EP0017202B1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
EP0017202B1
EP0017202B1 EP80101693A EP80101693A EP0017202B1 EP 0017202 B1 EP0017202 B1 EP 0017202B1 EP 80101693 A EP80101693 A EP 80101693A EP 80101693 A EP80101693 A EP 80101693A EP 0017202 B1 EP0017202 B1 EP 0017202B1
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EP
European Patent Office
Prior art keywords
tube
heat exchanger
width
diameter
height
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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
Application number
EP80101693A
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German (de)
French (fr)
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EP0017202A2 (en
EP0017202A3 (en
Inventor
Fritz O. Schwenkler
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Individual
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Individual
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Priority claimed from DE19792912998 external-priority patent/DE2912998A1/en
Priority claimed from DE19803005958 external-priority patent/DE3005958A1/en
Application filed by Individual filed Critical Individual
Priority to AT80101693T priority Critical patent/ATE933T1/en
Publication of EP0017202A2 publication Critical patent/EP0017202A2/en
Publication of EP0017202A3 publication Critical patent/EP0017202A3/en
Application granted granted Critical
Publication of EP0017202B1 publication Critical patent/EP0017202B1/en
Expired legal-status Critical Current

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    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/12—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically the surrounding tube being closed at one end, e.g. return type
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings

Definitions

  • the invention relates to an arrangement for heat exchange with at least one tube provided with a number of annular ribs, with a closely surrounding the ribs-sending guide body and an inflow nozzle and an outflow channel, wherein the height of the ribs of the finned tube is smaller than the diameter of the pipe.
  • Such an arrangement is known from DE-A-19 40 963.
  • the width E of the inflow opening of the inflow nozzle is smaller than the diameter of the tube and that the width A of the outflow opening of the outflow channel is smaller than the inlet opening of the inflow nozzle.
  • the width of the inflow nozzle first decreases in the direction of the flow direction to a smallest value E and then increases again by a small amount.
  • the proposed arrangement considerably improves the heat transfer values between the heat-carrying medium and the finned tubes.
  • Another advantage of the proposed arrangement is the lower tendency towards contamination, because the heat exchange tube is completely flowed around, so that, as in known arrangements, partial areas of the exchange surface do not lie in the “dead water of the flow”.
  • the width of the inflow opening is approximately the difference between the diameter of the tube and the simple height of a rib and / or that the width of the outlet opening A corresponds to approximately twice the height of a rib.
  • the height r of the ribs of the tube is approximately 0.15 to 0.3 times the diameter of the tube. With these values, the rib efficiency is particularly favorable. Furthermore, it is advantageous according to the invention that the diameter of the tube is at least 70 mm and the minimum thickness of a rib is 1.5 mm. With this increase in the pipe diameter, the heat transfer improves.
  • the guide bodies consist of two sheet metal bodies which are bent in a semicircular shape and are fastened in a housing.
  • the guide bodies consist of sheet metal parts bent in a quarter circle, the inflow openings lying opposite each other and being spatially offset from one another by approximately 90 ° with respect to the outflow channels.
  • the outflow opening of the outflow channel is formed from sheet metal parts running in parallel.
  • a further tube is provided which is arranged concentrically to the finned tube and which is connected via a flange to a further flange arranged on the finned tube.
  • This arrangement allows the inner tube to be easily removed, which allows convenient control of the inner exchange surface in heat exchangers which are subject to a safety check.
  • the outer tube is conveniently closed at its end with a bottom.
  • the ribbing and the outer tube only extend over part of its length.
  • the cross-section of the non-finned part of the tube is expanded and a flange that can be connected to a housing and a pipe socket are arranged on this part.
  • 5 is the finned tube, on which annular fins 3 are arranged, designated. It is composed of two semicircular vanes.
  • Fig. 1 are designed as flow baffles 4, surrounded so that an annular gap 2 is formed between the baffles 4 and the tube 5.
  • Both flow guide plates 4 go in the axial direction into an inflow nozzle 1, which runs parallel to the finned tube 5 and has an inflow opening. 1.1 and an outflow channel 1.2.
  • the inflow nozzles 1 and the outflow channels each consist of sheets which are fastened to a housing 21.
  • the width E of the inflow nozzle 1 first decreases in the direction of the flow direction to a minimum value E and then increases again by a small amount,
  • the smallest width of the inlet opening 1.1 of the nozzle is smaller than the diameter of the tube 5. Very favorable heat transfer values can be achieved if the width of the inlet opening corresponds approximately to the difference between the sizes of the tube diameter d and the simple height r of a rib 3.
  • the width A of the outflow opening of the outflow channel 1.2 is smaller than that of the inlet opening 1.1. Very favorable heat transfer values can be achieved with a width A of the outlet opening if this corresponds approximately to twice the height r of a rib 3.
  • the flow guide plates are each designed in a quarter circle and the two inflow openings lie opposite one another, while the two outflow openings are each offset by 90 ° with respect to the outflow openings.
  • a second tube 6 is arranged concentrically to the finned tube and fixed in position by spacers 7.
  • One end of the finned tube 5 is closed by a base 8.
  • the ribbing of the outer tube 5 extends only over part of its length. It increases in diameter outside the ribbing and ends in a flange 15 which is connected to a flange 14 of the inner tube 6.
  • a pipe socket 10 is arranged on the non-finned part of the tube 5, through which one of the two gases or liquids can flow.
  • the finned tube 5 is provided in its wider section 3.1 with a further flange 16 which is connected to the flange 13 of a housing 21.
  • a further flange 16 which is connected to the flange 13 of a housing 21.
  • the gas or liquid flows into the housing from the left in the direction of the arrow in FIG. 1 and is passed through the inflow nozzle 1 into the annular gap 2 between the finned tube 5 of the flow guide plates 4.
  • the gas or liquid enters from two opposite points and flows around the finned tube only by 90 ° in each case in order to emerge again at the two outlet openings.
  • This arrangement is particularly advantageous in the case of pulsating flows, since vibrations are prevented by the flow from two sides.
  • the heat exchange tube can be conveniently pulled out of the housing 12 after loosening the housing flange connection 13.
  • the expansion of the inner tube 6 is possible by loosening the flange connection 14, so that simple assembly and inexpensive maintenance and cleaning of the heat exchanger is possible.

