/08—Reinforcing means for header boxes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/04—Communication passages between channels

Definitions

  • the invention relates to the field of heat exchangers and in particular to exchangers intended to be traversed by a fluid under high pressure.
  • the invention relates more particularly to air conditioning evaporators that can be traversed by a gaseous refrigerant, as is the case with natural gases such as carbon dioxide or CO 2 .
  • a gaseous refrigerant such as carbon dioxide or CO 2 .
  • Such exchangers find particular application in motor vehicles.
  • this fluid in an air conditioning circuit traversed by a refrigerant of this type, this fluid remains substantially in the gaseous state and under a very high pressure which is between 100 and 150 bar.
  • the burst pressure recommended is generally three times the value of the nominal operating pressure.
  • the document FR 2 793 016 discloses a collector box formed of a multiplicity of flat plates stacked having fluid passage slots. The distribution is ensured by these flat plates and the header comprises a cover also composed of a multiplicity of stacked plates. All these plates are assembled together by brazing.
  • the document JP 2002-1588722 discloses a header comprising an extruded tank closed by flat end plates.
  • the abutment of the tubes is provided either by an intermediate flat plate disposed between the tubes and the tank, or by a specific profile of the tank section.
  • the object of the invention is in particular to overcome the aforementioned drawbacks.
  • the invention proposes for this purpose a heat exchanger collector box, comprising a collector plate provided with openings for the insertion of heat exchange tubes, and a lid defining distribution channels communicating with the tubes.
  • the lid is a metal bar having an inner face and a face opposite outer, while the distribution channels are grooves made in the material thickness of the metal bar, opening on the inner face, while allowing material to remain in order to close the volume of the lid at its level. longitudinal ends. '
  • the cover is made by machining a thick metal bar, which simplifies its manufacture and allows for an element that can withstand high pressures.
  • the communication passages are delimited by a distribution plate interposed between the collector plate and the inner face of the cover.
  • the communication passages are grooves of the metal bar opening on the one hand on the distribution channels and on the other hand on the inner face of the cover.
  • the distribution channels and the communication passages are machined.
  • the lid is obtained from an extruded metal bar.
  • the outer face of the extruded metal bar is shaped so as to have a profile comprising a plurality of domes, or arches, in correspondence of the channels.
  • the distribution channels may have a constant inner section along their entire length, or a variable inner section over their entire length.
  • the lid may comprise a single series of channels which each extend over the length of the metal bar. This is particularly the case of a return cover, located opposite a cover having arrangements for the entry and exit of the fluid.
  • the lid may also include at least two sets of channels each extending over a portion of the length of the metal bar. This is particularly the case of a lid comprising, as mentioned above, arrangements for the entry and exit of the fluid.
  • the channels advantageously have a bottom with a U-shaped transverse profile, which makes it possible to improve the resistance to the pressure of the fluid.
  • the channels advantageously, in the vicinity of an end face of the metal bar, a curved longitudinal profile delimited by a radius.
  • the invention in another aspect, relates to a heat exchanger comprising a bundle of tubes and at least one header as previously defined.
  • This heat exchanger is advantageously made in the form of an evaporator.
  • a particular embodiment proposes that the heat exchanger comprises at least two passes and that the inner sections of the distribution channels make it possible to control and balance the flow rate of the fluid in the passes.
  • the operation b) comprises the preparation of a distribution plate delimiting the communication passages, while the operation d) comprises the interposition of the distribution plate between the collector plate and the face inside the lid.
  • the operation b) comprises the realization of the communication passages in the form of grooves made by machining in the transverse direction of the metal bar, opening on the one hand on the distribution channels and on the other hand. on the other hand on the inside of the lid, while the operation b) comprises the direct assembly of the collector plate against the inner face of the lid.
