EP0798527A1 - Spiral heat exchanger - Google Patents

Spiral heat exchanger Download PDF

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Publication number
EP0798527A1
EP0798527A1 EP96202200A EP96202200A EP0798527A1 EP 0798527 A1 EP0798527 A1 EP 0798527A1 EP 96202200 A EP96202200 A EP 96202200A EP 96202200 A EP96202200 A EP 96202200A EP 0798527 A1 EP0798527 A1 EP 0798527A1
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EP
European Patent Office
Prior art keywords
sheets
heat exchanger
sheet
angular sectors
winding
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.)
Granted
Application number
EP96202200A
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German (de)
French (fr)
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EP0798527B1 (en
Inventor
Hubert Antoine
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Antoine Hubert
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Antoine Hubert
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Filing date
Publication date
Priority to ES96202200T priority Critical patent/ES2111410T3/en
Application filed by Antoine Hubert filed Critical Antoine Hubert
Priority to AT96202200T priority patent/ATE159097T1/en
Priority to EP96202200A priority patent/EP0798527B1/en
Priority to DE69600073T priority patent/DE69600073T2/en
Priority to PCT/BE1997/000088 priority patent/WO1998005916A1/en
Priority to AU39348/97A priority patent/AU3934897A/en
Priority to US09/308,647 priority patent/US6263961B1/en
Publication of EP0798527A1 publication Critical patent/EP0798527A1/en
Application granted granted Critical
Publication of EP0798527B1 publication Critical patent/EP0798527B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • F28D9/0012—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 apparatus having an annular form
    • F28D9/0018—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 apparatus having an annular form without any annular circulation of the heat exchange media
    • 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
    • F28D9/04—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 spirally-wound plates or laminae
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/355—Heat exchange having separate flow passage for two distinct fluids
    • Y10S165/398—Spirally bent heat exchange plate