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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)

Description

Die Erfindung bezieht sich auf eine Anordnung zum Wärmeaustausch mit mindestens einem mit einer Anzahl von kreisringförmigen Rippen versehenen Rohr, mit einem die Rippen eng umschlie-Senden Leitkörper und einer Einströmdüse und einem Ausströmkanal, wobei die Höhe der Rippen des Rippen rohres kleiner ist als der Durchmesser des Rohres. Eine solche Anordnung ist aus der DE-A-19 40 963 bekannt.The invention relates to an arrangement for heat exchange with at least one tube provided with a number of annular ribs, with a closely surrounding the ribs-sending guide body and an inflow nozzle and an outflow channel, wherein the height of the ribs of the finned tube is smaller than the diameter of the pipe. Such an arrangement is known from DE-A-19 40 963.

Bei solchen Wärmeaustauschern besteht das Problem, die zu kühlenden oder zu erhitzenden Gase oder Flüssigkeiten in möglichst guten Kontakt zur Wärmeaustauschfläche zu bringen. Bei der oben erwähnten bekannten Anordnung ist die Breite der Eintrittsöffnung und der Austrittsöffnung gleich groß. Sie beträgt etwa des Doppelte der Höhe der Rippen des Rippenrohres. Außerdem ist dort die Auströmdüse als Diffusor ausgebildet. Bei dieser bekannten Anordnung ergibt sich bereits gegenüber konventionellen Anordnung eine verbesserte Umströmung der Wärmeaustauschfläche. Sie ist jedoch bei Rohren größeren Durchmessers aus strömungstechnischen Gründen, insbesondere wegen der sehr starken Beschleunigungen des strömenden Mediums im Bereich der Einlaufdüse und der damit verbundenen Strömungswiderstände ungünstig.The problem with such heat exchangers is to bring the gases or liquids to be cooled or heated into as good a contact as possible with the heat exchange surface. In the known arrangement mentioned above, the width of the inlet opening and the outlet opening is the same. It is about twice the height of the fins of the finned tube. In addition, the discharge nozzle is designed as a diffuser. In this known arrangement there is already an improved flow around the heat exchange surface compared to the conventional arrangement. However, it is unfavorable in pipes of larger diameter for fluidic reasons, in particular because of the very strong accelerations of the flowing medium in the area of the inlet nozzle and the associated flow resistances.