  • the operation c) comprises the preparation of an extruded metal bar and the machining of the channels by means of a multistage rotary tool capable of simultaneously machining the channels over at least a portion of the length of the metal bar.
  • FIG. 1 shows, in exploded view, a heat exchanger 10 having a beam 12 mounted between an upper manifold 14 and a lower manifold 16, the heat exchanger being considered upright .
  • the beam 12 is composed, in the example, of two rows of tubes 18 (only one of which is visible in FIG. 1) and corrugated inserts 20 common to both rows of tubes.
  • the header box 14 is provided with two inlet / outlet pipes 22 and 24 serving respectively to the admission and evacuation of a fluid flowing through the tubes of the bundle.
  • the heat exchanger 10 is in the form of an evaporator capable of being traversed by a refrigerant fluid operating in the supercritical state, in particular CO 2 , the pressure of which can reach values of order of 100 to 150 bar.
  • This fluid exchanges heat with a flow of air that scans the tube bundle to produce a flow of air conditioning, especially in a motor vehicle.
  • the header box 14 comprises a header plate 26 provided with openings 28 for receiving the tubes of the bundle.
  • the openings 28 are of elongate shape and arranged in two rows corresponding to the two rows of tubes.
  • the collecting plate 26 is generally rectangular in shape and comprises, along its two long sides, crimping members 30. It comprises an extension 32 in which holes 34 and 36 are provided for the respective mounting of the tubes 22 and 24. .
  • a distribution plate 38 having two rows of slotted communication passages 40, each communicating with a tube 18 and a row of slotted communication passages 42, of greater width which each communicate with two adjacent tubes belonging to the two rows of the beam.
  • the passages 40 and 42 contribute to the distribution of the fluid and to its circulation in the tubes of the bundle according to a defined route, which will be described later with reference to Figure 13.
  • a cover 44 intended to be held against the collector plate, trapping the distribution plate 38, under the action of the crimping members 30.
  • the lower manifold 16 is made in a similar manner except that it has no extension. It consists of a manifold plate 46, a distribution plate 48 and a cover 50. Note that the distribution plate 48 has two rows of passages 52, slot-shaped, each communicating with a tube of beam at its lower part.
  • Figure 2 shows a cross-sectional view of the manifold 14.
  • Figure 2 shows the header plate 26, the distribution plate 38 and the cover 44.
  • the header plate 26 is a stamped plate having a flat inner face 54 for receiving the distribution plate 38 and an outer face 56 from which extend collars 58 respectively surrounding the openings 28 for receiving the tubes.
  • the outer face 56 is directed downwards and the collars 58 are also directed downwards. These collars are thus arranged in two rows corresponding to the two rows of openings 28.
  • the collars and the openings have a rectangular general section to allow the reception of flat tubes 18 having a homologous external section.
  • the crimping members 30 are, as already indicated, formed along the two long sides of the collecting plate 26. They are in the form of a folded, slot-shaped edge with a number of tabs or teeth 60 (see also Figure 1).
  • the distribution plate 38 has a flat inner face 62 adapted to come into contact with the flat inner face 54 of the header plate and an opposite outer plane face 64, able to receive the cover 44.
  • passages 40 and 42 In the thickness of the distribution plate, are arranged passages 40 and 42, in the form of slits, supra. In Figure 2 there are two passages 40 which communicate respectively with two adjacent tubes respectively belonging to the two rows of tubes of the beam.
  • the distribution plate 38 forms an insertion stop for the tubes as seen in FIG. 2.
  • the respective ends of the tubes can not exceed the plane defined by the inner face 54 of the collector plate.
  • the cover 44 is made from a thick metal bar having two parallel edges 66 (FIG. 2) for supporting the crimping members 30. Thus, when the tabs 60 are folded, they hold the cover in the direction of the collector plate by trapping the distribution plate.
  • the lid 44 comprises, as seen in the section of FIG. 2, a series of bosses 68, six in number in the direction cross. These bosses 68 respectively define channels 70 communicating with the tubes of the beam via the communication passages 40 and 42 (slot-shaped) of the distribution plate.
