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WO2010000311A1 - Bloc échangeur thermique et procédé de fabrication d'un bloc échangeur thermique - Google Patents

Bloc échangeur thermique et procédé de fabrication d'un bloc échangeur thermique Download PDF

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Publication number
WO2010000311A1
WO2010000311A1 PCT/EP2008/058451 EP2008058451W WO2010000311A1 WO 2010000311 A1 WO2010000311 A1 WO 2010000311A1 EP 2008058451 W EP2008058451 W EP 2008058451W WO 2010000311 A1 WO2010000311 A1 WO 2010000311A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
segment
outlet
inlet
exchanger block
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.)
Ceased
Application number
PCT/EP2008/058451
Other languages
German (de)
English (en)
Inventor
Tamacz Niepalla
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
A-Heat Allied Heat Exchange Technology AG Germany
Original Assignee
A-Heat Allied Heat Exchange Technology AG Germany
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 A-Heat Allied Heat Exchange Technology AG Germany filed Critical A-Heat Allied Heat Exchange Technology AG Germany
Priority to PCT/EP2008/058451 priority Critical patent/WO2010000311A1/fr
Publication of WO2010000311A1 publication Critical patent/WO2010000311A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F28F9/0243—Header boxes having a 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
    • F28D1/05383—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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2225/00—Reinforcing means
    • F28F2225/08—Reinforcing means for header boxes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
    • F28F2260/02—Heat exchangers or heat exchange elements having special size, e.g. microstructures having microchannels

