EP0720720B1 - Echangeur de chaleur a canaux - Google Patents

Echangeur de chaleur a canaux Download PDF

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Publication number
EP0720720B1
EP0720720B1 EP94928255A EP94928255A EP0720720B1 EP 0720720 B1 EP0720720 B1 EP 0720720B1 EP 94928255 A EP94928255 A EP 94928255A EP 94928255 A EP94928255 A EP 94928255A EP 0720720 B1 EP0720720 B1 EP 0720720B1
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EP
European Patent Office
Prior art keywords
heat exchanger
flow
channels
fact
described under
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
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EP94928255A
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German (de)
English (en)
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EP0720720A1 (fr
Inventor
Eberhard Dipl.-Ing. Paul
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Individual
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Individual
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Publication date
Priority claimed from DE19934333164 external-priority patent/DE4333164C2/de
Priority claimed from DE19934333904 external-priority patent/DE4333904C2/de
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Publication of EP0720720A1 publication Critical patent/EP0720720A1/fr
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Publication of EP0720720B1 publication Critical patent/EP0720720B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0025—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being formed by zig-zag bend 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • 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
    • F28F9/001—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core
    • 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
    • F28G—CLEANING OF INTERNAL OR EXTERNAL SURFACES OF HEAT-EXCHANGE OR HEAT-TRANSFER CONDUITS, e.g. WATER TUBES OR BOILERS
    • F28G1/00—Non-rotary, e.g. reciprocated, appliances
    • F28G1/02—Non-rotary, e.g. reciprocated, appliances having brushes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/08—Fastening; Joining by clamping or clipping
    • F28F2275/085—Fastening; Joining by clamping or clipping with snap connection
    • 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
    • F28F2280/02—Removable elements

