EP2026028B1 - Échangeur de chaleur, en particulier pour véhicule automobile - Google Patents

Échangeur de chaleur, en particulier pour véhicule automobile Download PDF

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Publication number
EP2026028B1
EP2026028B1 EP08018381.7A EP08018381A EP2026028B1 EP 2026028 B1 EP2026028 B1 EP 2026028B1 EP 08018381 A EP08018381 A EP 08018381A EP 2026028 B1 EP2026028 B1 EP 2026028B1
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EP
European Patent Office
Prior art keywords
plate
heat exchanger
tube
flow
tubes
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP08018381.7A
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German (de)
English (en)
Other versions
EP2026028A3 (fr
EP2026028A2 (fr
Inventor
Hans-Joachim Dipl.-Ing. Krauss
Hagen Dipl.-Ing. Mittelstrass
Walter Dipl.-Ing. Demuth
Martin Dipl.-Ing. Kotsch
Karl-Heinz Dipl.-Ing. Staffa
Christoph Dipl.-Ing. Walter
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Mahle Behr GmbH and Co KG
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Mahle Behr GmbH and Co KG
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Publication of EP2026028A2 publication Critical patent/EP2026028A2/fr
Publication of EP2026028A3 publication Critical patent/EP2026028A3/fr
Application granted granted Critical
Publication of EP2026028B1 publication Critical patent/EP2026028B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F28D1/0478—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag the conduits having a non-circular cross-section
    • 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • 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
    • F28F2280/00—Mounting arrangements; Arrangements for facilitating assembling or disassembling of heat exchanger parts