Definitions

  • Heat exchanger block and a method of manufacturing a heat exchanger block
  • the invention relates to a heat exchanger block and to a method for producing a heat exchanger block according to the preamble of the independent claims 1 and 14.
  • Heat exchangers are used in refrigerators, e.g. in ordinary
  • the laminated heat exchangers serve, like all types of heat exchangers, to transfer heat between two media, for example, but not only, to transfer from a cooling medium to air or vice versa, as is known, for example, from a classic household refrigerator in which heat is released to the ambient air via the heat exchanger for generating a cooling capacity in the interior of the refrigerator.
  • the ambient medium outside the heat exchanger e.g. Water, oil or often simply the ambient air, which absorbs heat or transfers heat to the heat exchanger, for example, is either cooled or heated accordingly.
  • the second medium may e.g. be a liquid refrigerant or heat transfer or a vaporizing or condensing refrigerant.
  • the surrounding medium e.g. the air
  • the coolant that circulates in the heat exchanger system. This is compensated by greatly different heat transfer surfaces for the two media:
  • the medium with the high heat transfer coefficient flows in the tube, which on the outside by thin sheets (ribs, fins) has a greatly enlarged surface at which the heat transfer, for. takes place with the air.
  • the lamellar spacing is chosen differently for different applications. Purely thermodynamically, however, it should be as small as possible, but not so small that the air-side pressure loss is too large. An economic optimum is about 2 mm, which is a typical value for condenser and recooler.
  • the efficiency is essentially determined by the fact that the heat that is transferred between the fin surface and the air, must be transmitted through heat conduction through the fins to the pipe. This heat transfer is all the more effective, the higher the conductivity or the thickness of the lamella, but also the smaller the distance between the tubes. This is called the lamella efficiency.
  • a lamellar material is therefore nowadays predominantly aluminum used, which has a high thermal conductivity (about 220 W / mK) to economic conditions.
  • the pipe pitch should be as small as possible, but this leads to the problem that you need many pipes.
  • Many pipes mean high costs because the pipes (usually made of copper) are considerably more expensive than the thin aluminum fins. This material cost could be reduced by reducing the tube diameter and wall thickness, i.
  • minichannel or microchannel heat exchangers have been developed, which are manufactured according to a completely different process and almost correspond to the ideal of a laminated heat exchanger: many small tubes with small spacings.
  • microchannel heat exchanger uses extruded aluminum sections which have very many small channels with a diameter of, for example, about 1 mm.
  • FIG. 1 two known per se heat exchanger 2 in the form of extruded profiles 2 are shown schematically.
  • the two extruded profiles 2 of Fig. 1 are preferably in thermal contact with a corrugated cooling fin 200, so that the heating means 3, which is conveyed through the microchannels 21, its heat with the Transportfluidum 201, preferably air 201, for example, with a non shown fan in the direction of the arrows 201 is transported through the heat exchanger block 1, can exchange better.
  • extruded profiles may e.g. be made easily and in a variety of forms from a variety of materials in suitable extrusion.
  • other methods of making microchannel heat exchangers are known, such as e.g. the
  • Microchannel heat exchangers have become established in mobile use during the 90s.
  • the low weight, the small block depth and the limited dimensions that are required here are the ideal conditions for this.
  • Car coolers and condensers and evaporators for car air conditioning systems are today almost exclusively realized with mini-channel heat exchangers.
  • the known heat exchanger blocks are thus composed of a plurality of individual MicroChannel heat exchangers, ie from the extruded profiles shown in Fig. 1, wherein each inlet side of the heat exchanger with an inlet segment and an outlet side of the heat exchanger with an outlet segment is pressure-resistant.
  • FIGS. 2 and 3 schematically show a known heat exchanger block 1 'in the non-operating state.
  • FIG. 2 for example, a known heat exchanger block 1 'is partially shown schematically in longitudinal section.
  • FIG. 3 shows a section along the section line I-I according to FIG. 2.
  • the solder joints 13 'on which the microchannel heat exchanger 2' is soldered to the microchannels 21 'at the inlet segment 6' can be clearly seen.
  • the inlet and outlet segments have diameters of 30-60mm, lengths of up to 4m or more, and the MicroChannel heat exchangers are typically spaced apart, for example, from 6mm to 20mm. It is understood that in individual cases, the geometric dimensions of a special heat exchanger block can also deviate significantly from the above values up or down.
  • solder joints 13 'between the heat exchangers 2' per se and the inlet segments 6 'and the outlet segments which are often also referred to as inlet header 6' or outlet header, or simply referred to as headers, do in the known
  • Heat exchanger blocks 1 'always problems This is because the heating means 3 'in the heat exchanger block 1' under relatively high pressures P ', often in the range of 10 bar to 60 bar, or even under even higher working pressures P', the plant often a test pressure of well over 100 bar for safety reasons. Typical working values for the operating pressure are for example 42 bar. A typical test pressure for such a system can be 120 bar, for example.
  • FIG. 4 shows the heat exchanger block 1 'of FIG. 2 in the operating state. Inside the heat exchanger block 1 now prevails the high operating pressure P ', which causes the inlet segment 6' with respect to the heat exchanger 2 'bends, causing enormous stresses at the solder joints 13'.
  • the dashed line shows the heat exchanger block 1 for comparison in the non-operating state according to FIG. 2. It can clearly be seen how much the inlet segment 6 'is bent below the operating pressure P' in comparison with the non-operating state.
  • the object of the invention is therefore to provide an improved heat exchanger block which overcomes the problems known from the prior art.
  • a heat exchanger block should be made available in which the high operating pressures do not lead to the bending loads known from the prior art.
  • a new heat exchanger block is to be proposed, which can be operated safely even under high operating pressure, allows long maintenance intervals and has a much longer service life than the heat exchanger blocks.
  • the dependent claims relate to particularly advantageous embodiments of the invention.