Definitions

  • the invention relates to a heat exchanger for, in particular two flowing fluids with parallel flow channels, the cross section of layers lying on top of each other Sheets with a meandering profile is formed, one the flow channels of the underlying one Covering the panel and being adjacent to each side Different fluids can flow through flow channels are.
  • Such a heat exchanger has become known from DD 243 088 A1.
  • the heat exchanger that became known from DD 243 088 Al is made up of individual ones in an S-shape Profile sheet metal strips built up, the profile of which is meandering Has cross section.
  • the inside angle of the meandering Profile-formed open trapezoids are, however greater than 90 °, so that an overlying panel in the can intervene underneath and slide in.
  • the flow cross sections, flow velocities, effective Heat exchange surfaces and the static controllability of the overall structure in an uncontrolled manner are also be made up of individual ones in an S-shape Profile sheet metal strips built up, the profile of which is meandering Has cross section.
  • the inside angle of the meandering Profile-formed open trapezoids are, however greater than 90 °, so that an overlying panel in the can intervene underneath and slide in.
  • the invention is based on the object, one To further develop heat exchangers of the type mentioned in the introduction, that the superimposed panels no longer interlock slide, but that the boards without stabilizing Intermediate sheets can lie on top of each other and become one stable overall structure results, with economical use of materials a maximum heat exchange surface with thin sheets is achieved in a confined space.
  • Heat exchanger is therefore a compact heat exchanger with a high specific heat exchange surface, for the most diverse Heat exchange tasks between gaseous and / or liquid Media as well as an evaporator, condenser and flow reactor applicable with exothermic and endothermic processes is.
  • a heat exchanger between gaseous media the heat exchanger can be used for waste heat, for example from exhaust air in buildings, factories and warehouses as well use in combination with extractor hoods.
  • the heat exchanger can be used to preheat dry air in drying systems, for preheating combustion air such as in Bakeries, for drying processes or forced air cooling, for Condensation in tumble dryers for ventilation in livestock farming in stables and for heat exchange purposes in power plants and use exhaust gas treatment systems.
  • combustion air such as in Bakeries
  • forced air cooling for Condensation in tumble dryers for ventilation in livestock farming in stables and for heat exchange purposes in power plants and use exhaust gas treatment systems.
  • the heat exchanger can be used in car washes or in household appliances such as washing machines, dishwashers used will.
  • Other areas of application are in air conditioning, in cooling processes such as control cabinet cooling or evaporative cooling, condensation, in evaporation technology such as as a film evaporator, in refrigeration systems, Continuous gas heaters and in boilers, forming stations for hot water and steam as well as in the automotive industry, for example for waste heat use and heating of the passenger compartment.
  • the heat exchanger in the automotive industry due to its high compactness and small size can be used excellently for preheating wash water for windscreen and headlight washer systems and for charge air cooling in the turbocharger engine.
  • the heat exchanger can be made of aluminum, steel, stainless steel, etc. Metals and alloys, or of plastics or Paper or other materials.
  • the inner angles of the meandering profile are preferred formed open trapezoids larger than 70 ° so that Relationship between material expenditure and heat exchange area of the flow channel is as optimal as possible and the ratio from heat transfer coefficient to weight or price of the heat exchanger is kept as large as possible.
  • the walls of the flow channels are the heat exchanger roughened and / or with the flow of the flowing Structures influencing fluids.
  • a channel flow especially in larger dimensions smooth channels, the risk of deterioration in heat transfer through a laminar boundary layer of the flowing
  • fluid on the walls which leads to the invention roughened and / or structured duct wall as flow-specific baffles within the flow channel e.g. to create turbulence or spiral flows or double spiral flows, which increases the heat exchange between the fluids is increased or optimized.
  • the fluid is into the individual flow channels via inclined surfaces and / or deflectable so that the fluids in selected flow channels for example a flow channel level or only one end half of the heat exchanger initiated can be.
  • About the number of closed shut-off elements can also the residence time of the fluids in the Set the heat exchanger and thus the heat transfer coefficient and influence the flow direction of the fluids. Consequently hydraulic cleaning is also possible.
  • Especially adjustable flaps can control the flow and heat exchange performance vary. These flaps can be driven or move magnets.
  • Flow control elements via the the fluids can be introduced into the flow channels from the outside or are redirectable within the heat exchanger, so the inlet and outlet of each fluid at any angle lead into and out of the heat exchanger or within redirect the heat exchanger, the flow pressure losses be minimized.
  • a flow distributor and a are particularly preferred Flow combiner for a fluid as one in the flow direction over the entire cross-section of the flow level (s) extending flat channel section without flow channels trained and the flow channels of the other Fluids in this (n) flow plane (s) at their respective Ends, especially with an inclined surface, closed are. Then it flows into the heat exchanger e.g. about its total cross-sectional area introduced fluid into all open Flow channels without entering the flow channels of the other fluids. So one can only have an opening cross-section fluid flowing into the heat exchanger to all desired flow channels in the heat exchanger into one Checkerboard-like flow cross-section can be distributed and so with low flow pressure loss, since none 90 ° deflection, maximum heat exchange can be achieved.
  • this is the profile forming the flow channels compressed into a plane at its respective ends.