Definitions

  • the invention relates to a heat exchanger with pipes and with an end piece, which has a tube plate consisting of plates.
  • Such a heat exchanger is for example in the EP 0 563 471 A1 described.
  • the local heat exchanger is designed as a double-row flat tube evaporator, which is flowed through in two bends. Between the flat tubes are corrugated fins, which are covered by ambient air.
  • the refrigerant flows through the seen in the main flow direction of the air rear row of flat tubes first from top to bottom and is then collected and deflected by a deflecting counter to the flow direction of the air, enters the first, ie front row of flat tubes and flows through them from bottom to top. In this design, the refrigerant is thus deflected "in the depth", ie counter to the flow direction of the air.
  • the flow paths for the refrigerant each comprise two sections, each section corresponding to a tube length.
  • the distribution and collection of the refrigerant is carried out by a collecting and distributing device, which is formed by a plurality of stacked, soldered together plates. It is in the essentially around a base plate, an overlying distributor plate with a longitudinally extending partition and a cover plate with inlet and outlet opening for the refrigerant.
  • the deflector arranged on the opposite side is composed of individual plates. This results in a low overall height for this evaporator.
  • a so-called stop plate is provided, which is placed in each case on the bottom plate and forms a stop for the pipe ends.
  • a disadvantage of this evaporator design is that the refrigerant is distributed unevenly on the individual tubes due to the over the entire width of the evaporator extending distribution or collection chamber.
  • the double-row design requires increased installation costs.
  • An evaporator for a fuel cell system which includes a header having a bottom plate and a cover plate attached thereto. Fuel passes through a connecting part in a fuel distribution chamber, from there into guide channels and through openings in the bottom plate in heat receiving ducts of the evaporator.
  • the plates of the head are small in number, but very expensive in their production.
  • the heat receiving channels are acted upon very unevenly with fuel depending on the pressure distribution in the fuel distributor chamber and in the guide channels.
  • the EP 0 328 414 A discloses a heat exchanger, eg an evaporator for a vehicle air conditioner, comprising a plurality of ribbed U-shaped tubes having free ends permanently attached, eg, adhesively bonded to an end plate assembly formed from a number of end plate means defining connecting channels, the pairs from free ends of the tubes to provide at least one flow passage for heat exchange fluid.
  • the end plate means are permanently joined together, for example by gluing, to form with the end portions of the U-shaped tubes a permanently bonded integral end plate assembly.
  • the DE 692 19 107 T2 discloses a two-pass evaporator with elongate tubes and header.
  • Each distributor head consists of several layers arranged together soldered plates.
  • the upper header may therefore consist of three plates, including a cover plate, a header plate and a tube plate.
  • the object of the invention is to provide a heat exchanger, in which a simple and / or lightweight construction and optionally at the same time a uniform distribution of a medium to a plurality of flow paths and / or a pressure-stable construction of the heat exchanger can be realized.
  • a heat exchanger with the features of claim 1.
  • a heat exchanger according to the invention on tubes which can be flowed through by a first medium and a second medium flow around, so that through walls of the tubes Heat from the first to the second medium or vice versa transferable.
  • there are heat transfer channels in the tubes, through which the first medium can be conducted wherein a single tube has either a heat transfer channel or as a so-called multi-chamber tube a plurality of adjacent heat transfer channels.
  • the tubes may have a circular, an oval, a substantially rectangular or any other cross section.
  • the tubes are designed as flat tubes.
  • optionally ribs, in particular corrugated fins are arranged between the tubes, wherein the tubes and the ribs are in particular solderable to one another.
  • the heat exchanger various uses are conceivable, for example as an evaporator of a refrigerant circuit, in particular an automotive air conditioning system.
  • the first medium is a refrigerant, for example, R134a or R744
  • the second medium is air, whereby heat is transferred from the air to the refrigerant.
  • the heat exchanger is also suitable for other media, where appropriate, the heat is also transferable from the first to the second medium.
  • At least two collection chambers are present, wherein the first medium can be conducted from a first to a second collection chamber.
  • the first medium can be conducted along one or more flow paths, which optionally consist of several sections.
  • a flow path section in the sense of the invention is to be understood as meaning one or more heat transfer channels which run from one side of the heat exchanger to an opposite side and are connected hydraulically in parallel to one another.
  • the heat transfer channels of a flow path section are arranged, for example, in a single tube, one on several tubes However, distributed arrangement of the heat transfer channels of a flow path section is also conceivable.
  • the heat exchanger has an end piece, which comprises a tube plate consisting of adjacent plates, wherein the adjacent plates consist of a bottom plate, a voltage applied to the bottom plate baffle plate and applied to the Urnschplatte Abdeckpiatte.
  • the bottom plate is connectable to ends of the tubes by the bottom plate, for example, has recesses into which the pipe ends are receivable.
  • other types of connection between pipes and the bottom plate are conceivable, for example, by extensions at the edges of recesses in the bottom plate, so that the tubes are attachable to the extensions.
  • Recesses in the deflection plate serve for the formation of passage channels and / or deflection channels, which can be closed fluid-tight with respect to an environment of the heat exchanger with a cover plate. Due to the plate structure of the tube plate a very pressure-stable construction of the tail and the entire heat exchanger is possible.
  • the tube bottom comprehensive tail is provided with a collecting box, which has at least one collecting chamber for the first medium in a housing. As a result, an optionally necessary anyway component is integrated into the tail and ensures a compact and therefore simple construction of the heat exchanger.
  • Flow path sections can be connected to one another by means of deflection channels in the deflection plate.
  • the heat exchanger can be built flexibly for various applications due to its modular design.
  • a tube is inserted to a predetermined stop in the tube sheet to achieve increased manufacturing reliability and thus a simplified production.
  • the stop is realized by a web between two recesses in the bottom plate, which is receivable in a recess in a pipe end, wherein the web is substantially as wide as the recess in the pipe end.
  • the recess is slightly wider than the web to facilitate insertion of the tube into the bottom plate.
  • the insertion depth of the tube is given by the height of the recess in the pipe end.
  • the recess is higher than the web, whereby the risk of unwanted clogging of one or more heat transfer channels by solder located on the bottom plate during a. Soldering process is reduced.
  • the height difference is, for example, 1 mm or more, on the other hand, should be less than the thickness of the baffle, since the pipe otherwise abuts the cover plate.
  • a height difference that is about half as large as the thickness of the baffle plate.
  • a basic idea of the invention is to design a plurality of plates of the tubesheet in one piece in order to reduce the number of production and, if necessary, the cost of materials.
  • the tube plate then only consists of a plate in which the bottom plate, the baffle plate and the cover plate are integrated.
  • the cost of materials for the tubesheet and thus also for the heat exchanger is reduced by one or more, preferably all plates of the tubesheet have additional recesses between passage and / or deflection channels, the For example, as breakthroughs or lateral indentations are formed.
  • the plates are severed between passage and / or deflection channels, whereby the plates may disintegrate into many small sub-plates. This allows a particularly lightweight construction, which has a positive effect on material costs and weight of the heat exchanger alike.
  • the bottom plate, the baffle plate and / or the cover plate on an edge of at least one opening on an extension which engages in an opening of an adjacent plate.
  • a simplified construction is made possible according to the principles of the invention by U-shaped tubes, wherein the tubes are simply or repeatedly formed into an even simpler design. As a result, in the region of the U-shaped forming two pipe-floor connections and possibly a deflection channel can be saved. With the exclusive use of U-tubes, it is even possible to save an end piece, if on one side of the heat exchanger all deflections are realized by Rohrumformungen. In this case, the ends of each tube are connectable to the same bottom plate.
  • Preferred embodiments of the heat exchanger according to the invention are the subject of the subordinate claims. According to a preferred embodiment, it is to provide the heat exchanger with exactly one end piece, in which in particular a collecting box is integrated with two collecting chambers. This is possible except through the use of U-tubes through any conceivable hydraulic connection of pipes on a side opposite exactly one end of the heat exchanger, for example by placing suitably constructed caps on a plurality of, in particular two tubes.
  • an optionally integrated into the tail collecting tank with the cover plate is soldered fluid-tight or welded.
  • the collecting box is integrally formed with the cover plate, whereby the production is simplified.
  • a particularly lightweight design is achieved by a tubular design of the collecting tank according to a further embodiment of the invention.
  • the cover plate on edges of openings on extensions which engage in openings of a housing of the collecting tank.
  • it is possible according to a further embodiment to provide openings of the collection box housing with extensions which engage in openings of the cover plate. In both cases, the manufacturing safety is increased by an alignment of the mutually aligned openings in the cover plate and in the collection box housing.
  • the passage openings which are formed by the mutually aligned openings in the cover plate and in the collection box housing, have different flow cross-sections.
  • an adaptation of the distribution of the first medium to the flow conditions in the associated collection chamber is made possible in a simple manner.
  • a uniform distribution over a plurality of flow paths is desirable, but also a deliberately uneven distribution is conceivable, for example, at uneven mass flow of the second medium over an end face of the heat exchanger.
  • the passage openings are arranged with different flow cross-sections upstream of the heat transfer channels, whereby the flow in the flow paths is particularly easily compensated.
  • the passage openings on the outlet side can be made larger, for example with a flow cross section which corresponds to the flow cross section of the respective flow path.
  • the Heat exchangers for example, used as an evaporator in a refrigerant circuit, the pressure conditions along the circuit are more advantageous for the performance of the heat exchanger when flow cross sections are narrowed before heating the refrigerant, as in a narrowing of the flow cross sections after heating.
  • the flow cross-sections of the passage openings are adaptable according to an embodiment of a pressure distribution of the first medium within the respective collection chamber.
  • the flow cross sections can be adapted to a density distribution of the first medium within the respective collection chamber.
  • the density of a medium is to be understood as the physical density in single-phase media, while in the case of multiphase media, for example in media which are partly liquid and partly gaseous, a density averaged over the volume in question is to be understood.
  • the cross sectional areas of the first and second plenums are different from one another in a preferred embodiment.
  • the cross-sectional areas of the collecting chambers can be adapted to the density ratios of the first medium in the chambers.
  • heat exchanger according to the invention relate to the interconnection of the flow path sections by means of deflection channels in the deflection plate.
  • flow path sections which are arranged side by side in the main flow direction of the second medium are connected to one another by a deflection channel are.