Es ist die Aufgabe der Erfindung, die oben beschriebene Anordnung im Sinne einer weiteren Verbesserung der Umströmung der Wärmeaustauschfläche und einer Verminderung des Strömungswiderstandes weiterzubilden, um eine höhefe Strömungsgeschwindigkeit und eine Verbesserung des Wärmeüberganges zu erreichen. Eine weitere Aufgabe der Erfindung besteht darin, die Demontage der Rohre und damit die Beseitigung von Verschmutzungen zu erleichtern.It is the object of the invention to further develop the arrangement described above in the sense of a further improvement in the flow around the heat exchange surface and a reduction in the flow resistance in order to achieve a higher flow rate and an improvement in the heat transfer. Another object of the invention is to facilitate the disassembly of the pipes and thus the removal of dirt.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß die Breite E der Einströmöffnung der Einströmdüse kleiner ist als der Durchmesser des Rohres, und daß die Breite A der Ausströmöffnung des Ausströmkanales kleiner ist als die Eintrittsöffnung der Einströmdüse. Die Breite der Einströmdüse vermindert sich zuerst in Richtung der Strömungsrichtung auf einen kleinsten Wert E und vergrößert sich dann wieder um einen geringen Betrag. Durch die vorgeschlagene Anordnung werden die Wärmeübergangswerte zwischen dem wärmeführenden Medium und den Rippenrohren beträchtlich verbessert. Ein weiterer Vorteil der vorgeschlagenen Anordnung ist die geringere Neigung zu Verschmutzungen, weil das Wärmeaustauschrohr voll umströmt ist, daß also nicht wie bei bekannten Anordnungen Teilbereiche der Austauschfläche im « Totwasser der Strömung liegen.This object is achieved in that the width E of the inflow opening of the inflow nozzle is smaller than the diameter of the tube and that the width A of the outflow opening of the outflow channel is smaller than the inlet opening of the inflow nozzle. The width of the inflow nozzle first decreases in the direction of the flow direction to a smallest value E and then increases again by a small amount. The proposed arrangement considerably improves the heat transfer values between the heat-carrying medium and the finned tubes. Another advantage of the proposed arrangement is the lower tendency towards contamination, because the heat exchange tube is completely flowed around, so that, as in known arrangements, partial areas of the exchange surface do not lie in the “dead water of the flow”.

Besonders günstige Wärmeübergangswerte lassen sich erfindungsgemäß dadurch erreichen, daß die Breite der Einströmöffnung etwa die Differenz zwischen dem Durchmesser des Rohres und der einfachen Höhe einer Rippe beträgt und/oder daß die Breite der Austrittsöffnung A etwa der zweifachen Höhe einer Rippe entspricht.Particularly favorable heat transfer values can be achieved according to the invention in that the width of the inflow opening is approximately the difference between the diameter of the tube and the simple height of a rib and / or that the width of the outlet opening A corresponds to approximately twice the height of a rib.

Dabei beträgt erfindungsgemäß die Höhe r der Rippen des Rohres etwa das 0,15- bis 0,3-fache des Durchmessers des Rohres. Mit diesen Werten wird der Rippenwirkungsgrad besonders günstig. Weiterhin ist es erfindungsgemäß vorteihaft, daß der Durchmesser des Rohres mindestens 70 mm und die Mindeststärke einer Rippe 1,5 mm beträgt. Mit von diesem Wert ausgehender Vergrößerung des Rohrdurchmessers verbessert sich der Wärmeübergang.According to the invention, the height r of the ribs of the tube is approximately 0.15 to 0.3 times the diameter of the tube. With these values, the rib efficiency is particularly favorable. Furthermore, it is advantageous according to the invention that the diameter of the tube is at least 70 mm and the minimum thickness of a rib is 1.5 mm. With this increase in the pipe diameter, the heat transfer improves.

In zweckmäßiger Weise ist vorgesehen, daß die Leitkörper aus zwei in einem Gehäuse befestigten halbkreisförmig gebogenen Blechkörpern bestehen.It is expediently provided that the guide bodies consist of two sheet metal bodies which are bent in a semicircular shape and are fastened in a housing.