  • Profile sheets manufactured using the deep-drawing process with an acute-angled trapezoidal shape Cross section can be easily compressed, so that with a meandering basic profile also structures closing certain flow channels easy to manufacture.
  • channel sections are each only open to a fluid Have front half and this entry and exit side Face halves of a fluid preferably diagonally opposite in the direction of flow, so the Flows through the heat exchanger according to the invention diagonally and with respect a flow short-circuit of the heat exchanger is prevented.
  • Those forming the flow channels are particularly preferred Panels can be arranged in a housing, which can preferably also be dismantled, what the assembly and disassembly as well as the Cleaning of the individual parts forming the heat exchanger facilitated.
  • a housing which can preferably also be dismantled, what the assembly and disassembly as well as the Cleaning of the individual parts forming the heat exchanger facilitated.
  • the heat exchanger package is also a V-shaped sealing element easily removable from a one-piece housing.
  • a fin heat exchanger also falls within the scope of the invention, in which a fluid, e.g. Air, parallel flow channels with rectangular profile, trapezoidal profile or excessive trapezoidal profile or similar parts of profile pieces.
  • a fluid e.g. Air
  • parallel flow channels with rectangular profile, trapezoidal profile or excessive trapezoidal profile or similar parts of profile pieces.
  • another fluid e.g. with a liquid
  • the heat exchanger designated by 1 in FIG. 1a has a housing 2, in which by means of a continuous sheet metal strip 3 flow channels 4 for two fluids, for example A, B are formed. Inscribed in the drawing a filled arrow the fluid A, an unfilled Arrow the fluid B.
  • the metal strip 3 has a meandering shape Profile whose open inside angle ⁇ is less than Are 90 °. Inside the housing 2 is the meandering Sheet metal strip 3 itself arranged in a serpentine or S-shape, that parallel flow channel planes are formed. The sheet profile lies on a flow level the underlying sheet metal profile, as shown schematically at 5 is indicated.
  • the two longitudinal edges 6a, b of the Sheet metal strip 3 are either with each other or with the housing 2 connected leakage-free, so that laterally adjacent Flow channels 4 each completely from a different fluid and flows hermetically separated from one another by sheet metal will. As shown in Fig. 1b, mixing takes place of the fluids flowing through the flow channels 4 A, B does not take place. Due to the almost square structure of the Flow channels 4 are used for heat exchange between the two Fluids A, B each on four sides of a channel 4, such as it is indicated by the double arrows 7. The heat exchange surface can only be compared to one of parallel Double plates of existing heat exchangers.
  • FIG. 2a To further increase the heat exchange, flow through the two fluids A, B according to FIG. 2a, the flow channels 4 in opposite flow direction.
  • a channel flow especially in larger flow channels with smooth walls, as shown in Fig. 2a the risk of deterioration in heat transfer between the two fluids A, B through the training each a laminar boundary layer of the flowing fluid the smooth wall.
  • the figures 2b to e show across and formed obliquely to the flow direction of the flow channels 4 Flow baffles in the form of furrows 8a to 8d, over which the flow behavior of the flowing Influences fluids.
  • FIG. 3a shows an exploded view of the otherwise superimposed ones Profile sheets.
  • the illustration shows how the profile of the quasi-flat flat plates (see Fig. 3c) merges into the meandering profile structure, the Transition e.g. from level 9 to the "trapezoidal roof” 10 over the oblique discharge surfaces 10a; analogously, the Transition to the "Trapez Valley”.
  • the flow course in this Transition area (channel distributor) is from the sectional view 3b can be seen, it being clearly recognizable that the entry of the medium A from a flat, flat Gap (first flow level) in the channels of two flow levels (Partial streams A 'and A "according to FIG. 4), whereby the checkerboard-like flow profile well shown in FIG. 4 arises.
  • the flow channels 4 shown in FIG. 4 differ from those of FIG. 1a in that on the outside diagonally adjacent flow channels 4a, b of a fluid are connected to one another via openings 11. This is shown in the rear view of FIG. 4 for the outer flow channels 4a, b.
  • the front part of Fig. 4 shows the separate inflow of the two fluids A, B in adjacent flow levels in the countercurrent process.
  • the introduction of a fluid into the flow channels 4a, 4b is achieved in that elevations 10 are provided with closed inclined surfaces 10a.
  • the fluid flow A is split up via the inclined surface 10a into a first partial flow A 'and a second partial flow A ".
  • the lateral sealing of the flow channels open to the outside 4 takes place either through a smooth side wall 15a or by profiling according to the flow levels Sidewall 15b (Fig. 6a).
  • the introduction of the fluids A, B in This embodiment is carried out through side openings 16 in the side walls 15a, b. Because the flow planes of the other Fluids with an S-shaped overlay of the sheet metal strip resulting from the bending edge closed the fluid can be open over the entire Cross section 16 of the side walls 15 are fed.
  • the derivative the fluid takes place according to FIG. 6a via the end face of the flow channels 4, so that the introduction and discharge of the both fluids A, B are each perpendicular to each other.
  • Fig. 6b In the case of an overlapping S-shape in the direction of flow Profile sheet strips, as shown in Fig. 6b, are the profiled side parts 15b with corresponding recesses Mistake.
  • Fig. 6c again illustrates each Entry and exit directions running at right angles to one another the fluids A, B in the heat exchanger 1.
  • FIG. 7a shows a heat exchanger 101 which can be dismantled and which consists of two housing halves 102a, b which can be connected to one another, a profiled sheet 103 which forms flow channels 104 and a cover 117 with flow deflection elements 117a.
  • the identically designed housing halves 102a, b have two preferably square openings 118a, b and two side openings 119a, b, into which the covers 117 (with and without flow control elements 117a) can be inserted.