  • One speaks then of a deflection in the width This makes it possible to connect several or possibly all flow path sections within a row or within a row of pipes together to form a flow path.
  • the interconnected flow path sections are aligned in the main flow direction of the second medium.
  • One speaks then of a deflection in the depth This makes it possible to connect flow paths for the first medium parallel or antiparallel to the main flow direction of the second medium. This leads to an at least partial countercurrent construction of the heat exchanger.
  • two flow path sections are interconnected within a tube by a deflection channel. This means that the first medium flows in one direction through the tube and flows back in the opposite direction through the same tube.
  • the number of sections of at least one flow path is divisible by two.
  • a two-row arrangement of the flow path sections is easily interconnected by the first half of the sections of a flow path arranged in a first row and connected by deflections in the width, whereas the second half of the sections arranged in a second row and also through Deflections in the width is connected to each other, wherein the two halves of the flow path are connected by a deflection in the depth.
  • This deflection in depth is done for example in a deflection of a baffle plate of a tube plate on the Sammelkammem opposite side of the heat exchanger.
  • the number of sections of the flow path is divisible by four.
  • the first and last flow path sections within one or more rows of tubes are not acted upon as hydraulically first sections of flow paths, since in the edge region of collection chambers, which are usually arranged along rows of tubes, the flow and / or pressure conditions of the first medium unfavorable for an admission of flow paths are.
  • two adjacent flow paths are mirror-symmetrical to each other.
  • deflection channels communicate at least two flow paths.
  • an additional compensation of the flow is effected within the flow paths.
  • communication of the optionally adjacent deflection channels is particularly easy to accomplish, for example by omitting a web which may otherwise be present between two deflection channels.
  • a flow cross section of a flow path changes during its course. This is very easy to realize, for example, by flow path sections with few heat transfer channels over correspondingly configured deflection channels with flow path sections are connected to many heat transfer channels. An adaptation of the flow cross section of a flow path to a density of the first medium changing along the flow path is particularly preferred.
  • An embodiment is advantageous in which all sections of at least one flow path in the main flow direction of the second medium are aligned with one another. Particularly advantageously, all flow paths of the heat exchanger are formed in this manner, whereby a pure countercurrent construction of the heat exchanger in a simple manner, namely by appropriately configured deflection channels in a baffle is possible.
  • the heat exchanger consists of flat tubes through which a liquid and / or vapor refrigerant flows, corrugated fins exposed to ambient air, a collection and distribution device for the supply and removal of the refrigerant, arranged between the flat tubes.
  • each one flat tube has two parallel flow sections, which flows through one after the other and are connected via the deflection, wherein each flat tube end a groove between the two flow Sections in the middle of the flat tube end and that the bottom plate between the receiving openings webs, which in terms of their dimensions Height and width correspond to the grooves and each form a joint connection with the grooves.
  • the deflection device is formed by a further base plate with receiving openings and webs, which form a joint connection with the end-side groove of the flat tubes.
  • the deflection device additionally has a channel plate with through slots and a closed cover plate.
  • the collecting and distributing device has a channel plate with channel openings and webs between the channel openings, a cover plate with refrigerant inlet and -austrittsö réelleen and a refrigerant supply and a refrigerant discharge channel, which are arranged parallel to each other and in the longitudinal direction of the heat exchanger on wherein the bottom plate, the channel plate and the cover plate are arranged one above the other in such a way that the openings in the plates are aligned with the flat tube ends.
  • the refrigerant inlet openings are formed as calibrated bores, wherein the diameter of the bores is in particular variable.
  • the cover plate and the refrigerant supply and -abbowkanäle are integrally formed.
  • the heat exchanger which is particularly useful as an evaporator for motor vehicle air conditioners, consisting of flat tubes, which are flowed through by a liquid and / or vapor refrigerant, arranged between the flat tubes, acted upon by ambient air corrugated fins, a collecting and distributing device for the supply and the removal of the refrigerant, wherein the Collection and distribution device consists of a plurality of stacked, perforated plates, whereby refrigerant channels are formed, wherein the ends of the flat tubes are held in receiving openings of a bottom plate, and a deflection device for deflecting the refrigerant in the flow direction of the ambient air.
  • the heat exchanger consists of a series of flat tubes, wherein in each case a flat tube two parallel flow sections, which are successively flowed through and connected via the deflection, and wherein the collecting and distributing device has a between refrigerant inlet and outlet arranged calibration device, which serves as a cover plate is formed with calibration openings for the refrigerant distribution.
  • the calibration openings are arranged on the refrigerant inlet side.
  • the calibration openings have different flow cross sections.
  • the flow cross sections of the calibration openings are preferably larger in the direction of the pressure drop of the refrigerant in the feed channel.
  • the flow cross sections of the calibration openings are variable as a function of the specific volume of the refrigerant or its vapor content.
  • the flat tubes are designed as serpentine segments and the deflection device is arranged in the collecting and distributing device.
  • the collecting and distributing device has a channel plate with through-channel openings for deflecting the refrigerant and channel openings with webs, a cover plate with refrigerant inlet and outlet openings and a refrigerant supply and a refrigerant discharge channel.
  • the channel openings with webs are in each case with the first flat tube end of the Serpentine segment arranged in alignment, whereas the through-channel openings are arranged in alignment with the second flat tube end of the serpentine segment, wherein the refrigerant inlet and -austrittsö réelleen are aligned with the channel openings and the through-channel openings are covered by the cover plate.
  • the serpentine segments have two or three deflections in width.
  • the flat tubes are designed as U-tubes, that is, each with a deflection (in width).
  • Two U-tubes are particularly preferably connected in series on the refrigerant side, and two adjacent channel openings, which are assigned to a U-tube outlet and a U-tube inlet, are in refrigerant communication with each other through a transverse channel in the channel plate.
  • the width b of the channel openings in the channel plate is greater than the width a of the receiving openings in the bottom plate.
  • the depth of the groove in the flat tube ends is greater than the thickness of the bottom plate.
  • one or more of the following dimensions apply to the heat exchanger: Width: 200 to 360 mm, in particular. 260 to 315 mm Height: 180 to 280 mm, in particular. 200 to 250 mm Depth: 30 to 80 mm, preferably 35 to 65 mm Volume: 0.003 to 0.006 m3, in particular.
  • Fig. 1 shows as the first embodiment, an evaporator for an operated with CO 2 as a refrigerant automotive air conditioning system, in an exploded view.
  • This evaporator 1 is designed as a single-row flat tube evaporator and has a plurality of flat tubes, of which only two flat tubes 2, 3 are shown.
  • These flat tubes 2, 3 are formed as extruded multi-chamber flat tubes, which have a plurality of flow channels 4. All flat tubes 2, 3 have the same length l and the same depth t.
  • a groove 5, 6 symmetrical to the central axis 2c in the flat tube 2 is incorporated.
  • corrugated fins 7 Between the individual flat tubes 2, 3 are corrugated fins 7, which are acted upon by ambient air in the direction of the arrow L.
  • the corrugated fins 7 are continuous in the depth direction, but may also be interrupted, for example in the middle of the depth t, in order to ensure better condensate drainage and / or thermal separation.
  • a bottom plate 8 is shown, in which a first row of slot-shaped openings 9a - 9f and a second series of such openings 10a - 10f are arranged.
  • the openings 9a and 10a, 9b and 10b, etc. lie in the direction of the depth (air flow direction L) one behind the other and leave between each webs 11a, 11b - 11f. With regard to their width in the depth direction, these webs 11a-11f correspond to the width of the cutout 5 of the pipe ends 2a.
  • the number of openings 9a-9f or 10a-10f corresponds to the number of flat tubes 2, 3.
  • baffle 12 in which two rows of openings 13a - 13f and 14a - 14f (partially hidden) are arranged.
  • the arrangement of the apertures 13a-f and 14a-f corresponds to the arrangement of the apertures 9a-9f or 10a-10f, but the apertures 13a-f and 14a-f are larger in their width b and depth than the corresponding dimensions of the apertures 9a - 9f or 10a - 10f, each having only a width of a, which corresponds to the thickness of the flat tubes 2, 3.
  • Between the openings 13a, 14a, 13b, 14b - 13f u. 14f are each webs 15a - 15f left. With regard to their dimensions in the depth direction, these webs 15a-15f are smaller than the corresponding dimensions of the webs 11a-11f of the bottom plate 8.
  • a so-called cover plate 16 which has a first row of refrigerant inlet openings 17a-17f and a second row of refrigerant outlet openings 18a-18f.
  • These openings 17a - 17f u. 18a-18f are preferably formed as circular bores and adapted in terms of their diameter to the desired refrigerant distribution or flow rate.
  • a collecting box 19 with a housing and in each case a collecting chamber 20, 21 for the supply and the discharge of the refrigerant.
  • the collection box has openings 22a-f and 23a-f for both collection chambers on its underside, shown in dashed lines, which correspond in terms of position and size to the openings 17a-f and 18a-f.
  • a further bottom plate 24 which has two rows of slot-shaped openings 25a-f and 26a-f analogous to the first bottom plate 8. Also located between the openings 25a and 26a to 25f and 26f are webs 27a-f (partially concealed), these webs, with respect to their width in the depth direction, corresponding to the width of the recess 6 in the end of the flat tube 2.
  • a further baffle plate 28 is shown, the continuous deflection channels 29a - 29f has. These deflection channels 29a-f extend over the entire depth t of the flat tubes 2, 3.
  • a cover plate 30 which has no openings, but closes the deflection channels 29a-29f with respect to the surroundings of the heat exchanger.
  • the above-described constituent parts of the evaporator 1 are mounted as follows: On the flat tube ends 2a, etc., the bottom plate 8 is placed, so that the webs 11a - 11f come to lie in the recesses 5 of the flat tube ends. About the bottom plate 8 then the baffle 12, the cover plate 16 and the collection box 19 with the collection chambers 20, 21 are stacked. In an analogous manner, the lower bottom plate 24 is pushed onto the flat tube ends 2b, so that the webs 27a - 27f come to lie in the recesses 6; Thereafter, the channel plate 28 and the cover plate 29 are added. After the evaporator 1 is thus joined together, it is soldered in a soldering furnace to form a solid block. During the soldering process, the plates by a form or non-positive tension held in position to each other. But it is also possible to first mount the tail of base plate, baffle and cover plate and then connect with flat tubes.
  • the refrigerant in this case CO 2 , thus flows through the evaporator initially on the front side from top to bottom, specifically in the front section 2 d of the flat tube 2, in the lower, consisting of the plates 24, 28, 30 tube plate in depth deflected and flows on the back of the evaporator 1, ie in the rear flow section 2e of the flat tube 2 from bottom to top, corresponding to the arrows R1, R2 and R3 to the collection chamber 21st
  • Fig. 2 shows a further embodiment of the invention, namely an evaporator 40, in which the aforementioned flat tubes are formed as serpentine segments 41.
  • a serpentine segment 41 consists of four flat tube legs 42, 43, 44 u. 45, which are interconnected by three Umlenkbögen 46, 47, 48. Between the individual Flachrohrschenkeln 42 - 45 corrugated fins 49 are arranged.
  • the other parts of the evaporator are also shown in an exploded view, ie a bottom plate 50, a baffle 51, a cover plate 52 and collecting chambers 53, 54 for a refrigerant supply or removal.
