EP0576963B1 - Récupérateur de chaleur pour montage dans l'enveloppe d'une chaudière - Google Patents

Récupérateur de chaleur pour montage dans l'enveloppe d'une chaudière Download PDF

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Publication number
EP0576963B1
EP0576963B1 EP93109913A EP93109913A EP0576963B1 EP 0576963 B1 EP0576963 B1 EP 0576963B1 EP 93109913 A EP93109913 A EP 93109913A EP 93109913 A EP93109913 A EP 93109913A EP 0576963 B1 EP0576963 B1 EP 0576963B1
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EP
European Patent Office
Prior art keywords
edges
heat exchanger
walls
wall
water
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
Application number
EP93109913A
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German (de)
English (en)
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EP0576963A1 (fr
Inventor
Hans Dr. Viessmann
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Individual
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Individual
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
    • F24H1/24—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers
    • F24H1/26—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body
    • F24H1/28—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body including one or more furnace or fire tubes
    • F24H1/282—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body including one or more furnace or fire tubes with flue gas passages built-up by coaxial water mantles
    • 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
    • F28D9/0031—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 for one heat-exchange medium being formed by paired plates touching each other
    • 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

Definitions

  • the invention relates to a secondary heat exchanger for installation in the boiler housing and it also relates to a method for its production.
  • Such heat exchangers which, however, are not intended and suitable as secondary heat exchangers behind the combustion chamber for boilers, are known, for example, from DE-C-925 721 and DE-A-3 014 506. These heat exchangers are not secondary heat exchangers insofar as they contain the combustion chamber itself and the heating gases do not flow axially but also in a spiral. The same also applies to a heat exchanger according to EP-A-0 123 995.
  • Such helically wound heat exchangers are so inexpensive in terms of flow, their compactness and Surprisingly, even the heat exchanger may be found that such heat exchangers, as far as is known, have not been introduced as secondary heat exchangers integrated into the boiler housing behind the combustion chamber, and probably not because it is extremely difficult, on the one hand, the resulting, also spiral channels for the media involved in the heat exchanger to be closed on their narrow sides and on the other hand the sheets involved while maintaining their necessary distance from one another, ie without being able to wind spirally at all.
  • the invention is based on the task, based on the known principle of a spirally wound heat exchanger to design it in a special design so that the components involved, ie essentially the two walls, with regard to the winding process, can be dimensioned as thinly as possible, but the whole is still sufficiently pressure-stable in the finished state that that actually does not belong to the heat exchanger, separate spacers can be dispensed with and that, finally, during the winding process to form a spiral, the edges to be connected by welding do not warp, or practically not undulate, and also the wall surfaces cannot deform.
  • This training is based on a special manufacturing method in which the welding of the two wall parts takes place during the winding process but immediately after the assembly and the completed differential bending.
  • the two wall parts can still be independent of each other, but already in an assembled form of spiral bending, which is yes for the two parts in radially different spiral planes, follow and are only welded to each other after the bend, whereby it should be noted that "after the bend” does not mean the completion of the entire spiral winding, but only the differential bending processes during the whole spiral winding.
  • the procedure according to method claim 9 is advantageous, the further method claim constituting a further development which has an advantageous effect on the heat exchanger, since the outwardly bent edge of the inner wall is also kept shorter in radial extension can, since the spacing function is taken over by the spacer extending to the welding point. It is essential for the bend width of both edges involved that they remain weldable to each other either in the overlapped position or in the aligned position, the inwardly facing, bent edge being kept as small as possible, since this is more subject to wave deformation during bending than that after outside-facing edge.
  • the axially oriented wave embossings pointing into the gas-carrying interior have a triple function: on the one hand they contribute to the pressure stability of the walls, on the other hand they increase the heat exchange surface and form the spacers on the gas side for the winding process. "Essentially parallel to the winding axis" is to be understood here that the wave embossments intersect weakly in the assembled state and can thereby be supported selectively. It is important that the crimped edges are not also partially covered with these wave embossings, since this would lead to practically predetermined kinks, which is precisely what is to be avoided.
  • an advantageous embodiment consists in that the inner wall is provided with at least one wave embossing extending perpendicular to the winding axis.
  • the middle region of the outer wall which is at risk of being drawn in, is supported and at a precise distance held, and on the other hand, this results in a division of the flow channel on the water side, so that the water can flow through the water in series connection of the two channels in counterflow or, depending on the arrangement of the flow and return connections in parallel flow.
