WO2005075913A1 - Dispositif d'echange de chaleur et procede de fabrication d'un tel dispositif - Google Patents

Dispositif d'echange de chaleur et procede de fabrication d'un tel dispositif Download PDF

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Publication number
WO2005075913A1
WO2005075913A1 PCT/EP2005/001032 EP2005001032W WO2005075913A1 WO 2005075913 A1 WO2005075913 A1 WO 2005075913A1 EP 2005001032 W EP2005001032 W EP 2005001032W WO 2005075913 A1 WO2005075913 A1 WO 2005075913A1
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WO
WIPO (PCT)
Prior art keywords
flow
flat tube
approximately
section
flow device
Prior art date
Application number
PCT/EP2005/001032
Other languages
German (de)
English (en)
Inventor
Gerrit WÖLK
Original Assignee
Behr Gmbh & Co. Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Behr Gmbh & Co. Kg filed Critical Behr Gmbh & Co. Kg
Priority to EP05707146A priority Critical patent/EP1716377A1/fr
Priority to US10/588,381 priority patent/US20080035305A1/en
Publication of WO2005075913A1 publication Critical patent/WO2005075913A1/fr

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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
    • 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
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making

Definitions

  • Heat exchange device and method of making such a device
  • the present invention relates to a heat exchanger for a high-pressure cooling circuit, in particular to a high-pressure cooler, in particular a high-pressure gas cooler, and / or high-pressure auxiliary heater.
  • a high-pressure cooling circuit is to be understood as a cooling circuit in which a fluid flowing through the cooling circuit, at least in sections, under an operating pressure of approximately 110 bar to 130 bar, in particular approximately 125 bar. and / or which cooling circuit must be designed for burst pressures in a range from 270 bar to 360 bar according to applicable safety regulations.
  • high-pressure heat exchangers in high-pressure cooling circuits, hereinafter referred to as high-pressure heat exchangers for short, are known from the prior art.
  • FIG. 10 shows a section of such a, in this case double-row, high-pressure heat exchanger or double-row high-pressure gas cooler from the prior art.
  • tubes 1000 are arranged in two parallel planes.
  • the tubes arranged in one plane are also aligned parallel to each other.
  • the tubes 1000 have a flat tube-like shape which has a long side 1002 in cross section 1001 and a side 1003 which is considerably shorter than this long side 1002.
  • a coolant flows through the (flat) tube 1000 in a longitudinal direction 1004, for which purpose a plurality of flow channels 1005 are generally provided in the flat tube 1000, essentially parallel to the longitudinal direction 1004 or to a longitudinal axis of the flat tube 1000.
  • the coolant is at least in this section under an operating pressure of approximately 125 bar.
  • the high-pressure heat exchanger or high-pressure gas cooler is designed for burst pressures in the range from 270 bar to 360 bar.
  • the flat tube 1000 In end sections 1009 at both ends 1008 of the flat tube 1000, the flat tube 1000 according to the prior art each has a continuous twist or twist (torsion) about its longitudinal axis up to 90 °.
  • Both ends 1007 of the flat tube 1000 in the prior art which are rotated by 90 ° in this way are connected to collection and / or distribution devices 1008 in the manner of hollow bodies in a liquid-tight and / or gas-tight manner.
  • connection with one another is understood to mean a connection in such a way that a liquid and / or gaseous fluid, such as, for example, the coolant, can flow in a liquid-tight and / or gas-tight manner through this connection.
  • a liquid and / or gaseous fluid such as, for example, the coolant
  • the long side 1002 of the cross section 1001 of the flat tube 1000 runs essentially parallel to a longitudinal axis (main direction of expansion) of the hollow body-like collecting and / or distributing device 1008. Due to the rotation of the flat tube ends 1007, measurement of the hollow body-like collection and / or distribution device 1008, ie an inner cross section of the hollow body-like collection and / or distribution device 1008, and thus a material thickness can be reduced. As a result, the bursting pressures required in accordance with the safety regulations and the prevailing operating pressures with reduced material thicknesses and material expenditures can be achieved for the hollow body-like collection and / or distribution device 1008.
  • the rotation of the flat tube ends 1007 disadvantageously reduces a surface of the flat tube 1000 that can be used for heat exchange, in particular for cooling, and thus an end face of the high-pressure heat exchanger that can be used for cooling.
  • the twisting of the flat tube ends 1007 also disadvantageously limits a transverse division of a heat exchanger matrix of the gas cooler.
  • the twisting of the flat tube ends 1007 also increases the manufacturing costs that are required to produce the flat tubes.
  • the object of the present invention is therefore to provide a high-pressure heat exchanger which is less expensive to produce than the prior art and less restrictive in its geometry even with small material thicknesses. This is achieved according to the invention by the device for exchanging heat and by the method for producing a device for exchanging heat with the features according to the respective independent patent claim.
  • the inventive device for exchanging heat has at least one throughflow device and at least one collection and / or distribution device connected to the at least one throughflow device at a connection point.