Definitions

  • the invention relates to a heat exchanger wound in a spiral, where the fluids arrive, circulate and open in countercurrent, in the direction of the winding axis.
  • recuperators for gas turbines In the wide field of application of heat exchangers, one of the most demanding applications is that of recuperators for gas turbines. Indeed, they must be compact, high efficiency, inexpensive and reliable.
  • Efficiency and compactness can be obtained by using the concept of primary surface, with channels of small hydraulic diameter and by circulating the two counter-current fluids.
  • the cost price will be low if the exchanger consists of the assembly of a small number of printed elements and continuously wound to form a roll.
  • the pressure drops will be reduced if the passage sections offered to the two fluids are sufficient: this is obtained by circulating the fluids axially and not tangentially in a spiral exchanger.
  • the exchangers are subjected to high thermal loads and thermal shocks resulting from transient variations in the operation of the turbine. Reliability is linked to resistance to thermal shock.
  • Heat exchangers consisting of a winding of a pair of sheets, between which the fluids pass countercurrently, in the axial direction of the roll thus formed, are known: see for example a recent patent (1995) from the company Rolls- Royce. These coiled exchangers distribute the flow by cutouts made in the sheet and welded in pairs at the time of winding.
  • the distribution and the collection of flows are carried out in plate exchangers stacked by cutouts made in the plates.
  • the edges of these cutouts are brazed or welded during stacking [see US Pat. No. 4,073,340] or lined with a seal, as in the well-known plate exchangers from Alfa-Laval.
  • the invention aims to produce a heat exchanger formed by winding a pair of sheets where the fluids circulate in counter-current in the direction of the axis of the winding and arrive and open on the opposite faces of the cylindrical roller constituted by the 'leaf rolling.
  • This avoids creating distribution cutouts inside the exchanger, which eliminates both stress concentrations, welding problems, inspection and repair of these flanges embedded in the mass of the exchanger.
  • This results in greater freedom in the choice of dimensions and shapes of the distributor-collectors, since they are external to the exchanger itself.
  • the wrapped exchanger concept eliminates the need for closing bars, since there is no longer any edge to close.
  • the exchanger consists of a core 1 to which are attached scoops 8 for supplying and discharging air 2, FIGS. 1 and 3.
  • the air penetrates by angular sectors 5 regularly spaced and alternating with angular sectors 6 for the outlet of the gases.
  • the core consists of a winding of a pair of sheets a and b around a z axis, Figure 1.
  • the sheet a is wrinkled longitudinally, that is to say along the winding axis z, while the sheet b is transversely, that is to say along the tangential winding direction ( Figures 4 and 5).
  • the sheet a has three axial zones of wrinkles: zones II and IV near the edges and central zone III ( Figure 4).
  • the sheet b is wrinkled on these same three zones and also comprises, on the zones I and V of entry-exit, flanges 7 offset alternately to form the gates of arrival-exit of the fluids (FIGS. 5 and 2).
  • the offset edges of b come against the edge of a and vice versa, during winding. They are definitively brazed together, once the core has been wound up ( Figure 2). The alternative offset of the edges of b must be done during winding and in synchronization with it. It is indeed necessary that the gills thus formed are of increasing length at each winding turn and in angular phase to form very regular angular sectors.
  • the scoops 8 are then brazed on the faces of the core 1, with their edges 9 brazed on the edges 10 of the angular sectors, as indicated in FIG. 3.
  • the sum of the heights of the wrinkles of a and b is constant over all areas; it is worth the offset of b on the zones I and V and allows the winding without radial deformation of the pair ab, because it is of constant thickness equivalent to the sum of the heights of the wrinkles of a and b, as illustrated by the figure 6.
  • zones II and IV the wrinkles of a and b have comparable heights: being perpendicular and in contact with their crests, they allow the passage of air and gas in both axial and tangential directions: these zones are distribution zones of the flow from the entry sectors to zone III; these are cross-flow zones, as shown in Figure 7.
  • zone III the flows are essentially parallel and opposite; that is to say against the current (Figure 7), because the tangential wrinkles of b are minimal and those of a, axial, are large ( Figure 6).
  • This type of exchanger can also be produced by replacing the wrinkles printed in relief by fins of the same height, filling with flat sheets.

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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

The heat exchanger is constituted by a core (1) to which are fixed inlet and outlet air scoops. On one face of the core the air penetrates through regularly spaced angular sectors (5) and gas leaves through alternate angular sectors (6). On the core opposite face the air leaves through angularly spaced angular sectors (3) alternating with gas inlet angular sectors (4). The core is formed by winding a pair of sheets around an axis (z). One sheet is longitudinally rippled whilst the other sheet is transversely rippled. The first sheet has three axial ripple zones near the edges and a central zone. The other sheet is also rippled on these same three zones and also has inlet-outlet zones, with its edges alternately curved to form fluid inlet-outlet scoops.

Description

L'invention concerne un échangeur de chaleur enroulé en spirale, où les fluides arrivent, circulent et débouchent à contrecourant, dans la direction de l'axe d'enroulement.The invention relates to a heat exchanger wound in a spiral, where the fluids arrive, circulate and open in countercurrent, in the direction of the winding axis.

Dans le vaste champ d'application des échangeurs de chaleur, une des applications les plus exigeantes est celle des récupérateurs pour turbines à gaz. En effet, ils doivent être compacts, de haute efficacité, peu chers et fiables.In the wide field of application of heat exchangers, one of the most demanding applications is that of recuperators for gas turbines. Indeed, they must be compact, high efficiency, inexpensive and reliable.