  • the bottom plate 50 has a front row of slot-shaped openings 55 a, 55 b u.
  • This web 60a is in turn smaller than the recess 58 of the flat tube leg 42.
  • a deflection channel 61 Adjacent to the opening 59a and at a distance corresponding to that of the flat tube ends 42a-45a, a deflection channel 61 is arranged which extends over the entire depth of the flat tube leg 45. Adjacent to the deflection channel 61 then follows an opening 59b, which corresponds in size to the opening 59a. It corresponds to the next Flachrohrserpentinensegment, which is not shown here.
  • Above the baffle 51 is the cover plate 52, in the front row two refrigerant supply openings 62, 63 and in the rear row two refrigerant outlets 64 u. 65 has. The latter correspond in terms of size and location with the dashed lines in the collection chambers 53, 54 openings (without reference number).
  • the refrigerant flow path is illustrated by arrows: First, the refrigerant leaves the collection chamber 53 via the arrow E1, then follows the arrows E2, E3, E4 and enters the front flow section of the flat tube leg 42 and flows through the entire serpentine segment 41 on its front side and enters E6 from the last leg 45, enters the deflection channel 61, where it is deflected in accordance with the arrow U in the depth, and then, following the arrow R1, to flow through the back of the serpentine segment, ie in the opposite direction as on the Front. Finally, this refrigerant flow passes via the arrow R2, ie through the opening 64 into the collecting chamber 54.
  • serpentine segment portion 41 can also be traversed in the opposite direction in the width, ie in the drawing from left to right or from outside to inside. In view of the end face of the evaporator, this would therefore flow symmetrically from the outside to the inside on the front side; in the middle, both refrigerant flows - combined in a common deflection channel, which then functions as a mixing chamber - can be deflected in depth and again on the rear side flow from the inside to the outside.
  • Fig. 3 shows a further embodiment of the invention, namely an evaporator 70, the flat tubes of individual U-tubes 71a, 71b, 71c, etc. are formed. It is thus a serpentine segment section with a deflection and two legs 72 u. 73.
  • the not visible in the drawing ends of this flat tube leg 72 u. 73 are analogously, ie as described above, fixed in a bottom plate 74 with corresponding receptacles.
  • a baffle 75 is arranged, which alternately two in the depth direction one behind the other slot-shaped openings 76, 77, leaving a web 78 and a depth direction has continuous deflection channel 79.
  • the cover plate - analogous to the embodiments described above - is omitted in this illustration.
  • the flow of the refrigerant takes place according to the arrows; i.e.
  • the refrigerant enters at E in the front flow section of the U-tube 71a, first flows down, is deflected down, then flows upwards and enters the deflection channel 79, where it is deflected according to the arrow U, then flows on the back down, is deflected there and then flows back up to pass through the arrow A through the opening 77.
  • the supply and discharge of the refrigerant will be described with reference to the following figure, corresponding to the sections IV - IV and V - V.
  • Fig. 4 shows a section along the line IV - IV through the evaporator according to Fig. 3 in an enlarged view and supplemented by a cover plate 80 and a collection box 81 and a collection box 82.
  • the remaining parts are denoted by the same reference numerals as in Fig. 3 referred to, ie the baffle 75, the bottom plate 74 and the flat tube leg 71c.
  • the baffle 75 has two apertures 76c and 77c which are separated by the web 78c.
  • a refrigerant inlet opening 83 is provided, which is arranged with an aligned refrigerant opening 84 in the collecting box 81.
  • a refrigerant discharge opening 85 in the cover plate 80 and an aligned refrigerant opening 86 are arranged in the header box 82.
  • the collecting boxes 81, 82 are sealed tightly and pressure-resistant with the cover plate 80, as are the other parts 80, 75, 74 and 71c.
  • Fig. 5 shows a further section along the line V - V in Fig. 3 , ie through the deflection channel 79d. Same parts are in turn with the same Reference numbers designated. It can be seen that the refrigerant, represented by the arrows, is deflected in the left flat tube section from bottom to top in the deflection channel 79d to the right and reaches the right or rear portion of the flat tube leg 71c to flow there from top to bottom.
  • Fig. 6 shows as a further embodiment of the invention, an evaporator 90, which in turn is constructed of U-tubes 91a, 91b, 91c, etc.
  • the ends of the U-tube legs are again - which is not shown in the drawing - received in a bottom plate 92, over which a baffle plate 93 is located.
  • the baffle plate 93 has a configuration of openings, in which in each case after two U-tubes, so z. B. 91a and 91b, a pattern repeated.
  • Fig. 1 are collection chambers 20 and 21 and in Fig. 4 Collecting boxes 81 and 82 for the supply and discharge of refrigerant shown.
  • a distribution device according to the DE 33 11 579 A1 , ie a coiled profile body, or according to the DE 31 36 374 A1 the applicant, a so-called slide body, use, so that a uniform refrigerant distribution and thus a uniform temperature distribution is achieved at the evaporator.
  • Fig. 7 shows a cross section of a heat exchanger 110 with an end piece 120, which has a bottom plate 130, a baffle 140, a cover plate 150 and manifolds 160, 170.
  • a tube 180 is received in two openings 190, 200 in the bottom plate 130, wherein a recess 210 in one end of the tube 180 rests against a web 220 of the bottom plate 130.
  • the recess 210 is slightly higher than the web 220, so that the pipe end protrudes slightly beyond the bottom plate 130.
  • Heat transfer channels (not shown) in the pipe 180 communicate with passages 230, 240 in the baffle plate 140.
  • the passages 230, 240 are again via recesses 250, 260 in the cover plate 150 and recesses 270, 280 in the housings 290, 300 of the headers 160, 170 connected to collection chambers 310, 320.
  • the edges of the recesses 250, 260 are provided with extensions 330, 340, which engage in the recesses 270, 280, whereby an orientation of the headers 160, 170 with respect to the cover plate 150 is accomplished such that the recesses 250th or 260 in the cover plate 150 with the recesses 270 and 280 in the collection box housings 290, 300 are aligned.
  • Fig. 8 shows a development of the heat exchanger Fig. 6
  • the configuration of Umlenkkanälen has in the heat exchanger 410 also a pattern that repeats after every two U-tubes 420, and that corresponds to a flow path through the heat exchanger 410.
  • two adjacent flow paths are arranged mirror-symmetrically to each other. This means that either the passageways 430, 440 of a flow path 450 adjacent to the passageways 460, 470 of an adjacent flow path 480 or a deflection channel 490 of a flow path 500 adjacent to one Deflection channel 510 of an adjacent flow path 520 comes to rest.
  • the flow paths 450, 480, 485, 500, 520, 550, 560 each consist of eight sections, whereas the flow path 445 consists of only four sections to reduce a pressure drop along the flow path 445, also due to the unfavorable flow conditions in the peripheral areas of one heat exchanger. In this case, mixing with the adjacent flow path 450 is also appropriate.
  • Fig. 9 11 shows another example of a connection pattern of flow path sections of a heat exchanger 610.
  • the flow path sections 620 on the inlet side 630 of the heat exchanger 610 have a smaller flow cross section than the flow path sections 640 on the exit side 650.
  • this asymmetry serves for a Adapting the flow cross-sections to the density of the first medium along the flow paths 660.
  • FIG. 12 shows another example of a wiring pattern of flow path portions of a heat exchanger 710 accomplished by a configuration of pass and turn passages of a baffle 720.
  • the flow paths 730 and 740 respectively each aligned so that an inlet and an outlet of the first medium, given by passages 750, 760 and 770, 780, as far as possible from edges 790 and 800 of the heat exchanger 710 are arranged.
  • FIG. 12 shows another example of a wiring pattern of flow path sections of a heat exchanger 810 accomplished by a configuration of the bypass and bypass passages 812, 814 of a baffle 820.
  • the flow path sections are in the order 1 (down) - 2 (up) - 3 (down) - 4 (up) - 5 (down) - 6 (up) etc. interconnected with each other.
  • Fig. 12 shows a tube sheet 1010 with a cover plate 1020 and a plate 1030, which is formed by a one-piece design of a baffle plate with a bottom plate.
  • the cover plate 1020 has recesses 1040 for connection to two collection chambers, while in the plate 1030 passageways 1050 of the baffle plate and below it narrower tube receptacles 1060 can be seen in the bottom plate.
  • FIGS. 13 and 14 show the tubesheet Fig. 12 in a cross section or in a longitudinal section, in each case in the installed state with a tube 1070th
  • Fig. 15 shows a similar tube sheet 1110, the cover plate 1120 has no recesses.
  • deflection channels 1140 are arranged for deflection in the depth.
  • Fig. 16 shows a further possibility of the embodiment of a two-part tube sheet 1210.
  • the baffle plate is integrally formed with the cover plate, whereby a plate 1220 is formed.
  • the plate has a Deflection channel 1230 for a deflection in the depth, which is given by a curvature.
  • the bottom plate 1240 is also curved, so that the 1260 received in the recess 1250 of the bottom plate 1240 tube 1260 is held firm and thus more pressure stable.
  • the tube 1260 abuts the edge 1270, 1280 of the Umlenkkanals 1230, since the curvature in the plate 1220 is not as wide as the curvature in the plate 1240th
  • Fig. 17 shows a heat exchanger 1310 in pure countercurrent construction.
  • the pure countercurrent design is characterized in that deflections take place only in depth, but not in width. It does not matter from how many sections the flow paths exist. The flow paths may for example consist of four sections, in each case then three deflections in depth are necessary.
  • the heat exchanger 1310 has flow paths 1320, each with a deflection in the depth and thus with two flow path sections, which are aligned with each other in the main flow direction of the second medium on.
  • the upper end piece 1330 has a tube plate 1340 and two collection boxes not shown for clarity.
  • the tube plate consists of a bottom plate 1350, a baffle 1360, which serves in this case only a passage of the first medium, and a cover plate 1370 with openings 1380 for connection to the collecting boxes.
  • the lower end consists of only one plate 1400, in which a bottom plate, a baffle plate and a cover plate is integrated. The construction of the plate 1400 will be described with reference to the following FIGS. 18 and 19 explained.
  • Fig. 18 shows a cross section and Fig. 19 a broken oblique view of the plate 1400 from Fig. 17 .
  • a tube 1410 is received in a recess 1420, which also serves as a deflection channel for the first medium, wherein the deflection channel is closed to the outside through the area 1430 of the plate 1400.
  • a rejuvenation points the Recess 1420 edges 1440, 1450, which serve the pipe 1410 as a stop.
  • the tube 1410 serves to represent two sections (downwards 1460 and upwards 1470) of a flow path.
  • Fig. 20 shows a similarly constructed tube sheet 1800, which is also constructed in one piece and on the Umlenkkanäle 1820 and the pipe stops 1830 addition openings 1810 in the region of the cover plate to be connectable to one or two headers.
  • the invention allows a heat exchanger, which consists of a series of tubes (for the realization of heat transfer channels), two plates (the tubesheets) and two tubes (the collection boxes). This is an extremely simple and also pressure-stable construction of the heat exchanger feasible.
  • FIGS. 21 to 24 show exemplary embodiments of a tube sheet with little material and thus associated with low material costs and low weight.
  • the tube sheet 2010 in Fig. 21 has between the pipe receiving recesses 2020 with the pipe stop edges 2030 for material savings as openings 2040 formed recesses.
  • the tube sheet 2110 in FIG Fig. 22 provided as side notches 2120 formed recesses.
  • the tubesheet 2210 in FIGS. 23 and 24 is completely severed between the 2220 pipe receiving cutouts. In this case, the tubes 2230 may be stabilized only by the corrugated fins 2240.
  • FIG. 12 shows another example of a wiring pattern of flow path portions of a heat exchanger 2310 accomplished by a configuration of pass and turn channels 2320, 2330 of a baffle 2340.
  • the flow path sections are in the order 1 (down) -2 (up) -3 (down) - 4 (up) - 5 (down) - 6 (up) interconnected.
  • a tube for each flow path section.
  • a tube preferably contains two or more flow path sections, for example the flow path sections 1, 4 and 5 or the flow path sections 2, 3 and 6.
  • flat tubes are particularly well suited for this purpose. Any further interconnection patterns of flow path sections are also conceivable over the ones shown.