  • a connection is understood to mean a connection such that a liquid and / or gaseous fluid, such as a coolant, in particular carbon dioxide, is liquid and / or gas-tight under high pressure, for example an operating pressure of approximately 110 bar to 130 bar, especially of approximately 125 bar.
  • a liquid and / or gaseous fluid such as a coolant, in particular carbon dioxide
  • the flow device according to the invention has a predetermined length (flow device length) and a flat tube-like cross section.
  • a flat tube-like cross section is understood to mean a cross-sectional shape which has a long side (depth) and a side which is considerably shorter than this long side (height).
  • a fluid under a high pressure for example an operating pressure of approximately 110 bar to 130 bar, in particular approximately 125 bar, can flow through the flow device and the collection and / or distribution device.
  • the flow device according to the invention has a straight course along the entire flow device length along a longitudinal axis of the flow device.
  • a straight course along the longitudinal axis is understood to mean a course in which the throughflow device or the flat tube-like cross section of the throughflow device is neither twisted, twisted or twisted about the longitudinal axis nor does the longitudinal axis itself have a curved or curved course.
  • the long side of the flat tube-like cross section of the flow device hereinafter also referred to as the (flow device) depth, has a length of approximately 5 mm to 6.1 mm, in particular of 5 mm to 5.9 mm.
  • the long side of the flat tube-like cross section of the flow device has an angle of approximately 90 ° with respect to a main direction of expansion of the collection and / or distribution device.
  • the device according to the invention for heat exchange or the flow device according to the invention is based on the non-trivial finding that with cross-sectional depths of the flow device of approximately 5 mm to 6.1 mm, in particular of 5 mm to 5.9 mm, cross-section twists at the ends of the flow device are dispensed with can.
  • the now straight flow device is connected to a collection and / or distribution device in such a way that the long side of the flat tube-like cross section of the flow device has an angle of approximately 90 ° with respect to the main direction of expansion of the collection and / or distribution device, with the device according to the invention achieves or achieves bursting pressures above the required 270 bar even with reduced material thicknesses and / or it can also be operated with reduced material thicknesses in a high pressure range.
  • a connection is made at a connection point between at least one flow device and at least one collection and / or distribution device, which connection is taken from a group, which soldered, welded or adhesive connections contains.
  • the at least one throughflow device is preferably inserted and / or soldered into the at least one collecting and / or distributing device.
  • a connection is understood to mean a connection in such a way that a liquid and / or gaseous fluid, such as a coolant, can flow liquid-tight and / or gas-tight under high pressure, such as an operating pressure of approximately 125 bar, through this connection.
  • a liquid and / or gaseous fluid such as a coolant
  • the flow device and the collection and / or distribution device have the specifications mentioned above.
  • the straight flow device according to the invention can thus be used to achieve a larger, finned end surface which is relevant for heat exchange than in a comparable, twisted flow device.
  • the invention results in a lower use of material and consequently lower material costs in comparison to conventional multi-row heat exchangers.
  • Handling of the straight flow-through devices in the manufacture of high-pressure heat exchangers, in particular high-pressure coolers and / or high-pressure auxiliary heaters, and there in particular in the case of a pipe feed for a cassette, is also simplified.
  • the flow device for example a flat tube, has a height or cross-sectional height of approximately 1 mm to 2 mm and / or a length of approximately 200 mm to 800 mm. Below the height is the one above, opposite the long side, i.e. to understand the depth, much shorter side of the flat tube-like cross section.
  • An internal passage height of a channel within the flat tube is preferably between 0.4 mm and 1 mm.
  • the flow-through device has at least one inner flow channel essentially parallel to the longitudinal axis of the flow-through device, preferably a plurality of inner flow channels essentially parallel to the longitudinal axis.
  • the at least one flow channel can have a shape that is essentially circular or elliptical, polygonal or rectangular, or has mixed forms thereof, for example rectangular with more or less rounded corners.
  • the at least one flow channel is flowed through at least in sections by a medium (fluid), such as a coolant, which is capable of flow, at an operating pressure of approximately 125 bar.
  • flowable media or fluids are understood to mean liquid and / or gaseous media of any viscosity, such as, in particular, but not exclusively, oils, liquids, in particular high heat of vaporization, water, air or gases, for example carbon dioxide, and refrigerants which evaporate or condense can.
  • the flowable media can also contain additives, for example to inhibit corrosion.
  • the collection and / or distribution device can provide a recess for connecting the flow device.
  • a cross section of the recess is adapted to the flat tube-like cross section of the flow device.
