EP0055711B1 - Echangeur de chaleur a profil bas et son procede de fabrication - Google Patents

Echangeur de chaleur a profil bas et son procede de fabrication Download PDF

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Publication number
EP0055711B1
EP0055711B1 EP81900865A EP81900865A EP0055711B1 EP 0055711 B1 EP0055711 B1 EP 0055711B1 EP 81900865 A EP81900865 A EP 81900865A EP 81900865 A EP81900865 A EP 81900865A EP 0055711 B1 EP0055711 B1 EP 0055711B1
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EP
European Patent Office
Prior art keywords
passages
fluid
group
core
portions
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Expired
Application number
EP81900865A
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German (de)
English (en)
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EP0055711A1 (fr
EP0055711A4 (fr
Inventor
Alexander Goloff
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Caterpillar Inc
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Caterpillar Tractor Co
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Publication of EP0055711A1 publication Critical patent/EP0055711A1/fr
Publication of EP0055711A4 publication Critical patent/EP0055711A4/fr
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Publication of EP0055711B1 publication Critical patent/EP0055711B1/fr
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    • 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
    • F28F3/042—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 in the form of local deformations of the element
    • 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

Definitions

  • This invention relates to a low profile heat exchanger module for use in heat furnaces, steel melting furnaces, gas turbines which use recuperators and the like, and a method for forming the same.
  • FR-A-2315674 Another example of a primary surface heat exchager is illustrated in FR-A-2315674 in which a number of heat exchange cores are provided, each core being formed from a number of stacked sheets with upturned edges to maintain the sheets spaced apart. This requires a large number of welds to connect the sheets together which is undesirable.
  • a major drawback of the prior art heat exchanger construction has been the presence of high stress concentration factors which have resulted from the need to crush the edges. In some applications the effect has been that of producing a multiplicity of cracks. Another problem has been the failure of the weld to penetrate at certain junctions, which results in a preformed crack. While such stress concentration factors may not be significant when the assembly is preloaded in compression, as intended, and when the transients are not steep, high stresses which lead to premature failures may appear under severe operating conditions and after prolonged periods of operation during which the preload is likely to be relaxed.
  • DE-A-2523151 discloses a heat exchange core formed from a plurality of walls connected together in series to define fluid flow passages between adjacent pairs of walls, the ends of alternate passages being closed.
  • the relatively thin walls are only supported at each end and this can lead to problems during use when the walls may flex and inhibit fluid flow along the passages.
  • a heat exchange core comprises a unitary strip providing a plurality of walls in series to define fluid flow passages between adjacent pairs of walls, a portion of each end of every alternate passage, forming a first group of passages, being closed, the closed portions on the end of the core being in alignment and a portion of each end of the remaining passages, forming a second group of passages, being closed, the closed portions of the second group on each end of the core being in alignment with each other whereby the closed end portions of each group of passages are adjacent open end portions and offset from closed end portions of the other group of passages, the walls being undulated between the open ends of the fluid passages, and is characterised in that a plurality of rows of spaced apart bosses are provided between the open ends of the fluid passages, the bosses separating adjacent walls and guiding fluid flow along the passages in use.
  • a method of forming a heat exhange core comprises pleating a unitary, elongate strip of heat conducting material to form a plurality of walls defining fluid passages therebetween, whereby the open side of each fluid passage opens in a direction opposite to that of the next adjacent fluid passages on either side thereof; closing a portion of each open end of every alternate fluid passage to form a first group of fluid passages having adjacent aligned closed portions and aligned open portions at either end thereof; closing a portion of each open end of the remaining fluid passages to form a second group of fluid passages having adjacent aligned closed portions and aligned open portions at either end thereof whereby the closed end portions of each group of fluid passages are adjacent the open end portions and offset from the closed end portions of the other group of fluid passages; and forming undulations in the unitary strip prior to pleating the strip, the undulations extending between the side edges thereof, characterised in that a plurality of rows of spaced apart bosses are provided between