  • bosses are suitably arranged to allow the refrigerant fluid to penetrate inside the manifold 14 via the manifold 22, then circulate in the tubes of the bundle between the manifold 14 and the manifold 16 and leave the exchanger by the outlet pipe 24.
  • the manner in which the circulation of the fluid occurs in the beam will be described in detail below.
  • the cover 44 has a generally rectangular shape, the bosses 68 each extending in the longitudinal direction.
  • the metal bar forming the cover 44 is a thick bar having an inner face 72, made flat, adapted to be applied against the flat outer face 64 of the distribution plate 38 ( Figure 2). It is more specifically an extruded bar whose profile, before machining, is shown in FIG. 3. It can be seen that this bar comprises, opposite the inner face 72, a shaped outer face 74, the profile defines the six bosses 68, domed or arched, and the two bearing edges 66. The profile of the bar is further limited by two side faces 76.
  • the channels 70 are obtained by machining from the inner face 72 to obtain the profile shown in FIG. 4. It can be seen that the channels 70 are formed by U-shaped grooves with a rounded bottom in correspondence with the aforementioned domes or arches. As a result, the profile obtained after machining ( Figure 4) defines a succession of arches having a sufficient thickness to allow good resistance to pressure. Given the fact that the machining is performed in a metal bar, the thickness of the latter can be controlled so as to obtain each time a wall of sufficient thickness to withstand the operating pressures of the manifold and therefore of the heat exchanger.
  • FIG. 5 shows how the machining of the channels can be achieved by means of a single rotating tool 78 made in the form of a multi-stage cutter rotatable about an axis XX and comprising a series of crowns 80 with a profile rounded, here six in number, to simultaneously realize the six channels 70 in the cover 44.
  • the machining is performed by moving the tool in the longitudinal direction of the bar, the axis of rotation of the tool being oriented transversely.
  • FIG. 6 shows a channel 70 having an end 82 terminating at a distance A of an end face 84 of the cover 44.
  • This end 82 has, in the vicinity of the end face 84, a profile. longitudinal curved delimited by a radius R. This latter advantageously corresponds to the radius of the crowns 80 of the machining tool 78.
  • R radius
  • the end of each of the channels 70 is made non-emergent which avoids the recourse to end plates to close the channels.
  • the other end of the channels 70 is made analogously. In other words, the throats that the channels are formed in the thickness of material of the metal bar, opening on the inner face 72, while allowing the material to remain so as to close the volume of the lid at its longitudinal ends (end faces 84).
  • FIG. 7 shows, in longitudinal section, a cover 44 according to the invention in one embodiment. It can be seen that this cover has two series of channels 70A and 70B, the channels 70A having a longer length than the channels 70B and extending on the extension side 32 (FIG. 1). In the example, the channels 70A and 70B have a constant inner section along their entire length.
  • Figure 8 shows, in longitudinal section, the cover 50 of the opposite header, which extends over a shorter length than the cover 44 and which has a single series of channels 70C to form return.
  • the channels 70C extend over the entire length and here again have a constant inner section.
  • the cover 44 of FIG. 7 and the cover 50 of FIG. 8 make it possible to define an evaporator with four circulation passes.
  • Figure 9 illustrates a variant of the cover 44 of Figure 7 in which the channels 70B have a constant inner section, while the channels 70A have a variable inner section, the bottom of the channels having a slope having an angle A1.
  • FIG. 10 illustrates a variant of the cover 50 of FIG. 8 and it can be seen that the channels 70C also have a variable inner section whose bottom has a double slope defined by two opposite angles A2.
  • FIG 11 shows another type of profile with variable inner section for a channel 70C.
  • Each of the channels 70C has a main portion 85 made by a first machining and a deeper central portion 86 made by a second machining.
  • This profile requires a first machining by a tool similar to that described above and a second machining to form, over a portion of the length of the channel, the central portion 86 deeper.
  • FIG. 12 illustrates another variant in which the channels 70 have a variable inner section made by a single machining, and therefore by a single tool.