  • the recess can have additional shapes, which serve, for example, as an insertion bevel for flat tubes.
  • the collection and / or distribution device has a tubular cross section.
  • an inner diameter of the tubular cross section of the collection and / or distribution device is approximately equal to the (cross section) depth of the flow device.
  • the device according to the invention is particularly suitable for a high-pressure heat exchanger, in particular a high-pressure cooler, in particular a high-pressure gas cooler, and / or a high-pressure auxiliary heater.
  • Such a heat exchanger has a plurality, as a rule a multiplicity, of flow devices according to the invention, such as flat tubes, which are arranged in at least one plane, essentially parallel to one another and at a predeterminable distance.
  • Ribs or corrugated ribs preferably in series, can be arranged between two adjacent flow devices.
  • a corrugated fin height can be approximately 2 mm to 8 mm.
  • the corrugated fins of one plane can also be separate corrugated fins.
  • corrugated fin that is continuous over several levels can be provided.
  • the plurality of flow devices are furthermore connected at least at one end at a connection point to a collection and / or distribution device in an essentially gas-tight and / or liquid-tight manner.
  • the plurality of flow-through devices are preferably arranged in two levels, the ends of the flow-through devices being connected in one plane to a collecting and / or distributing device.
  • the flow devices of two adjacent levels can also be offset from one another.
  • a cooler and / or an auxiliary heater according to the above heat exchanger are each arranged between two adjacent flow devices, for example between adjacent flat tubes.
  • a coolant under high pressure flows through the plurality of flat tubes, a heat exchange between the coolant and an air surrounding the plurality of flat tubes being promoted.
  • a device for air conditioning an air conducted into a vehicle interior of a motor vehicle has at least one compressor, a heater and / or evaporator according to the above preferred embodiment, an expansion valve and a cooler according to the above embodiment.
  • the compressor and the expansion valve are known from St. It is also known that in high-pressure cooling circuits, the coolant is under high pressure at least in a section of the cooling circuit which extends from an outlet of the compressor via the high-pressure heat exchanger to the expansion valve.
  • FIG. 1 is a partial view of an inventive device for exchanging heat, a heat exchanger of a gas cooler.
  • FIG. 2 is a diagram which shows a relationship between the geometric dimensions of components of a device for exchanging heat, a heat exchanger of a gas cooler, according to the invention;
  • FIG. 3 shows a graph with a relationship between a block depth of a two-row gas cooler with flat tubes according to the invention and a flat tube depth of a tube according to the invention for two burst pressures;
  • FIG. 4 shows a graph with a relationship between a flat tube depth of a tube according to the invention and a block depth of a two-row gas cooler with flat tubes according to the invention for two burst pressures;
  • Fig. 5 is a graphical representation with a relationship between an air flow velocity and a gas cooler output for a gas cooler with flat tubes according to the invention and for a comparable Gas cooler with twisted flat tubes most gas cooler matrix;
  • FIG. 6 shows a graphical representation with a relationship between an air flow velocity and a gas cooler output for a gas cooler with flat tubes according to the invention and for a comparable gas cooler with twisted flat tubes according to a second gas cooler matrix;
  • FIG. 7 shows a graph with a relationship between a flat tube width and a weight of a gas cooler matrix for different gas cooler matrices
  • FIG. 8 shows a graphical representation with a relationship between an air flow velocity and a weight-related gas cooler output for a gas cooler with flat tubes according to the invention and for a comparable gas cooler with twisted flat tubes according to a first gas cooler matrix;
  • FIG. 9 shows a graphical representation with a relationship between an air flow velocity and a weight-related gas cooler output for a gas cooler with flat tubes according to the invention and for a comparable gas cooler with twisted flat tubes according to a second gas cooler matrix;
  • Fig. 10 is a partial view of a conventional heat exchanger of a gas cooler with several conventional twisted flat tubes according to the prior art.
  • a block depth of the two-row gas cooler 110 is approximately 16 mm.
  • reference numeral 100 relates in each case to a (flat) tube of the two-row gas cooler 110 according to the invention.
  • the flat tube 100 has a tube length of approximately 670 mm and a flat tube-like cross section 101 with a long side, a flat tube depth of 5.8 mm and a side which is considerably shorter than this long side and a flat tube width of 1.5 mm.
  • the flat pipe 100 has a straight pipe run along the entire pipe length along a pipe longitudinal axis.
  • the tubes 100 are arranged in two planes 102, 103 which are parallel to one another.
  • the flat tubes 100 are also arranged parallel to one another at a distance of approximately 2 mm to 10 mm, preferably between 4 mm and 8 mm and in particular of approximately 6 mm.
  • Corrugated fins 106 are arranged along the pipe length or in the longitudinal direction 104 of the pipes 100 between two parallel flat tubes 100 arranged in parallel in a plane 102, 103.
  • the two-row gas cooler 110 has a total fin density of 75 fins / dm.