  • the housing 102, 602, the cover 117, 617, the gap 627 and the connecting rib 6 are preferably made of plastic and can be connected to one another in a detachable and simple manner.
  • the end faces 103 'of the profiled sheet 103 are V-shaped and, when the two housing halves 102a, b are connected, are in a form-fitting manner against likewise V-shaped stops 102' within the respective housing half 102a, b, a seal preferably being inserted for sealing purposes, which is adapted to the sealing surface 102.
  • the flow directing elements 117a consist of parallel baffles 117a 'spaced apart from one another and one or two cover surface (s) 117b.
  • both the end angle ⁇ of the V-shaped end face of the profiled plate 103 and the deflection angle of the flow deflecting elements 117 are 45 °, so that the fluids between the guide plates 117a can be introduced or discharged parallel to the flow direction via the end sides of the heat exchanger 101, as in the fig. 7a, b is shown. If the covers with flow guide elements 117a are inserted into the front openings, the laterally entering fluids A, B can also be introduced into the heat exchanger 101 parallel to the flow direction.
  • FIG. 7c shows the flow planes 4 A , 4 B which are each open for a fluid and closed by end strips, which correspond to those of FIG. 4 with the exception of the V-shaped end face.
  • the two housing halves 102a, b can be easily connected or detached to one another by means of fastening means in the form of locking brackets 121 which engage with projections 120 on the heat exchanger 101.
  • the covers 117 can also be easily attached or detached using a similar locking mechanism between projections 117c on the covers 117 and locking brackets 121 '.
  • 7d shows the longitudinal section of the assembled heat exchanger 101, a flexible intermediate piece 121 being installed here for improved expansion absorption and assembly. This adapter can also be attached to the end of the heat exchanger.
  • FIG. 8 is another embodiment of a heat exchanger 201 shown, in which the one-piece housing halves in FIG. 7a 102a, b in turn through two housing quarters 202a ', a ", b', b" are formed.
  • the individual housing quarters 202 and the front cover 222 and die die side covers 223 covering side openings 219 are attached with locking brackets 221, which in turn with Projections 220 and 217c on the housing quarters 202a, b and cooperate on the end parts 217c.
  • the one assembled State of the heat exchanger 201 to the heat exchanger package pressed housing parts are each with sealant 224 sealed.
  • the profiled sheet 203 is on the ends of rectangular end faces 203 '.
  • the front Covers 222 with protrusions 217c are made by means of Seal 224 and clamping means tightly connected to the housing.
  • FIG. 9 shows a heat exchanger designed analogously to FIG. 7a 103 in a housing 602, which, however, in one piece is.
  • the exploded view shows that the housing 602 consists of a continuous, rectangular channel 602, which is easy to produce as a drawn part.
  • the seal on the V-shaped end face 103 ' takes place via a removable V-shaped sealing element 623, the front and side preferably square and identically shaped openings 618 ', the inflow and outflow both at the end as well as sideways.
  • the locking of the V-shaped Sealing elements in the housing are made by inserting them a cover 617 or other connecting element 626, 627 through the side housing opening 619 into the lateral opening 619 'of the V-shaped sealing element 623 into where the plug-in element snaps away.
  • a cover 617 or other connecting element 626, 627 through the side housing opening 619 into the lateral opening 619 'of the V-shaped sealing element 623 into where the plug-in element snaps away.
  • an 8-shaped frame seal 624 is provided for sealing.
  • This seal 624 can 625 over the entire surface be so that an incoming medium is filtered at the same time becomes.
  • connection between housings (modular form) and between Housing with V-shaped connecting element 625 and connecting elements is preferably a removable Snap connection realized, preferably from Plug part 628 and receptacle (socket) part 628 'there.
  • the figures 10 and 11 show a fin heat exchanger 701, where the ribs are turned back and forth and a rectangle-like Own profile structure.
  • the flow channels 704 are made of a, in particular gaseous, fluid A flows through like air, the heat exchange with a in particular liquid fluid B takes place in pipes 705, 705 'perpendicular to the flow channels 704 the profiled sheet 703 flows through.
  • the tubes 705, 705 ' have either a round (Fig. 10) or an elongated cross section (Fig. 11).
  • the advantages of the finned heat exchanger 701 can be seen in that the heat transfer is intensified on the air side. This is due to the fact that with liquid-air heat exchangers on the Air side due to media only a significantly lower heat transfer is possible, the heat exchange surface on the Air side (heat exchange fins) are designed so that on The largest possible heat exchange surface accommodated in a confined space is, which in the best case at the same time in itself should be structured to match the heat transfer coefficient on the Increase air side. This goal can be achieved with the profiled Generate metal strips 703, with its profile shape no parallel ribs are created, but by the and turning and stacking a checkerboard-like Structure arises.
  • the channel wall is corrugated or structured differently, so Turbulence or spiral flows arise.
  • Rib profiling is the one actively involved in the heat exchange Rib area increased by approx. 60%. It can be used for the same outer dimensions of a finned heat exchanger the heat exchange surface and thus the compactness and heat exchange performance be increased significantly, or while maintaining one required heat exchange surface is the entire fin heat exchanger in its outer dimensions much smaller.
  • Fig. 12 is another embodiment of a fin heat exchanger 701 'shown by two gaseous fluids A, B at right angles and in separate flow channels is flowed through. Due to the large profile surface of the Fluid A the heat exchange with the fluid B can also be increased here.
  • fig. 13a to 13c show the rib profile Rectangular profile, a trapezoidal profile, an elevated trapezoidal profile, the trapezoidal cones are acute-angled, or the like Profiles.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Defrosting Systems (AREA)

