EP0729001B1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
EP0729001B1
EP0729001B1 EP96102422A EP96102422A EP0729001B1 EP 0729001 B1 EP0729001 B1 EP 0729001B1 EP 96102422 A EP96102422 A EP 96102422A EP 96102422 A EP96102422 A EP 96102422A EP 0729001 B1 EP0729001 B1 EP 0729001B1
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EP
European Patent Office
Prior art keywords
tubes
ring
heat exchanger
central tube
gas
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Expired - Lifetime
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EP96102422A
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German (de)
French (fr)
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EP0729001A1 (en
Inventor
Hans Dr. Förster
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Ingenieurbuero Dr Forster
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Ingenieurbuero Dr Forster
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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
    • F28D9/04—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
    • 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
    • F28D7/16—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 in parallel spaced relation
    • F28D7/163—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 in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1669—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 in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having an annular shape; the conduits being assembled around a central distribution tube
    • 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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • 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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
    • F28F2009/224—Longitudinal partitions
    • 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
    • Y10S165/40—Shell enclosed conduit assembly
    • Y10S165/401—Shell enclosed conduit assembly including tube support or shell-side flow director
    • Y10S165/405—Extending in a longitudinal direction
    • Y10S165/406—Helically or spirally shaped

Definitions

  • the invention relates to a heat exchanger for small liquid and Large gas / steam volume flows with a cylindrical outer jacket as a pressure body preferably using straight, externally finned or laminated pipes with cross flow and cross-counter flow guidance of the heat exchanging Currents.
  • Such heat exchangers can be used, for example, for heating Air and technical gases including the use of the cold supply of Gas / steam flows, for the use of waste heat flows with small temperature differences under countercurrent conditions or for cooling liquids due to cold air or refrigerant vapors.
  • a heat exchanger (patent no. DD 218 167 B1) is known in which the inlet and outlet Exit of the gas / vapor phase in a subdivided central pipe without nozzle on cylindrical outer jacket takes place, with a thermal in the central tube insulating partition is installed.
  • the cross-countercurrent between a liquid volume flow and a very large one Gas / steam volume flow realized, the gas / steam volume flow one Flows through a single channel from 0 ° to 360 ° or double flow from 0 ° to 180 ° and is then withdrawn again on the outlet side of the central tube.
  • the Ribbed pipes lie exactly across the gas / steam flow and allow the multi-flow on the liquid side with cross-counterflow guidance of the heat exchanging media.
  • this principle is very large Gas / steam quantities instructed. It is not for smaller amounts of gas / steam possible to compact devices with high heat exchange area density shape.
  • the invention has for its object a heat exchanger with cross-countercurrent guidance of heat exchanging flows for moderately large gas / steam volumes and to carry out small to very small liquid volume flows in such a way that large temperature increases or decreases in the flowing media can be realized are with minimal pressure losses on the gas side and both the pressure bearing
  • the surface and the surface to be sealed are kept to a minimum Manufacturing costs significantly reduced compared to conventional solutions and with sufficient freedom in the design of the flow cross-sections for the Liquid phase the density of the heat-exchanging surface is increased.
  • the object is achieved by a heat exchanger for small liquid and large gas / vapor volume flows, with a central tube, a cylindrical Outer jacket as a pressure body and in the annular space between the central tube and the outer jacket arranged tubes, solved such that the annular space between the central tube and Outer jacket through cylinder jackets arranged concentrically around the central tube a plurality of concentric ring channels is divided by partitions that both the central tube with the innermost cylinder jacket and the successive ones Connect cylinder jackets to each other, and through openings between the Central tube and the innermost ring channel and between the successive Ring channels are connected such that the gas / steam volume flows from the central tube in the innermost ring channel and after each ring-shaped flow through a ring channel pass into the subsequent ring channel, and that those arranged in the ring channels Pipes on the front of the heat exchanger so connected that the Liquid flows when flowing through the pipes in cross-counterflow Gas / vapor phase is carried in the ring channels.
  • the solution according to the invention can both with a row of tubes per ring channel can also be realized with several rows of pipes.
  • the ratio of the volume flows of the available gas / steam quantity to the Amounts of liquid are crucial.
  • the partitions of the Ring channels not from solid walls but from smooth, insulating foils formed over the e.g. finned tubes are wrapped tightly on these and an outside play-free design of the ring channels to the heat exchange tubes and thus improved conditions for heat transfer offer, the insulating release film at its ends in e.g. metallic Clamped rails or profiles and the external clamping of the release film is connected to a fixed clamping profile by means of springs and by winding the release film with low pressure loss transitions between the Ring channels are created which make separate partitions unnecessary.
  • the proposed heat exchanger is characterized by concentrically arranged ring channels 1, which are formed by a central tube 6 and concentrically arranged cylinder jackets 2 or separating foils 16 between two tube sheets 3 and 4.
  • tubes 5 with ribs or fins are fitted in the axial direction.
  • the inflow through a gas / vapor phase (higher volume flow) preferably takes place through the central tube 6 and the outflow via a collector 7.
  • the concentrically arranged cylinder jackets 2 are open at the end of the ring channel 1 to the ring channel above it. Via these openings 8, the gas / vapor phase on the outside of the finned or laminated pipes 5 passes into the respective subsequent ring channel 1 when an approximately full circular path has been completed through this medium.
  • insulating separating foils 16 are used, this is preferably wound undivided from ring channel 1 to ring channel 1 over the enlarged tube outer surfaces (ribs, fins), which each form the channel end with the partition wall 14 and thus the openings 8 at the transition to the next channel.
  • the end of the film 16 is clamped into the longitudinal profiles of a film tensioner 18, which is guided over two guide angles 19 and is held in tension by means of tension springs 20.
  • the clamping profile 21 serves both as a fixed point of the spring and for guiding the film 16.
  • Concentric deflection chambers 13 of the end chambers 11 and 12 are radial
  • the liquid phase passes into the following concentric deflection space 13 Transition openings 15 or via nozzle 10 to the outside.
  • the deflection rooms 13 are formed by chamber webs 17 which can be placed variably.
  • the number of Ring channels 1 and the tubes 5 is not limited.