  • the water-carrying duct simply remains open at both ends and, depending on the boiler design, is connected in a suitable manner in a liquid-tight manner to the boiler's supply and return areas with corresponding openings.
  • the center of the spiral is formed by a correspondingly large filling body which, in the case mentioned above, forms the return space to which the spiral or the water-carrying channel is connected with its inner end .
  • the filler body is not hollow and consists of suitably thermally resilient material, results according to claim 3. This embodiment, which will be explained in more detail, however, cannot be produced from strips continuously drawn from coils.
  • the secondary heat exchanger consists in a known manner of a water-carrying and a gas-carrying interior 3, 3 ', which spaces are separated from one another by walls 1, 2, which extend parallel to one another and are spirally wound around a packing 5, and are sealed off from one another by cranked edges.
  • the inner wall 1 which is bent at the top and bottom with respect to the winding axis WA, has edges 4 corresponding to the maximum width B of the water-carrying interior 3.
  • the outer wall 2 has inwardly bent edges 6 with a maximum half width B, which edges 6 overlap the edges 4 of the inner wall 1 or are flush with them and are connected to them in a liquid-tight manner.
  • Such a NWT is shown in plan view according to FIG. 5, from which it can also be seen that the inner winding end of the spiral naturally does not begin in the center of the spiral, but on a filler 5, which in the embodiment according to FIGS. 4, 5 is a hollow body is formed and forms the return port. A winding from the center is not allowed since the bending radii would be too small. 4, 5, it is a NWT with a relatively large height H, and in consideration of this, the inner wall 1 is provided with a central wave embossing 10 extending perpendicular to the winding axis WA, the depth of which is width B. corresponds to the water-bearing interior 3. This wave embossing 10 (see also FIG.
  • edges 4, 6, which overlap in the sense of FIG. 2 with a basic dimensioning, as shown, or aligned to each other according to FIG. 3 takes place during the winding process, specifically differentially immediately behind the bending point, ie, after the bending has been carried out, since a previous welding would result in bending a tube with a flat cross section, largely rigid in itself wanting, which would lead to tension, kinks and sweat cracks.
  • An overlap of the edges 4, 6 in the sense of FIG. 2 is preferred, since this ensures a more problem-free welding.
  • the width B1 of the gas-carrying interior 3 ' is determined by the height H1 of two point-to-point wave embossments 7 in the walls 1, 2, which thus simultaneously form spacers during winding.
  • the wave embossments 7 can be formed as shown in FIG. 2A or also in FIG. 3A. It is essential in both cases that these end at a distance D in front of the edges 4, 6 or also in front of the central wave embossing 10, if there is one.
  • the NWT according to FIGS. 6, 7 differs from the above-described exemplary embodiment in that the two walls 1, 2 are formed from a band blank that is twice the length of the spiral course and which in the region of its center M is made of bent edges 4, 6 and at least deep wave embossments 7 are kept free and are bent by 180 ° in this area and on the overflow channel 8 formed in this way and parallel to the winding axis WA, the areas free of edges 4, 6 are closed with cover surfaces 9.
  • FIGS. 8, 9, in which the bending area is designated 12.
  • FIG. 9A In a top view, this is illustrated again in FIG. 9A with reference to FIG. 7.
  • This structure is then introduced with the overflow channel 8 first into a spiral winding device and wound into a spiral, as can be seen in FIG. 7.
  • the return connection RA would, as indicated by dashed lines in FIGS Overflow channel 8 are connected.
  • the return is initiated on the outside of the spiral, goes inwards to the overflow channel 8, arrives there in the other part of the water-carrying interior 3 and flows there from the inside to the outside in a suitable manner into the water-carrying interior IK of the boiler housing to arrive, ie in this case the NWT would be a parallel counterflow.
  • a separating web 13 could also be used in the overflow channel 8, as is indicated by dash-dotted lines in FIG. 8, in alignment with the wave embossing 10. If both parts of the water-carrying interior are then connected in a suitable manner to separate flow and return connections, there are separate interiors, the part on the fume cupboard being connected, for example, to underfloor heating, the temperature level of which is known to be lower. Otherwise, this configuration can also be realized in the NWT according to FIGS. 4, 5, if, as shown, it has a wave embossing 10, it does not require a separating web 13, but a corresponding breakdown of the hollow body forming the filler 5, such as, for example 4 indicated by dashed lines.
  • the spacer AH which protrudes between the two incoming sheet metal strips, and outer guides AF ensure precise spacing between the two walls 1, 2, which is particularly suitable for the embodiment according to FIG. 3.
  • the rollers 18 of the winding device 17 are, as indicated, arranged radially adjustable therein, in accordance with the increase in the circumferential plane of the spiral during winding. Since the spiral is already welded and can be removed after the winding is finished, this procedure is preferred. However, it is also possible to carry out the winding first, and only then carry out the welding with the planar spiral remaining held in the winding device 17, the welding device 14 being guided in a correspondingly controlled manner. Furthermore, it should be pointed out that, in particular in the embodiment according to FIGS. 4, 5, the two inner ends of the walls 1, 2 are first welded to the filler 5 designed as a hollow body and this, also located in the winding device 17, forms the winding core.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Steam Or Hot-Water Central Heating Systems (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Claims (10)