Claims (13)

  1. L'échangeur thermique, (1) pour deux fluides circulants (A, B) en particulier, ayant des canaux d'écoulement parallèles (4) qui, de profil, apparaissent sous forme d'une couche de plaques superposées dessinant des méandres, chaque plaque supérieure recouvrant les canaux d'écoulement (4) de la plaque sous-jacente et, l'ensemble des canaux d'écoulement (4) longeants pouvant être emprunté par des fluides différents; le tout caractérisé par le fait que les angles intérieurs  des trapèzes ouverts, formés par les plaques en méandres, sont inférieurs à 90°
  2. L'échangeur thermique selon la demande N°1 est caractérisé par le fait que les angles intérieurs  sont supérieurs à 70°.
  3. L'échangeur thermique selon les demande N°1 et 2, caractérisé par le fait que toutes les plaques de l'échangeur thermique (1) composées d'une seule bande continue (3) sont disposées de sorte que les canaux d'écoulement (4) des deux fluides (A, B) soient complètement séparés l'un de l'autre.
  4. L'échangeur thermique selon une des demandes susmentionnées se caractérisant par le fait que les parois des canaux d'écoulement (4) sont rugueuses et/ou qui sont équipées de structures (8a, 8b, 8c, 8d) régulant l'écoulement du fluide (A, B).
  5. L'échangeur thermique selon une des demandes susmentionnées caractérisé par le fait que les afflux répétitifs dans les canaux d'écoulement (4) peuvent être générés puisqu'une plaque posée dans le sens de l'écoulement passe à intervalles déterminés et sur une courte longueur, à une section plate (13), ceci accompagné par une compression engendrant un tourbillon.
  6. L'échangeur thermique selon une des demandes susmentionnées se caractérisant par le fait qu'un fluide peut être introduit dans les différents canaux d'écoulement et/ou évacué par des surfaces inclinées (12 a, b).
  7. L'échangeur thermique selon une des demandes susmentionnées caractérisé par le fait que dans la zone des orifices d'entrée et de sortie des canaux d'écoulement (4), des éléments d'acheminement (117 a) sont disposés par lesquels les fluides (A, B) peuvent être introduits de l'extérieur dans les canaux d'écoulement (4) ou ils peuvent être détournés dans l'échangeur thermique (101).
  8. L'échangeur thermique selon une des demandes susmentionnées caractérisé par le fait qu'un distributeur d'écoulement et un convergeur d'écoulement pour le premier fluide sont constitués sous forme d'une section plate du canal (14;114)) et sans canaux d'écoulement qui s'étend dans le sens de l'écoulement et sur toute la longueur de la / des surfaces d'écoulement, et que les canaux d'écoulement (4;104) du second fluide de cette / ces surfaces d'écoulement sont fermés à leurs extrémités respectives, surtout celles qui présentent une surface inclinée (12A).
  9. L'échangeur thermique selon une des demandes susmentionnées caractérisé par le fait que le profil formant les canaux d'écoulement est aplati (9) à ses extrémités respectives.
  10. L'échangeur thermique selon la demandes N°9 caractérisé par le fait que les deux profils longeants et aplatis (9) peuvent être pliés vers la paroi d'about (16b) qui ferme la surface d'écoulement
  11. L'échangeur thermique selon la demandes N°8 caractérisé par le fait que les sections de canal (114) présentent la moitié de la paroi d'about (103') sous forme de V de préférence qui n'est ouverte que pour un seul fluide et que les moitiés de parois d'about (103') sur les côtés d'entrée et de sortie sont disposés de préférence en diagonal et dans le sens de l'écoulement.
  12. L'échangeur thermique selon une des demandes susmentionnées caractérisé par le fait que les plaques formant les canaux d'écoulement (4) peuvent être aménagées de préférences dans un boítier démontable (2;102;602).
  13. Jeu de pièce d'échangeurs thermiques selon une des demandes de 1 à 12 caractérisé par le fait que plusieurs échangeurs thermiques peuvent être branchés latéralement et / ou l'un derrière l'autre et / ou en diagonal.
EP94928255A 1993-09-27 1994-09-27 Echangeur de chaleur a canaux Expired - Lifetime EP0720720B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE4333164 1993-09-27
DE19934333164 DE4333164C2 (de) 1993-09-27 1993-09-27 Rippenwärmetauscher mit profilierter Rippenform
DE19934333904 DE4333904C2 (de) 1993-09-27 1993-09-27 Kanalwärmetauscher
DE4333904 1993-09-27
PCT/DE1994/001118 WO1995009338A1 (fr) 1993-09-27 1994-09-27 Echangeur de chaleur a canaux