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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)

Description

Die Erfindung bezieht sich auf einen Wärmeübertrager für kleine Flüssigkeits- und große Gas-/Dampf-Volumenströme mit zylindrischem Außenmantel als Druckkörper unter vorzugsweiser Verwendung gerader, außen berippter oder lamellierter Rohre mit Queranströmung und Kreuz-Gegenstrom-Führung der wärmeaustauschenden Ströme. Anwendbar sind solche Wärmeübertrager zum Beispiel zur Erhitzung von Luft und technischen Gasen einschließlich der Nutzung des Kältevorrates von Gas-/Dampfströmen, zur Nutzung von Abwärmeströmen bei geringen Temperaturdifferenzen unter Gegenstrombedingungen oder zur Abkühlung von Flüssigkeiten durch kalte Luft bzw. Kältemitteldämpfe.The invention relates to a heat exchanger for small liquid and Large gas / steam volume flows with a cylindrical outer jacket as a pressure body preferably using straight, externally finned or laminated pipes with cross flow and cross-counter flow guidance of the heat exchanging Currents. Such heat exchangers can be used, for example, for heating Air and technical gases including the use of the cold supply of Gas / steam flows, for the use of waste heat flows with small temperature differences under countercurrent conditions or for cooling liquids due to cold air or refrigerant vapors.