Bei einer weiteren Ausführungsform der Erfindung ist vorgesehen, daß die Leitkörper aus viertelkreisförmig gebogenen Blechteilen bestehen, wobei sich die Einströmöffnungen jeweils gegenüber liegen und gegenüber den Ausströmkanälen jeweils um etwa 90° räumlich versetzt gegeneinander angeordnet sind.In a further embodiment of the invention it is provided that the guide bodies consist of sheet metal parts bent in a quarter circle, the inflow openings lying opposite each other and being spatially offset from one another by approximately 90 ° with respect to the outflow channels.

Nach einem weiteren Merkmal der Erfindung ist vorgesehen, daß die Ausströmöffnung des Ausströmkanales aus parallel verlaufenden Blechteilen gebildet ist.According to a further feature of the invention, it is provided that the outflow opening of the outflow channel is formed from sheet metal parts running in parallel.

Bei einer Weiterbildung der Erfindung ist vorgesehen, daß innerhalb des Rippenrohres eine konzentrisch zu diesem angeordnetes weiteres Rohr vorgesehen ist, welches über einen Flansch mit einem weiteren am Rippenrohr angeordneten Flansch verbunden ist.In a further development of the invention it is provided that within the finned tube a further tube is provided which is arranged concentrically to the finned tube and which is connected via a flange to a further flange arranged on the finned tube.

Diese Anordnung erlaubt es, das Innenrohr leicht herauszunehmen, was eine bequeme Kontrolle der inneren Austauschfläche bei Wärmeaustauschern, welche einer sicherheitstechnischen Kontrolle unterliegen, gestattet.This arrangement allows the inner tube to be easily removed, which allows convenient control of the inner exchange surface in heat exchangers which are subject to a safety check.

Bei dieser Ausführungsform ist in zweckmäßiger Weise das äußere Rohr an seinem Ende mit einem Boden verschlossen.In this embodiment, the outer tube is conveniently closed at its end with a bottom.

Weiterhin ist erfindungsgemäß vorgesehen, daß sich die Berippung und des äußeren Rohres nur auf einen Teil seiner Länge erstreckt.It is further provided according to the invention that the ribbing and the outer tube only extend over part of its length.

Dabei ist an der nicht berippten Partie des Rohres dessen Querschnitt erweitert und an dieser Partie ist ein mit einem Gehäuse verbindbarer Flansch sowie ein Rohrstutzen angeordnet.The cross-section of the non-finned part of the tube is expanded and a flange that can be connected to a housing and a pipe socket are arranged on this part.

Weitere Ausbildungsformen der Erfindung sind aus den beiden Ausführungsbeispielen zu entnehmen.Further embodiments of the invention can be found in the two exemplary embodiments.

Es zeigen :

  • Fig. 1 einen Querschnitt durch einen in ein Gehäuse eingebauten Wärmeaustauscher nach der Erfindung,
  • Fig. 2 einen Querschnitt durch einen von zwei Seiten angeströmten Wärmeaustauscher nach der Erfindung,
  • Fig. 3 einen Längsschnitt durch einen Wärmeaustauscher nach der Erfindung.
Show it :
  • 1 shows a cross section through a heat exchanger according to the invention installed in a housing,
  • 2 shows a cross section through a heat exchanger according to the invention, flow from two sides,
  • Fig. 3 shows a longitudinal section through a heat exchanger according to the invention.

In den Zeichnungen ist mit 5 das Rippenrohr, auf dem ringförmige Rippen 3 angeordnet sind, bezeichnet. Es ist von zwei halbkreisförmigen Leitkörpern, die bei. Fig. 1 ais Strömungsleitbleche 4 ausgebildet sind, umgeben, so daß zwischen den Leitblechen 4 und dem Rohr 5 ein Ringspalt 2 entsteht. Die. beiden Strömungsleitbleche 4 gehen in axialer Richtung in eine parallel zum Rippenrohr 5 verlaufende Einströmdüse 1 mit einer Einströmöffnung. 1.1 und einem Ausströmkanal 1.2 über. Die Einströmdüsen 1 sowie die Ausströmkanäle bestehen jeweils aus Blechen, die an einem Gehäuse 21 befestigt sind. Die Breite E der Einströmdüse 1 vermindert sich zuerst in Richtung der Strömungsrichtung auf einen kleinsten Wert E und vergrößert sich dann wieder um einen geringen Betrag,In the drawings, 5 is the finned tube, on which annular fins 3 are arranged, designated. It is composed of two semicircular vanes. Fig. 1 are designed as flow baffles 4, surrounded so that an annular gap 2 is formed between the baffles 4 and the tube 5. The. Both flow guide plates 4 go in the axial direction into an inflow nozzle 1, which runs parallel to the finned tube 5 and has an inflow opening. 1.1 and an outflow channel 1.2. The inflow nozzles 1 and the outflow channels each consist of sheets which are fastened to a housing 21. The width E of the inflow nozzle 1 first decreases in the direction of the flow direction to a minimum value E and then increases again by a small amount,