  • the bottom of each channel has an inclined portion 87 defined by a slope of angle A3 and a portion 89 of constant depth. It is understood that the machining tool must be moved in a controlled manner relative to the metal bar to control the machining depth.
  • channels of variable internal section so of varying depth, allows each time to control the flow of fluid in the tubes that open into the channels in question.
  • FIG. 13 shows, schematically, the distribution of a fluid for a four-pass exchanger, here an evaporator, in which the covers 44 and 50 are shown schematically.
  • the fluid enters the collecting box associated with the cover 44 as shown by the F1 arrow. It opens into 70.1 channels of decreasing depth.
  • the fluid then travels a portion of the tubes 18 of a first row corresponding to a first pass P1 to open into a series of channels 70.2 of variable profile cover 50. These channels 70.2 extend over the entire length of the cover 50 and have a profile similar to that of Figure 10.
  • the fluid then leaves the channels 70.2 by another part of the tubes of the first row to form a second pass P2 and thus gain channels 70.3 of the cover 44 which, in the example, have a constant inner section.
  • the fluid flows from these channels 70.3 to other channels 70.4 as shown by the arrow F2.
  • These channels 70.4 also have a constant inner section.
  • the fluid then leaves the upper header by traversing a portion of the tubes of the second row to constitute a third pass P3 and win channels 70.5 also extending over the entire length of the cover 50. These channels 70.5 have a profile similar to the channels 70.2.
  • the fluid then leaves the lower manifold to form a fourth pass P4 through a portion of the tubes of the second row. The fluid thus gains 70.6 channels having a variable inner section similar to that of the channels 70.1.
  • the fluid then leaves the heat exchanger as shown by the arrow F3.
  • the components of the manifold are each made from a metal plate, preferably aluminum alloy, with a thickness sufficient to withstand the significant pressures of the refrigerant fluid. .
  • the fact of making several bosses 68 on the cover makes it possible to form small volume channels 70 limiting the effect of the pressure of the fluid on the components of the collector plate.
  • operation b) comprises the preparation of a distribution plate 38 or 48 which delimits the communication passages 40 and 42
  • operation d) comprises the interposition of the distribution plate between the header plate 26 or 46 and the inner face 72 of the cover.
  • the cover 14 is crimped on the header plate 26 by means of crimping members 30, enclosing the distribution plate.
  • FIG 14 which relates to another embodiment in which the cover 88 is similar to the cover 44 described above and comprises two series of channels 70A and 70B in the form of parallel longitudinal grooves made in the longitudinal direction of the metal bar.
  • the cover further includes communication passages 90 and 92 which are functionally analogous to the previously described communication passages 40 and 42.
  • these communication passages 90 and 92 are here parallel transverse grooves made by machining in the transverse direction of the metal bar, opening on the one hand on the distribution channels 70A and 70B and on the other hand on the inner face 94 of the lid ( Figures 15 and 16).
  • the communication passages 90 and 92 are spaced apart by a pitch P corresponding to that of the tubes.
  • the assembly operation d) thus comprises the direct assembly of the manifold plate 28 or 46 against the inner face 94 of the cover 88.
  • the cover is crimped directly on the collector plate.
  • the cover 88 thus groups the functions of passage and distribution of the fluid. This makes it possible to reduce the number of parts of the heat exchanger, to facilitate the assembly process and to reduce the risk of leakage.
  • the inner face 94 of the cover 88 can be machined by forming recesses or steps 96 ( Figures 15 and 16) forming stops for the introduction of the tubes 18.
  • the entire heat exchanger can be then brazed, in a single operation, by passing through a suitable brazing furnace.
  • solder plating provides a connection between the various components.
  • the manifold 16 is made in a similar manner to the manifold 14, except that it does not have an extension for mounting fluid inlet and outlet manifolds.
  • the manifold of the invention is capable of many variants. It finds a main application to heat exchangers traversed by a high-pressure refrigerant, in particular to air-conditioning evaporators traversed by a fluid in the supercritical state such as CO 2 , such as those intended for motor vehicles.