Bekannt ist ein Wärmeübertrager (Patent-Nr. DD 218 167 B1), bei dem der Ein- und Austritt der Gas-/Dampf-Phase in einem unterteilten Zentralrohr ohne Stutzen am zylindrischem Außenmantel erfolgt, wobei in das Zentralrohr eine thermisch dämmende Trennwand eingebaut ist. Bei dieser Konstruktion wird der Kreuz-Gegenstrom zwischen einem Flüssigkeits-Volumenstrom und einem sehr großen Gas-/Dampf-Volumenstrom realisiert, wobei der Gas-/Dampf-Volumenstrom einen Ringkanal einflutig von 0° bis 360° oder zweiflutig von 0° bis 180° durchströmt und danach auf der Austrittsseite des Zentralrohres wieder abgezogen wird. Die berippten Rohre liegen dabei exakt quer zur Gas-/Dampf-Strömung und gestatten die Mehrflutigkeit auf der Flüssigkeitsseite mit Kreuz-Gegenstrom-Führung der wärmeaustauschenden Medien. Dieses Prinzip ist allerdings auf sehr große Gas-/Dampf-Mengen angewiesen. Für kleinere Gas-/Dampf-Mengen ist es nicht möglich, kompakte Apparate mit großer Wärmeaustausch-Flächendichte zu gestalten.A heat exchanger (patent no. DD 218 167 B1) is known in which the inlet and outlet Exit of the gas / vapor phase in a subdivided central pipe without nozzle on cylindrical outer jacket takes place, with a thermal in the central tube insulating partition is installed. With this construction, the cross-countercurrent between a liquid volume flow and a very large one Gas / steam volume flow realized, the gas / steam volume flow one Flows through a single channel from 0 ° to 360 ° or double flow from 0 ° to 180 ° and is then withdrawn again on the outlet side of the central tube. The Ribbed pipes lie exactly across the gas / steam flow and allow the multi-flow on the liquid side with cross-counterflow guidance of the heat exchanging media. However, this principle is very large Gas / steam quantities instructed. It is not for smaller amounts of gas / steam possible to compact devices with high heat exchange area density shape.

Eine Anwendung des beschriebenen Wärmeübertragerprinzips mit mehreren in radialer Richtung parallelgeschalteten Rohrreihen für 2/2-flutige Ausführung und Teilkondensation von kondensierbaren Gasinhaltsstoffen ist in DE 41 02 294 A1 angegeben. Hier wird auch eine Ausführung mit Schwimmkopf gezeigt. Wegen der radialen Parallelschaltung der Rippenrohre und der 2/2-Flutigkeit ist diese Konstruktion ebenfalls nur für sehr große Gas-/Dampfmengen einsetzbar, also eher für Turboverdichter und nicht für Kolbenverdichter, wie in der zitierten Patentschrift angegeben. Analoge Anmerkungen gelten für die Patentschrift DE 41 02 293 A1. Hier werden sehr große Zentralrohre, Schwimmkopf und Einbau von Tropfenabscheidern vorgeschlagen, wobei die Gasphase in einem gesonderten Tunnel innerhalb des Zentralrohres abgezogen wird. Auch diese Ausführung ist für mittlere Gas- oder Dampfvolumenströme ungeeignet und bietet der Gasphase nur einen kurzen Strömungsweg an, der die Anwendung wie in den vorbeschriebenen Fällen auf geringe Temperaturzu- oder -abnahme der Medien einschränkt.An application of the described heat exchanger principle with several in Radial direction parallel pipe rows for 2/2-pipe version and Partial condensation of condensable gas constituents is in DE 41 02 294 A1 specified. A version with a floating head is also shown here. Because of the radial parallel connection of the finned tubes and the 2/2-flow is this Construction can also only be used for very large amounts of gas / steam, so rather for turbocompressors and not for piston compressors, as in the cited patent specified. Analogous comments apply to patent specification DE 41 02 293 A1. Here are very large central pipes, floating head and installation of droplet separators proposed, the gas phase in a separate tunnel is withdrawn within the central tube. This version is also for medium Gas or steam volume flows are unsuitable and offers only one gas phase short flow path of the application as in the cases described above restricted to a slight increase or decrease in temperature of the media.

Der Erfindung liegt die Aufgabe zugrunde, einen Wärmeübertrager mit Kreuz-Gegenstrom-Führung der wärmetauschenden Ströme für mäßig große Gas/Dampf-Volumina und kleine bis sehr kleine Flüssigkeitsvolumenströme so auszuführen, daß große Temperaturzunahmen bzw. -abnahmen der strömenden Medien realisierbar sind bei minimalen Druckverlusten auf der Gasseite und sowohl die drucktragende Oberfläche als auch die abzudichtende Fläche minimal gehalten, der Fertigungsaufwand gegenüber herkömmlichen Lösungen beträchtlich gesenkt und bei genügender Freiheit der Gestaltung der Strömungsquerschnitte für die Flüssigphase die Dichte der wärmeaustauschenden Oberfläche erhöht wird.The invention has for its object a heat exchanger with cross-countercurrent guidance of heat exchanging flows for moderately large gas / steam volumes and to carry out small to very small liquid volume flows in such a way that large temperature increases or decreases in the flowing media can be realized are with minimal pressure losses on the gas side and both the pressure bearing The surface and the surface to be sealed are kept to a minimum Manufacturing costs significantly reduced compared to conventional solutions and with sufficient freedom in the design of the flow cross-sections for the Liquid phase the density of the heat-exchanging surface is increased.