  • rows of spaced apart bosses are formed in the walls of the heat exchange core and have the dual function of maintaining the walls of the passages spaced apart while at the same time assisting in guiding fluid flow along the passages.
  • a further advantage is that the spaces between the bosses induce fluid turbulence in the flow path and thus enhance still further the . heat transfer characteristics in the core. In this way, maximum heat exchange efficiency is achieved.
  • a low profile heat exchanger may be constructed from one or more heat exchange cores in accordance with the invention.
  • Each core is formed from a single sheet of thin material which has been pleated to any depth desired. Before pleating, the longitudinal edges of thin sheet may be serrated to provide fluid entrance ramps that minimise blockage, and the surface of the sheet may be embossed to define flow channels and to provide a means for directing flow and controlling turbulence.
  • a heat exchange core comprises a unitary strip providing a plurality of walls in series to define fluid flow passages between adjacent pairs of walls, a portion of each end of every alternate passage, forming a first group of passages, being closed, the closed portions on each end of the core being in alignment and a portion of each end of the remaining passages, forming a second group of passages, being closed, the closed portions of the second group on each end of the core being in alignment with each other whereby the closed end portions of each group of passages are adjacent open end portions and offset from closed end portions of the other group of passages, the walls being undulated between the open ends of the fluid passages, wherein a plurality of rows of spaced apart bosses are provided between the open ends of the fluid passages, the bosses separating adjacent walls and guiding fluid flow along the passages in use; and is characterised in that a strip is attached to the walls and extends across at least one end of the heat exchange core between the closed and open end portions of
  • a method of forming a heat exchange core comprises pleating a unitary, elongate strip of heat conducting material to form a plurality of walls defining fluid passages therebetween, whereby the open side of each fluid passage opens in a direction opposite to that of the next adjacent fluid passages on either side thereof; closing a portion of each open end of every alternate fluid passage to form a first group of fluid passages having adjacent, aligned closed portions and aligned open portions at either end thereof; closing a portion of each open end of the remaining fluid passages to form a second group of fluid passages having adjacent closed portions and aligned open portions at either end thereof whereby the closed end portions of each group of fluid passages are adjacent the open end portions and offset from the closed end portions of the other group of fluid passages, and forming undulations in the unitary strip prior to pleating the strip, the undulations extending between the side edges thereof and comprising a plurality of rows of spaced apart bosses between the open ends of the fluid passages
  • one or more strips which are preferably corrugated, assists in holding each core in its pleated form.
  • Figure 1 illustrates a single sheet used to form one of the pleated assemblies of a heat exchange core.
  • the single sheet indicated generally at 10, is a long rectangular strip of heat exchange material, for example a suitable thin metal, such as heat resistant steel.
  • the width of the sheet 10 indicated at 12 determines the length of the resulting pleated assembly, and may be varied by the designer to fit the desired heat exchanger application.
  • the longitudinal edges of the sheet are serrated or cut in a sawtooth pattern so that the distance 14 between notches 16 is about equal to the desired height of the pleated assembly.
  • the apexes or points of the serrated edge are shown at 18, and the distance of an edge 20 extending between notch 16 and point 18 should preferably be equal to the height of the pleated assembly as indicated at 14 to eliminate fluid flow blockage.
  • the assembly may be about 1-2 inches (2.3-5 cm) in height at 14 and the width 12 may be about 6 ⁇ 7 inches (15 ⁇ 17 cm).