  1. Echangeur thermique intercalé à la suite pour le montage dans un bâti de chaudière de chauffage constitué par un espace intérieur conducteur d'eau et un espace intérieur conducteur de gaz (3, 3'), espaces qui sont séparés l'un de l'autre par des parois (1, 2) qui s'étendent parallèlement l'une à l'autre, qui sont enroulées en forme de spirale autour d'un corps de remplissage (5) et qui sont fermés l'un contre l'autre par des coudures de bord,
    la paroi intérieure (1) par rapport à l'axe d'enroulement (WA) présentant en haut et en bas des bords (4) coudés vers l'extérieur, correspondant au maximum à la largeur (B) de l'espace intérieur conducteur d'eau (3) et la paroi extérieure (2) présentant des bords (6) coudés vers l'intérieur avec au maximum la moitié de la largeur (B), bords (6) qui mordent sur les bords (4) de la paroi intérieure (1) ou qui sont alignés avec ceux-ci et qui sont reliés à ceux-ci de manière étanche au liquide, des estampages ondulés (7) des deux parois (1, 2), orientés dans le sens de passage, tournés dans l'espace intérieur conducteur de gaz (3') qui peut être traversé parallèlement à l'axe d'enroulement (WA) et qui est ouvert côté afflux et côté décharge, étant formés et placés à un écart (D) des bords (4, 6) dans les parois (1, 2) en s'appuyant mutuellement et l'espace intérieur conducteur d'eau (3) étant fermé aux deux extrémités de la spirale à l'exception des ouvertures de raccord aller et retour.
  2. Echangeur thermique selon la revendication 1,
    caractérisé en ce
    que la paroi intérieure (1) est pourvue d'au moins un estampage ondulé (10) qui s'étend perpendiculairement à l'axe d'enroulement (WA) dont la profondeur correspond à la largeur (B) de l'espace intérieur (3) conducteur d'eau.
  3. Echangeur thermique selon la revendication 1 et 2,
    caractérisé en ce
    que les deux parois (1, 2) sont formées par une longue découpe de bande qui correspond au double de la longueur du cours de la spirale qui est exempte, dans la zone de son milieu (M), de bords coudés (4, 6) et d'estampages ondulés (7) tout au moins profonds, qui est recourbée de 180° dans cette zone et que les zones exemptes de bords (4, 6) sont fermées sur le canal de trop-plein (8) formé, qui est parallèle à l'axe d'enroulement (WA), en bas et en haut par des surfaces de recouvrement (9).
  4. Echangeur thermique selon la revendication 3 avec un estampage ondulé longitudinal (10),
    caractérisé en ce
    qu'une barrette de séparation (13) est placée dans le canal de trop-plein (8) en étant alignée sur l'estampage ondulé (10).
  5. Echangeur thermique selon la revendication 3 avec un estampage ondulé longitudinal (10),
    caractérisé en ce
    qu'une des surfaces de recouvrement (9) est configurée comme raccord retour (RA).
  6. Echangeur thermique selon la revendication 1 ou 2,
    caractérisé en ce
    que le corps de remplissage (5) est configuré comme corps creux formant le raccord retour.
  7. Echangeur thermique selon la revendication 2 et 6,
    caractérisé en ce
    que l'espace intérieur du corps de remplissage (5) configuré comme corps creux est divisé en au moins deux espaces retour (I, II) et que les parties de l'espace intérieur conducteur d'eau (3) de l'échangeur thermique intercalé à la suite sont raccordées à ceux-ci.
  8. Procédé pour la fabrication d'un échangeur thermique intercalé à la suite selon la revendication 1,
    caractérisé en ce
    que les deux parois (1, 2) sont soudées l'une à l'autre en étant étanches au liquide vers l'extérieur sur leurs bords (4, 6) pendant l'enroulement en spirale avec cintrage différentiel directement après le cintrage par guidage radial continu d'un dispositif de soudage (A).
  9. Procédé selon la revendication 8,
    caractérisé en ce
    que les deux parois (1, 2) sont configurées comme bandes de tôle de bobines d'un dispositif d'estampages ondulés et de coudures de bord et ensuite les bandes de tôle estampées sont introduites dans un dispositif d'assemblage et un dispositif d'enroulement en spirale directement placé derrière.
  10. Procédé selon la revendication 8 ou 9,
    caractérisé en ce
    que les deux parois (1, 2) sont guidées lors de l'assemblage le long d'un écarteur (AH) maintenu de manière stationnaire entre les parois (1, 2) qui s'étend jusqu'au point de soudure (S).
EP93109913A 1992-07-01 1993-06-22 Récupérateur de chaleur pour montage dans l'enveloppe d'une chaudière Expired - Lifetime EP0576963B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4221528 1992-07-01
DE4221528A DE4221528A1 (de) 1992-07-01 1992-07-01 Nachschaltwärmetauscher für den Einbau in Heizkesselgehäuse und Verfahren zu dessen Herstellung