Erfindungsgemäß wird die Aufgabe durch einen Wärmeübertrager für kleine Flüssigkeits- und große Gas-/Dampfvolumenströme, mit einem Zentralrohr, einem zylindrischen Außenmantel als Druckkörper und im Ringraum zwischen Zentralrohr und Außenmantel angeordneten Rohren, derart gelöst, daß der Ringraum zwischen Zentralrohr und Außenmantel durch konzentrisch um das Zentralrohr angeordnete Zylindermäntel in eine Mehrzahl von konzentrischen Ringkanälen unterteilt ist, die durch Trennwände, die sowohl das Zentralrohr mit dem innersten Zylindermantel als auch die aufeinanderfolgenden Zylindermäntel jeweils untereinander verbinden, und durch Öffnungen zwischen dem Zentralrohr und dem innersten Ringkanal sowie jeweils zwischen den aufeinanderfolgenden Ringkanälen derart verbunden sind, daß die Gas-/Dampf-Volumenströme vom Zentralrohr in den innersten Ringkanal und nach jeweils ringförmiger Durchströmung eines Ringkanals in den nachfolgenden Ringkanal übertreten, und daß die in den Ringkanälen angeordneten Rohre an den Stirnseiten des Wärmeübertragers so miteinander in Verbindung stehen, daß die Flüssigkeitsströme bei der Durchströmung der Rohre im Kreuz-Gegenstrom zur Gas-/Dampfphase in den Ringkanälen geführt wird.According to the invention, the object is achieved by a heat exchanger for small liquid and large gas / vapor volume flows, with a central tube, a cylindrical Outer jacket as a pressure body and in the annular space between the central tube and the outer jacket arranged tubes, solved such that the annular space between the central tube and Outer jacket through cylinder jackets arranged concentrically around the central tube a plurality of concentric ring channels is divided by partitions that both the central tube with the innermost cylinder jacket and the successive ones Connect cylinder jackets to each other, and through openings between the Central tube and the innermost ring channel and between the successive Ring channels are connected such that the gas / steam volume flows from the central tube in the innermost ring channel and after each ring-shaped flow through a ring channel pass into the subsequent ring channel, and that those arranged in the ring channels Pipes on the front of the heat exchanger so connected that the Liquid flows when flowing through the pipes in cross-counterflow Gas / vapor phase is carried in the ring channels.

Die erfindungsgemäße Lösung kann sowohl mit einer Rohrreihe pro Ringkanal als auch mit mehreren Rohrreihen realisiert werden. Für die Wahl der Ausführung ist das Verhältnis der Volumenströme der verfügbaren Gas-/Dampf-Menge zu den Flüssigkeitsmengen entscheidend.The solution according to the invention can both with a row of tubes per ring channel can also be realized with several rows of pipes. For the choice of execution is the ratio of the volume flows of the available gas / steam quantity to the Amounts of liquid are crucial.

In einer besonderen Ausgestaltung der Vorrichtung werden die Trennwände der Ringkanäle nicht von festen Wänden sondern von glatten, isolierenden Folien gebildet, die über die z.B. berippten Rohre gewickelt werden, auf diesen eng anliegen und eine außen spielfreie Gestaltung der Ringkanäle zu den Wärmeaustauschrohren und damit verbesserte Bedingungen für die Wärmeübertragung bieten, wobei die isolierende Trennfolie an ihren Enden in z.B. metallischen Schienen oder Profilen eingespannt und die äußere Einspannung der Trennfolie über Federn dehnungsweich mit einem festangeordneten Spannprofil verbunden ist und durch das Aufwickeln der Trennfolie druckverlustarme Übergänge zwischen den Ringkanälen entstehen, die separate Trennwände entbehrlich machen.In a special embodiment of the device, the partitions of the Ring channels not from solid walls but from smooth, insulating foils formed over the e.g. finned tubes are wrapped tightly on these and an outside play-free design of the ring channels to the heat exchange tubes and thus improved conditions for heat transfer offer, the insulating release film at its ends in e.g. metallic Clamped rails or profiles and the external clamping of the release film is connected to a fixed clamping profile by means of springs and by winding the release film with low pressure loss transitions between the Ring channels are created which make separate partitions unnecessary.