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  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
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Claims (11)

  1. Echangeur de chaleur, en particulier pour un véhicule automobile, comprenant des tubes qui peuvent être traversés par un premier milieu, dans des canaux de transfert de chaleur, et entourés par un deuxième milieu, où le premier milieu peut être dirigé le long d'un ou de plusieurs trajet(s) d'écoulement, et comprenant au moins une pièce d'extrémité qui comporte un plateau à tubes se composant de plaques disposées les unes sur les autres, où les plaques disposées les unes sur les autres se composent d'une plaque de fond (50), d'une plaque de retour de flux (51) venant en appui sur la plaque de fond et d'une plaque de recouvrement (52) venant en appui sur la plaque de retour de flux, où des extrémités des tubes peuvent être reliées à la plaque de fond du plateau à tubes et où au moins un canal de circulation et / ou de retour de flux (61) est formé par un évidement placé dans la plaque de retour de flux (51) du plateau à tubes et, grâce à la plaque de recouvrement, peut être fermé de façon étanche au fluide, par rapport à un milieu environnant de l'échangeur de chaleur, où la plaque de retour de flux (51) est configurée en formant une seule et même pièce avec la plaque de fond (50) et avec la plaque de recouvrement (52), où un tube est façonné en une fois ou plusieurs fois pour avoir à peu près une forme en U, et les extrémités du tube façonné au moins au nombre de un peuvent être reliées à la même plaque de fond (50), caractérisé en ce que la plaque de fond (50), la plaque de retour de flux (51) et / ou la plaque de recouvrement (52) sont séparées dans des zones comprises entre des canaux de circulation et / ou de retour de flux et / ou présentent des évidements sous la forme de percées (2040) ou d'encoches (2120), où la plaque de fond (50), la plaque de retour de flux (51) et / ou la plaque de recouvrement (52) présentent, sur un bord d'au moins une percée, un prolongement qui s'engage dans une percée d'une plaque adjacente.
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que l'échangeur de chaleur présente précisément une pièce d'extrémité comprenant un plateau à tubes se composant de plaques placées les unes sur les autres.
  3. Echangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que les tubes sont brasés ou soudés avec la plaque de fond (50).
  4. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que les tubes sont configurés comme des tubes plats (42 - 45), en comportant en particulier des ailettes ondulées (49) placées entre ces tubes plats.
  5. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que les trajets d'écoulement se composent de plusieurs tronçons, où un canal de retour de flux (61), qui est formé par un évidement placé dans la plaque de retour de flux (51), relie l'un à l'autre les canaux de transfert de chaleur de deux tronçons de trajet d'écoulement qui peuvent être traversés, l'un après l'autre, par le premier milieu, en particulier d'après des critères prédéfinis.
  6. Echangeur de chaleur selon la revendication 5, caractérisé en ce que les deux tronçons de trajet d'écoulement reliés l'un à l'autre sont disposés l'un à côté de l'autre dans la direction principale d'écoulement du deuxième milieu.
  7. Echangeur de chaleur selon la revendication 5, caractérisé en ce que les deux tronçons de trajet d'écoulement reliés l'un à l'autre sont alignés l'un par rapport à l'autre dans la direction principale d'écoulement du deuxième milieu.
  8. Echangeur de chaleur selon l'une quelconque des revendications 5 à 7, caractérisé en ce que les deux tronçons de trajet d'écoulement reliés l'un à l'autre sont disposés dans un seul tube.
  9. Echangeur de chaleur selon l'une quelconque des revendications 5 à 8, caractérisé en ce que des canaux de retour de flux (530, 540) d'au moins deux trajets d'écoulement (550, 560) communiquent entre eux.
  10. Echangeur de chaleur selon l'une quelconque des revendications 5 à 9, caractérisé en ce qu'une section d'écoulement d'un trajet d'écoulement se modifie en passant d'un tronçon à un tronçon qui fait suite hydrauliquement.
  11. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un tube présente un évidement (58) au niveau d'une extrémité tubulaire (42a, 45a), et le plateau à tubes présente un logement tubulaire comportant une partie pleine (56a - 56c), où l'évidement et la partie pleine présentent une même largeur et, en particulier, une même hauteur.
EP08018381.7A 2001-12-21 2002-12-19 Échangeur de chaleur, en particulier pour véhicule automobile Expired - Lifetime EP2026028B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10163202 2001-12-21
DE10234118 2002-07-26
DE10240556 2002-08-29
EP02798351A EP1459027B1 (fr) 2001-12-21 2002-12-19 Echangeur thermique notamment destine a un vehicule
PCT/EP2002/014581 WO2003054466A1 (fr) 2001-12-21 2002-12-19 Echangeur thermique notamment destine a un vehicule

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP02798351A Division EP1459027B1 (fr) 2001-12-21 2002-12-19 Echangeur thermique notamment destine a un vehicule
EP02798351.9 Division 2002-12-19

Publications (3)

Publication Number Publication Date
EP2026028A2 EP2026028A2 (fr) 2009-02-18
EP2026028A3 EP2026028A3 (fr) 2012-06-20
EP2026028B1 true EP2026028B1 (fr) 2018-07-18

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EP02795237A Expired - Lifetime EP1459026B1 (fr) 2001-12-21 2002-12-19 Echangeur thermique notamment destine a un vehicule
EP08018381.7A Expired - Lifetime EP2026028B1 (fr) 2001-12-21 2002-12-19 Échangeur de chaleur, en particulier pour véhicule automobile
EP02793087A Expired - Lifetime EP1459025B1 (fr) 2001-12-21 2002-12-19 Dispositif d'echange de chaleur
EP02798351A Expired - Lifetime EP1459027B1 (fr) 2001-12-21 2002-12-19 Echangeur thermique notamment destine a un vehicule

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EP02793087A Expired - Lifetime EP1459025B1 (fr) 2001-12-21 2002-12-19 Dispositif d'echange de chaleur
EP02798351A Expired - Lifetime EP1459027B1 (fr) 2001-12-21 2002-12-19 Echangeur thermique notamment destine a un vehicule

Country Status (13)

