EP0627607A2 - Steam-heated heat exchanger - Google Patents

Steam-heated heat exchanger Download PDF

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Publication number
EP0627607A2
EP0627607A2 EP94105670A EP94105670A EP0627607A2 EP 0627607 A2 EP0627607 A2 EP 0627607A2 EP 94105670 A EP94105670 A EP 94105670A EP 94105670 A EP94105670 A EP 94105670A EP 0627607 A2 EP0627607 A2 EP 0627607A2
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EP
European Patent Office
Prior art keywords
heating
heat exchanger
steam
pipes
flow line
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Granted
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EP94105670A
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German (de)
French (fr)
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EP0627607B1 (en
EP0627607A3 (en
Inventor
Ulrich Alfred Martin
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Wieland Werke AG
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Wieland Werke AG
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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
    • F28D7/02—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 helically coiled
    • F28D7/024—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 helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration

Definitions

  • the invention relates to a steam-heated heat exchanger, in particular for controlling the heat transfer on the condensate side, with a housing which has a steam-heated heating system and through which the secondary heating medium flows and which can be connected at the upstream end to a return and at the downstream end to a flow for the secondary heating medium , and with heating steam through which heating steam flows in parallel and in counterflow to the secondary heating medium, which are connected at the upstream end to a steam supply and at the downstream end to a condensate return.
  • the heating tubes are all arranged together in a single housing and their ends are connected to two tube plates, of which the tube side on the flow side is arranged laterally in the housing wall in the upper housing part, during the condensate-side tube plate closes the housing at the bottom and separates it from a condensate collection chamber.
  • the heating pipes are helically coiled, with the slope of the windings decreasing from top to bottom and thus the heat-exchanging surface increasing accordingly in the direction from the steam inlet to the condensate outlet.
  • Such heat exchangers have proven themselves many times in practice; the heat exchanger is easy to control and no noise is generated at all steam pressures. However, the manufacture of such a heat exchanger is very complex and expensive.
  • the invention has for its object to design a heat exchanger of the type mentioned in such a way that it has a simple structure while maintaining the good technical properties, in particular controllability and noiselessness and can therefore be manufactured very easily and cost-effectively.
  • the housing consists of a series of jacket tubes through which the secondary heating medium flows in parallel, in each of which one of the heating tubes is arranged in such a way that the jacket tubes open with their tube end on the flow side into a common secondary flow line for the secondary heating medium , and that the heating pipes on the flow side through the mouth of the respective jacket pipe into the secondary flow line in and through the wall to the outside to the common steam flow.
  • each jacket tube forms a structural unit with its heating tube and the heat exchanger according to the invention can be constructed in modules from these structural units, the structural units being able to be produced in series and correspondingly in a cost-saving manner and connected to the secondary flow line.
  • the inventive design of this connection with the leadership of the heating pipes through the supply line is essential because it ensures that the heating pipes at the steam inlet are very well cooled by the secondary heating medium flowing out of the jacket pipes and flowing through the supply line, and heat pockets that are from the Current of the secondary heating medium can not be detected and flushed, can not arise. This ensures that no boiling, crackling or cracking noises can occur in the heat exchanger due to overheating on the secondary side.
  • the heating pipes in the region of the mouth of the casing pipe into the secondary flow line and within the secondary flow line itself have the smallest possible heat exchange surface, in particular are smooth-walled. They therefore emit less heat in this area and this heat can be easily removed from the secondary heating medium flowing through the supply line.
  • the jacket pipes are in the region of their mouth in the secondary flow line Cross section narrowed. This constriction leads to an increased flow rate of the secondary heating medium in the mouth area with correspondingly effective washing around the heating pipe.
  • the narrowed mouth region of the jacket tube is expediently formed by a short axial connecting piece, into which the jacket tube merges with a shell that is convex toward the outside.
  • the heating pipes in the jacket pipes are helically wound at a distance from their mouth into the secondary flow line, the outer coil diameter being equal to the inside diameter of the jacket pipe and a displacer being arranged in the interior of the coil, which prevents the secondary heating medium from essentially reducing the jacket pipes can flow through the clear spiral cross section of the heating tubes, which would be disadvantageous for the heat transfer.