L'efficacité et la compacité peuvent s'obtenir en utilisant le concept de surface primaire, avec des canaux de petit diamètre hydraulique et en faisant circuler les deux fluides à contrecourant.
Le prix de revient sera peu élevé si l'échangeur est constitué par l'assemblage d'un petit nombre d'éléments imprimés et enroulés en continu pour former un rouleau.
Les pertes de charge seront réduites si les sections de passage offertes aux deux fluides sont suffisantes : ceci s'obtient en faisant circuler les fluides axialement et non tangentiellement dans un échangeur spirale. Les échangeurs sont soumis à de fortes charges thermiques et aux chocs thermiques résultant des variations transitoires de fonctionnement de la turbine. La fiabilité est liée à la résistance aux chocs thermiques.Efficiency and compactness can be obtained by using the concept of primary surface, with channels of small hydraulic diameter and by circulating the two counter-current fluids.
The cost price will be low if the exchanger consists of the assembly of a small number of printed elements and continuously wound to form a roll.
The pressure drops will be reduced if the passage sections offered to the two fluids are sufficient: this is obtained by circulating the fluids axially and not tangentially in a spiral exchanger. The exchangers are subjected to high thermal loads and thermal shocks resulting from transient variations in the operation of the turbine. Reliability is linked to resistance to thermal shock.

Des échangeurs de chaleur constitués d'un enroulement d'une paire de feuillets, entre lesquels les fluides passent à contrecourant, dans le sens axial du rouleau ainsi formé, sont connus : voir pour exemple un brevet récent (1995) de la société Rolls-Royce. Ces échangeurs enroulés distribuent le flux par des découpes pratiquées dans la feuille et soudées par paires au moment de l'enroulement.Heat exchangers consisting of a winding of a pair of sheets, between which the fluids pass countercurrently, in the axial direction of the roll thus formed, are known: see for example a recent patent (1995) from the company Rolls- Royce. These coiled exchangers distribute the flow by cutouts made in the sheet and welded in pairs at the time of winding.

Une difficulté intéressante dans la conception des échangeurs de chaleur est la distribution du flux entrant dans les multiples petits canaux sièges de l'échange de chaleur et ensuite, la collecte de ces nombreux flux en un seul flux sortant. Ce processus doit avoir lieu sans pertes de charge excessives, ni création de contraintes mécaniques excessives dues aux gradients thermiques.An interesting difficulty in the design of heat exchangers is the distribution of the flow entering the multiple small channels which are the seat of the heat exchange and then, the collection of these numerous flows in a single outgoing flow. This process must take place without excessive pressure drops, or creation of excessive mechanical stresses due to thermal gradients.

La distribution et la collecte des flux s'effectuent dans les échangeurs à plaques empilées par des découpes pratiquées dans les plaques. Les rebords de ces découpes sont brasées ou soudées lors de l'empilement [ voir brevet US 4 073340 ] ou garnis d'un joint d'étanchéité, comme dans les échangeurs à plaque de la société Alfa-Laval bien connus.The distribution and the collection of flows are carried out in plate exchangers stacked by cutouts made in the plates. The edges of these cutouts are brazed or welded during stacking [see US Pat. No. 4,073,340] or lined with a seal, as in the well-known plate exchangers from Alfa-Laval.

D'autres échangeurs à plaques empilées n'ont pas ces découpes [ voir SAE 851254 : Development, Fabrication and application of a Primary Surface Gas Turbine Recuperator, E.L.Parsons], mais les côtés des plaques sont alors garnies de barrettes de fermeture.Other stacked plate heat exchangers do not have these cutouts [see SAE 851254: Development, Fabrication and application of a Primary Surface Gas Turbine Recuperator, E.L. Parons], but the sides of the plates are then fitted with closing strips.