Die kleinste Breite der Einströmöffnung 1.1 der Düse ist kleiner als der Durchmesser des Rohres 5. Sehr günstige Wärmeübertragungswerte lassen sich erreichen, wenn die Breite der Einströmöffnung etwa der Differenz der Größen des Rohrdurchmessers d und der einfachen Höhe r einer Rippe 3 entspricht.The smallest width of the inlet opening 1.1 of the nozzle is smaller than the diameter of the tube 5. Very favorable heat transfer values can be achieved if the width of the inlet opening corresponds approximately to the difference between the sizes of the tube diameter d and the simple height r of a rib 3.

Die Breite A der Ausströmöffnung des Ausströmkanales 1.2 ist kleiner als die der Eintrittsöffnung 1.1. Sehr günstige Wärmeübertragungswerte lassen sich bei einer Breite A der Austrittsöffnung erreichen, wenn diese etwa der zweifachen Höhe r einer Rippe 3 entspricht.The width A of the outflow opening of the outflow channel 1.2 is smaller than that of the inlet opening 1.1. Very favorable heat transfer values can be achieved with a width A of the outlet opening if this corresponds approximately to twice the height r of a rib 3.

Bei der in Fig. 2 dargestellten Anordnung sind die Strömungsleitbleche jeweils viertelkreisförmig gestaltet und die beiden Einströmöffnungen liegen sich gegenüber, während die beiden Ausströmöffnungen um jeweils 90° gegenüber den Ausströmöffnungen versetzt angeordnet sind.In the arrangement shown in FIG. 2, the flow guide plates are each designed in a quarter circle and the two inflow openings lie opposite one another, while the two outflow openings are each offset by 90 ° with respect to the outflow openings.

Innerhalb des Rippenrohres. 5 ist ein zweites Rohr 6 konzentrisch zum Rippenrohr angeordnet und durch Distanzstücke 7 in seiner Lage fixiert. Dans eine Ende des Rippenrohres 5 ist durch einen Boden 8 verschlossen. Die Berippung des äußeren Rohres 5 erstreckt sich nur über einen Teil seiner Länge. Es vergrößert sich außerhalb der Berippung in seinem Durchmesser und endet in einem Flansch 15, der mit einem Flansch 14 des inneren Rohres 6 verbunden ist.Inside the finned tube. 5, a second tube 6 is arranged concentrically to the finned tube and fixed in position by spacers 7. One end of the finned tube 5 is closed by a base 8. The ribbing of the outer tube 5 extends only over part of its length. It increases in diameter outside the ribbing and ends in a flange 15 which is connected to a flange 14 of the inner tube 6.

Weiter ist an der nicht berippten Partie des Rohres 5 ein Rohrstutzen 10 angeordnet, durch weichen das eine der beiden Gase oder Flüssigkeiten abströmen kann.Furthermore, a pipe socket 10 is arranged on the non-finned part of the tube 5, through which one of the two gases or liquids can flow.

Das Rippenrohr 5 ist in seiner breiteren Partie 3.1 mit einem weiteren Flansch 16 versehen, der mit dem Flansch 13 eines Gehäuses 21 verbunden ist. In der Regel werden mehrere Gehäuse zu einem Rohrbündel zusammengebaut.The finned tube 5 is provided in its wider section 3.1 with a further flange 16 which is connected to the flange 13 of a housing 21. As a rule, several housings are assembled into a tube bundle.

Das Gas oder die Flüssigkeit strömt in der Figur 1 von links in Richtung des Pfeiles in das Gehäuse ein und wird durch die Einströmdüse 1 in den Ringspalt 2 zwischen dem Rippenrohr 5 der Strömungsleitbleche 4 geleitet.The gas or liquid flows into the housing from the left in the direction of the arrow in FIG. 1 and is passed through the inflow nozzle 1 into the annular gap 2 between the finned tube 5 of the flow guide plates 4.