  • a preferred range for the rib density is from 65 to 85 ribs / dm.
  • the flat tubes 100 are flowed through by a coolant under high pressure in the longitudinal direction 104, for which purpose a plurality of flow channels 105 are provided in the flat tube 100, essentially parallel to the longitudinal direction 104 or the longitudinal axis of the flat tube 100.
  • a pair of header tanks 120 having two header tubes 123, 124, are connected to each flat tube end 121 at a designated connection point to extend in one direction, a main direction of expansion, perpendicular to the longitudinal direction 104 of each tube 100.
  • the coolant also flows through these under high pressure.
  • the flat tube-like cross section 101 or the long side of the flat tube-like cross section 101 of the tube 100 has a predetermined angle of approximately 90 ° at the respective connection point with respect to the main direction of expansion of the collecting tanks 120.
  • a recess for the connection of the flat tube 100 is provided on the part of the collecting tanks 120.
  • a cross section of the recess is adapted to the cross section 101 of the flat tube 100.
  • the recess has an additional shape, an insertion bevel for the flat tubes 100.
  • connection with one another is understood to mean a connection in such a way that a liquid and / or gaseous fluid, such as the coolant in this case, can flow liquid and / or gas-tight through this connection.
  • the collecting tanks 120 and the collecting pipes 123, 1124 each have a tubular cross section 122, an inner diameter 200 of the tubular cross section 122 being approximately equal to the pipe depth of the flat pipe 100.
  • a collecting pipe wall thickness 201 is dependent on a required burst pressure.
  • Fig. 2 shows geometric relationships for determining the block depth.
  • T (Ges) 2 * T (FI) + 2 xd (wall, manifold) + b (gap),
  • T denotes the flat tube depth
  • d wall, manifold
  • d gap
  • FIG. 3 shows a graphic representation with a relationship between a block depth of a two-row gas cooler with flat tubes according to the invention and a flat tube depth of a flat tube according to the invention for two bursting pressures, namely 270 bar and 360 bar.
  • the flat tube depth T (Fl) ⁇ 6 mm for straight flat tubes in double-row high-pressure gas coolers with a block depth of 16 mm is therefore sufficient for a bursting pressure of 270 bar.
  • T (FL) reduces a contact area between a corrugated fin and the flat tube at a constant block depth. For this reason, one should
  • Block depth of 16 mm the individual flat tube depth also not less than be about 5 mm. The same must also be taken into account for other companies.
  • Fig. 3 also shows that with a block depth of 14 mm for double-row gas coolers, the flat tube depth T (FI) ⁇ 5.20 mm is sufficient for a burst pressure of 270 bar with straight flat tubes.
  • FIG. 4 shows a graph with a relationship between a flat tube depth of a tube according to the invention and a block depth of a two-row gas cooler with flat tubes according to the invention for two bursting pressures, namely 270 bar and 360 bar.
  • Fig. 4 shows, for example, that with a burst pressure of 270 bar (360 bar) and a block depth of 15 mm, a flat tube depth of approximately 5.2 mm (5.6 mm) is sufficient for straight flat tubes.
  • Fig. 5 and Fig. 6 show a gas cooler performance over an air flow velocity under given boundary conditions.
  • Gas cooler 1 has conventional flat tubes with twisted flat tube ends and with a flat tube depth of 7 mm.
  • Gas cooler 2 has the flat tubes according to the invention with a straight tube run and with a flat tube depth of 5.8 mm.
  • the gas cooler 2 Due to the larger end face of the gas cooler 2, the disadvantage of the smaller flat tube depth and thus reduced contact area between the corrugated fin and the flat tube can be approximately equalized.
  • the gas cooler 2 has a nem same mass flow on a higher refrigerant side.
  • Gas cooler 1 has conventional flat tubes with twisted flat tube ends and with a flat tube depth of 7 mm.
  • Gas cooler 2 has the flat pipes according to the invention with a straight pipe run and with a flat pipe depth of 5.8 mm.
  • the gas cooler 2 Due to the larger end face of the gas cooler 2, the disadvantage of the smaller flat tube depth and thus reduced contact area between the corrugated fin and the flat tube can be approximately equalized.
  • the gas cooler 2 has a higher refrigerant-side pressure drop for the same mass flow.
  • FIG. 7 shows a graphical representation with a relationship between a flat tube width and a weight of a gas cooler matrix for different gas cooler matrices.
  • Fig. 7 shows a significantly lower weight for gas coolers according to the flat tube depth T (FI) ⁇ 6 mm.
  • Fig. 8 and Fig. 9 show a weight-related gas cooler performance, which is obtained by dividing the gas cooler performance by the weight of the heat exchanger matrix, over the air inflow velocity under given boundary conditions.
  • the gas cooler performance shown relates to the gas coolers already discussed in Fig. 5 and Fig. 6.
  • Fig. 8 and Fig. 9 show that the weight-related gas cooler output for the two gas coolers with the flat tubes according to the invention with a flat tube depth T (FI) ⁇ 6.1 mm is significantly greater compared to the two gas coolers with conventional flat tubes with a flat tube depth of 7 mm.
  • the present invention can be applied in particular to coolers or auxiliary heaters of a high-pressure cooling circuit.
  • An embodiment of the respective heat exchanger matrix is not limited to the geometries described above. It can be chosen arbitrarily within the scope of the inventive flat tube geometry and the burst pressure requirements.