Die erfindungsgemäße Lösung bietet folgende Vorteile:The solution according to the invention offers the following advantages:

Durch die konzentrische Anordnung mehrerer Ringkanäle ineinander und deren Position zu einem Zentralrohr ist eine kompakte Bauweise mit einer hohen Dichte der wärmeaustauschenden Oberfläche möglich. Weisen die Medien nach der Wärmeübertragung Temperaturen auf, die nahe der jeweiligen Umgebungstemperatur liegen, und platziert man diesen Ein- bzw. Austrittspunkt der wärmetauschenden Medien am Außendurchmesser des erfindungsgemäßen Wärmeübertragers, dann ist die Ausführung einer thermischen Dämmung auf dem zylindrischen Außenmantel des erfindungsgemäßen Wärmeübertragers nicht notwendig oder minimierbar. Durch die Ausführung als Rundkörper ist die Möglichkeit einer hervorragenden Abdichtung zwischen dem erfindungsgemäßen Wärmeübertrager und der Umwelt gegeben, so daß auch der Wärmeübergang von/zu gefährlichen und/oder umweltschädlichen Medien realisiert werden kann. Die zylindrische Form bietet die Möglichkeit, dünnwandige Apparate auszuführen, die für höhere Drücke in den Ringkanälen und in den Rohren geeignet sind. Durch die gewählte Anordnung der Rohre zu den Öffnungen in den Zylindermänteln ist ein exakter Kreuz-Gegenstrom zwischen den wärmeübertragenden Medien und ein exakter Querstrom zu den Rippen bzw. Lamellen der Rohre gewährleistet. Durch die Verwendung glatter isolierender Folien sind die Druckverluste in den Ringkanälen sehr gering, zumal dadurch gerundete Gasübertritte anstelle eckiger Trennwände zwischen den Ringkanälen entstehen. Gleichzeitig werden einzelne Fenster in den Zylindermänteln entbehrlich, weil durch Übergang der Trennfolie von Ringkanal zu Ringkanal der volle Übertrittsquerschnitt für die Gasphase zur Verfügung steht. Ein wesentlicher Vorteil bei Verwendung einer Trennfolie anstelle fester Zylindermäntel ist das Anliegen der Folie an der Außenkontur des Rohres. Auf diese Weise wird die Strömung in die vergrößerten Außenflächen der Rohre (Rippen, Lamellen) zwangsgeführt, was den Wärmeübergang stark verbessert. Schließlich entstehen durch die Verwendung einer solchen Trennfolie anstelle starrer Zylindermäntel fertigungstechnische und Kostenvorteile. Ferner erhöht sich die Kompaktheit weiter und die Masse des Apparates wird reduziert. Due to the concentric arrangement of several ring channels in each other and their Position to a central pipe is a compact design with a high density the heat-exchanging surface possible. Assign the media after the Heat transfer temperatures close to the ambient temperature and you place this entry or exit point of the heat-exchanging media on the outside diameter of the invention Heat exchanger, then the execution of thermal insulation on the not cylindrical outer jacket of the heat exchanger according to the invention necessary or minimizable. The execution as a round body is the Possibility of an excellent seal between the invention Given heat exchangers and the environment, so that the heat transfer from / to dangerous and / or environmentally harmful media. The Cylindrical shape offers the possibility of running thin-walled apparatus for higher pressures in the ring channels and in the pipes are suitable. Through the selected arrangement of the pipes to the openings in the cylinder jackets is a exact cross-countercurrent between the heat transfer media and a exact cross flow to the fins or fins of the pipes guaranteed. Through the The use of smooth insulating foils is the pressure loss in the ring channels very low, especially as a result of rounded gas transfers instead of angular partition walls arise between the ring channels. At the same time, individual windows in the Cylinder jackets can be dispensed with, because the transition of the separating film from the ring channel to Ring channel the full cross section for the gas phase is available. A Significant advantage when using a release film instead of fixed cylinder jackets is the contact of the film with the outer contour of the pipe. In this way the Flow into the enlarged outer surfaces of the pipes (fins, fins) positively guided, which greatly improves the heat transfer. Eventually arise by using such a release film instead of rigid cylinder jackets manufacturing and cost advantages. The compactness further increases and the mass of the apparatus is reduced.