  • the configuration of the serrated edges of the sheet 10 can be altered to meet varying structural requirements.
  • the apexes 18 may be rounded instead of pointed, and the edge 20 can be curved rather than straight.
  • the pleated assembly is formed in a manner depicted in Figures 2 and 3 or 2' and 3.
  • the serrated sheet of heat exchange material 10 is divided into sections or walls 22 and 24 which are embossed by means of conventional dies, shaped rollers or any other embossing techniques.
  • the embossing serves to separate the subsequently formed pleats of the heat exchanger accurately and to guide the fluid flow through the completed heat exchanger.
  • the embossing may space the pleates for a distance of about .030 inches (0.076 cm).
  • each section 22 and 24 may be embossed in a U-shaped or Z-shaped configuration respectively as shown by the rows of bosses 26 on section 22 and the rows of bosses 28 on section 24. While only four rows of bosses 26 and four rows of bosses 28 are shown, the number of rows could be much higher and is limited only by the size of the sections 22 and 24.
  • Fluid flow channels 27 are defined on the face of each section 22 and 24 between the rows of bosses 26 and 28. The interruptions between bosses in a row induce fluid turbulence in the flow path defined thereby and thus enhance the heat transfer characteristics of the pleated assembly formed from the sheet 10.
  • the sheet 10 will be pleated into a pleated assembly which forms part of the core of the heat exchanger module depicted in Figure 6, it is necessary to embosss the sheet so that the pleats are spaced far enough apart to allow fluid flow between them. This is accomplished by embossing sections 22 and 24 in opposite directions. Thus in Figure 2, the bosses 26 on section 22 project upwardly, while the bosses 28 on section 24 project downwardly. This alternate. arrangement is maintained throughout the length of the sheet 10.
  • the sheet 10 is pleated by folding it along lines or crest portions 34 between the sections or walls 22 and 24.
  • Pleating may be accomplished mechanically in any conventional manner, such as on machines utilizing dull-edged knife blades like those used for pleating filter paper in the manufacture of air cleaners and oil filters, but which have been modified to pleat thin metal or heat exchange material rather than paper.
  • Figure 3 shows the embossed sheet 10 being pleated and compressed at the lower end 36 to form the pleated assembly shown in Figure 4.
  • the sections 22 and 24 of the sheet are compressed together until the raised bosses 26 and 28 contact the next adjacent section of the sheet.
  • the height of such bosses accurately controls the spacing between adjacent sections when the sheet 10 is pleated and compressed.
  • bosses on adjacent sections 22 and 24 be precluded from nesting when the sections are compressed together. This may be accomplished, as illustrated in Figure 2, by placing the bosses on section 24 so that they fall in the spaces between the bosses on section 22 when the two sections are pleated.
  • the bosses may be of different depths, and it is possible to have both deep and shallow bosses on the same sheet.
  • the pleated assembly is also held together by welds 42 and 44 which plug one side of the open ends of the fluid passages between sections 22 and 24, leaving the remaining sides 43 and 45 open.
  • the passages are plugged at both ends, although only one end is shown in Figure 5. Additional external clamping may be provided to preload the heat exchanger pleats.
  • the heat exchanger module 46 may be formed by stacking at least two pleated assemblies 38 within a housing 48 as shown in Figure 6.
  • the upper pleated assembly 38a is placed over the lower pleated assembly 38b with a spacer 50 between them.
  • the spacer 50 is essentially either a solid sheet or a mesh or perforated strip and is shown extending along the entire length of line 34 between sections of the pleated assemblies from point 52 to point 54. However, the spacer 50 may be placed so that it stops short of points 52 and 54. It is possible, by varying the thickness and the length of the spacer 50, to reduce fluid flow blockage beyond the reduction achieved by means of the fluid entry ramps defined by edges 20. As previously mentioned in discussing Figure 1, the length of edges 20 should be equal to pleat depth 14 to minimize fluid flow blockage.
  • the ramps are shown to be straight, longer ramps may be achieved within the same dimensions by curving edges 20, thus lengthening the ramps while maintaining the compactness of the unit.
  • Hot and cold fluid manifolds are attached to the ends of the two stacked pleated assemblies as shown in Figure 6, and result in a low profile heat exchanger.