L'invention vise à réaliser un échangeur de chaleur formé par enroulement d'une paire de feuilles où les fluides circulent à contrecourant dans le sens de l'axe de l'enroulement et arrivent et débouchent sur les faces opposées du rouleau cylindrique constitué par l'enroulement des feuilles. On évite ainsi de créer des découpes de distribution à l'intérieur de l'échangeur, ce qui élimine à la fois les concentrations de contraintes, les problèmes de soudage, d'inspection et de réparation de ces rebords noyés dans la masse de l'échangeur. Il en résulte une plus grande liberté dans le choix des dimensions et des formes des distributeurs-collecteurs, car ils sont extérieurs à l'échangeur proprement dit. Le concept d'échangeur enroulé permet de se passer des barrettes de fermeture, puisqu'il n'y a plus de bord à fermer.The invention aims to produce a heat exchanger formed by winding a pair of sheets where the fluids circulate in counter-current in the direction of the axis of the winding and arrive and open on the opposite faces of the cylindrical roller constituted by the 'leaf rolling. This avoids creating distribution cutouts inside the exchanger, which eliminates both stress concentrations, welding problems, inspection and repair of these flanges embedded in the mass of the exchanger. This results in greater freedom in the choice of dimensions and shapes of the distributor-collectors, since they are external to the exchanger itself. The wrapped exchanger concept eliminates the need for closing bars, since there is no longer any edge to close.

L'invention est décrite ci-après à l'aide d'un exemple avec référence aux dessins joints, dans lesquels :

  • La figure 1 est une vue en perspective de l'échangeur montrant les flux des fluides (air et gaz), entrant et sortant de l'échangeur.
  • La figure 2 est une vue partielle des ouïes de distribution d'air et de gaz sur une des faces de l'échangeur.
  • La figure 3 montre un secteur d'amenée d'air coiffé de son écope de distribution, en vue éclatée.
  • La figure 4 montre un des deux feuillets, avant enroulement, en vue partielle plane.
  • La figure 5 montre l'autre feuillet, avant enroulement, en vue partielle plane.
  • La figure 6 représente une paire de feuillets accolés dans l'échangeur, en section radiale.
  • La figure 7 fait apparaître le trajet de l'air et du gaz, entre une paire de feuillets, d'une face de l'échangeur à l'autre, en vue partielle.
The invention is described below using an example with reference to the accompanying drawings, in which:
  • Figure 1 is a perspective view of the exchanger showing the flow of fluids (air and gas) entering and leaving the exchanger.
  • FIG. 2 is a partial view of the air and gas distribution openings on one of the faces of the exchanger.
  • Figure 3 shows an air supply sector capped with its distribution scoop, in exploded view.
  • Figure 4 shows one of the two sheets, before winding, in partial plan view.
  • Figure 5 shows the other sheet, before winding, in partial plan view.
  • FIG. 6 represents a pair of sheets placed side by side in the exchanger, in radial section.
  • Figure 7 shows the path of air and gas, between a pair of sheets, from one side of the exchanger to the other, in partial view.

L'échangeur est constitué d'un noyau 1 auquel sont fixés des écopes 8 d'amenée et d'évacuation d'air 2, figures 1 et 3.The exchanger consists of a core 1 to which are attached scoops 8 for supplying and discharging air 2, FIGS. 1 and 3.

Sur une face du noyau, l'air pénètre par des secteurs angulaires 5 régulièrement espacés et alternant avec des secteurs angulaires 6 de sortie des gaz.On one face of the core, the air penetrates by angular sectors 5 regularly spaced and alternating with angular sectors 6 for the outlet of the gases.

Sur la face opposée du noyau, l'air sort par des secteurs angulaires 3 régulièrement espacés et alternant avec des secteurs angulaires 4 d'entrée des gaz (figure 1).
Le noyau est constitué d'un enroulement d'une paire de feuillets a et b autour d'un axe z, figure 1.On the opposite face of the core, the air exits through angular sectors 3 regularly spaced and alternating with angular sectors 4 of gas inlet (Figure 1).
The core consists of a winding of a pair of sheets a and b around a z axis, Figure 1.