AusführungsbeispielEmbodiment

Die Erfindung soll nachstehend anhand eines Ausführungsbeispiels erläutert werden.The invention is explained below using an exemplary embodiment become.

Dabei zeigen:

Fig. 1
einen Axialschnitt durch den erfindungsgemäßen Wärmeübertrager mit drei konzentrisch angeordneten Ringkanälen;
Fig. 2
einen Radialschnitt durch den gas-/dampfdurchströmten Teil des erfindungsgemäßen Wärmeübertragers mit gleichsinniger Strömungsrichtung im Ringkanal;
(Die berippten oder lamellierten Rohre sind in Fig. 2 nicht dargestellt.)
Fig. 3
einen Schnitt durch die Endkammer des erfindungsgemäßen Wärmeübertragers mit drei konzentrisch angeordneten Ringkanälen, wobei drei Rohre zu einem Zug für die Flüssigkeit zusammengefaßt sind;
Fig. 4
eine technische Lösung für die Befestigung des äußeren Endes der Trennfolie mit Darstellung der Gasübertritte bei Verwendung von Trennfolien.
Show:
Fig. 1
an axial section through the heat exchanger according to the invention with three concentrically arranged ring channels;
Fig. 2
a radial section through the gas / vapor-flowed part of the heat exchanger according to the invention with the same direction of flow in the ring channel;
(The finned or laminated tubes are not shown in Fig. 2.)
Fig. 3
a section through the end chamber of the heat exchanger according to the invention with three concentrically arranged ring channels, three tubes are combined to form a train for the liquid;
Fig. 4
a technical solution for the attachment of the outer end of the separating film with representation of the gas transfer when using separating films.

Der vorschlagsgemäße Wärmeübertrager ist charakterisiert durch konzentrisch ineinander angeordnete Ringkanäle 1, die von einem Zentralrohr 6 und konzentrisch angeordneten Zylindermänteln 2 oder Trennfolien 16 zwischen zwei Rohrböden 3 und 4 gebildet werden. In diesen Ringkanälen 1 sind Rohre 5 mit Rippen- oder Lamellenbestückung in axialer Richtung eingebaut. Die Anströmung durch eine Gas-/Dampf-Phase (höherer Volumenstrom) erfolgt vorzugsweise durch das Zentralrohr 6 und die Abströmung über einen Sammler 7. Die konzentrisch angeordneten Zylindermäntel 2 sind am Ende des Ringkanals 1 zum darüber liegenden Ringkanal offen. Über diese Öffnungen 8 tritt die Gas-/Dampf-Phase auf der Außenseite der berippten oder lamellierten Rohre 5 in den jeweils folgenden Ringkanal 1 über, wenn eine annähernd volle Kreisbahn durch dieses Medium absolviert wurde. Bei Verwendung von isolierenden Trennfolien 16 wird diese vorzugsweise ungeteilt von Ringkanal 1 zu Ringkanal 1 über die vergrößerten Rohraußenflächen (Rippen, Lamellen) aufgewickelt, die beim Übergang zum nächsten Kanal jeweils den Kanalabschluß mit der Trennwand 14 und damit die Öffnungen 8 bilden.
Für das faltenfreie Anliegen der Folie 16 an den Rohren 5 wird das Ende der Folie 16 in Längsprofile eines Folienspanners 18 eingespannt, der über zwei Führungswinkel 19 geführt und über Spannfedern 20 dehnungsweich auf Spannung gehalten wird. Das Spannprofil 21 dient dabei sowohl als Festpunkt der Feder als auch zur Führung der Folie 16. The proposed heat exchanger is characterized by concentrically arranged ring channels 1, which are formed by a central tube 6 and concentrically arranged cylinder jackets 2 or separating foils 16 between two tube sheets 3 and 4. In these ring channels 1, tubes 5 with ribs or fins are fitted in the axial direction. The inflow through a gas / vapor phase (higher volume flow) preferably takes place through the central tube 6 and the outflow via a collector 7. The concentrically arranged cylinder jackets 2 are open at the end of the ring channel 1 to the ring channel above it. Via these openings 8, the gas / vapor phase on the outside of the finned or laminated pipes 5 passes into the respective subsequent ring channel 1 when an approximately full circular path has been completed through this medium. If insulating separating foils 16 are used, this is preferably wound undivided from ring channel 1 to ring channel 1 over the enlarged tube outer surfaces (ribs, fins), which each form the channel end with the partition wall 14 and thus the openings 8 at the transition to the next channel.
For the wrinkle-free contact of the film 16 on the tubes 5, the end of the film 16 is clamped into the longitudinal profiles of a film tensioner 18, which is guided over two guide angles 19 and is held in tension by means of tension springs 20. The clamping profile 21 serves both as a fixed point of the spring and for guiding the film 16.