  • Inlet manifolds 56 provide hot fluid, for example hot exhaust gas from a gas turbine, through fluid passages 58. This hot fluid follows the path shown by the white arrows 58 to outlet manifolds 60 which collect the previously hot fluid after heat has been transferred therefrom in the heat exchanger core.
  • cool fluid as, for example air from the compressor of a gas turbine engine, is supplied to the path shown by arrows 64 by a cool fluid inlet manifold 62. This cool fluid flows through the pleated assemblies 38a and 38b along the paths indicated by the dark arrows, is heated, and then is collected by an outlet manifold 66.
  • the corrugated strips 40 are preferably welded to the housing 48 to form the manifolding.
  • the width of corrugated strip 40 introduces a desired flexibility into the heat exchanger unit, as it allows the reduction of stresses in the presence of thermal gradients. It is also possible, but less desirable, to weld rigid manifolding directly to the pleated assemblies, which is not shown in Figure 6. However, this means of attaching the manifolding to the pleated assembly does not provide the flexibility and consequent dissipation of thermal stresses possible with the arrangement shown in Figure 6.
  • FIG. 7 illustrates an end view of the heat exchanger module 46 used as a recuperator for receiving hot exhaust uunand compressed air from a gas turbine engine.
  • Hot gas input manifolds 56 are at the top and bottom and the hot combustion air output manifold 66 is in the center. Hot gas flows in alternate passages 58 while air to be heated flows in the opposite direction through the intermediate passages 64.
  • the housing 48 closes the open ends of the passages 58.
  • FIG. 8 A second embodiment of the present invention is diagrammatically shown in Figures 8, 9, and 10.
  • Heat exchanger sheet material 72 which has been serrated along the longitudinal edges in the same manner as sheet 10 in Figure 1 and subsequently embossed, is bent between points 68 and 70 by passing it over shaped rollers, which are not shown in Figure 8, prior to pleating to form a sheet which is rippled in cross section (Figure 9).
  • This structure provides flexibility to the pleats in the direction 68-70.
  • Figure 10 which corresponds to Figure 3, shows the rippled sheet 72 being pleated and compressed into a bent pleated assembly 74.
  • the method depicted in Figures 8, 9, and 10 results in increased flexibility, not only in the pleats themselves, but also in the welded plugs 42 and 44 used to seal alternate flow passages as shown in Figures 5 and 7.
  • the compressed pleated assembly shown at 36 in Figure 3 can be made to assume an arcuate shape or even an "S" shape, (not shown) when viewed in the direction of the crest portions or edges 34, as depicted in Figure 11.
  • the sheet 10 can be treated in an alternate method after pleating to enhance fluid flow and flexibility. This is accomplished as shown in Figure 12.
  • a pleated and compressed sheet, indicated generally at 76, is passed over a roller 78, which causes the pleats to separate as at 80 while remaining compressed at 82, thus allowing cams, rollers, pawls, or other suitable mechanisms to be introduced into the wide gaps at 80 to spread the pleats at edge 34 to any desired distance.
  • the pleated and compressed sheet After passing over roller 78, the pleated and compressed sheet passes over roller 84 where the wide gaps 80 become compressed at 86 and the pleats which were compressed at 82 become separated at 88, thus permitting the same type of cams, rollers or pawls to bow the pleats as at 34, resulting in a compact and bowed, pleated assembly after the core passes over the roller 84 as shown in Figure 11.
  • This introduces flexibility in the direction of the width of the strip thus minimizing thermal stresses.
  • the heat exchanger module 46 may be effectively employed as a recuperator for a gas turbine engine or for other heat exhange applications, as, for example, in steel heat treating or melting furnaces.
  • the inlet manifold 62 is connected to a source of cool fluid to be heated while the inlet manifolds 56 are connected to a source of heated fluid.
  • the inlet manifolds 56 would be connected to receive hot exhaust gases from the engine while the inlet manifold 62 would be connected to receive compressor discharge air from the engine.
  • the cooler discharge air passes through the pleated assemblies 38a and 38b with the counter flowing hot exhaust gas, the air is heated by the heat transfer provided by heat exchange sections 22 and 24.
  • the exhaust gas then passes out of the outlet manifolds 60 and is normally vented to the atmosphere while the heated air passes to the outlet manifold 66.
  • This outlet manifold is connected to the combustor of the gas turbine engine and proceeds on through the engine in the conventional manner.