Le feuillet a est ridé longitudinalement, c'est-à-dire selon l'axe d'enroulement z, tandis que le feuillet b l'est transversalement, c'est-à-dire selon la direction tangentielle d'enroulement (figures 4 et 5). Le feuillet a possède trois zones axiales de rides : les zones II et IV près des bords
et la zone III centrale (figure 4).
Le feuillet b est ridé sur ces mêmes trois zones et comporte également, sur les zones I et V d'entrée-sortie, des rebords 7 déportés alternativement pour former les ouïes d'arrivée-sortie des fluides (figures 5 et 2).The sheet a is wrinkled longitudinally, that is to say along the winding axis z, while the sheet b is transversely, that is to say along the tangential winding direction (Figures 4 and 5). The sheet a has three axial zones of wrinkles: zones II and IV near the edges
and central zone III (Figure 4).
The sheet b is wrinkled on these same three zones and also comprises, on the zones I and V of entry-exit, flanges 7 offset alternately to form the gates of arrival-exit of the fluids (FIGS. 5 and 2).

Les rebords déportés de b viennent contre le rebord de a et vice versa, lors de l'enroulement. Ils sont définitivement brasés ensemble, une fois l'enroulement du noyau terminé (figure 2).
Le déport alternatif des rebords de b doit se faire lors de l'enroulement et en synchronisation avec celui-ci. Il faut en effet que les ouïes ainsi formées soient de longueur croissante à chaque tour d'enroulement et en phase angulaire pour former des secteurs angulaires bien réguliers. Les écopes 8 sont ensuite brasées sur les faces du noyau 1, avec leurs bords 9 brasés sur les bords 10 des secteurs angulaires, comme indiqué figure 3.The offset edges of b come against the edge of a and vice versa, during winding. They are definitively brazed together, once the core has been wound up (Figure 2).
The alternative offset of the edges of b must be done during winding and in synchronization with it. It is indeed necessary that the gills thus formed are of increasing length at each winding turn and in angular phase to form very regular angular sectors. The scoops 8 are then brazed on the faces of the core 1, with their edges 9 brazed on the edges 10 of the angular sectors, as indicated in FIG. 3.

La somme des hauteurs des rides de a et de b est constante sur toutes les zones ; elle vaut le déport de b sur les zones I et V et permet l'enroulement sans déformation radiale de la paire ab, car elle est d'épaisseur constante équivalant à la somme des hauteurs des rides de a et de b, comme illustré par la figure 6.The sum of the heights of the wrinkles of a and b is constant over all areas; it is worth the offset of b on the zones I and V and allows the winding without radial deformation of the pair ab, because it is of constant thickness equivalent to the sum of the heights of the wrinkles of a and b, as illustrated by the figure 6.

Ceci permet aussi de joindre, par brasage par exemple, les feuilles a et b aux points de contact 11 des lignes de crête des rides. Ces points forment un quadrillage, intersection des lignes de crête des rides.This also makes it possible to join, by soldering for example, the sheets a and b to the contact points 11 of the crest lines of the wrinkles. These points form a grid, intersection of the crest lines of the wrinkles.

En ne brasant ainsi entre elles que les paires de feuilles entre lesquelles circule le fluide de pression supérieure à l'autre, on assure ainsi une rétention locale de la surpression de ce fluide, sans avoir besoin d'une enceinte de pressurisation. Les paires de feuilles ainsi jointes sont rigides en flexion, tout en étant souples en cisaillement, ce qui réduit les contraintes dues aux inévitables gradients thermiques.By thus brazing together only the pairs of sheets between which circulates the fluid of higher pressure than the other, this ensures local retention of the overpressure of this fluid, without the need for a pressurization chamber. The pairs of sheets thus joined are rigid in bending, while being flexible in shearing, which reduces the stresses due to the inevitable thermal gradients.

Dans les zones II et IV, les rides de a et de b ont des hauteurs comparables : étant perpendiculaires et en contact par leurs crêtes, elles permettent le passage de l'air et du gaz dans les deux directions axiale et tangentielle : ces zones sont des zones de distribution du flux à partir des secteurs d'entrée vers la zone III ; ce sont des zones à flux croisés, comme indiqué sur la figure 7. Dans la zone III, les flux sont essentiellement parallèles et opposés ; c'est-à-dire à contrecourant (figure 7), car les rides tangentielles de b sont minimes et celles de a, axiales, sont grandes (figure 6).In zones II and IV, the wrinkles of a and b have comparable heights: being perpendicular and in contact with their crests, they allow the passage of air and gas in both axial and tangential directions: these zones are distribution zones of the flow from the entry sectors to zone III; these are cross-flow zones, as shown in Figure 7. In zone III, the flows are essentially parallel and opposite; that is to say against the current (Figure 7), because the tangential wrinkles of b are minimal and those of a, axial, are large (Figure 6).