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US (4) US7318470B2 (fr)
EP (4) EP1459026B1 (fr)
JP (4) JP2005513403A (fr)
KR (1) KR100925910B1 (fr)
CN (2) CN100342196C (fr)
AT (3) ATE461407T1 (fr)
AU (3) AU2002360056A1 (fr)
BR (3) BR0215235A (fr)
CA (1) CA2471164C (fr)
DE (6) DE50214246D1 (fr)
ES (1) ES2316640T3 (fr)
MX (1) MXPA04006151A (fr)
WO (3) WO2003054465A1 (fr)

Families Citing this family (166)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE50214246D1 (de) 2001-12-21 2010-04-08 Behr Gmbh & Co Kg Wärmeübertrager, insbesondere für ein kraftfahrzeug
DE10322406A1 (de) * 2003-05-16 2004-12-02 Api Schmidt-Bretten Gmbh & Co. Kg Platten-Wärmeübertrager
JP4248931B2 (ja) * 2003-05-20 2009-04-02 カルソニックカンセイ株式会社 熱交換器
DE10336625A1 (de) * 2003-08-05 2005-03-10 Behr Gmbh & Co Kg Vorrichtung zum Austausch von Wärme und Verfahren zu deren Herstellung
DE10349150A1 (de) * 2003-10-17 2005-05-19 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere für Kraftfahrzeuge
FR2863044B1 (fr) * 2003-11-27 2006-01-13 Valeo Climatisation Module pour l'echange de chaleur entre fluides en circulation
DE102004001786A1 (de) * 2004-01-12 2005-08-04 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere für überkritischen Kältekreislauf
US7775067B2 (en) * 2004-03-17 2010-08-17 Showa Denko K.K. Heat exchanger header tank and heat exchanger comprising same
DE102004011608A1 (de) * 2004-03-18 2005-10-13 Obrist Engineering Gmbh Wärmetauscher einer Fahrzeugklimaanlage
CN100487344C (zh) * 2004-04-12 2009-05-13 昭和电工株式会社 热交换器
JP2005326135A (ja) * 2004-04-12 2005-11-24 Showa Denko Kk 熱交換器
DE102004044861A1 (de) * 2004-09-14 2006-03-16 Behr Gmbh & Co. Kg Wärmetauscher für Kraftfahrzeuge
DE102004048767A1 (de) * 2004-10-05 2006-04-06 Behr Gmbh & Co. Kg Verfahren zur Herstellung eines Wärmeübertragers
DE102004056557A1 (de) * 2004-11-23 2006-05-24 Behr Gmbh & Co. Kg Dimensionsoptimierte Vorrichtung zum Austausch von Wärme und Verfahren zur Optimierung der Dimensionen von Vorrichtungen zum Austausch von Wärme
DE102004058499A1 (de) * 2004-12-04 2006-06-14 Modine Manufacturing Co., Racine Wärmeübertrager, insbesondere für Kraftfahrzeuge
JP2006183962A (ja) 2004-12-28 2006-07-13 Denso Corp 蒸発器
JP2006194522A (ja) * 2005-01-13 2006-07-27 Japan Climate Systems Corp 熱交換器
KR101090225B1 (ko) * 2005-01-27 2011-12-08 한라공조주식회사 열교환기
EP1859217A1 (fr) * 2005-03-07 2007-11-28 Behr GmbH & Co. KG Echangeur thermique, en particulier evaporateur d'une installation de climatisation pour vehicules
US7275394B2 (en) * 2005-04-22 2007-10-02 Visteon Global Technologies, Inc. Heat exchanger having a distributer plate
DE102005020499A1 (de) 2005-04-29 2006-11-09 Behr Gmbh & Co. Kg Verdampfer, insbesondere Heckverdampfer für ein Kraftfahrzeug
DE102006025727A1 (de) * 2005-08-04 2007-02-08 Visteon Global Technologies, Inc., Van Buren Township Wärmeübertrager für Fahrzeuge und Verfahren zu seiner Herstellung
DE102005059920B4 (de) 2005-12-13 2019-07-04 Mahle International Gmbh Wärmetauscher, insbesondere Verdampfer
DE102005059919A1 (de) * 2005-12-13 2007-06-14 Behr Gmbh & Co. Kg Wärmetauscher, insbesondere Verdampfer
JP2007198721A (ja) * 2005-12-26 2007-08-09 Denso Corp 熱交換器
DE102006004710A1 (de) * 2006-01-31 2007-08-02 Behr Gmbh & Co. Kg Wärmeübertrageranordnung, insbesondere eines Heckverdampfers in einem Kraftfahrzeug
FR2898405B1 (fr) * 2006-03-07 2008-06-06 Valeo Systemes Thermiques Echangeur de chaleur, en particulier refroidisseur de gaz, comportant deux nappes de tubes reliees
JP4811087B2 (ja) * 2006-03-31 2011-11-09 株式会社デンソー 熱交換器
JP4724594B2 (ja) * 2006-04-28 2011-07-13 昭和電工株式会社 熱交換器
DE102006035951B4 (de) * 2006-07-31 2019-09-05 Mahle International Gmbh Wärmetauscher in Plattenbauweise, insbesondere Verdampfer und Vorrichtung zur Montage eines Sammlers in Plattenbauweise
KR101280618B1 (ko) * 2006-09-04 2013-07-02 한라비스테온공조 주식회사 증발기
DE102006046671A1 (de) * 2006-09-29 2008-04-03 Behr Gmbh & Co. Kg Wärmetauscher in Plattenbauweise, insbesondere Verdampfer für eine Kraftfahrzeug-Klimaanlage
US20080105419A1 (en) * 2006-11-07 2008-05-08 Kwangheon Oh Heat exchanger
US7965508B2 (en) * 2007-03-27 2011-06-21 Denso Corporation Cooling device for electronic component and power converter equipped with the same
EP2140219B1 (fr) * 2007-04-12 2023-07-12 AutomotiveThermoTech GmbH Véhicules à moteur
WO2008141744A1 (fr) * 2007-05-22 2008-11-27 Behr Gmbh & Co. Kg Échangeur de chaleur
JP5114771B2 (ja) * 2007-05-29 2013-01-09 株式会社ケーヒン・サーマル・テクノロジー 熱交換器
WO2008147361A1 (fr) * 2007-06-01 2008-12-04 Carrier Corporation Échangeur de chaleur à écoulement parallèle avec connecteurs
KR100941301B1 (ko) * 2007-06-15 2010-02-11 주식회사 경동나비엔 열교환기
JP5046771B2 (ja) * 2007-07-27 2012-10-10 三菱重工業株式会社 冷媒蒸発器
JP4972488B2 (ja) * 2007-08-07 2012-07-11 昭和電工株式会社 熱交換器
FR2921471A1 (fr) * 2007-09-21 2009-03-27 Hades Soc Par Actions Simplifi Boitier repartiteur de fluide caloporteur, pour le couplage d'une pompe a chaleur a une pluralite de circuits de captage et de distribution de chaleur
US9328966B2 (en) * 2007-11-01 2016-05-03 Modine Manufacturing Company Heat exchanger with a baffle reinforcement member
CN101487669B (zh) * 2008-01-17 2012-08-22 开利公司 包括多管式分配器的热交换器
EP2090851A1 (fr) 2008-02-15 2009-08-19 Delphi Technologies, Inc. Échangeur de chaleur doté d'une chambre de mélange
WO2009105454A2 (fr) * 2008-02-22 2009-08-27 Liebert Corporation Collecteur à plaques stratifiées pour un échangeur de chaleur à microcanaux
EP2108909A1 (fr) * 2008-04-07 2009-10-14 Delphi Technologies, Inc. Échangeur thermique fourni avec un bloc de fixation
DE102008025910A1 (de) 2008-05-29 2009-12-03 Behr Gmbh & Co. Kg Wärmeübertrager
EP2131131A1 (fr) 2008-06-06 2009-12-09 Scambia Industrial Developments AG Échangeur de chaleur
CN102105761B (zh) * 2008-06-10 2012-11-14 汉拏空调株式会社 使用HFO1234yf制冷剂的管片式蒸发器
FR2933178A1 (fr) * 2008-06-26 2010-01-01 Valeo Systemes Thermiques Echangeur de chaleur et carter pour l'echangeur
US9759495B2 (en) * 2008-06-30 2017-09-12 Lg Chem, Ltd. Battery cell assembly having heat exchanger with serpentine flow path
DE102008047560A1 (de) 2008-09-16 2010-04-15 Behr Gmbh & Co. Kg Verwendung einer Aluminiumlegierung, Herstellung eines Verdampfers unter Verwendung der Aluminiumlegierung und Verdampfer für eine insbesondere mit CO2 betriebene Kraftfahrzeugklimaanlage
JP5408951B2 (ja) * 2008-10-16 2014-02-05 三菱重工業株式会社 冷媒蒸発器およびそれを用いた空調装置
TWI361880B (en) * 2008-11-17 2012-04-11 Heat exchanging module and working fluid distributor thereof and method for manufacturing heat exchange module
DE102008058210A1 (de) 2008-11-19 2010-05-20 Voith Patent Gmbh Wärmetauscher und Verfahren für dessen Herstellung
FR2941522B1 (fr) 2009-01-27 2012-08-31 Valeo Systemes Thermiques Echangeur de chaleur pour deux fluides, en particulier evaporateur de stockage pour dispositif de climatisation
US8177932B2 (en) * 2009-02-27 2012-05-15 International Mezzo Technologies, Inc. Method for manufacturing a micro tube heat exchanger
JP5904351B2 (ja) * 2009-03-16 2016-04-13 藤本　雅久 吸収冷却器、熱交換器
FR2943775B1 (fr) * 2009-03-24 2012-07-13 Valeo Systemes Thermiques Echangeur de stockage pourvu d'un materiau stockeur et boucle de climatisation ou circuit de refroidissement comprenant un tel echangeur.
US20100275619A1 (en) * 2009-04-30 2010-11-04 Lg Chem, Ltd. Cooling system for a battery system and a method for cooling the battery system
US8403030B2 (en) * 2009-04-30 2013-03-26 Lg Chem, Ltd. Cooling manifold
US8663829B2 (en) 2009-04-30 2014-03-04 Lg Chem, Ltd. Battery systems, battery modules, and method for cooling a battery module
FR2947332B1 (fr) * 2009-06-25 2011-07-22 Valeo Systemes Thermiques Boite collectrice pour echangeur de chaleur ayant une aptitude au brasage amelioree
US8399118B2 (en) * 2009-07-29 2013-03-19 Lg Chem, Ltd. Battery module and method for cooling the battery module
US8399119B2 (en) * 2009-08-28 2013-03-19 Lg Chem, Ltd. Battery module and method for cooling the battery module
DE102009041524A1 (de) * 2009-09-15 2011-03-24 Mahle International Gmbh Plattenwärmetauscher
CN101660870B (zh) * 2009-09-16 2012-07-18 三花丹佛斯（杭州）微通道换热器有限公司 具有改进制冷剂分配性能的换热器
DE102009044119A1 (de) * 2009-09-28 2011-03-31 Contitech Kühner Gmbh & Cie. Kg Innerer Wärmetauscher, insbesondere für Kraftfahrzeugklimaanlagen
DE102009047620C5 (de) * 2009-12-08 2023-01-19 Hanon Systems Wärmeübertrager mit Rohrbündel
JP4715963B1 (ja) * 2010-02-15 2011-07-06 ダイキン工業株式会社 空気調和機用熱交換器
US8203839B2 (en) * 2010-03-10 2012-06-19 Toyota Motor Engineering & Manufacturing North America, Inc. Cooling devices, power modules, and vehicles incorporating the same
CN101799253A (zh) * 2010-03-18 2010-08-11 王子异 一种具有密封盖板结构的热交换器
JP5687937B2 (ja) 2010-03-31 2015-03-25 モーディーン・マニュファクチャリング・カンパニーＭｏｄｉｎｅ Ｍａｎｕｆａｃｔｕｒｉｎｇ Ｃｏｍｐａｎｙ 熱交換器
DE202010007533U1 (de) * 2010-06-02 2010-08-19 Tfc Cooling Products E.K. Wärmetauscher