  • the heating tubes in the coiled area are expediently designed as finned tubes with tube coils lying close to one another.
  • jacket pipes are connected at the upstream end through a side connection piece to a common secondary return line running next to the jacket pipes for the secondary heating medium, and that the condensate ends of the heating pipes are each axially through the end wall of their Jacket tube passed through and connected to a common condensate manifold. This also enables simple and cost-saving pre-assembly at the return or condensate end of the jacket and heating pipes.
  • the structure of the heat exchanger according to the invention has the further advantage that the secondary flow and return line, as well as the steam flow line and the condensate manifold, either with one of their two or with their two line ends to the flow and return for the secondary heating medium or the common steam flow and the common condensate return can be connected.
  • the pre-assembled and pre-assembled heat exchanger with the secondary supply and return lines, the steam supply line and the condensate manifold therefore has a wide range of connection options to the primary-side energy supply system and the secondary-side energy consumer system.
  • Figure 1 shows a heat exchanger according to the invention in longitudinal section, Figure 2 in plan view.
  • a steam-heated heat exchanger for the condensate-side control of the heat transfer has a secondary heating medium, in particular water, through which jacket tubes 1 flow in parallel, of which only two are present in the exemplary embodiment, but which, depending on the desired heat transfer capacity, can also be provided in a substantially larger number.
  • Each jacket pipe 1 is connected at the upstream end 1 '' to a return line, not shown, and at the downstream end 1 'to a flow line, also not shown, of the secondary energy consumer system for the secondary heating medium in a manner to be described in more detail below.
  • each jacket tube 1 there is a heating tube 2 for passing the heating steam or the condensate, wherein the heating steam flows through all heating tubes 2 in parallel and in countercurrent to the secondary heating medium.
  • the heating pipes 2 are connected at the upstream end 2 ′′ to a steam supply, which is itself not shown, and at the downstream end 2 ′ to a condensate return of the primary energy supply system, also not shown in the drawing.
  • the jacket pipes 1 open with their pipe end 1 'on the flow side into a common secondary flow pipe 3 for the secondary heating medium.
  • the heating pipes 2 are led on the flow side through the mouth 4 of the respective casing pipe 1 into the secondary flow pipe 3 and out through the wall thereof to a common steam flow pipe 5 which runs parallel to the secondary flow pipe 3 on its side facing away from the casing pipes 1.
  • the heating tubes 2 are in the area of the mouth 4 of their respective jacket pipe 1 and within the secondary flow line 3 self-extending section 6 with the smallest possible heat exchange surface, namely in the exemplary embodiment smooth-walled.
  • the jacket tubes 1 are narrowed in cross-section in the area of their mouth 4 into the secondary flow line 3, this narrowed mouth area in detail from a short axial connecting piece 7 and in the transition from this connecting piece 7 to the cylindrical part of the jacket pipe 1 from a convexly curved outward Shell section 8 formed. This constriction leads to an increase in the flow rate of the secondary heating medium and thus to a good cooling of the sections 6 of the heating pipes 2 passing through the mouth area and the cross section of the flow line 3.
  • the heating tubes 2 are then helically coiled on their section 6, which runs straight and has a smooth wall in the mouth region of the jacket tubes 1, the outer coil diameter being equal to the inside diameter of the jacket tube 1.
  • a displacement body 9 which in the exemplary embodiment is designed as a tube, which is closed on the front side at the return-side end 1 '' of the jacket tube 1, but is open on the front side at the forward-side end 1 'and this prevents the flow of the secondary heating medium through the otherwise free interior of the coiled tubing occurs.
  • the heating tubes 2 are formed in the coiled area as finned tubes with tube coils lying close together.
  • the jacket pipes 1 are connected by a laterally attached connector 10 to a common secondary return line 11 running next to the jacket pipes 1 for the secondary heating medium.
  • this return line 11 all jacket pipes 1 are connected to the common return of the cooled secondary heating medium from the secondary energy consumer system, this connection being able to be made either at one of the two ends of the return line 11 or at both line ends.
  • the secondary flow of the energy consumer system is also connected via the secondary flow line 3 common to all the casing pipes 1, the connection again being able to be carried out at one of the two ends of this flow line 3 or at both ends thereof.
  • the condensate-side ends 2 'of the heating tubes 2 are each guided axially through the end wall of their casing tube 1 and connected to a common condensate manifold 12 which is to be connected to the condensate return of the primary energy supply system in a manner not shown in the figure.

