EP0532051B1 - Heat exchanger with lamella fins - Google Patents

Heat exchanger with lamella fins Download PDF

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Publication number
EP0532051B1
EP0532051B1 EP92115721A EP92115721A EP0532051B1 EP 0532051 B1 EP0532051 B1 EP 0532051B1 EP 92115721 A EP92115721 A EP 92115721A EP 92115721 A EP92115721 A EP 92115721A EP 0532051 B1 EP0532051 B1 EP 0532051B1
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EP
European Patent Office
Prior art keywords
heat exchanger
tubes
blades
fins
indentations
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
EP92115721A
Other languages
German (de)
French (fr)
Other versions
EP0532051A1 (en
Inventor
Peter Goebel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
N.V. VAILLANT S.A.
Vaillant Austria GmbH
Vaillant GmbH
Vaillant SARL
Vaillant Ltd
Original Assignee
Vaillant Austria GmbH
Nv Vaillant Sa
Joh Vaillant GmbH and Co
Vaillant GmbH
Vaillant SARL
Vaillant Ltd
Vaillant BV
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Vaillant Austria GmbH, Nv Vaillant Sa, Joh Vaillant GmbH and Co, Vaillant GmbH, Vaillant SARL, Vaillant Ltd, Vaillant BV filed Critical Vaillant Austria GmbH
Publication of EP0532051A1 publication Critical patent/EP0532051A1/en
Application granted granted Critical
Publication of EP0532051B1 publication Critical patent/EP0532051B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
    • 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
    • F28F1/325—Fins with openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media

Definitions

  • the invention relates to a finned heat exchanger according to the preamble of the independent claim.
  • the aim of the invention is to avoid these disadvantages and to propose a finned heat exchanger of the type mentioned at the beginning in which the formation of dead spaces is avoided.
  • the features of claim 2 lead to a particularly intensive swirling of the flue gases flowing through the channels between the fins and thus to an improved detachment of condensate drops adhering to the fins.
  • the measures according to claim 3 result in turbulence and also targeted guidance of the flue gas stream and the condensate that forms. This ensures that temperature-related condensate is pressed out of the flue gas paths of the heat exchanger.
  • a finned heat exchanger in which the tubes with circumferential bores of the fins provided with a substantially U-shaped cross section, can be achieved according to claim 4 that dead spaces in which it corrosion of the slats can easily be avoided.
  • the depressions according to claim 5 allow easy pouring of the caverns with resin.
  • the plate pack can be pressed together in such a way that the plate resiliently abuts the adjacent plates or their collars.
  • fins 3 are held, which are penetrated by tubes 4 arranged in two rows running one below the other.
  • the heat exchanger formed by the tubes 4 and the fins 3 is acted upon by the flames 11 of a gas-blown tumble burner 10.
  • incisions 7 which are arranged centrally between the tubes 4 forming the upper row also facing the lintel burner. The incisions bring about an equalization of the temperature distribution in the individual fins 3.
  • impressions 8 are arranged, the depth of these impressions 8 increasing towards the edge of the fins 3 and being open at the edge, as can be seen from FIG remaining outlet cross section is in the shadow of the pipes of the upper row of pipes.
  • the tubes 4 are held in bores of the lamellae 3 which have a substantially U-shaped collar 6 in cross section, these simultaneously serving as spacers for determining the distance between the individual lamellae 3.
  • 4 displacers 5 are arranged inside the lower tubes.
  • the collars 6 are flared by a small angular amount, for example approximately 3 °. H. they deviate from a parallel position in relation to the plane of the lamella 3. This results in a certain spring action and the entire package of lamellae 3 can be pressed together, as a result of which the collars 6 of lamellae 3 lie essentially close to the respectively adjacent lamellae 3.
  • the tubes 4, which are arranged in the two rows, are offset from one another, so that the cuts 7 aligned with the tubes of the lower row of tubes and the impressions 8 are also offset from one another.
  • the smoke gases 12 are deflected by the impressions 8, so that they flow around the pipes 4 in a large angular range and therefore their heat to a large extent to the pipes 4 or the heating or flowing in them Dispense hot water.
  • FIG. 4 shows the design of the edge region 9 of the heat exchanger or its fins 3.
  • the edges 9 of the fins 3 are angled, the edges 9 of the fins 3 resting against one another and resulting in cavities 13 through which flue gases can flow.
  • the lamella heat exchanger according to FIG. 5 differs from that according to FIG. 1 in that, instead of the impressions 8, 3 cuts 7, 7 'are arranged on both edges of the fins, which run essentially transversely to the flow direction of the flue gases 12. Bends 20 are arranged at the lower edge of the slats 3, which surround the incisions 7 'and divide the flue gas flow in the same way as the impressions 8 according to FIG. 1.
  • the smoke gases 12 are deflected by the embossments 8, so that they flow around the pipes 4 in a large angular range and therefore their heat to a large extent to the pipes or to the heating or guided therein Dispense hot water. If the condensate accumulates due to the temperature, the flue gas flow and the condensate are led out of the heat exchanger separately depending on the degree of wetting of the heat exchanger. The condensate will escape through the open area under the pipes and the flue gas through the triangular open areas 7 in the impressions 8 or in the area between the adjacent pipes of the lower row of pipes. This prevents the resulting condensate from clogging the heat exchanger, the pressure loss across the heat exchanger increasing on the flue gas side and the area blocked by condensate leading to severe heat transfer losses.
  • FIGS. 6 and 7 show details of the lamellae 3.
  • the lamellae 3 are provided in the vicinity of the collars 6 with depressions 15 which run essentially radially to the bores for receiving the tubes and extend into the area of the caverns caused by the collars 6 14, which are delimited by the corresponding tube 4, the collar 6 of the one lamella 3 and the second lamella 3 resting on this collar 6.
  • These caverns 14 are filled with a resin or lacquer which can be introduced into the caverns 14 via the depressions 15.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Defrosting Systems (AREA)
  • Fuel Cell (AREA)