Ce type d'échangeur peut aussi être réalisé en remplaçant les rides imprimées en relief par des ailettes de même hauteur, garnissant des feuilles planes.This type of exchanger can also be produced by replacing the wrinkles printed in relief by fins of the same height, filling with flat sheets.

Claims (6)

Echangeur de chaleur cylindrique obtenu par l'enroulement d'une paire de feuilles, les deux fluides circulant à contrecourant dans le sens axial de l'enroulement entre les paires adjacentes de feuilles, caractérisé en ce que les deux fluides arrivent et débouchent sur les faces opposées de l'enroulement, par des secteurs angulaires régulièrement espacés.Cylindrical heat exchanger obtained by winding a pair of sheets, the two fluids circulating in opposite directions in the axial direction of the winding between adjacent pairs of sheets, characterized in that the two fluids arrive and open on the faces opposite of the winding, by regularly spaced angular sectors. Echangeur de chaleur selon la revendication 1, caractérisé en ce que les secteurs angulaires consécutifs sont formés par la juxtaposition d'ouïes obtenues par le déport alternatif du rebord d'une des feuilles sur l'autre.Heat exchanger according to claim 1, characterized in that the consecutive angular sectors are formed by the juxtaposition of louvers obtained by the alternative offset of the edge of one of the sheets on the other. Echangeur de chaleur selon la revendication 2, caractérisé en ce que l'une des feuilles est imprimée en relief d'un motif de rides longitudinales et l'autre feuille d'un motif de rides transversales.Heat exchanger according to claim 2, characterized in that one of the sheets is printed in relief with a pattern of longitudinal wrinkles and the other sheet of a pattern of transverse wrinkles. Echangeur de chaleur selon la revendication 3, caractérisé en ce que les paires de feuilles sont brasées ou jointes deux par deux aux points de contact des lignes de crête des rides.Heat exchanger according to claim 3, characterized in that the pairs of sheets are brazed or joined two by two at the points of contact of the crest lines of the wrinkles. Echangeur de chaleur selon la revendication 2, caractérisé en ce que l'une des feuilles est garnie d'ailettes longitudinales, l'autre d'ailettes transversales.Heat exchanger according to claim 2, characterized in that one of the sheets is provided with longitudinal fins, the other with transverse fins. Echangeur de chaleur selon la revendication 5, caractérisé en ce que les paires de feuilles sont brasées ou jointes deux par deux aux points de contact des lignes de crête des ailettes.Heat exchanger according to claim 5, characterized in that the pairs of sheets are brazed or joined two by two at the points of contact of the crest lines of the fins.
EP96202200A 1996-08-05 1996-08-05 Spiral heat exchanger Expired - Lifetime EP0798527B1 (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
AT96202200T ATE159097T1 (en) 1996-08-05 1996-08-05 SPIRAL HEAT EXCHANGER
EP96202200A EP0798527B1 (en) 1996-08-05 1996-08-05 Spiral heat exchanger
DE69600073T DE69600073T2 (en) 1996-08-05 1996-08-05 Spiral heat exchanger
ES96202200T ES2111410T3 (en) 1996-08-05 1996-08-05 SPIRAL HEAT EXCHANGER.
PCT/BE1997/000088 WO1998005916A1 (en) 1996-08-05 1997-07-28 Spiral heat exchanger
AU39348/97A AU3934897A (en) 1996-08-05 1997-07-28 Spiral heat exchanger
US09/308,647 US6263961B1 (en) 1996-08-05 1997-07-28 Spiral heat exchanger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP96202200A EP0798527B1 (en) 1996-08-05 1996-08-05 Spiral heat exchanger