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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)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Hydrogen, Water And Hydrids (AREA)

Abstract

The heat exchanger, which is intended, in particular, for controlling heat transfer on the condensate side, has a row of enclosing tubes (tubular jackets) (1) to which the secondary heating medium flows in parallel and in each of which there is located a heating tube (tubular heater) (2) through which steam or condensate flows in counterflow to the secondary heating medium. The enclosing tubes (1) open in a common secondary flow line (pipe) (3) with their tube ends (1') on the feed side. The heating tubes (2) are led with a smooth-walled section (6) through the opening (4) of the respective enclosing tube (1) into the secondary flow line (3) and outwards through the wall thereof to a common steam flow line (5). <IMAGE>

Description

Die Erfindung betrifft einen dampfbeheizten Wärmeübertrager, insbes. für kondensatseitige Regelung der Wärmeübertragung, mit einem ein dampfbeheiztes Heizsystem aufweisenden, vom sekundären Heizmedium durchströmten Gehäuse, das am stromauf liegenden Ende an einen Rücklauf und am stromab liegenden Ende an einen Vorlauf für das sekundäre Heizmedium anschließbar ist, und mit vom Heizdampf parallel und im Gegenstrom zum sekundären Heizmedium durchströmten Heizrohren, die am stromauf liegenden Ende an einen Dampfvorlauf und am stromab liegenden Ende an einen Kondensatrücklauf angeschlossen sind.The invention relates to a steam-heated heat exchanger, in particular for controlling the heat transfer on the condensate side, with a housing which has a steam-heated heating system and through which the secondary heating medium flows and which can be connected at the upstream end to a return and at the downstream end to a flow for the secondary heating medium , and with heating steam through which heating steam flows in parallel and in counterflow to the secondary heating medium, which are connected at the upstream end to a steam supply and at the downstream end to a condensate return.

Bei einem aus der DE-PS 11 19 883 bekannten Wärmetauscher dieser Art sind die Heizrohre alle zusammen in einem einzigen Gehäuse angeordnet und mit ihren Enden an zwei Rohrböden angeschlossen, von welchen der vorlaufseitige Rohrboden im oberen Gehäuseteil seitlich in der Gehäusewand angeordnet ist, während der kondensatseitige Rohrboden das Gehäuse nach unten abschließt und von einem Kondensatsammelraum trennt. Die Heizrohre sind schraubenförmig gewendelt, wobei die Steigung der Windungen von oben nach unten ab- und damit die wärmetauschende Oberfläche in Richtung vom Dampfeintritt zum Kondensataustritt entsprechend zunimmt. Derartige Wärmetauscher haben sich in der Praxis vielfach bewährt; der Wärmetauscher läßt sich hervorragend regeln und es entstehen bei allen Dampfdrücken keinerlei Geräusche. Jedoch ist die Fertigung eines solchen Wärmetauschers sehr aufwendig und teuer.In a heat exchanger of this type known from DE-PS 11 19 883, the heating tubes are all arranged together in a single housing and their ends are connected to two tube plates, of which the tube side on the flow side is arranged laterally in the housing wall in the upper housing part, during the condensate-side tube plate closes the housing at the bottom and separates it from a condensate collection chamber. The heating pipes are helically coiled, with the slope of the windings decreasing from top to bottom and thus the heat-exchanging surface increasing accordingly in the direction from the steam inlet to the condensate outlet. Such heat exchangers have proven themselves many times in practice; the heat exchanger is easy to control and no noise is generated at all steam pressures. However, the manufacture of such a heat exchanger is very complex and expensive.

Der Erfindung liegt die Aufgabe zugrunde, einen Wärmetauscher der eingangs genannten Art so auszubilden, daß er unter Beibehaltung der guten technischen Eigenschaften, insbes. Regelbarkeit und Geräuschfreiheit, einen einfachen Aufbau besitzt und daher sehr leicht und kostensparend gefertigt werden kann.The invention has for its object to design a heat exchanger of the type mentioned in such a way that it has a simple structure while maintaining the good technical properties, in particular controllability and noiselessness and can therefore be manufactured very easily and cost-effectively.