Im Kreuz-Gegenstrom zur Gas-/Dampf-Phase in den Ringkanälen 1 wird die Flüssigphase (geringer Volumenstrom) über einen Stutzen 9 zu- und über einen Stutzen 10 abgeführt. Es ist möglich, Teilströme der Flüssigkeit entsprechend Ihres Temperaturniveaus über einen weiteren, nicht dargestellten Stutzen zwischen den Stutzen 9 und 10 zu entnehmen oder zuzuführen. Durch die Endkammern 11 und 12 werden konzentrisch angeordnete Umlenkräume 13 gebildet, wobei durch Kammerstege 17 jeweils eine begrenzte Anzahl von Rohren 5 zu einem Strömungsgang zusammengefaßt werden, so daß die Flüssigphase axial zwischen den Umlenkräumen 13 durch die Rohre 5 strömt und so schrittweise im Kreuz-Gegenstrom zur Gas-/Dampf-Phase in den Ringkanälen 1 geführt wird. Am Ende der konzentrischen Umlenkräume 13 der Endkammern 11 und 12 erfolgt der radiale Übertritt der flüssigen Phase in den folgenden konzentrischen Umlenkraum 13 über Übertrittsöffnungen 15 oder über Stutzen 10 nach außen. Die Umlenkräume 13 werden durch variabel platzierbare Kammerstege 17 gebildet. Die Anzahl der Ringkanäle 1 und der Rohre 5 ist nicht begrenzt.In cross-countercurrent to the gas / vapor phase in the ring channels 1 Liquid phase (low volume flow) via a nozzle 9 and via a Dissipated nozzle 10. It is possible to make partial flows of the liquid according to your Temperature levels over a further nozzle, not shown, between the To remove or feed nozzle 9 and 10. Through the end chambers 11 and 12 concentrically arranged deflection spaces 13 are formed, whereby by Chamber webs 17 each have a limited number of tubes 5 to one Flow can be summarized so that the liquid phase axially between the deflection spaces 13 flows through the tubes 5 and so gradually in cross-counterflow is led to the gas / vapor phase in the ring channels 1. At the end of Concentric deflection chambers 13 of the end chambers 11 and 12 are radial The liquid phase passes into the following concentric deflection space 13 Transition openings 15 or via nozzle 10 to the outside. The deflection rooms 13 are formed by chamber webs 17 which can be placed variably. The number of Ring channels 1 and the tubes 5 is not limited.