Abstract

Finned heat exchanger having tubes (4) which are arranged in at least one row and through which a fluid to be heated flows, and which are penetrated by the fins (3), which are arranged parallel to one another. In order to avoid the formation of dead spaces due to the formation of drops of condensate, it is provided that there are provided in the region of the rim of the fins (3) that lies downstream of the flue gas current, impressions (8) which are open towards said rim and are arranged between the rows of tubes (4) nearest said rim of the fins (3). <IMAGE>

Description

Die Erfindung bezieht sich auf einen Lamellenwärmetauscher gemäß dem Oberbegriff des unabhängigen Patentanspruchs.The invention relates to a finned heat exchanger according to the preamble of the independent claim.

Bei solchen bekannten Lamellenwärmetauschern sind zumeist rechteckige Lamellen vorgesehen, die mit Ausnahme der die Rohre unmittelbar umgebenden Bereiche, die gemäß der US-PS 42 79 298 einen im wesentlichen zylindrisch ausgebildeten Flansch und kleine stromauf des Flansches angeordnete Einprägungen aufweisen, eben ausgebildet sind. Dadurch ergeben sich zwischen den Lamellen Kanäle mit einer durchgehend gleichbleibenden lichten Weite. Bei dieser Gestaltung der Lamellen bei einem einreihigen oder mehrreihigen Wärmetauscher kann es bei temperaturbedingtem Anfall von Kondensat zu einem örtlichen Verschließen des Kanales zwischen zwei Lamellen und damit zur Ausbildung von toten Strömungswegen kommen. Dies führt aber zu einer erheblichen Verschlechterung des Wirkungsgrades.In such known finned heat exchangers, mostly rectangular fins are provided which, with the exception of the areas immediately surrounding the tubes, which according to US Pat. No. 4,279,298 have a substantially cylindrical flange and small impressions arranged upstream of the flange, are flat. This results in channels with a constant clear width between the slats. With this design of the fins in a single-row or multi-row heat exchanger, the condensation can be closed locally between two fins in the event of temperature-related accumulation of condensate and thus dead flow paths can be formed. However, this leads to a considerable deterioration in efficiency.

Ziel der Erfindung ist es, diese Nachteile zu vermeiden und einen Lamellenwärmetauscher der eingangs erwähnten Art vorzuschlagen, bei dem die Ausbildung von Toträumen vermieden ist.The aim of the invention is to avoid these disadvantages and to propose a finned heat exchanger of the type mentioned at the beginning in which the formation of dead spaces is avoided.

Erfindungsgemäß wird dies durch die kennzeichnenden Merkmale des unabhängigen Patentanspruchs erreicht.According to the invention this is achieved by the characterizing features of the independent claim.