Es umströmt ablösungsfrei die gesamte äußere Wärmeaustauschfläche des Wärmeaustauschrohres, welche aus der freien Fläche des Rippenrohres 5 und der aufgebrachten Berippung 3 besteht.It flows around the entire outer heat exchange surface of the heat exchange tube without detachment, which consists of the free surface of the finned tube 5 and the ribs 3 applied.

Das Gas oder die Flüssigkeit tritt aus der rechten Seite wieder aus, wobei die Einströmdüse 1 die strömungstechnischen Abströmverluste verringert. Durch die besondere oben geschilderte Dimensionierung der Öffnungen des Rohres und der Rippen ergeben sich gegenüber bekannten Rohren wesentlich verbesserte Wärmeübertragungswerte. Bei Versuchen mit den angegebenen Werten hat sich gezeigt, daß bei gleichem Raumbedarf und gleichem Materialbedarf im günstigsten Falle etwa eine Verdoppelung gegenüber konventionellen Wärmeaustauschern erzielbar ist.The gas or the liquid emerges again from the right-hand side, the inflow nozzle 1 reducing the outflow losses in terms of flow. The special dimensioning of the openings of the tube and the fins described above results in significantly improved heat transfer values compared to known tubes. Experiments with the specified values have shown that, with the same space requirement and the same material requirement, in the most favorable case, a doubling compared to conventional heat exchangers can be achieved.

Bei der in Fig. 2 dargestellten Anordnung tritt das Gas bzw. die Flüssigkeit von zwei gegenüberliegenden Stellen aus ein und umströmt das Rippenrohr nur um jeweils um 90° um an den beiden Austrittsöffnungen wieder auszutreten. Diese Anordnung ist insbesondere bei pulsierenden- Strömungen von Vorteil, da durch die Anströmung von zwei Seiten Schwingungen verhindert werden.In the arrangement shown in FIG. 2, the gas or liquid enters from two opposite points and flows around the finned tube only by 90 ° in each case in order to emerge again at the two outlet openings. This arrangement is particularly advantageous in the case of pulsating flows, since vibrations are prevented by the flow from two sides.

In dem in Fig. 3 dargestellten Längsschnitt eines Wärmeaustauschrohres ist durch Pfeile die Fließrichtung der zweiten Flussigkeit oder des zweiten Gases im Ringraum 9 angedeutet. Das Gas tritt in das Innenrohr 6 von rechts ein, kehrt am Boden 8 des Rippenrohres 5 seine Richtung um und strömt in den Zwischenraum zwischen dem Rippenrohr 3 und dem inneren Rohr 6 zurück und verläßt den Innenraum des Rippenrohres 3 durch den Rohrstutzen 10.In the longitudinal section of a heat exchange tube shown in FIG. 3, the direction of flow of the second liquid or of the second gas in the annular space 9 is indicated by arrows. The gas enters the inner tube 6 from the right, reverses its direction at the bottom 8 of the finned tube 5 and flows back into the space between the finned tube 3 and the inner tube 6 and leaves the interior of the finned tube 3 through the pipe socket 10.

Das Wärmeaustauschrohr kann nach Lösen der Gehäuseflanschverbindung 13 aus dem Gehäuse 12 bequem herausgezogen werden. Der Ausbau des Innenrohres 6 ist durch Lösung der Flanschverbindung 14 möglich, so daß eine einfache Montage und eine kostengünstige Wartung und Reinigung des Wärmeaustauschers möglich ist.The heat exchange tube can be conveniently pulled out of the housing 12 after loosening the housing flange connection 13. The expansion of the inner tube 6 is possible by loosening the flange connection 14, so that simple assembly and inexpensive maintenance and cleaning of the heat exchanger is possible.

Claims (10)