  • the invention thus relates to a heat exchanger block comprising a heat exchanger having a plurality of microchannels for exchanging heat between a heating medium and a transport fluid, wherein an inlet side of the heat exchanger with an inlet segment and / or an outlet side of the heat exchanger with an outlet segment such flow-tight manner, so that the heat medium in the operating state for exchanging heat with the transport fluid, can be supplied to the outlet segment under a prescribable operating pressure through the multiplicity of microchannels of the heat exchanger from the inlet segment.
  • a stiffening element is provided at the inlet segment and / or at the outlet segment, so that a deformation of the heat exchanger block due to the operating pressure of the heating means can be prevented.
  • the stiffening element according to the invention thus prevents the header, ie the inlet segment or the outlet segment, from practically not deforming even under very high operating pressures, ie not bending at a high operating pressure as described above, as is the case with the heat exchanger blocks of the prior art is known.
  • a heat exchanger block according to the invention there is no longer any fear of cracks or damage to the solder joints between the MicroChannel heat exchangers and the headers, since the solder joints are practically no longer subjected to any mechanical stresses due to the known damaging bending loads.
  • inventive heat exchanger blocks are not only much safer than those known from the prior art, have a longer life and longer maintenance intervals, but in particular the headers, so the inlet and outlet segments can be easier, that is especially easier, with thinner outer walls and so with less Material expenses are constructed, because the stiffening element mechanically stabilize the header and consolidate.
  • the stiffening element is not connected directly to the header, ie only to the inlet segment or only to the outlet segment, not to the heat exchanger itself, so that deformation of the inlet segment and / or the outlet segment can be prevented.
  • the inlet segment and the outlet segment can be formed by a common combination segment, which ensures both the inflow of the heat medium to the heat exchanger and the return of the heat from the heat exchanger.
  • a very specific embodiment is always in question when the heat exchanger is designed so that the inflow and outflow of the heating medium takes place on one and the same side of the heat exchanger.
  • the inlet segment and / or the outlet segment and / or the combination segment has a substantially circular cross-section.
  • the stiffening element extends substantially over an entire length of the inlet segment and / or the outlet segment and / or the combination segment.
  • the stiffening element with the inlet segment and / or the outlet segment and / or the combination segment is particularly preferably soldered, and in particular soldered over the entire length of the inlet segment and / or the outlet segment and / or the combination segment with these.
  • soldered soldered, and in particular soldered over the entire length of the inlet segment and / or the outlet segment and / or the combination segment with these.
  • Stiffening element is connected differently with the header, for example, with this screwed.
  • the stiffening element encloses the inlet segment and / or the outlet segment and / or the combination segment on the opposite side of the heat exchanger roof-shaped.
  • the stiffening element is formed as a plank, preferably as a flat plank and extends at a predeterminable angle with respect to a surface of the heat exchanger along the inlet segment and / or the outlet segment and / or the combination segment.
  • the stiffening element can for example also be channel-shaped formed as a groove, and / or the stiffening element may be formed as a hollow tube or as a compact rod, preferably with polygonal, round or oval cross-section.
  • the heat exchanger can in this case be designed and connected to the header such that an inner surface of the inlet segment and / or the outlet segment and / or the combination segment forms a substantially continuous surface with the inlet side and / or the outlet side of the heat exchanger.
  • the inlet side and / or the outlet side of the heat exchanger can also be configured such that a predeterminable region of the inlet side and / or the outlet side of the heat exchanger projects into an inner flow region of the inlet segment and / or the outlet segment and / or the combination segment ,
  • Heat exchanger block is made of a metal and / or a metal alloy, in particular of a single metal or a single Metal alloy, in particular made of stainless steel, in particular made of aluminum or an aluminum alloy, and / or is made of a metal combination, wherein preferably a sacrificial metal is provided as corrosion protection, and / or wherein the heat exchanger block at least partially with a protective layer, in particular with a Corrosion protection layer is provided.
  • the inventive heat exchanger block is often a cooler, a condenser or an evaporator, in particular for a mobile or stationary heating system, cooling system or air conditioning, in particular a cooler device for a machine, a data processing system or for a building or a heat exchanger block for another suitable Application.
  • the invention further relates to a method of manufacturing a heat exchanger block comprising a heat exchanger having a plurality of microchannels for exchanging heat between a heating medium and a transport fluid.
  • a heat exchanger block comprising a heat exchanger having a plurality of microchannels for exchanging heat between a heating medium and a transport fluid.
  • an inlet side of the heat exchanger with an inlet segment and / or an outlet side of the heat exchanger with an outlet segment such pressure-tight flow-connected, that the heating means in the operating state for exchanging heat with the Transportfluidum, under a predetermined operating pressure through the plurality of microchannels of the heat exchanger from the inlet segment Outlet segment can be supplied.
  • a stiffening element is provided at the inlet segment and / or at the outlet segment, so that deformation of the heat exchanger block due to the operating pressure of the heating means is prevented.
  • a modular system comprising the heat exchanger is preferred itself and the stiffening element provided.
  • the individual parts of the modular system are joined together and then together pressure-resistant and fluidly connected to each other, in particular pressure-resistant soldered together.
  • FIG. 1 MicroChannel heat ashtray in a heat exchanger block according to the invention
  • FIG. 2 shows a heat exchanger block known from the prior art in the non-operating state
  • Fig. 3 is a section along the section line l-l according to Fig. 2;
  • FIG. 4 shows the heat exchanger block of FIG. 2 in the operating state
  • Fig. 5 shows a first embodiment of an inventive
  • Heat exchanger block with roof-shaped stiffening element
  • FIG. 6 shows a second embodiment according to FIG. 5;
  • FIG. 7 shows a third exemplary embodiment according to FIG. 5;