US9151540B2 (en) 2010-06-29 2015-10-06 Johnson Controls Technology Company Multichannel heat exchanger tubes with flow path inlet sections
US9267737B2 (en) 2010-06-29 2016-02-23 Johnson Controls Technology Company Multichannel heat exchangers employing flow distribution manifolds
JP4983998B2 (ja) * 2010-09-29 2012-07-25 ダイキン工業株式会社 熱交換器
US8662153B2 (en) 2010-10-04 2014-03-04 Lg Chem, Ltd. Battery cell assembly, heat exchanger, and method for manufacturing the heat exchanger
EP2444770B1 (fr) * 2010-10-20 2020-02-12 ABB Schweiz AG Échangeur de chaleur comprenant un caloduc pulsatif
JP5413433B2 (ja) * 2010-11-09 2014-02-12 株式会社デンソー 熱交換器
DE102011003649A1 (de) * 2011-02-04 2012-08-09 Behr Gmbh & Co. Kg Wärmeübertrager
CN102095315B (zh) * 2011-03-04 2012-01-25 刘小江 一种蜂窝孔式换热器
JP2012225634A (ja) * 2011-04-04 2012-11-15 Denso Corp 熱交換器
KR101283591B1 (ko) 2011-09-19 2013-07-05 현대자동차주식회사 차량용 열교환기
US9671181B2 (en) * 2011-09-30 2017-06-06 L&M Radiator, Inc. Heat exchanger with improved tank and tube construction
JP5796563B2 (ja) * 2011-11-29 2015-10-21 株式会社デンソー 熱交換器
JP5796564B2 (ja) * 2011-11-30 2015-10-21 株式会社デンソー 熱交換器
US9105950B2 (en) 2012-03-29 2015-08-11 Lg Chem, Ltd. Battery system having an evaporative cooling member with a plate portion and a method for cooling the battery system
US9379420B2 (en) 2012-03-29 2016-06-28 Lg Chem, Ltd. Battery system and method for cooling the battery system
US9605914B2 (en) 2012-03-29 2017-03-28 Lg Chem, Ltd. Battery system and method of assembling the battery system
US8852781B2 (en) 2012-05-19 2014-10-07 Lg Chem, Ltd. Battery cell assembly and method for manufacturing a cooling fin for the battery cell assembly
KR101339250B1 (ko) * 2012-06-11 2013-12-09 현대자동차 주식회사 차량용 열교환기
KR101315359B1 (ko) * 2012-06-27 2013-10-08 주식회사 고산 열교환기
US9306199B2 (en) 2012-08-16 2016-04-05 Lg Chem, Ltd. Battery module and method for assembling the battery module
DE102013106209B4 (de) 2012-09-20 2020-09-10 Hanon Systems Klimatisierungsvorrichtung eines Kraftfahrzeuges mit einer Wärmeübertrageranordnung zur Wärmeaufnahme
US9083066B2 (en) 2012-11-27 2015-07-14 Lg Chem, Ltd. Battery system and method for cooling a battery cell assembly
US8852783B2 (en) 2013-02-13 2014-10-07 Lg Chem, Ltd. Battery cell assembly and method for manufacturing the battery cell assembly
US20140231059A1 (en) * 2013-02-20 2014-08-21 Hamilton Sundstrand Corporation Heat exchanger
DE102013203222A1 (de) 2013-02-27 2014-08-28 Behr Gmbh & Co. Kg Wärmeübertrager
CN111928678A (zh) * 2013-03-15 2020-11-13 开利公司 用于风冷式冷却器的热交换器
EP2984433A1 (fr) * 2013-04-10 2016-02-17 Carrier Corporation Unité d'échange thermique à banc multiple à tube plié
US9647292B2 (en) 2013-04-12 2017-05-09 Lg Chem, Ltd. Battery cell assembly and method for manufacturing a cooling fin for the battery cell assembly
US20160116231A1 (en) * 2013-05-15 2016-04-28 Mitsubishi Electric Corporation Stacking-type header, heat exchanger, and air-conditioning apparatus
JP6038302B2 (ja) * 2013-05-15 2016-12-07 三菱電機株式会社 積層型ヘッダー、熱交換器、及び、空気調和装置
EP2998680B1 (fr) * 2013-05-15 2018-11-07 Mitsubishi Electric Corporation Colonne stratifiée, échangeur de chaleur, et climatiseur
WO2014184916A1 (fr) * 2013-05-15 2014-11-20 三菱電機株式会社 Colonne stratifiée, échangeur de chaleur et climatiseur
WO2014205799A1 (fr) * 2013-06-28 2014-12-31 Ingersoll Rand (China) Industrial Technologies Échangeurs thermiques à microcanaux
US9184424B2 (en) 2013-07-08 2015-11-10 Lg Chem, Ltd. Battery assembly
DE112014004189T5 (de) * 2013-09-12 2016-06-02 Hanon Systems Wärmetauscher zum Kühlen eines elektrischen Bauteils
EP3051245B1 (fr) * 2013-09-26 2019-05-01 Mitsubishi Electric Corporation Collecteur de type stratifié, échangeur thermique, et appareil de climatisation
EP2857783A1 (fr) * 2013-10-04 2015-04-08 ABB Technology AG Dispositif d'échange de chaleur basé sur un tuyau à chaleur pulsée
US9257732B2 (en) 2013-10-22 2016-02-09 Lg Chem, Ltd. Battery cell assembly
CN105683701A (zh) * 2013-10-29 2016-06-15 三菱电机株式会社 换热器和空调装置
US9444124B2 (en) 2014-01-23 2016-09-13 Lg Chem, Ltd. Battery cell assembly and method for coupling a cooling fin to first and second cooling manifolds
EP3112791B1 (fr) * 2014-01-27 2018-12-19 Mitsubishi Electric Corporation Collecteur stratifié, échangeur thermique et dispositif de climatisation
DE102014203038A1 (de) * 2014-02-19 2015-08-20 MAHLE Behr GmbH & Co. KG Wärmeübertrager
DE102014204935A1 (de) * 2014-03-17 2015-10-01 Mahle International Gmbh Heizkühlmodul
US10084218B2 (en) 2014-05-09 2018-09-25 Lg Chem, Ltd. Battery pack and method of assembling the battery pack
US10770762B2 (en) 2014-05-09 2020-09-08 Lg Chem, Ltd. Battery module and method of assembling the battery module
BR112016030166B1 (pt) * 2014-06-27 2021-03-30 Titanx Holding Ab Trocador de calor
DE102014219210A1 (de) * 2014-09-22 2016-03-24 Mahle International Gmbh Wärmeübertrager
US9484559B2 (en) 2014-10-10 2016-11-01 Lg Chem, Ltd. Battery cell assembly
US9412980B2 (en) 2014-10-17 2016-08-09 Lg Chem, Ltd. Battery cell assembly
US9786894B2 (en) 2014-11-03 2017-10-10 Lg Chem, Ltd. Battery pack
US10060685B2 (en) * 2014-11-04 2018-08-28 Mitsubishi Electric Corporation Laminated header, heat exchanger, and air-conditioning apparatus
DE102014117256B8 (de) 2014-11-25 2022-01-05 Denso Automotive Deutschland Gmbh Wärmetauscher für eine Klimaanlage eines Fahrzeugs
US9627724B2 (en) 2014-12-04 2017-04-18 Lg Chem, Ltd. Battery pack having a cooling plate assembly
JP2016153718A (ja) * 2015-02-12 2016-08-25 カルソニックカンセイ株式会社 熱交換器、熱交換器の組み立て装置、及び熱交換器の組み立て方法
WO2016178278A1 (fr) * 2015-05-01 2016-11-10 三菱電機株式会社 Colonne stratifiée, échangeur de chaleur et climatiseur
US9816766B2 (en) * 2015-05-06 2017-11-14 Hamilton Sundstrand Corporation Two piece manifold
US11480398B2 (en) * 2015-05-22 2022-10-25 The Johns Hopkins University Combining complex flow manifold with three dimensional woven lattices as a thermal management unit
US9960465B2 (en) 2015-07-30 2018-05-01 Lg Chem, Ltd. Battery pack
CN106482398A (zh) * 2015-08-28 2017-03-08 杭州三花家电热管理系统有限公司 微通道换热器
US11421947B2 (en) * 2015-09-07 2022-08-23 Mitsubishi Electric Corporation Laminated header, heat exchanger, and air-conditioning apparatus
US9755198B2 (en) 2015-10-07 2017-09-05 Lg Chem, Ltd. Battery cell assembly
US10821509B2 (en) * 2016-01-20 2020-11-03 General Electric Company Additive heat exchanger mixing chambers
US20170211888A1 (en) * 2016-01-21 2017-07-27 Hamilton Sundstrand Corporation Heat exchanger with center manifold and thermal separator
US10267576B2 (en) * 2016-01-28 2019-04-23 L & M Radiator, Inc. Heat exchanger with tanks, tubes and retainer
JP6803061B2 (ja) * 2016-09-26 2020-12-23 伸和コントロールズ株式会社 熱交換器
EP3926258B1 (fr) * 2016-10-26 2022-09-14 Mitsubishi Electric Corporation Distributeur et échangeur de chaleur
US10563895B2 (en) * 2016-12-07 2020-02-18 Johnson Controls Technology Company Adjustable inlet header for heat exchanger of an HVAC system
JP6746234B2 (ja) * 2017-01-25 2020-08-26 日立ジョンソンコントロールズ空調株式会社 熱交換器、及び、空気調和機
JP6716016B2 (ja) * 2017-03-31 2020-07-01 三菱電機株式会社 熱交換器およびそれを備えた冷凍サイクル装置
JP6717256B2 (ja) 2017-05-10 2020-07-01 株式会社デンソー 冷媒蒸発器およびその製造方法
US11435149B2 (en) * 2017-07-31 2022-09-06 Gd Midea Heating & Ventilating Equipment Co., Ltd. Heat exchanger and household appliance
DE102017218818A1 (de) * 2017-10-20 2019-04-25 Mahle International Gmbh Wärmeübertrager
US11629896B2 (en) * 2018-05-01 2023-04-18 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus
CN110530180A (zh) * 2018-05-25 2019-12-03 三花控股集团有限公司 换热器
US11624565B2 (en) 2018-05-25 2023-04-11 Hangzhou Sanhua Research Institute Co., Ltd. Header box and heat exchanger
CN110530065A (zh) * 2018-05-25 2019-12-03 三花控股集团有限公司 换热器
CN109405573B (zh) * 2018-10-15 2024-01-12 李小强 换热装置
CN109316769B (zh) * 2018-10-15 2023-06-16 李强 降膜蒸发器的布膜组件
JP7097986B2 (ja) * 2018-10-29 2022-07-08 三菱電機株式会社 熱交換器及び冷凍サイクル装置
WO2020095798A1 (fr) * 2018-11-07 2020-05-14 ダイキン工業株式会社 Échangeur de chaleur et climatiseur
CN109520355A (zh) * 2018-12-21 2019-03-26 广东美的白色家电技术创新中心有限公司 换热装置及制冷设备
CN110118505A (zh) * 2019-06-19 2019-08-13 浙江银轮机械股份有限公司 集流管组件及热交换器
CN112186213B (zh) * 2019-07-02 2022-07-15 钦瑞工业股份有限公司 燃料电池堆的流道板改良结构
DE202019103964U1 (de) * 2019-07-18 2020-10-21 Akg Verwaltungsgesellschaft Mbh Wärmeaustauscher
EP4012296A4 (fr) * 2019-08-07 2022-09-21 Daikin Industries, Ltd. Échangeur de chaleur et dispositif de pompe à chaleur
JP6939869B2 (ja) * 2019-11-14 2021-09-22 ダイキン工業株式会社 熱交換器
US20230032094A1 (en) * 2019-12-12 2023-02-02 Zhejiang Sanhua Automotive Components Co., Ltd. Heat exchanger and assembly method therefor
CN112432522B (zh) * 2020-03-31 2022-09-06 杭州三花研究院有限公司 换热器
EP3907459A1 (fr) * 2020-05-04 2021-11-10 Valeo Autosystemy SP. Z.O.O. Échangeur de chaleur
CN117321373A (zh) * 2021-05-18 2023-12-29 东芝开利株式会社 热交换器以及制冷循环装置
US20230392837A1 (en) * 2022-06-03 2023-12-07 Trane International Inc. Evaporator charge management and method for controlling the same