1. A heat exchange arrangement comprising at least one tube (5) provided with a plurality of annular fins (3), a guide member (4) closely surrounding the fins (3), and an inlet nozzle (1) and an outlet duct (1.2), the height (r) of the fins (3) of the finned tube (5) being smaller than the diameter (d) of the tube (5), characterised in that the smallest width (E) of the inlet opening (1.1) is smaller than the diameter (d) of the tube (5), and the width (A) of the outlet opening of the outlet duct (1.2) is smaller than the width (E) of the inlet opening (1.1) of the inlet nozzle (1).
2. A heat exchanger as claimed in claim 1, characterised in that the width (E) of the inlet opening (1.1) is at most the difference between the diameter (d) of the tube (5) and the height (r) of a fin (3).
3. A heat exchanger as claimed in claim 2, characterised in that the width (A) of the outlet opening of the outlet duct (1.2) is about twice the height (r) of a fin (3).
4. A heat exchanger as claimed in claim 1, 2 or 3, characterised in that the height (r) of the fins (3) of the tube (5) is about 0.15-0.3 times the diameter of the tube (5).
5. A heat exchanger as claimed in claim 1, 2, 3 or 4, characterised in that the diameter of the tube (5) is at least 70 mm, and the minimum thickness of a fin (3) is 1.5 mm.
6. A heat exchanger as claimed in claim 1, 2, 3, 4 or 5, characterised in that the guide member (4) consists of two plate members bent into semicircular shape and fixed in a casing (Figure 1).
7. A heat exchanger as claimed in claim 1, 2, 3. 4, 5 or 6, characterised in that the guide member consists of plate portions (4.1) bent into quarter- circular shape, wherein the inlet openings (1.1) lie opposite each other and are spatially offset by about 90° from the outlet ducts (1.2) (Figure 2).
8. A heat exchanger as claimed in one of the preceding claims, characterised in that the outlet opening of the outlet duct (1.2) is formed from plate portions which extend parallel to each other.
9. A heat exchanger as claimed in one of the preceding claims, characterised in that a further tube (6) is provided inside and concentric to the finned tube (5), and is connected by a flange (14) to a further flange (15) disposed on the finned tube (5), and in that the outer finned tube (5) is closed at its end by means of a plate (8).
10. A heat exchanger as claimed in one of the preceding claims, characterised in that the finning of the outer finned tube (5) extends only over part of its length, and the cross-section of the tube (5) widens out over the unfinned part thereof, there being disposed on this part a flange (16) which can be connected to a casing (21), and a pipe connection piece (10).
EP80101693A 1979-03-31 1980-03-29 Heat exchanger Expired EP0017202B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT80101693T ATE933T1 (en) 1979-03-31 1980-03-29 HEAT EXCHANGER.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19792912998 DE2912998A1 (en) 1979-03-31 1979-03-31 Finned heat exchanger pipe - has closely fitting external guide fins generating flow round heat exchange surface
DE2912998 1979-03-31
DE3005958 1980-02-16
DE19803005958 DE3005958A1 (en) 1980-02-16 1980-02-16 Heat exchanger with finned inner tube - has larger inlet than outlet for external chamber and second chamber inside

Publications (3)

Publication Number Publication Date
EP0017202A2 EP0017202A2 (en) 1980-10-15
EP0017202A3 EP0017202A3 (en) 1980-11-26
EP0017202B1 true EP0017202B1 (en) 1982-04-28

Family

ID=25778514

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80101693A Expired EP0017202B1 (en) 1979-03-31 1980-03-29 Heat exchanger

Country Status (2)

Country Link
EP (1) EP0017202B1 (en)
DE (1) DE3060325D1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992014110A1 (en) * 1991-02-08 1992-08-20 Withyman Brian Arthur Frederic Heat-transfer conduits for use particularly in solar heating systems, and improvements relating to such systems
CN110030849A (en) * 2019-04-17 2019-07-19 苏宇贵 Package heat-exchanger rig and its application method

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE335361C (en) * 1921-03-31 Dipl Jng Heinrich Foege Heat exchange device for pipe systems
DE138943C (en) *
GB500389A (en) * 1937-11-16 1939-02-08 British Leyland Motor Corp Improvements in and relating to tubular heat exchangers for fluids
FR841618A (en) * 1938-01-28 1939-05-24 Heat exchange process, and construction devices
GB850532A (en) * 1957-09-20 1960-10-05 Carves Simon Ltd Improvements in and relating to heat exchangers
GB934631A (en) * 1959-12-11 1963-08-21 Andre Huet Tubular heat exchanger
US3160145A (en) * 1962-07-20 1964-12-08 Avy L Miller Fluid heater
DE1940963A1 (en) * 1969-08-12 1971-02-25 Maschf Augsburg Nuernberg Ag Heat exchanger made of finned tubes with cross flow

Also Published As

Publication number Publication date
EP0017202A2 (en) 1980-10-15
DE3060325D1 (en) 1982-06-09
EP0017202A3 (en) 1980-11-26

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