Claims (5)

  1. Heat exchanger for small volume flows of liquid and large volume flows of gas or vapour with a central tube (6), a cylindrical shell as pressure body and tubes (5) located in the ring space between a central tube (6) and the shell characterized thereby,
    that the ring space between central tube (6) and the shell is divided in a number of concentric ring channels (1) by cylindrical shells (2) that are concentrically arranged around the central tube (6), whereby the ring channels (1) are connected by separation walls (14), connecting the central tube (6) with the inner cylindrical shell and the successive cylindrical shells with each other and by openings (8) between the central tube (6) and the inner ring channel and between the successive ring channels (1) in a way, that the gas/vapour streams from the central tube (6) enter the inner ring channel and after a annular flow through a ring channel (1) the succeeding ring channels in cross stream to the tubes (5), whereby the tubes (5) in the ring channels are connected in such a way at the front side of the heat exchanger, that the liquid stream, flowing through the tubes (5), is lead in cross-counter-current flow with the gas/vapour phase in the ring channels (1).
  2. Heat exchanger according to claim 1 characterized thereby,
    that the separation walls (14) between the ring channels (1) are built in in diagonal position after a nearly complete circular path in the respective ring channel or thereby that separation walls are shaped by a preferably undivided separation foil (16) that is winded over the outer shape of the heat transferring tubes (5) and that simultaneously openings (8) are created by the transition of the separation foil (16) from one ring channel to the other.
  3. Heat exchanger according to claim 1 and 2 characterized thereby,
    that the cylindrical shells (2) are built of one or more layers and/or of thermal insulating material.
  4. Heat exchanger according to claim 1 to 3 characterized thereby,
    that the tubes (5) are equiped with surface increasing devices on the outside.
  5. Heat exchanger according to claim 2 with separation walls made by winding of insulating foil (2) characterized thereby,
    that the separation foil is fixed at the outer end in a foil tensioner (18), which is connected with a stationery tension profiles (21) by springs (20), whereby the tension profile (21) also lead the separation foil to the envelope circle of the outer row of tubes.
EP96102422A 1995-02-20 1996-02-17 Heat exchanger Expired - Lifetime EP0729001B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19505746 1995-02-20
DE19505746 1995-02-20

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EP0729001A1 EP0729001A1 (en) 1996-08-28
EP0729001B1 true EP0729001B1 (en) 1999-09-01

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Application Number Title Priority Date Filing Date
EP96102422A Expired - Lifetime EP0729001B1 (en) 1995-02-20 1996-02-17 Heat exchanger

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EP (1) EP0729001B1 (en)
DE (1) DE19601579C2 (en)

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DE19650086C1 (en) * 1996-12-03 1998-03-12 Hans Dr Ing Foerster Heat transmitter for gas-fluid heat exchange
US6772830B1 (en) * 1999-07-21 2004-08-10 Stone & Webster, Inc. Enhanced crossflow heat transfer
DE10151787C2 (en) * 2001-10-19 2003-09-25 Daimler Chrysler Ag Apparatus for heat exchange and autothermal reforming
DE10303595B4 (en) 2003-01-30 2005-02-17 Visteon Global Technologies, Inc., Dearborn Multi-channel heat exchanger and connection unit
DE102005043936B4 (en) * 2005-09-15 2008-08-21 Förster, Hans, Dr. Ing. Heat exchanger with internally ribbed pipes
DE102007058334B3 (en) * 2007-12-04 2008-12-04 Förster, Hans, Dr.-Ing. Heat exchanger for e.g. heat transmission of gaseous fluid, has central tube controlled for supplying and discharging shell-side medium through prechamber and deflection chamber at axial ends of cylindrical apparatus
WO2009089460A2 (en) * 2008-01-09 2009-07-16 International Mezzo Technologies, Inc. Corrugated micro tube heat exchanger
US8177932B2 (en) 2009-02-27 2012-05-15 International Mezzo Technologies, Inc. Method for manufacturing a micro tube heat exchanger
CN103486896B (en) * 2013-07-30 2015-05-27 杭州三花微通道换热器有限公司 Manifold assembly and heat exchanger with same
CN109141076A (en) * 2018-10-10 2019-01-04 上海尚实能源科技有限公司 A kind of heat exchanger
IT202100022496A1 (en) 2021-08-30 2023-03-02 Isola Res Lab S R L SYSTEM FOR HEATING FOOD AND FOOD IN GENERAL

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DE19601579A1 (en) 1996-08-22
US5690169A (en) 1997-11-25
EP0729001A1 (en) 1996-08-28
DE19601579C2 (en) 1997-12-18

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