  • FIG. 8 shows a fourth exemplary embodiment according to FIG. 5;
  • Fig. 9 shows an embodiment with a stepped
  • Fig. 10 shows an embodiment with a trained as a groove
  • Fig. 1 1 shows a second embodiment according to FIG. 10
  • Fig. 13 shows another embodiment with a tube as
  • Fig. 14 shows a first embodiment with internal
  • FIG. 15 shows a second embodiment according to FIG. 14;
  • Fig. 16 shows an embodiment with a rolled
  • Fig. 17 shows an embodiment with an inwardly directed
  • FIGS. 2 to 4 show known heat exchangers, are provided with apostrophes.
  • Fig. 5 a first embodiment of an inventive heat exchanger block is shown with roof-shaped stiffening element in a schematic drawing. Clearly visible is the heat exchanger 2 with a plurality of microchannels 21, which is soldered at the solder joints 13 with the inlet segment 6.
  • the roof-shaped stiffening element 9 extends substantially over the entire length of the header 6 and is also firmly soldered thereto over the entire length.
  • the inlet side 5 of the heat exchanger 2 is designed such that the predeterminable region 22 of the inlet side 5 of the heat exchanger 2 projects into an inner flow region 12 of the inlet segment 6, as shown.
  • FIGS. 5 to 13 only one representative segment 6 or one outlet segment 8 is shown. Completely analogously, another header, ie an outlet segment 8, an inlet segment 6 or a combination segment 10, could also be represented in each case.
  • FIG. 6 differs from that of FIG. 5 only in that, instead of an inlet segment 6, an outlet segment 8 is shown by way of example and representative of the two other possible types of headers.
  • the essential difference to the example of FIG. 5, however, is that the outlet side 7 of the heat exchanger 2 is formed semicircular so that an inner surface 11 of the Outlet segment 8 with the outlet side 7 of the heat exchanger) forms a continuous surface.
  • this type of construction is somewhat more complicated than that of FIG. 5, it can, in some cases, show advantageous behavior in terms of the flow behavior, as is well known to the person skilled in the art.
  • roof-shaped embodiments of stiffening elements 9 according to the invention are shown with reference to FIGS. 7 and 8, which guarantee an even higher stability, so that, for example, even higher working pressures P of the heating means 3 in the operating state are possible.
  • Fig. 9 shows an embodiment with a step-shaped stiffening element 9, wherein in addition reinforcing elements 900 are provided which fix the heat exchanger 2 even better on the header 6, 8, so that extremely high working pressures for the heating means 3 are possible.
  • FIGS. 10 and 11 An exemplary embodiment with a stiffening element 9 designed as a groove is shown by way of example with reference to FIGS. 10 and 11.
  • Such an embodiment of the heat exchanger block 1 may be useful for reasons of space, for example, if therefore the available space is limited according to the representation above the heat exchanger 2.
  • such embodiments also provide a particularly good protection against deformation or bending perpendicular to the heat exchanger 2 along the longitudinal axis of the header 6, 8, 10th Fig. 12 shows a very simple embodiment with a plank as a stiffening element, which can be made particularly simple and inexpensive.
  • Fig. 13 another embodiment with four tubes 93 as a stiffening element 9 is shown schematically, which are additionally connected to each other via stiffening bridges 94 to improve the stiffening. It is understood that such stiffening bridges 94 may be absent in certain cases, because a sufficient stability is ensured even without stiffening bridges 94.
  • FIGS. 14 to 17 show further variants of a heat exchanger block 1 according to the invention, which are equipped with internal stiffening elements 9.
  • Heat exchanger blocks 1 with internal stiffening elements 9 are particularly important for the practice because they require on the one hand no additional space outside the inlet, outlet or combination element 6, 8, 10. However, what is even more important is the fact that an enormous rigidity can be achieved with internal stiffening elements 9 with relatively little material expenditure, so that a heat exchanger block 1 with internal stiffening element 9 can be exposed to a particularly high operating pressure without fear of damage are.
  • FIG. 14 is a particularly simple embodiment of a heat exchanger 1 with inner Versannonselement 9.
  • the stiffening element 9 as shown in FIG. 14 is simply a web 9, which substantially over the entire Läbnge on the inner wall of the inlet, Auslass- or Combination element 6, 8, 10 is provided.
  • the stiffening element is preferably soldered over the soldering track 131 over its entire length on the inner surface 11. It is understood that the stiffening element 9 is not necessary, as in FIG.
  • stiffening element 9 can also be made more complicated within the inlet, outlet or combination element 6, 8, 10, e.g. as shown schematically in Fig. 15 or be configured in any other suitable form.
  • the internal stiffening element 9 of FIG. 14 and FIG. 5 is preferably soldered via the solder joints 131 or solder traces 131 to the inner surface 11 of the inlet, outlet or combination element 6, 8, 10.
  • the stiffening element 9 may also be otherwise connected to the inlet, outlet or combination element 6, 8, 10, e.g. be connected via a weld, a screw or other known to those skilled in the type of connection.
  • the inner surface 11 and / or the stiffening element 9 are provided in a conventional manner with solder material prior to assembly of the heat exchanger block, so that the entire heat exchanger block 1 can be soldered substantially completely in a single soldering.
  • solder material for example only the end caps on the inlet, outlet or combination elements 6, 8, 10 or other minor attachments may but need not be treated in a separate operation.
  • Fig. 16 an embodiment is shown with a rolled stiffening element 9 in a schematic manner.
  • the stiffening element 9 is not formed by soldering an additional component, for example by soldering an additional web, as shown in Fig. 14 or Fig. 15.
  • the stiffening element 9 is formed in that the stiffening element 9 is mechanically rolled into the tubular inlet, outlet or combination element 6, 8, 10.
  • the inlet, outlet or combination element 6, 8, 10 may, for example, also be cast in the appropriate form or produced differently. It is crucial that the stiffening element 9 extends substantially over the entire length of the inlet, outlet or combination element 6, 8, 10 in the form of a dent.
  • the stiffening element 9 is formed as a bend 9 or fold 9 on the inlet, outlet or combination element 6, 8, 10.
  • the inlet, outlet or combination element 6, 8, 10 can be composed, for example, of two with respect to the longitudinal half-tubes, wherein on one of the half tubes, first the inflection 9 or fold 9 is formed and then the two half-tubes at the solder seam 131st for an inlet, outlet or combination element 6, 8, 10 are soldered.