Durch diese Maßnahmen ist sichergestellt, daß temperaturbedingtes Kondensat von den die Kanäle zwischen den Lamellen durchströmenden Rauchgasen mitgerissen wird und so die vorhandene Wärmetauscherfläche effektiver genutzt wird, wodurch sich ein deutlich höherer Kondensationswirkungsgrad ergibt. Bedingt ist dies durch die Einprägungen beziehungsweise durch die mit Abwinkelungen versehenen Einschnitte der Lamellen, die zu einer Verwirbelung des Rauchgasstromes in den Zwischenräumen zwischen den Lamellen führen.These measures ensure that temperature-related condensate is entrained by the flue gases flowing through the ducts between the fins and that the available heat exchanger surface is used more effectively, resulting in a significantly higher condensation efficiency. This is due to the embossing or the angled incisions in the lamellae, which lead to a swirling of the flue gas flow in the spaces between the lamellae.

Die Merkmale des Anspruchs 2 führen zu einer besonders intensiven Verwirbelung der die Kanäle zwischen den Lamellen durchströmenden Rauchgase und damit zu einer verbesserten Ablösung allenfalls an den Lamellen anhaftender Kondensattropfen.The features of claim 2 lead to a particularly intensive swirling of the flue gases flowing through the channels between the fins and thus to an improved detachment of condensate drops adhering to the fins.

Durch die Maßnahmen gemäß Anspruch 3 ergibt sich eine Verwirbelung sowie auch eine gezielte Führung des Rauchgasstroms und des sich bildenden Kondensates. Damit wird erreicht, daß temperaturbedingtes Kondensat aus den Rauchgaswegen des Wärmetauschers herausgepreßt wird.The measures according to claim 3 result in turbulence and also targeted guidance of the flue gas stream and the condensate that forms. This ensures that temperature-related condensate is pressed out of the flue gas paths of the heat exchanger.

Bei einem erfindungsgemäßen Lamellenwärmetauscher, bei dem die Rohre mit umlaufenden, im Querschnitt im wesentlichen U-förmigen Krägen versehene Bohrungen der Lamellen durchsetzen, kann nach Anspruch 4 erreicht werden, daß Toträume, in denen es leicht zur Korrosion der Lamellen kommen kann, vermieden werden.In a finned heat exchanger according to the invention, in which the tubes with circumferential bores of the fins provided with a substantially U-shaped cross section, can be achieved according to claim 4 that dead spaces in which it corrosion of the slats can easily be avoided.

Die Vertiefungen gemäß Anspruch 5 ermöglichen ein einfaches Ausgießen der Kavernen mit Harz.The depressions according to claim 5 allow easy pouring of the caverns with resin.

Durch die Merkmale des Anspruchs 6 kann das Lamellenpaket derart zusammengepreßt werden, daß die Lamellen federnd an den benachbarten Lamellen beziehungsweise deren Krägen anliegen.Due to the features of claim 6, the plate pack can be pressed together in such a way that the plate resiliently abuts the adjacent plates or their collars.

Die Erfindung wird nun anhand der Zeichnung näher erläutert.The invention will now be explained in more detail with reference to the drawing.

Dabei zeigen:

  • Figur 1 schematisch einen erfindungsgemäßen Wärmetauscher,
  • Figur 2 einen Schnitt entlang der Linie II-II in der Figur 1,
  • Figur 3 einen Schnitt entlang der Linie I-I in der Figur 1,
  • Figur 4 einen Schnitt entlang der Linie IV-IV in der Figur 1,
  • Figur 5 schematisch eine weitere Ausführungsform eines erfindungsgemäßen Wärmetauschers,
  • Figur 6 ein Detail des Schnittes nach der Linie IV-IV in der Figur 5 und
  • Figur 7 ein Detail der Lamellen nach der Figur 6.
Show:
  • FIG. 1 schematically shows a heat exchanger according to the invention,
  • FIG. 2 shows a section along the line II-II in FIG. 1,
  • FIG. 3 shows a section along line II in FIG. 1,
  • FIG. 4 shows a section along the line IV-IV in FIG. 1,
  • FIG. 5 schematically, a further embodiment of a heat exchanger according to the invention,
  • Figure 6 shows a detail of the section along the line IV-IV in Figure 5 and
  • FIG. 7 shows a detail of the slats according to FIG. 6.

In allen Figuren bedeuten gleiche Bezugszeichen jeweils die gleichen Einzelheiten.In all figures, the same reference numerals denote the same details.