Diese Aufgabe wird nach der Erfindung dadurch gelöst, daß das Gehäuse aus einer Reihe von vom sekundären Heizmedium parallel durchströmten Mantelrohren besteht, in denen je eins der Heizrohre angeordnet ist, daß die Mantelrohre mit ihrem vorlaufseitigen Rohrende in einer gemeinsamen sekundären Vorlaufleitung für das sekundäre Heizmedium münden, und daß die Heizrohre vorlaufseitig durch die Mündung des jeweiligen Mantelrohres hindurch in die sekundäre Vorlaufleitung hinein und durch deren Wandung hindurch nach außen zum gemeinsamen Dampfvorlauf geführt sind.This object is achieved according to the invention in that the housing consists of a series of jacket tubes through which the secondary heating medium flows in parallel, in each of which one of the heating tubes is arranged in such a way that the jacket tubes open with their tube end on the flow side into a common secondary flow line for the secondary heating medium , and that the heating pipes on the flow side through the mouth of the respective jacket pipe into the secondary flow line in and through the wall to the outside to the common steam flow.

Der durch die Erfindung erreichte Vorteil besteht zunächst darin, daß jedes Mantelrohr mit seinem Heizrohr eine Baueinheit bildet und der erfindungsgemäße Wärmetauscher aus diesen Baueinheiten modulmäßig aufgebaut werden kann, wobei die Baueinheiten serienmäßig und entsprechend kostensparend gefertigt und an die sekundäre Vorlaufleitung angeschlossen werden können. Die erfindungsgemäße Ausbildung dieses Anschlusses mit der Führung der Heizrohre durch die Vorlaufleitung ist dabei von wesentlicher Bedeutung, weil sie gewährleistet, daß die Heizrohre am Dampfeintritt durch das aus den Mantelrohren aus- und die Vorlaufleitung durchströmende sekundäre Heizmedium sehr gut gekühlt werden und Wärmenester, die vom Strom des sekundären Heizmediums nicht erfaßt und durchspült werden, nicht entstehen können. Damit ist sichergestellt, daß im Wärmetauscher keine Brodel-, Knister- oder Knallgeräusche durch sekundärseitige Überhitzungen entstehen können.The advantage achieved by the invention is first of all that each jacket tube forms a structural unit with its heating tube and the heat exchanger according to the invention can be constructed in modules from these structural units, the structural units being able to be produced in series and correspondingly in a cost-saving manner and connected to the secondary flow line. The inventive design of this connection with the leadership of the heating pipes through the supply line is essential because it ensures that the heating pipes at the steam inlet are very well cooled by the secondary heating medium flowing out of the jacket pipes and flowing through the supply line, and heat pockets that are from the Current of the secondary heating medium can not be detected and flushed, can not arise. This ensures that no boiling, crackling or cracking noises can occur in the heat exchanger due to overheating on the secondary side.

Es empfiehlt sich daher auch, daß die Heizrohre im Bereich der Mündung des Mantelrohres in die sekundäre Vorlaufleitung und innerhalb der sekundären Vorlaufleitung selbst eine möglichst geringe Wärmetauschfläche aufweisen, insbes. glattwandig sind. Sie geben daher in diesem Bereich weniger Wärme ab und diese Wärme kann von dem die Vorlaufleitung durchströmenden sekundären Heizmedium problemlos abgeführt werden. Aus dem gleichen Grund sind in bevorzugter Ausführungsform die Mantelrohre im Bereich ihrer Mündung in die sekundäre Vorlaufleitung im Querschnitt verengt. Diese Verengung führt zu einer erhöhten Strömungsgeschwindigkeit des sekundären Heizmediums im Mündungsbereich mit entsprechend wirksamer Umspülung des Heizrohres. Zweckmäßigerweise ist der verengte Mündungsbereich des Mantelrohres von einem kurzen axialen Verbindungsstutzen gebildet, in den das Mantelrohr mit einer nach außen konvex gewölbten Schale übergeht.It is therefore also recommended that the heating pipes in the region of the mouth of the casing pipe into the secondary flow line and within the secondary flow line itself have the smallest possible heat exchange surface, in particular are smooth-walled. They therefore emit less heat in this area and this heat can be easily removed from the secondary heating medium flowing through the supply line. For the same reason, in a preferred embodiment, the jacket pipes are in the region of their mouth in the secondary flow line Cross section narrowed. This constriction leads to an increased flow rate of the secondary heating medium in the mouth area with correspondingly effective washing around the heating pipe. The narrowed mouth region of the jacket tube is expediently formed by a short axial connecting piece, into which the jacket tube merges with a shell that is convex toward the outside.