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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)

Claims (15)

1. Noyau d'échange de chaleur (38) comprenant une bande unitaire (10) formant plusieurs parois (22, 24) en série, qui délimitent des passages d'écoulement de fluide (58, 64) entre les deux parois de chaque paire de parois adjacentes, une partie (44) de chaque extrémité d'un passage sur deux, qui forment un premier groupe de passages (58), étant fermée, les parties fermées, qui se trouvent à chaque extrémité du noyau, étant en alignement et une partie (42) de chaque extrémité des passages restants, qui forment un second groupe de passages (64), étant fermée, les parties fermées du second groupe, qui se trouvent à chaque extrémité du noyau, étant en alignement mutuel, de telle sorte que les parties d'extrémité fermées de chaque groupe de passages sont adjacentes à des parties d'extrémité ouvertes (45, 43) et décalées par rapport aux parties d'extrémité fermées de l'autre groupe de passages, les parois étant ondulées entre les extrémités ouvertes des passages de fluide, plusieurs rangées de protubérances mutuellement, espacées (26, 28) étant prévues entre les extrémités ouvertes des passages de fluide, ces protubérances séparant les parois adjacentes et guidant l'écoulement des fluides le long des passages en cours d'utilisation; caractérisé en ce qu'une bande (40) est fixée aux parois (22, 24) et s'étend transversalement à au moins une extrémité du noyau d'échange de chaleur (38) entre les parties d'extrémité fermées et ouvertes (42, 43, 44, 45) des passages de fluide (58, 64).
2. Noyau (38) selon la revendication 1, dans lequel les protubérances (26, 28) ne sont formées que d'un seul côté de chaque paroi (22, 24), les protubérances de parois adjacentes (22, 24) s'étendant sur les faces en regard de celles-ci.
3. Noyau (38) selon la revendication 2, dans lequel les protubérances (26, 28) des parois adjacentes (22, 24) ne sont pas alignées de façon à empêcher un emboîtement des parois.
4. Noyau (38) selon l'une quelconque des revendications 1 à 3, dans lequel les protubérances (26, 28) sont allongées.
5. Noyau (38) selon l'une quelconque des revendications précédentes, dans lequel la bande (40) est ondulée de façon à assurer une certaine flexibilité dans le sens de sa longueur.
6. Echangeur de chaleur à surface primaire (46) comprenant au moins un noyau d'échange de chaleur (38), le ou chaque noyau comprenant une bande unitaire (10) formant plusieurs parois (22, 24) en série qui délimitent des passages d'écoulement de fluide (58, 64) entre les deux parois de chaque de parois adjacentes, une partie (44) de chaque extrémité d'un passage sur deux, qui forment un premier groupe de passages (58), étant fermée, les parties fermées, qui se trouvent à chaque extrémité du noyau, étant en alignement et une partie (42) de chaque extrémité des passages restants, qui forment un second groupe de passages (64), étant fermée, les parties fermées, du second groupe, qui se trouvent à chaque extrémité du noyau, étant en alignement mutuel, de telle sorte que les parties d'extrémité fermées de chaque groupe de passages sont adjacentes à des parties d'extrémité ouvertes (45, 43) et décalées par rapport parties d'extrémité fermées de l'autre groupe de passages, les parois étant ondulées entre les extrémités ouvertes des passages de fluide, plusieurs rangées de protubérances mutuellement espacées (26, 28) étant prévues entre les extrémités ouvertes des passages de fluide, ces protubérances séparant les parois adjacentes et guidant l'écoulement des fluides le long des passages en cours d'utilisation; un premier moyen d'admission de fluide (56) s'étendant transversalement aux parties ouvertes (43) du premier group de passages de fluide (58) et aux parties fermées (42) du second groupe de passages de fluide (64) à l'une des extrémités de noyau d'échange de chaleur (38); un premier moyen d'évacuation de fluide (60) disposé à l'autre extrémité du noyau d'échangeur de chaleur (38) et s'étendant transversalement aux parties ouvertes (43) du premier groupe de passages de fluide (58) et aux parties fermées (42) du second groupe de passages de fluide (64) à cette même extrémité, les premiers moyens d'admission et d'évacuation de fluide (56, 60) communiquant avec le premier groupe de passages de fluide (58); un second moyen d'admission de fluide (62) s'étendant transversalement aux parties ouvertes (45) du second group de passages de fluide (64) et aux parties fermées (44) du premier groupe de passages de fluide (58) à l'une des extrémités du noyau d'échange de chaleur (38); et un second moyen d'évacuation de fluide (66) disposé à l'extrémité du noyau d'échange de chaleur (38) opposée au second moyen d'admission de fluide (62), s'étendant transversalement aux parties ouvertes (45) du second groupe de passages de fluides (64) et transversalement aux parties fermées (44) du premier groupe de passages de fluide (58), les seconds moyens d'admission et d'évacuation (62, 66) communiquant avec le second groupe de passages de fluide (64), caractérisé en ce que, pour le ou pour chaque noyau d'échange de chaleur, une bande (40) est fixée aux parois (22, 24) et s'étend transversalement à au moins l'une des extrémités du noyau d'échange de chaleur (38) entre les parties d'extrémité fermées et ouvertes (42, 43, 44, 45) des passages de fluide (58, 64).