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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

L'invention concerne un bloc échangeur thermique (1) comprenant un échangeur thermique (2) avec une pluralité de microcanaux (21) pour réaliser l'échange thermique entre un fluide chaud (3) et un fluide de transport (4). Un côté d'entrée (5) de l'échangeur thermique (2) est relié fluidiquement, de manière à résister à la pression à un segment d'entrée (6) et/ou un côté de sortie (7) de l'échangeur thermique (2) est reliés fluidiquement, de manière à résister à la pression, à un segment de sortie (8), si bien qu'en service, pour l'échange de chaleur avec le fluide de transport (4), le fluide chaud (3) peut être conduit sous une pression de service (P) prédéterminable par la pluralité de microcanaux (21) de l'échangeur thermique (2) du segment d'entrée (6) au segment de sortie (8). Selon l'invention, il est prévu sur le segment d'entrée (6) et/ou sur le segment de sortie (8) un élément de renforcement (9), ce qui permet d'éviter une déformation du bloc échangeur thermique (1) en raison de la pression de service (P) du fluide chaud (3). L'invention concerne par ailleurs un procédé de fabrication d'un bloc échangeur thermique (1).
PCT/EP2008/058451 2008-07-01 2008-07-01 Bloc échangeur thermique et procédé de fabrication d'un bloc échangeur thermique Ceased WO2010000311A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/EP2008/058451 WO2010000311A1 (fr) 2008-07-01 2008-07-01 Bloc échangeur thermique et procédé de fabrication d'un bloc échangeur thermique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2008/058451 WO2010000311A1 (fr) 2008-07-01 2008-07-01 Bloc échangeur thermique et procédé de fabrication d'un bloc échangeur thermique

Publications (1)

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WO2010000311A1 true WO2010000311A1 (fr) 2010-01-07