Publications (2)

Publication Number Publication Date
EP0576963A1 EP0576963A1 (fr) 1994-01-05
EP0576963B1 true EP0576963B1 (fr) 1996-04-03

Family

ID=6462205

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93109913A Expired - Lifetime EP0576963B1 (fr) 1992-07-01 1993-06-22 Récupérateur de chaleur pour montage dans l'enveloppe d'une chaudière

Country Status (7)

Country Link
US (1) US5505255A (fr)
EP (1) EP0576963B1 (fr)
AT (1) ATE136357T1 (fr)
CA (1) CA2099095A1 (fr)
DE (2) DE4221528A1 (fr)
DK (1) DK0576963T3 (fr)
ES (1) ES2086829T3 (fr)

Families Citing this family (14)

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Publication number Priority date Publication date Assignee Title
DE4229146C1 (de) * 1992-09-01 1994-03-31 Hans Dr Viesmann Gasheizkessel
DE4413867A1 (de) * 1994-04-21 1995-10-26 Paul Grote Verfahren zur Herstellung eines rekuperativen Spiralwärmetauschers
AT402667B (de) * 1995-03-20 1997-07-25 Vaillant Gmbh Wasserheizer wasserheizer
ATE159097T1 (de) * 1996-08-05 1997-10-15 Hubert Antoine Spiral-wärmetauscher
SE9903367D0 (sv) * 1999-09-20 1999-09-20 Alfa Laval Ab A spiral 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
FR2809483B1 (fr) * 2000-05-26 2003-08-15 Spirec Perfectionnements aux echangeurs thermiques de type spirale
AUPR286801A0 (en) * 2001-02-05 2001-03-01 Burns, Alan Robert Heat exchanger
US7100630B2 (en) * 2003-12-12 2006-09-05 Newfrey Llc Water guard pressure balancer
KR101048565B1 (ko) * 2009-08-24 2011-07-11 남중우 스파이어럴 구조를 사용한 보일러 및 그의 제조방법
JP2015504507A (ja) 2011-11-28 2015-02-12 アルファ・ラバル・コーポレイト・エービー 堆積させない特性を有するスパイラル熱交換器
CN106288888B (zh) * 2016-08-02 2018-06-26 中国石油大学(华东) 一种螺旋板翅式换热器及其制作方法
WO2019008006A1 (fr) * 2017-07-07 2019-01-10 Bekaert Combustion Technology B.V. Segment coulé pour échangeur de chaleur sectionnel
JP7303647B2 (ja) * 2019-03-20 2023-07-05 株式会社Subaru スパイラル式熱交換器

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US2488549A (en) * 1947-03-01 1949-11-22 Jet Heet Inc Heat exchanger
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DE925721C (de) * 1953-01-08 1955-03-28 Rosenblads Patenter Ab Waermeaustauscher mit spiralfoermig verlaufenden Durchstroemkanaelen
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EP0123995A1 (fr) * 1983-04-27 1984-11-07 Etablissement Agura Chaudière à condensation avec élément échangeur de chaleur en spirale

Also Published As

Publication number Publication date
ATE136357T1 (de) 1996-04-15
US5505255A (en) 1996-04-09
DE4221528A1 (de) 1994-01-05
DE59302092D1 (de) 1996-05-09
EP0576963A1 (fr) 1994-01-05
CA2099095A1 (fr) 1994-01-02
DK0576963T3 (da) 1996-05-06
ES2086829T3 (es) 1996-07-01

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