Publications (2)

Publication Number Publication Date
EP0720720A1 EP0720720A1 (fr) 1996-07-10
EP0720720B1 true EP0720720B1 (fr) 1998-01-21

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EP94928255A Expired - Lifetime EP0720720B1 (fr) 1993-09-27 1994-09-27 Echangeur de chaleur a canaux

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EP (1) EP0720720B1 (fr)
AT (1) ATE162616T1 (fr)
AU (1) AU7738494A (fr)
DE (1) DE9490288U1 (fr)
DK (1) DK0720720T3 (fr)
WO (1) WO1995009338A1 (fr)

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DE202004011489U1 (de) * 2004-07-20 2005-12-08 Autokühler GmbH & Co. KG Wärmeaustauscher für Hochtemperatur-Anwendungen, insbesondere Ladeluftkühler
DE102004025640A1 (de) * 2004-05-25 2005-12-22 Hella Kgaa Hueck & Co. Scheinwerfer mit am Leuchtmittel angeordnetem Wärmetauscher
US7746634B2 (en) 2007-08-07 2010-06-29 Cooligy Inc. Internal access mechanism for a server rack
US7836597B2 (en) 2002-11-01 2010-11-23 Cooligy Inc. Method of fabricating high surface to volume ratio structures and their integration in microheat exchangers for liquid cooling system
US8157001B2 (en) 2006-03-30 2012-04-17 Cooligy Inc. Integrated liquid to air conduction module
US8254422B2 (en) 2008-08-05 2012-08-28 Cooligy Inc. Microheat exchanger for laser diode cooling
US8250877B2 (en) 2008-03-10 2012-08-28 Cooligy Inc. Device and methodology for the removal of heat from an equipment rack by means of heat exchangers mounted to a door
US8464781B2 (en) 2002-11-01 2013-06-18 Cooligy Inc. Cooling systems incorporating heat exchangers and thermoelectric layers
US8602092B2 (en) 2003-07-23 2013-12-10 Cooligy, Inc. Pump and fan control concepts in a cooling system
US10012450B2 (en) 2012-01-20 2018-07-03 Westwind Limited Heat exchanger element and method for the production
WO2022069587A1 (fr) 2020-09-30 2022-04-07 Zehnder Group International Ag Échangeur de chaleur à canaux

Families Citing this family (9)