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE69219107T2 (de) * 1992-03-31 1997-08-07 Modine Mfg Co Verdampfer

Family Cites Families (103)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1817948A (en) * 1929-11-16 1931-08-11 Carrier Construction Company I Heat exchange device
US2332336A (en) * 1941-01-16 1943-10-19 Gen Electric Elastic fluid condenser
US2950092A (en) * 1957-11-01 1960-08-23 Carrier Corp Heat exchange construction
GB991914A (en) * 1962-10-24 1965-05-12 Foster Wheeler Ltd Tube connecting members
US3416600A (en) * 1967-01-23 1968-12-17 Whirlpool Co Heat exchanger having twisted multiple passage tubes
US3703925A (en) * 1971-03-11 1972-11-28 Stewart Warner Corp Heat exchanger core
JPS5264733A (en) * 1975-11-21 1977-05-28 Hitachi Ltd Evaporator
DE3136374C2 (de) 1981-09-14 1985-05-09 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co KG, 7000 Stuttgart Kältemittelverdampfer, insbesondere für Klimaanlagen in Kraftfahrzeugen
US4502297A (en) * 1981-12-18 1985-03-05 Sueddeutsche Kuehlerfabrik Julius Fr. Behr Gmbh & Co., Kg Evaporator particularly suitable for air conditioners in automotive vehicles
DE3311579C2 (de) * 1983-03-30 1985-10-03 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co. KG, 7000 Stuttgart Wärmetauscher
JPS6124953A (ja) 1984-07-12 1986-02-03 株式会社デンソー 蒸発器
JPH0613957B2 (ja) * 1985-12-04 1994-02-23 松下冷機株式会社 熱交換器
JPS62153685A (ja) 1985-12-24 1987-07-08 Showa Alum Corp 熱交換器
US4936379A (en) * 1986-07-29 1990-06-26 Showa Aluminum Kabushiki Kaisha Condenser for use in a car cooling system
JPS63134267A (ja) 1986-11-27 1988-06-06 Alps Electric Co Ltd プリンタ
JPS63134267U (fr) * 1987-02-26 1988-09-02
EP0328414A3 (fr) * 1988-02-12 1989-09-27 Acr Heat Transfer Manufacturing Limited Echangeur de chaleur
DE3813339C2 (de) * 1988-04-21 1997-07-24 Gea Happel Klimatechnik Wärmetauscher für Kraftfahrzeuge und Verfahren zu seiner Herstellung
JPH01296087A (ja) * 1988-05-19 1989-11-29 Nippon Denso Co Ltd 熱交換用チューブ
JP2576197B2 (ja) 1988-06-29 1997-01-29 日本電装株式会社 熱交換器
JPH0258665U (fr) * 1988-10-18 1990-04-26
US5060563A (en) * 1989-05-22 1991-10-29 Rex Plant Apparatus for producing a vegetable product
US5036909A (en) * 1989-06-22 1991-08-06 General Motors Corporation Multiple serpentine tube heat exchanger
JPH0387169U (fr) * 1989-12-22 1991-09-04
JP2997816B2 (ja) * 1990-07-09 2000-01-11 昭和アルミニウム株式会社 コンデンサ
US5174373A (en) * 1990-07-13 1992-12-29 Sanden Corporation Heat exchanger
JP2997817B2 (ja) 1990-07-23 2000-01-11 昭和アルミニウム株式会社 熱交換器
US5314013A (en) * 1991-03-15 1994-05-24 Sanden Corporation Heat exchanger
US5241839A (en) 1991-04-24 1993-09-07 Modine Manufacturing Company Evaporator for a refrigerant
JP2864173B2 (ja) 1991-05-30 1999-03-03 株式会社ゼクセル 熱交換器
JPH0526592A (ja) 1991-07-19 1993-02-02 Matsushita Refrig Co Ltd 冷媒分流器とその製造方法
JPH0566073A (ja) * 1991-09-05 1993-03-19 Sanden Corp 積層型熱交換器
US5242016A (en) 1992-04-02 1993-09-07 Nartron Corporation Laminated plate header for a refrigeration system and method for making the same
US5172761A (en) * 1992-05-15 1992-12-22 General Motors Corporation Heat exchanger tank and header
JPH05346297A (ja) 1992-06-15 1993-12-27 Nippon Light Metal Co Ltd 熱交換器
JP2979926B2 (ja) * 1993-10-18 1999-11-22 株式会社日立製作所 空気調和機
JP3305460B2 (ja) * 1993-11-24 2002-07-22 昭和電工株式会社 熱交換器
EP0656517B1 (fr) * 1993-12-03 1999-02-10 Valeo Klimatechnik GmbH & Co. KG Echangeur de chaleur eau-air en aluminium pour véhicules automobiles
DE9400687U1 (de) * 1994-01-17 1995-05-18 Thermal Waerme Kaelte Klima Verdampfer für Klimaanlagen in Kraftfahrzeugen mit Mehrkammerflachrohren
JPH07305990A (ja) * 1994-05-16 1995-11-21 Sanden Corp 多管式熱交換器
US5622219A (en) 1994-10-24 1997-04-22 Modine Manufacturing Company High efficiency, small volume evaporator for a refrigerant
JP3367235B2 (ja) 1994-11-11 2003-01-14 株式会社デンソー 車両用空調装置の冷凍サイクル
JPH08254399A (ja) * 1995-01-19 1996-10-01 Zexel Corp 熱交換器
DE19515526C1 (de) * 1995-04-27 1996-05-23 Thermal Werke Beteiligungen Gm Flachrohrwärmetauscher mit mindestens zwei Fluten für Kraftfahrzeuge
DE19519740B4 (de) * 1995-06-02 2005-04-21 Mann + Hummel Gmbh Wärmetauscher
US7234511B1 (en) * 1995-06-13 2007-06-26 Philip George Lesage Modular heat exchanger having a brazed core and method for forming
FR2738905B1 (fr) * 1995-09-20 1997-12-05 Valeo Climatisation Tube d'echangeur de chaleur a canaux de circulation a contre-courant
JPH09189498A (ja) 1996-01-09 1997-07-22 Nippon Light Metal Co Ltd 熱媒体分流促進機構付ヘッダ及びその成形方法
EP0845648B1 (fr) 1996-11-27 2002-01-30 Behr GmbH & Co. Echangeur de chaleur à tubes plats, en particulier condenseur de type à serpentin
JPH10185463A (ja) 1996-12-19 1998-07-14 Sanden Corp 熱交換器
DE19719261C2 (de) * 1997-05-07 2001-06-07 Valeo Klimatech Gmbh & Co Kg Zweiflutiger Flachrohrverdampfer einer Kraftfahrzeugklimaanlage
DE19719256B4 (de) 1997-05-07 2005-08-18 Valeo Klimatechnik Gmbh & Co. Kg Mehr als zweiflutiger Flachrohrwärmetauscher für Kraftfahrzeuge mit Umlenkboden sowie Herstelungsverfahren
DE19729497A1 (de) * 1997-07-10 1999-01-14 Behr Gmbh & Co Flachrohr-Wärmeübertrager
EP0905467B1 (fr) * 1997-09-24 2003-06-18 Showa Denko K.K. Evaporateur
US5941303A (en) 1997-11-04 1999-08-24 Thermal Components Extruded manifold with multiple passages and cross-counterflow heat exchanger incorporating same
JPH11287587A (ja) 1998-04-03 1999-10-19 Denso Corp 冷媒蒸発器
DE19819247A1 (de) * 1998-04-29 1999-11-11 Valeo Klimatech Gmbh & Co Kg Wärmetauscher für Kraftfahrzeuge, insbesondere Wasser/Luft-Wärmetauscher oder Verdampfer
DE19825561A1 (de) * 1998-06-08 1999-12-09 Valeo Klimatech Gmbh & Co Kg Wärmetauscher mit verrippten Flachrohren, insbesondere Heizungswärmetauscher, Motorkühler, Verflüssiger oder Verdampfer, für Kraftfahrzeuge
DE19826881B4 (de) 1998-06-17 2008-01-03 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere Verdampfer
DE19830863A1 (de) * 1998-07-10 2000-01-13 Behr Gmbh & Co Flachrohr mit Querversatz-Umkehrbogenabschnitt und damit aufgebauter Wärmeübertrager
DE19833845A1 (de) * 1998-07-28 2000-02-03 Behr Gmbh & Co Wärmeübertrager-Rohrblock und dafür verwendbares Mehrkammer-Flachrohr
JP2000304472A (ja) 1999-04-23 2000-11-02 Calsonic Kansei Corp 冷凍サイクル用熱交換器
FR2793016B1 (fr) * 1999-04-30 2001-09-07 Valeo Climatisation Boite collectrice allongee pour echangeur de chaleur resistant aux fortes pressions internes
EP1065453B1 (fr) * 1999-07-02 2004-05-06 Denso Corporation Evaporateur de réfrigérant avec distribution de réfrigérant
JP2001027484A (ja) 1999-07-15 2001-01-30 Zexel Valeo Climate Control Corp サーペンタイン型熱交換器
DE19933913C2 (de) * 1999-07-20 2003-07-17 Valeo Klimatechnik Gmbh Verdampfer einer Kraftfahrzeugklimaanlage
JP2001059694A (ja) * 1999-08-20 2001-03-06 Zexel Valeo Climate Control Corp 熱交換器
US6185957B1 (en) * 1999-09-07 2001-02-13 Modine Manufacturing Company Combined evaporator/accumulator/suctionline heat exchanger
FR2803378B1 (fr) * 1999-12-29 2004-03-19 Valeo Climatisation Echangeur de chaleur a tubes a plusieurs canaux, en particulier pour vehicule automobile
JP2001194087A (ja) 2000-01-13 2001-07-17 Zexel Valeo Climate Control Corp 熱交換器
JP2001248995A (ja) 2000-03-03 2001-09-14 Zexel Valeo Climate Control Corp 熱交換器
JP2001330391A (ja) 2000-05-19 2001-11-30 Zexel Valeo Climate Control Corp 熱交換器
JP4686062B2 (ja) 2000-06-26 2011-05-18 昭和電工株式会社 エバポレータ
US6536517B2 (en) 2000-06-26 2003-03-25 Showa Denko K.K. Evaporator
DE10049256A1 (de) 2000-10-05 2002-04-11 Behr Gmbh & Co Serpentinen-Wärmeübertrager
DE10056074B4 (de) 2000-11-07 2017-03-23 Mahle International Gmbh Wärmeübertrager
JP3647375B2 (ja) 2001-01-09 2005-05-11 日産自動車株式会社 熱交換器
DE10105202A1 (de) * 2001-01-31 2002-08-01 Behr Gmbh & Co Wärmeübertrager-Rohrblock mit mehreren geschlitzten Sammelrohren
DE10123247B4 (de) 2001-05-12 2006-02-09 Hubert Herrmann Schutzhelm
TW552382B (en) * 2001-06-18 2003-09-11 Showa Dendo Kk Evaporator, manufacturing method of the same, header for evaporator and refrigeration system
EP1300645A3 (fr) * 2001-10-02 2008-09-03 Behr GmbH & Co. KG Procédé de fabrication d'une structure de connection de tubes plats pour échangeur de chaleur
EP1321734A1 (fr) * 2001-10-02 2003-06-25 Behr GmbH & Co. KG Echangeur de chaleur à tubes plats et procédé de fabrication
EP1300644A3 (fr) * 2001-10-02 2003-05-14 Behr GmbH & Co. KG Echangeur de chaleur et procédé de fabrication associé
DE50214246D1 (de) 2001-12-21 2010-04-08 Behr Gmbh & Co Kg Wärmeübertrager, insbesondere für ein kraftfahrzeug
JP3960233B2 (ja) * 2002-04-03 2007-08-15 株式会社デンソー 熱交換器
DE102005044291A1 (de) * 2005-09-16 2007-03-29 Behr Industry Gmbh & Co. Kg Stapelscheiben-Wärmeübertrager, insbesondere Ladeluftkühler
KR100645734B1 (ko) * 2005-12-14 2006-11-15 주식회사 경동나비엔 난방/온수 겸용 콘덴싱 보일러의 열교환기
JP5351386B2 (ja) * 2006-05-17 2013-11-27 カルソニックカンセイ株式会社 熱交換器の配管コネクタ
US8371366B2 (en) * 2006-10-03 2013-02-12 Showa Denko K.K. Heat exchanger
DK2079973T3 (da) * 2006-10-13 2012-08-13 Carrier Corp Varmeveksler med mange strømningsbaner, og hvor der findes tilbageløbs-forgreningsrør med indskudte fordelingsorganer
US8191615B2 (en) * 2006-11-24 2012-06-05 Dana Canada Corporation Linked heat exchangers having three fluids
DE102007024630A1 (de) * 2007-05-24 2008-11-27 Behr Gmbh & Co. Kg Wärmetauscher, insbesondere Ladeluftkühler oder Abgaskühler für eine Brennkraftmaschine eines Kraftfahrzeuges und dessen Herstellungsverfahren
JP5114771B2 (ja) * 2007-05-29 2013-01-09 株式会社ケーヒン・サーマル・テクノロジー 熱交換器
PL2014892T3 (pl) * 2007-07-11 2011-02-28 Joao De Deus & Filhos S A Zestaw wymiennika ciepła
CN101874192B (zh) * 2007-07-23 2012-04-18 东京滤器株式会社 板层积式热交换器
JP5046771B2 (ja) * 2007-07-27 2012-10-10 三菱重工業株式会社 冷媒蒸発器
GB0715979D0 (en) * 2007-08-15 2007-09-26 Rolls Royce Plc Heat exchanger
US8353330B2 (en) * 2007-11-02 2013-01-15 Halla Climate Control Corp. Heat exchanger
US8210246B2 (en) * 2008-03-11 2012-07-03 Delphi Technologies, Inc. High performance three-fluid vehicle heater
US8322407B2 (en) * 2008-04-29 2012-12-04 Honda Motor Co., Ltd. Heat exchanger with pressure reduction
JP4645681B2 (ja) * 2008-05-19 2011-03-09 株式会社デンソー 蒸発器ユニット
JP5142109B2 (ja) * 2008-09-29 2013-02-13 株式会社ケーヒン・サーマル・テクノロジー エバポレータ
US8408284B2 (en) * 2011-05-05 2013-04-02 Delphi Technologies, Inc. Heat exchanger assembly

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE69219107T2 (de) * 1992-03-31 1997-08-07 Modine Mfg Co Verdampfer

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WO2003054467A1 (fr) 2003-07-03
KR20040063952A (ko) 2004-07-14
EP1459027B1 (fr) 2008-10-29
US7318470B2 (en) 2008-01-15
US7481266B2 (en) 2009-01-27
EP1459025B1 (fr) 2010-03-17
EP1459027A1 (fr) 2004-09-22
US7650935B2 (en) 2010-01-26
DE50214246D1 (de) 2010-04-08
CN1620590A (zh) 2005-05-25
JP4121085B2 (ja) 2008-07-16
JP4331611B2 (ja) 2009-09-16
CA2471164A1 (fr) 2003-07-03
DE10260030A1 (de) 2003-07-03
ATE461407T1 (de) 2010-04-15
CN100368752C (zh) 2008-02-13
US20050039901A1 (en) 2005-02-24
BR0215235A (pt) 2004-11-16
DE10260107A1 (de) 2003-10-02
WO2003054465A1 (fr) 2003-07-03
US20090126920A1 (en) 2009-05-21
US20050006073A1 (en) 2005-01-13
EP1459026B1 (fr) 2010-02-24
JP2008180503A (ja) 2008-08-07
JP2005513403A (ja) 2005-05-12
AU2002363887A1 (en) 2003-07-09
AU2002358769A1 (en) 2003-07-09
EP2026028A3 (fr) 2012-06-20
DE50214296D1 (de) 2010-04-29
CA2471164C (fr) 2009-10-06
US8590607B2 (en) 2013-11-26
BR0215231A (pt) 2004-11-16
ATE412863T1 (de) 2008-11-15
WO2003054466A1 (fr) 2003-07-03
JP4473321B2 (ja) 2010-06-02
CN100342196C (zh) 2007-10-10
ES2316640T3 (es) 2009-04-16
EP1459026A1 (fr) 2004-09-22
BRPI0215085A2 (pt) 2016-06-28
AU2002360056A1 (en) 2003-07-09
DE10260029A1 (de) 2004-02-05
MXPA04006151A (es) 2004-11-01
EP2026028A2 (fr) 2009-02-18
JP2005513402A (ja) 2005-05-12
JP2005513401A (ja) 2005-05-12
CN1620589A (zh) 2005-05-25
ATE458975T1 (de) 2010-03-15
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DE50212972D1 (de) 2008-12-11
US20050103486A1 (en) 2005-05-19

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