In einem Halterahmen 1, der mittels einer Halterung 2 in einem nicht weiter dargestellten Gehäuseraum befestigt ist und eine wassergekühlte Brennkammer 19 bildet, sind Lamellen 3 gehalten, die von in zwei untereinander verlaufenden Reihen angeordneten Rohren 4 durchsetzt sind.In a holding frame 1, which is fastened by means of a holder 2 in a housing space, not shown, and a water-cooled Combustion chamber 19 forms, fins 3 are held, which are penetrated by tubes 4 arranged in two rows running one below the other.

Der durch die Rohre 4 und die Lamellen 3 gebildete Wärmetauscher wird von den Flammen 11 eines Gasgebläse-Sturzbrenners 10 beaufschlagt.The heat exchanger formed by the tubes 4 and the fins 3 is acted upon by the flames 11 of a gas-blown tumble burner 10.

Im Bereich des oberen und dem Brenner zugewandten Randes der Lamellen 3 sind diese mit Einschnitten 7 versehen, die mittig zwischen den die obere gleichfalls dem Sturzbrenner zugewandte Reihe bildende Rohre 4 angeordnet sind. Die Einschnitte bewirken eine Vergleichmäßigung der Temperaturverteilung in den einzelnen Lamellen 3.In the region of the upper edge of the fins 3 facing the burner, these are provided with incisions 7 which are arranged centrally between the tubes 4 forming the upper row also facing the lintel burner. The incisions bring about an equalization of the temperature distribution in the individual fins 3.

Im Bereich des stromab des beim dargestellten Ausführungsbeispiel von oben nach unten strömenden Rauchgasstromes liegenden Randes sind Einprägungen 8 angeordnet, wobei, wie aus der Figur 3 zu ersehen ist, die Tiefe dieser Einprägungen 8 gegen den Rand der Lamellen 3 zunimmt und randoffen ausgebildet ist und der verbleibende Austrittsquerschnitt im Schatten der Rohre der oberen Rohrreihe liegt.In the region of the edge lying downstream of the flue gas stream flowing from top to bottom in the illustrated embodiment, impressions 8 are arranged, the depth of these impressions 8 increasing towards the edge of the fins 3 and being open at the edge, as can be seen from FIG remaining outlet cross section is in the shadow of the pipes of the upper row of pipes.

Wie aus den Figuren 2 und 3 zu ersehen ist, sind die Rohre 4 in im Querschnitt im wesentlichen U-förmige Krägen 6 aufweisenden Bohrungen der Lamellen 3 gehalten, wobei diese gleichzeitig als Abstandhalter zur Festlegung des Abstandes zwischen den einzelnen Lamellen 3 dienen. Dabei sind im Inneren der unteren Rohre 4 Verdränger 5 angeordnet.As can be seen from FIGS. 2 and 3, the tubes 4 are held in bores of the lamellae 3 which have a substantially U-shaped collar 6 in cross section, these simultaneously serving as spacers for determining the distance between the individual lamellae 3. 4 displacers 5 are arranged inside the lower tubes.

Die Krägen 6 sind um einen kleinen Winkelbetrag, zum Beispiel um ca. 3° ausgestellt, d. h. sie weichen von einer parallelen Lage gegenüber der Ebene der Lamelle 3 ab. Dadurch ergibt sich eine gewisse Federwirkung und es kann das gesamte Paket der Lamellen 3 zusammengepreßt werden, wodurch die Krägen 6 der Lamellen 3 im wesentlichen dicht an der jeweils benachbarten Lamelle 3 anliegen.The collars 6 are flared by a small angular amount, for example approximately 3 °. H. they deviate from a parallel position in relation to the plane of the lamella 3. This results in a certain spring action and the entire package of lamellae 3 can be pressed together, as a result of which the collars 6 of lamellae 3 lie essentially close to the respectively adjacent lamellae 3.

Die Rohre 4, die in den beiden Reihen angeordnet sind, sind gegeneinander versetzt, so daß auch die mit den Rohren der unteren Rohrreihe fluchtenden Einschnitte 7 und die Einprägungen 8 gegeneinander versetzt angeordnet sind.The tubes 4, which are arranged in the two rows, are offset from one another, so that the cuts 7 aligned with the tubes of the lower row of tubes and the impressions 8 are also offset from one another.

Wie aus der Figur 1 zu ersehen ist, werden durch die Einprägungen 8 die Rauchgase 12 abgelenkt, so daß diese die Rohre 4 in einem großen Winkelbereich umströmen und daher ihre Wärme in einem hohen Ausmaß an die Rohre 4 beziehungsweise das in diesen strömende Heiz- oder Brauchwasser abgeben.As can be seen from FIG. 1, the smoke gases 12 are deflected by the impressions 8, so that they flow around the pipes 4 in a large angular range and therefore their heat to a large extent to the pipes 4 or the heating or flowing in them Dispense hot water.