7. Echangeur de chaleur à surface primaire (46) selon la revendication 6, dans lequel les premier et second moyens d'admission de fluide (56, 68) se trouvent aux extrémités opposées du noyau (38).
8. Echangeur de chaleur à surface primaire (46) selon la revendication 6 ou la revendication 7, comprenant deux noyaux d'échange de chaleur (38a, 38b) selon l'une quelconque des reven-, dications 1 à 5, les noyaux d'échange de chaleur (38a, 38b) étant mutuellement positionnés de telle façon que les parties (45) de chaque noyau, dans lesquelles s'ouvrent les seconds groupes respectifs de passages de fluide (64), soient adjacentes et en alignement; dans lequel le premier et le second moyens d'admission de fluide (56, 62) sont respectivement en communication avec le premier et le second groupes de passages de fluide (58, 64) de chaque noyau, et le premier et le second moyens d'évacuation de fluide (60, 66) sont respectivement en communication de fluide avec le premier et le second groupes de passages de fluide (58, 64) de chaque noyau.
9. Echangeur de chaleur à surface primaire (46) selon l'une quelconque des revendications 6 à 8, comportant en outre une enveloppe (48) délimitant partiellement les premiers et seconds moyens d'admission et d'évacuation de fluide, espacée de et enfermant les extrémités opposées du ou de chaque noyau d'échange de chaleur (38), dans lequel une bande (40) est fixée à chaque extrémité du ou de chaque noyau (38) et s'étend vers l'extérieur à partir de l'extrémité respective du noyau vers l'enveloppe (48) de façon à diviser l'intérieur de l'enveloppe en formant les premier et second moyens d'admission et d'évacuation de fluide.
10. Procédé de formation d'un noyau d'échange de chaleur (38), ce procédé consistant à plisser une bande allongée unitaire (10) de matériau conducteur de la chaleur de façon à former plusieurs parois délimitant entre elles des passages de fluide (58, 64), de sorte que le côté ouvert de chaque passage de fluide s'ouvre dans une direction oppposée à celle des passages de fluide immédiatement adjacents, de chaque côté de ceux-ci; à fernerune partie (44) de chaque extrémité ouverte d'un passage de fluide sur deux (58) de façon à former un premier groupe de passages de fluide (58) ayant des parties fermées alignées adjacentes (44) et des parties ouvertes alignées (43) à chacune de leurs extrémités; à fermer une partie (42) de chaque extrémité ouverte des passages de fluide restants (64) de façon à former un second groupe de passages de fluide (64) ayant des parties fermées alignées adjacentes (42) et des parties ouvertes alignées (45) à chacune de leurs extrémités, de telle sorte que les parties d'extrémité fermées (42, 44) de chaque groupe de passages de fluide sont adjacentes aux parties d'extrémité ouvertes (43, 45) et décalées par rapport aux parties d'extrémité fermées de l'autre groupe de passages de fluide, et à former des ondulations dans la bande unitaire (10) préalablement au plissage de cette bande (10), les ondulations s'étendant entre ses bords latéraux et comprenant plusieurs rangées de protubérances mutuellement espacées (26, 28) entre les extrémités ouvertes des passages de fluide, ces protubérances séparant les parois adjacentes et guidant l'écoulement des fluides le long des passages en cours d'utilisation; caractérisé par la fixation d'une bande allongée (40) transversalement à au moins l'une des extrémités de la bande unitaire (10) après l'opération de plissage.
11. Procédé selon la revendication 10, consistant en outre à découpler en dents de scie la bande unitaire de matériau conducteur de la chaleur (10) le long de chaque côté de celle-ci, préalablement à l'opération de plissage, de façon à former un sommet (18) à l'extrémité de chaque paroi (22, 24), les bords d'extrémité (20) étant inclinés à l'opposé de chaque côté du sommet (18) vers des pointes (16), au niveau des lignes de séparation (34) entre les parois respectives et les parois qui leur sont adjacentes.
12. Procédé selon la revendication 10 ou la revendication 11, consistant en outre à à fermer les extrémités de chaque passage de fluide du premier groupe de passages de fluide (58) le long des bords inclinées (20) s'étendant dans une première direction opposée à chaque sommet (18), et à fermer les extrémités de chaque passage de fluide du second groupe de passages de fluide (64) le long des bords inclinées (20) s'étendant dans une second direction opposée, à l'opposé du sommet (18).
13. Procédé selon l'une quelconque des revendications 10 à 12, consistant en outre à séparer partiellement des parois (22, 24) de la bande plissée (10) et à écarter les parois séparées d'une distance choisie à l'avance.
EP81900865A 1980-07-07 1980-07-07 Echangeur de chaleur a profil bas et son procede de fabrication Expired EP0055711B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US1980/000857 WO1982000194A1 (fr) 1980-07-07 1980-07-07 Echangeur de chaleur a profil bas et son procede de fabrication