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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)

Abstract

Le dispositif d'échange de chaleur selon la présente invention possède un dispositif d'écoulement et un dispositif de collecte et / ou répartition relié au dispositif d'écoulement au niveau d'un site de raccord. Le dispositif d'écoulement possède une longueur prédéterminée ainsi qu'une section transversale de type à tuyaux plats dans lesquels peut circuler un fluide se trouvant sous haute pression, par exemple sous une pression de fonctionnement d'environ 125 bars. Le dispositif d'écoulement présente un tracé linéaire sur toute la longueur dudit dispositif d'écoulement le long d'un axe longitudinal de ce dispositif d'écoulement. Le côté long de la section transversale de type à tuyaux plats du dispositif d'écoulement possède une longueur d'environ 5 mm à 6,1 mm. Au niveau du site de raccord, le côté long de la section transversale de type à tuyaux plats du dispositif d'écoulement présente un angle d'environ 90° par rapport à un sens d'extension principal du dispositif de collecte et / ou de répartition.
PCT/EP2005/001032 2004-02-04 2005-02-02 Dispositif d'echange de chaleur et procede de fabrication d'un tel dispositif WO2005075913A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP05707146A EP1716377A1 (fr) 2004-02-04 2005-02-02 Dispositif d'echange de chaleur et procede de fabrication d'un tel dispositif
US10/588,381 US20080035305A1 (en) 2004-02-04 2005-02-02 Device For Heat Exchange And Method For Producing One Such Device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004005621A DE102004005621A1 (de) 2004-02-04 2004-02-04 Vorrichtung zum Austausch von Wärme und Verfahren zur Herstellung einer derartigen Vorrichtung
DE102004005621.8 2004-02-04

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Publication Number Publication Date
WO2005075913A1 true WO2005075913A1 (fr) 2005-08-18

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US (1) US20080035305A1 (fr)
EP (1) EP1716377A1 (fr)
DE (1) DE102004005621A1 (fr)
WO (1) WO2005075913A1 (fr)

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DE102008055624A1 (de) 2007-12-10 2009-06-18 Behr Gmbh & Co. Kg Wärmeträger, insbesondere Heizkörper für Kraftfahrzeuge
JP6547695B2 (ja) * 2016-06-21 2019-07-24 株式会社デンソー 冷凍サイクル装置
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DE102018107639B3 (de) 2018-03-29 2019-08-08 Bundesrepublik Deutschland, Vertreten Durch Den Bundesminister Für Wirtschaft Und Energie, Dieser Vertreten Durch Den Präsidenten Der Bundesanstalt Für Materialforschung Und -Prüfung (Bam) Lastverteilungsvorrichtung und Verfahren zum synchronen Aufbringen einer definierten Andruckkraft auf eine Vielzahl von Proben, sowie Kit zum Belasten einer Vielzahl von Proben mit einer definierten Andruckkraft

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US20080035305A1 (en) 2008-02-14
EP1716377A1 (fr) 2006-11-02

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