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012148530A1 (fr) 2011-04-26 2012-11-01 Dow Global Technologies Llc Tensioactifs renouvelables dérivés d'alcools de sucres
CN105387732A (zh) * 2014-09-03 2016-03-09 Gea能量技术有限公司 用于蒸汽冷凝的设备
JP2016084994A (ja) * 2014-10-27 2016-05-19 ダイキン工業株式会社 熱交換器組立体および冷凍装置の室外ユニット

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JPH02247498A (ja) * 1989-03-20 1990-10-03 Nippondenso Co Ltd 熱交換器
US5236042A (en) * 1991-02-20 1993-08-17 Sanden Corporation Heat exchanger and method of making the same
US5570737A (en) * 1993-10-07 1996-11-05 Showa Aluminum Corporation Heat exchanger
JPH11337289A (ja) * 1998-05-27 1999-12-10 Showa Alum Corp 熱交換器
GB2344643A (en) * 1998-12-07 2000-06-14 Serck Heat Transfer Limited Heat exchanger core connection
JP2001241806A (ja) * 2000-02-28 2001-09-07 Sanden Corp 耐圧部品及び耐圧部品を用いた熱交換器並びに耐圧部品を用いた冷凍装置
JP2003172592A (ja) * 2001-12-06 2003-06-20 Denso Corp 熱交換器
FR2851815A1 (fr) * 2003-02-28 2004-09-03 Valeo Climatisation Boite collectrice pour echangeur de chaleur resistant a la pression
EP1557622A2 (fr) * 2004-01-22 2005-07-27 Hussmann Corporation Condenseur à microcanaux
DE102004002252A1 (de) * 2004-01-08 2005-08-04 Visteon Global Technologies, Inc., Dearborn Wärmeübertrager für Fahrzeuge
DE102006056545A1 (de) * 2005-11-29 2007-05-31 Showa Denko K.K. Wärmetauscher
WO2008048251A2 (fr) * 2006-10-13 2008-04-24 Carrier Corporation Procédé et appareil consistant à améliorer la distribution de fluide dans un échangeur de chaleur

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02247498A (ja) * 1989-03-20 1990-10-03 Nippondenso Co Ltd 熱交換器
US5236042A (en) * 1991-02-20 1993-08-17 Sanden Corporation Heat exchanger and method of making the same
US5570737A (en) * 1993-10-07 1996-11-05 Showa Aluminum Corporation Heat exchanger
JPH11337289A (ja) * 1998-05-27 1999-12-10 Showa Alum Corp 熱交換器
GB2344643A (en) * 1998-12-07 2000-06-14 Serck Heat Transfer Limited Heat exchanger core connection
JP2001241806A (ja) * 2000-02-28 2001-09-07 Sanden Corp 耐圧部品及び耐圧部品を用いた熱交換器並びに耐圧部品を用いた冷凍装置
JP2003172592A (ja) * 2001-12-06 2003-06-20 Denso Corp 熱交換器
FR2851815A1 (fr) * 2003-02-28 2004-09-03 Valeo Climatisation Boite collectrice pour echangeur de chaleur resistant a la pression
DE102004002252A1 (de) * 2004-01-08 2005-08-04 Visteon Global Technologies, Inc., Dearborn Wärmeübertrager für Fahrzeuge
EP1557622A2 (fr) * 2004-01-22 2005-07-27 Hussmann Corporation Condenseur à microcanaux
DE102006056545A1 (de) * 2005-11-29 2007-05-31 Showa Denko K.K. Wärmetauscher
WO2008048251A2 (fr) * 2006-10-13 2008-04-24 Carrier Corporation Procédé et appareil consistant à améliorer la distribution de fluide dans un échangeur de chaleur

Cited By (4)

* Cited by examiner, † Cited by third party
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WO2012148530A1 (fr) 2011-04-26 2012-11-01 Dow Global Technologies Llc Tensioactifs renouvelables dérivés d'alcools de sucres
CN105387732A (zh) * 2014-09-03 2016-03-09 Gea能量技术有限公司 用于蒸汽冷凝的设备
JP2016084994A (ja) * 2014-10-27 2016-05-19 ダイキン工業株式会社 熱交換器組立体および冷凍装置の室外ユニット
US10782035B2 (en) 2014-10-27 2020-09-22 Daikin Industries, Ltd. Heat exchanger assembly and outdoor unit of refrigerating apparatus

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