Publications (3)

Publication Number Publication Date
EP0055711A1 EP0055711A1 (fr) 1982-07-14
EP0055711A4 EP0055711A4 (fr) 1983-06-09
EP0055711B1 true EP0055711B1 (fr) 1985-10-09

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EP81900865A Expired EP0055711B1 (fr) 1980-07-07 1980-07-07 Echangeur de chaleur a profil bas et son procede de fabrication

Country Status (5)

Country Link
EP (1) EP0055711B1 (fr)
JP (1) JPS57500945A (fr)
CA (1) CA1140531A (fr)
DE (1) DE3071178D1 (fr)
WO (1) WO1982000194A1 (fr)

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DE4333904A1 (de) * 1993-09-27 1995-03-30 Eberhard Dipl Ing Paul Kanalwärmetauscher

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NL9201945A (nl) * 1992-11-05 1994-06-01 Level Energietech Bv Warmtewisselaar.
WO1995009338A1 (fr) * 1993-09-27 1995-04-06 Eberhard Paul Echangeur de chaleur a canaux
JPH0942869A (ja) * 1995-07-28 1997-02-14 Honda Motor Co Ltd 熱交換器
JPH0942867A (ja) * 1995-07-28 1997-02-14 Honda Motor Co Ltd 熱交換器
JPH0942865A (ja) * 1995-07-28 1997-02-14 Honda Motor Co Ltd 熱交換器
AUPN697995A0 (en) * 1995-12-04 1996-01-04 Urch, John Francis Metal heat exchanger
JP3685890B2 (ja) * 1996-10-17 2005-08-24 本田技研工業株式会社 熱交換器
JPH10122768A (ja) * 1996-10-17 1998-05-15 Honda Motor Co Ltd 熱交換器
CA2269058C (fr) * 1996-10-17 2003-04-15 Honda Giken Kogyo Kabushiki Kaisha Echangeur de chaleur
BR9712534A (pt) * 1996-10-17 1999-10-19 Honda Motor Co Ltd Permutador de calor
WO1998033030A1 (fr) * 1997-01-27 1998-07-30 Honda Giken Kogyo Kabushiki Kaisha Echangeur thermique
GB9719199D0 (en) * 1997-09-10 1997-11-12 Advanced Design & Mfg Ltd Heat recovering ventilator system
DE19813119A1 (de) * 1998-03-25 1999-10-07 Inst Energetik Und Umwelt Ggmb Turbulenzwärmerückgewinner und Anwendungen desselben
US6186223B1 (en) 1998-08-27 2001-02-13 Zeks Air Drier Corporation Corrugated folded plate heat exchanger
EP1085273A1 (fr) 1999-09-14 2001-03-21 FPL Wärmerückgewinnung-Lüftung GmbH Dispositif et méthode pour échange de chaleur
FR2913765B1 (fr) * 2007-03-16 2012-08-10 Pierre Vironneau Nappe de circulation de fluide, procede pour realiser une telle nappe et utilisation de telles nappes pour la realisation d'un echangeur thermique
US20130056186A1 (en) * 2011-09-06 2013-03-07 Carl Schalansky Heat exchanger produced from laminar elements
DE102016015125A1 (de) * 2016-12-19 2018-06-21 Menk Apparatebau Gmbh Lamellenanordnung und Wärmetauscher
US11035626B2 (en) * 2018-09-10 2021-06-15 Hamilton Sunstrand Corporation Heat exchanger with enhanced end sheet heat transfer
GB2604380A (en) * 2021-03-04 2022-09-07 Energy Recovery Ind Corporation Ltd An air to air counter flow heat exchanger

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DE4333904A1 (de) * 1993-09-27 1995-03-30 Eberhard Dipl Ing Paul Kanalwärmetauscher

Also Published As

Publication number Publication date
JPS57500945A (fr) 1982-05-27
EP0055711A1 (fr) 1982-07-14
EP0055711A4 (fr) 1983-06-09
CA1140531A (fr) 1983-02-01
DE3071178D1 (en) 1985-11-14
WO1982000194A1 (fr) 1982-01-21

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