Publications (2)

Publication Number Publication Date
EP0798527A1 true EP0798527A1 (en) 1997-10-01
EP0798527B1 EP0798527B1 (en) 1997-10-08

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EP96202200A Expired - Lifetime EP0798527B1 (en) 1996-08-05 1996-08-05 Spiral heat exchanger

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US (1) US6263961B1 (en)
EP (1) EP0798527B1 (en)
AT (1) ATE159097T1 (en)
AU (1) AU3934897A (en)
DE (1) DE69600073T2 (en)
ES (1) ES2111410T3 (en)
WO (1) WO1998005916A1 (en)

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BE1011595A3 (en) * 1997-12-09 1999-11-09 Ewa Nova Bvba Besloten Vennoot Improved heat exchanger and method to realise such a heat exchanger
WO2000028265A1 (en) * 1998-11-09 2000-05-18 Sorokine, Rouslan Rotational thermal power transformer with regenerator
WO2001035042A1 (en) * 1999-11-09 2001-05-17 Ateliers De Construction De Thermo-Echangeurs S.A. A coiled heat exchanger and a method for making a coiled heat exchanger
GB2372559A (en) * 2001-02-21 2002-08-28 Rolls Royce Plc A heat exchanger
WO2005017435A1 (en) * 2003-08-12 2005-02-24 Rolls-Royce Plc A heat exchanger and a method of manufacturing a heat exchanger

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JP3090915B1 (en) * 1999-04-16 2000-09-25 株式会社カンキョー Heat exchanger, method of manufacturing the same, and dehumidifier including the same
EP1308684B1 (en) * 2000-08-10 2007-10-10 Kankyo Co., Ltd. Heat exchanger, method of manufacturing the heat exchanger, and dehumidification machine including the heat exchanger
EP3234489B1 (en) * 2014-12-18 2020-04-08 Zehnder Group International AG Heat exchanger and air conditioning apparatus therewith
EP3469289B1 (en) * 2016-06-09 2021-01-27 Fluid Handling LLC. 3d spiral heat exchanger
CN111197937A (en) * 2018-11-16 2020-05-26 中国科学院工程热物理研究所 Heat exchanger and manufacturing method thereof
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BE1011595A3 (en) * 1997-12-09 1999-11-09 Ewa Nova Bvba Besloten Vennoot Improved heat exchanger and method to realise such a heat exchanger
WO2000028265A1 (en) * 1998-11-09 2000-05-18 Sorokine, Rouslan Rotational thermal power transformer with regenerator
WO2001035042A1 (en) * 1999-11-09 2001-05-17 Ateliers De Construction De Thermo-Echangeurs S.A. A coiled heat exchanger and a method for making a coiled heat exchanger
US6289978B1 (en) 1999-11-09 2001-09-18 Ateliers De Construction De Thermo-Echangeurs Sa Coiled heat exchanger and a method for making a coiled heat exchanger
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US6585034B2 (en) 2001-02-21 2003-07-01 Rolls-Royce Plc Heat exchanger
GB2372559B (en) * 2001-02-21 2005-01-05 Rolls Royce Plc A heat exchanger
WO2005017435A1 (en) * 2003-08-12 2005-02-24 Rolls-Royce Plc A heat exchanger and a method of manufacturing a heat exchanger
US7600316B2 (en) 2003-08-12 2009-10-13 Rolls-Royce Plc Heat exchanger and a method of manufacturing a heat exchanger
US7918268B2 (en) 2003-08-12 2011-04-05 Rolls-Royce Plc Heat exchanger

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WO1998005916A1 (en) 1998-02-12
AU3934897A (en) 1998-02-25
DE69600073T2 (en) 1998-04-16
ATE159097T1 (en) 1997-10-15
EP0798527B1 (en) 1997-10-08
ES2111410T3 (en) 1998-03-01
DE69600073D1 (en) 1997-12-11
US6263961B1 (en) 2001-07-24

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