Die Figur 4 zeigt die Ausbildung des Randbereiches 9 des Wärmetauschers beziehungsweise dessen Lamellen 3. Dabei sind die Ränder 9 der Lamellen 3 abgewinkelt, wobei die Ränder 9 der Lamellen 3 aneinander aufliegen und sich Hohlräume 13 ergeben, die von Rauchgasen durchströmbar sind.FIG. 4 shows the design of the edge region 9 of the heat exchanger or its fins 3. The edges 9 of the fins 3 are angled, the edges 9 of the fins 3 resting against one another and resulting in cavities 13 through which flue gases can flow.

Der Lamellenwärmetauscher nach der Figur 5 unterscheidet sich von jenem nach der Figur 1 dadurch, daß statt der Einprägungen 8 an beiden im wesentlichen quer zur Strömungsrichtung der Rauchgase 12 verlaufenden Rändern der Lamellen 3 Einschnitte 7, 7' angeordnet sind. Am unteren Rand der Lamellen 3 sind Abwinkelungen 20 angeordnet, die die Einschnitte 7' umgeben und den Rauchgasstrom ebenso aufteilen, wie die Einprägungen 8 nach der Figur 1.The lamella heat exchanger according to FIG. 5 differs from that according to FIG. 1 in that, instead of the impressions 8, 3 cuts 7, 7 'are arranged on both edges of the fins, which run essentially transversely to the flow direction of the flue gases 12. Bends 20 are arranged at the lower edge of the slats 3, which surround the incisions 7 'and divide the flue gas flow in the same way as the impressions 8 according to FIG. 1.

Wie auch aus der Figur 5 zu ersehen ist, werden durch die Einprägungen 8 die Rauchgase 12 abgelenkt, so daß diese die Rohre 4 in einem großen Winkelbereich umströmen und daher ihre Wärme in einem hohen Ausmaß an die Rohre beziehungsweise das in diesen geführte Heiz- oder Brauchwasser abgeben. Bei temperaturbedingt anfallendem Kondensat werden der Rauchgasstrom und das Kondensat je nach Benetzungsgrad des Wärmetauschers getrennt aus dem Wärmetauscher herausgeführt. Das Kondensat wird über die Freifläche unter den Rohren und das Rauchgas über die dreieckigen Freiflächen 7 in den Einprägungen 8 beziehungsweise in der Fläche zwischen den benachbarten Rohren der unteren Rohrreihe austreten. Somit wird verhindert, daß das anfallende Kondensat den Wärmetauscher zusetzt, der Druckverlust über den Wärmetauscher rauchgasseitig ansteigt und die durch Kondensat blockierte Fläche zu starken Wärmeübergangsverlusten führt.As can also be seen from FIG. 5, the smoke gases 12 are deflected by the embossments 8, so that they flow around the pipes 4 in a large angular range and therefore their heat to a large extent to the pipes or to the heating or guided therein Dispense hot water. If the condensate accumulates due to the temperature, the flue gas flow and the condensate are led out of the heat exchanger separately depending on the degree of wetting of the heat exchanger. The condensate will escape through the open area under the pipes and the flue gas through the triangular open areas 7 in the impressions 8 or in the area between the adjacent pipes of the lower row of pipes. This prevents the resulting condensate from clogging the heat exchanger, the pressure loss across the heat exchanger increasing on the flue gas side and the area blocked by condensate leading to severe heat transfer losses.

Figuren 6 und 7 zeigen Details der Lamellen 3. So sind die Lamellen 3 im Nahbereich der Krägen 6 mit Vertiefungen 15 versehen, die im wesentlichen radial zu den Bohrungen zur Aufnahme der Rohre verlaufen und sich bis in den Bereich der durch die Krägen 6 bedingten Kavernen 14 erstrecken, die von dem entsprechenden Rohr 4, dem Kragen 6 der einen Lamelle 3 und der an diesem Kragen 6 anliegenden zweiten Lamelle 3 begrenzt sind. Diese Kavernen 14 sind mit einem Harz oder Lack ausgegossen, das über die Vertiefungen 15 in die Kavernen 14 eingebracht werden kann.FIGS. 6 and 7 show details of the lamellae 3. Thus, the lamellae 3 are provided in the vicinity of the collars 6 with depressions 15 which run essentially radially to the bores for receiving the tubes and extend into the area of the caverns caused by the collars 6 14, which are delimited by the corresponding tube 4, the collar 6 of the one lamella 3 and the second lamella 3 resting on this collar 6. These caverns 14 are filled with a resin or lacquer which can be introduced into the caverns 14 via the depressions 15.