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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)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
EP07001090A 2006-01-31 2007-01-18 Sammelkasten mit Deckel für ein Hochdruckmedium, Wärmetauscher mit dem Sammelkasten und Herstellungsverfahren Active EP1813903B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0600884A FR2896862B1 (fr) 2006-01-31 2006-01-31 Boite collectrice avec couvercle pour fluide haute pression, echangeur de chaleur comportant une telle boite et procede pour sa fabrication

Publications (2)

Publication Number Publication Date
EP1813903A1 true EP1813903A1 (de) 2007-08-01
EP1813903B1 EP1813903B1 (de) 2008-07-30

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EP07001090A Active EP1813903B1 (de) 2006-01-31 2007-01-18 Sammelkasten mit Deckel für ein Hochdruckmedium, Wärmetauscher mit dem Sammelkasten und Herstellungsverfahren

Country Status (5)

Country Link
EP (1) EP1813903B1 (de)
AT (1) ATE403126T1 (de)
DE (1) DE602007000049D1 (de)
ES (1) ES2312143T3 (de)
FR (1) FR2896862B1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012052715A (ja) * 2010-08-31 2012-03-15 Mitsubishi Heavy Ind Ltd 熱交換器
EP1857763A3 (de) * 2006-05-18 2012-08-22 Doowon Climate Control Co., Ltd Endkammer für einen Hochdruckwärmetauscher
WO2013116177A3 (en) * 2012-02-02 2014-01-03 Carrier Corporation Method for fabricating flattened tube finned heat exchanger
US20170314792A1 (en) * 2014-11-14 2017-11-02 Daikin Industries, Ltd. Heat exchanger
EP3745069A4 (de) * 2018-05-17 2021-09-15 Zhejiang Sanhua Intelligent Controls Co., Ltd. Wärmetauscher

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2793015A1 (fr) * 1999-04-28 2000-11-03 Valeo Thermique Moteur Sa Echangeur de chaleur brase pour haute pression, en particulier pour vehicule automobile
US20020074113A1 (en) * 2000-12-20 2002-06-20 Abell Bradley D. Two piece heat exchanger manifold
US6446713B1 (en) * 2002-02-21 2002-09-10 Norsk Hydro, A.S. Heat exchanger manifold
US20030221819A1 (en) * 2002-05-29 2003-12-04 Halla Climate Control Corporation Heat exchanger for CO2 refrigerant
WO2005088225A1 (en) * 2004-03-17 2005-09-22 Showa Denko K.K. Heat exchanger header tank and heat exchanger comprising same
US20050284621A1 (en) * 2004-06-28 2005-12-29 Denso Corporation Heat exchanger

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2793015A1 (fr) * 1999-04-28 2000-11-03 Valeo Thermique Moteur Sa Echangeur de chaleur brase pour haute pression, en particulier pour vehicule automobile
US20020074113A1 (en) * 2000-12-20 2002-06-20 Abell Bradley D. Two piece heat exchanger manifold
US6446713B1 (en) * 2002-02-21 2002-09-10 Norsk Hydro, A.S. Heat exchanger manifold
US20030221819A1 (en) * 2002-05-29 2003-12-04 Halla Climate Control Corporation Heat exchanger for CO2 refrigerant
WO2005088225A1 (en) * 2004-03-17 2005-09-22 Showa Denko K.K. Heat exchanger header tank and heat exchanger comprising same
US20050284621A1 (en) * 2004-06-28 2005-12-29 Denso Corporation Heat exchanger

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1857763A3 (de) * 2006-05-18 2012-08-22 Doowon Climate Control Co., Ltd Endkammer für einen Hochdruckwärmetauscher
JP2012052715A (ja) * 2010-08-31 2012-03-15 Mitsubishi Heavy Ind Ltd 熱交換器
WO2013116177A3 (en) * 2012-02-02 2014-01-03 Carrier Corporation Method for fabricating flattened tube finned heat exchanger
CN104081149A (zh) * 2012-02-02 2014-10-01 开利公司 用于制造扁平管翅片热交换器的方法
CN104081149B (zh) * 2012-02-02 2017-05-17 开利公司 用于制造扁平管翅片热交换器的方法
US9901966B2 (en) 2012-02-02 2018-02-27 Carrier Corporation Method for fabricating flattened tube finned heat exchanger
US20170314792A1 (en) * 2014-11-14 2017-11-02 Daikin Industries, Ltd. Heat exchanger
US10465924B2 (en) * 2014-11-14 2019-11-05 Daikin Industries, Ltd. Heat exchanger
EP3745069A4 (de) * 2018-05-17 2021-09-15 Zhejiang Sanhua Intelligent Controls Co., Ltd. Wärmetauscher
US11268767B2 (en) 2018-05-17 2022-03-08 Hangzhou Sanhua Research Institute Co., Ltd. Heat exchanger

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Publication number Publication date
FR2896862B1 (fr) 2008-04-11
DE602007000049D1 (de) 2008-09-11
EP1813903B1 (de) 2008-07-30
ATE403126T1 (de) 2008-08-15
FR2896862A1 (fr) 2007-08-03
ES2312143T3 (es) 2009-02-16

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