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JP3362611B2 (ja) * 1996-09-12 2003-01-07 三菱電機株式会社 熱交換器および該熱交換器の熱交換部材の製造方法
DE19654364B4 (de) * 1996-12-24 2007-05-16 Behr Gmbh & Co Kg Strömungskanal, insbesondere für einen Gas-Flüssigkeit-Wärmeübertrager
ITVR20020051U1 (it) * 2002-08-26 2004-02-27 Benetton Bruno Ora Onda Spa Scambiatore di calore a piastre.
ATE492716T1 (de) * 2004-09-13 2011-01-15 Behr Gmbh & Co Kg Ladeluftkühler, insbesondere für kraftfahrzeuge
WO2012004100A1 (fr) * 2010-07-08 2012-01-12 Swep International Ab Échangeur de chaleur à plaques
CN105556233B (zh) 2013-07-19 2019-09-17 韦斯特温德有限公司 热/焓交换器元件及生产方法
PL3271676T3 (pl) 2015-03-17 2023-02-06 Zehnder Group International Ag Element wymiennika do kabiny pasażerskiej oraz kabina pasażerska wyposażona w taki element wymiennika
EP3671097B1 (fr) * 2018-12-19 2022-07-20 Valeo Autosystemy SP. Z.O.O. Système d'arrêt
IT201900025471A1 (it) 2019-12-24 2021-06-24 Novamont Spa Composizione polimerica per film con migliorate proprieta' meccaniche e disintegrabilita'

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GB655470A (en) * 1948-03-08 1951-07-25 Raymond Ernest Wigg Improvements in or relating to heat exchangers
DE2513505A1 (de) * 1975-03-26 1976-10-14 Thermal Waerme Kaelte Klima Waermerueckgewinnungsgeraet
DE2936057A1 (de) * 1979-09-06 1981-03-12 Bremshey Ag Mit einem sitz- oder liegemoebel kombinierbarer tisch.
WO1981002060A1 (fr) * 1980-01-14 1981-07-23 Caterpillar Tractor Co Echangeur de chaleur de faible contrainte et son procede de fabrication
EP0055711B1 (fr) * 1980-07-07 1985-10-09 Caterpillar Tractor Co. Echangeur de chaleur a profil bas et son procede de fabrication
IL93994A (en) * 1989-04-19 1994-07-31 Urch John Francis Heat Exchanger

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7836597B2 (en) 2002-11-01 2010-11-23 Cooligy Inc. Method of fabricating high surface to volume ratio structures and their integration in microheat exchangers for liquid cooling system
US8464781B2 (en) 2002-11-01 2013-06-18 Cooligy Inc. Cooling systems incorporating heat exchangers and thermoelectric layers
US8602092B2 (en) 2003-07-23 2013-12-10 Cooligy, Inc. Pump and fan control concepts in a cooling system
DE102004025640A1 (de) * 2004-05-25 2005-12-22 Hella Kgaa Hueck & Co. Scheinwerfer mit am Leuchtmittel angeordnetem Wärmetauscher
DE202004011489U1 (de) * 2004-07-20 2005-12-08 Autokühler GmbH & Co. KG Wärmeaustauscher für Hochtemperatur-Anwendungen, insbesondere Ladeluftkühler
US8157001B2 (en) 2006-03-30 2012-04-17 Cooligy Inc. Integrated liquid to air conduction module
US7746634B2 (en) 2007-08-07 2010-06-29 Cooligy Inc. Internal access mechanism for a server rack
US8250877B2 (en) 2008-03-10 2012-08-28 Cooligy Inc. Device and methodology for the removal of heat from an equipment rack by means of heat exchangers mounted to a door
US8254422B2 (en) 2008-08-05 2012-08-28 Cooligy Inc. Microheat exchanger for laser diode cooling
US8299604B2 (en) 2008-08-05 2012-10-30 Cooligy Inc. Bonded metal and ceramic plates for thermal management of optical and electronic devices
US10012450B2 (en) 2012-01-20 2018-07-03 Westwind Limited Heat exchanger element and method for the production
WO2022069587A1 (fr) 2020-09-30 2022-04-07 Zehnder Group International Ag Échangeur de chaleur à canaux

Also Published As

Publication number Publication date
AU7738494A (en) 1995-04-18
WO1995009338A1 (fr) 1995-04-06
EP0720720A1 (fr) 1996-07-10
ATE162616T1 (de) 1998-02-15
DE9490288U1 (de) 1996-07-04
DK0720720T3 (da) 1998-09-21

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