Claims (6)

  1. Multiple-blade heat exchanger provided with tubes arranged in at least one row and passed through by a fluid to be heated, such tubes extending through the multiple blades arranged parallel to one another and exposed to a flue gas originating from a burner, characterized in that the rims of the multiple blades (3) located downstream of the flue gas flow are provided either with indentations (8) essentially having the shape of an envelope of a cone of essentially circular-arc cross-section, or with essentially triangular notches (7') with bent sections (20) surrounding them, with such indentations (8) or notches (7'), respectively, being arranged between the tubes (4) of that row of tubes (4) which is located next to this downstream rim of the blades (3).
  2. Multiple-blade heat exchanger as claimed in Claim 1, characterized in that the depth of the indentations (8) increases towards the downstream rim of the blades (3).
  3. Multiple-blade heat exchanger as claimed in any of the preceding claims, characterized in that the depth of the indentations (8) is equivalent to one-half of the mutual distance of the blades (3).
  4. Multiple-blade heat exchanger as claimed in any of the preceding Claims 1 to 3 in which the tubes (4) extend through bores in the blades (3), which are provided with beaded collars (6) of essentially U-shaped cross-section, characterized in that the cavities (14) formed between the tubes (4) and the collars (6) and between the collars (6) and the adjacent blades (3) are filled with a cast-in resin or lacquer.
  5. Multiple-blade heat exchanger as claimed in Claim 4, characterized in that the blades (3) are provided with indentations (15) extending up to the cavities (14).
  6. Multiple-blade heat exchanger as claimed in Claim 4 or 5, characterized in that the ends of the collars (6) are bent slightly outwards relative to the blade plane by a small angle, for example an angle of about 3°.
EP92115721A 1991-09-12 1992-09-14 Heat exchanger with lamella fins Expired - Lifetime EP0532051B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0182891A AT396981B (en) 1991-09-12 1991-09-12 FLAT HEAT EXCHANGER
AT1828/91 1991-09-12

Publications (2)

Publication Number Publication Date
EP0532051A1 EP0532051A1 (en) 1993-03-17
EP0532051B1 true EP0532051B1 (en) 1996-09-25

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Family Applications (1)

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EP92115721A Expired - Lifetime EP0532051B1 (en) 1991-09-12 1992-09-14 Heat exchanger with lamella fins

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EP (1) EP0532051B1 (en)
AT (2) AT396981B (en)
DE (2) DE9212347U1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1295238B1 (en) * 1997-09-29 1999-05-04 Ferroli Spa PERFECTED PREMIXED CONDENSING BOILER, PARTICULARLY SUITABLE FOR THE PRODUCTION OF SANITARY WATER AND FOR HEATING
DE10315966B4 (en) * 2003-04-08 2007-04-05 Robert Bosch Gmbh Heat exchanger
NL2014432B1 (en) * 2015-03-10 2017-01-06 Atag Verwarming Nederland B V Heat exchanger and assembly of a heat exchanger and a burner.

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2412430C3 (en) * 1974-03-15 1979-10-11 Joh. Vaillant Gmbh U. Co, 5630 Remscheid Heat exchanger
DE2613747B2 (en) * 1976-03-31 1979-08-23 Volkswagenwerk Ag, 3180 Wolfsburg Tubular heat exchanger
US4279298A (en) * 1980-03-17 1981-07-21 Borg-Warner Corporation Heat exchanger with condensate blow-off suppressor
DE3219099C2 (en) * 1982-05-18 1985-05-02 Joh. Vaillant Gmbh U. Co, 5630 Remscheid Heat exchanger
DE3515426A1 (en) * 1985-04-29 1986-10-30 Fritz 7500 Karlsruhe Schwenkler Heat exchanger

Also Published As

Publication number Publication date
DE59207235D1 (en) 1996-10-31
AT396981B (en) 1994-01-25
DE9212347U1 (en) 1992-10-29
ATE143478T1 (en) 1996-10-15
ATA182891A (en) 1993-05-15
EP0532051A1 (en) 1993-03-17

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