Weiter empfiehlt es sich, die Anordnung so zu treffen, daß parallel zur sekundären Vorlaufleitung auf ihrer von den Mantelrohren abgewandten Seite eine Dampfvorlaufleitung verläuft, an welche die quer durch die sekundäre Vorlaufleitung hindurch geführten Heizrohre angeschlossen sind. Die wärmetauschende Oberfläche der in der Vorlaufleitung verlaufenden Heizrohrabschnitte ist dann optimal klein und die Wärmeabgabe an das sekundäre Heizmedium im Vorlaufrohr entsprechend niedrig.It is also advisable to make the arrangement such that a steam flow line runs parallel to the secondary flow line on its side facing away from the jacket pipes, to which the heating pipes running through the secondary flow line are connected. The heat-exchanging surface of the heating pipe sections running in the supply pipe is then optimally small and the heat output to the secondary heating medium in the supply pipe is correspondingly low.

Im übrigen sind die Heizrohre in den Mantelrohren mit Abstand von deren Mündung in die sekundäre Vorlaufleitung schraubenförmig gewendelt, wobei der äußere Wendeldurchmesser gleich dem Innendurchmesser des Mantelrohres ist und im Wendelinnenraum ein Verdrängerkörper angeordnet ist, der verhindert, daß das sekundäre Heizmedium die Mantelrohre im wesentlichen im lichten Wendelquerschnitt der Heizrohre durchströmen kann, was für den Wärmeübergang nachteilig wäre. Zweckmäßigerweise sind die Heizrohre im gewendelten Bereich als Rippenrohre mit dicht aneinander liegenden Rohrwendeln ausgebildet.Incidentally, the heating pipes in the jacket pipes are helically wound at a distance from their mouth into the secondary flow line, the outer coil diameter being equal to the inside diameter of the jacket pipe and a displacer being arranged in the interior of the coil, which prevents the secondary heating medium from essentially reducing the jacket pipes can flow through the clear spiral cross section of the heating tubes, which would be disadvantageous for the heat transfer. The heating tubes in the coiled area are expediently designed as finned tubes with tube coils lying close to one another.

Ein weiterer Vorschlag der Erfindung geht dahin, daß die Mantelrohre am stromauf liegenden Ende durch je einen seitlich angesetzten Stutzen an eine neben den Mantelrohren verlaufende gemeinsame sekundäre Rücklaufleitung für das sekundäre Heizmedium angeschlossen sind, und daß die kondensatseitigen Enden der Heizrohre jeweils axial durch die Stirnwand ihres Mantelrohres hindurchgeführt und mit einer gemeinsamen Kondensatsammelleitung verbunden sind. Dies ermöglicht auch am rücklauf- bzw. kondensatseitigen Ende der Mantel- und Heizrohre eine einfache und kostensparende Vormontage. Im übrigen bietet der Aufbau des erfindungsgemäßen Wärmetauschers den weiteren Vorteil, daß die sekundäre Vor- und Rücklaufleitung ebenso wie die Dampfvorlaufleitung und die Kondensatsammelleitung wahlweise mit jeweils einem ihrer beiden oder mit ihren beiden Leitungsenden an den Vor- und Rücklauf für das sekundäre Heizmedium bzw. an den gemeinsamen Dampfvorlauf und den gemeinsamen Kondensatrücklauf anschließbar sind. Der mit den sekundären Vor- und Rücklaufleitungen, der Dampfvorlaufleitung und der Kondensatsammelleitung vorgefertigte und vormontierte Wärmetauscher besitzt daher sehr vielseitige Anschlußmöglichkeiten an das primärseitige Energieversorgungssystem und das sekundärseitige Energieverbrauchersystem.Another proposal of the invention is that the jacket pipes are connected at the upstream end through a side connection piece to a common secondary return line running next to the jacket pipes for the secondary heating medium, and that the condensate ends of the heating pipes are each axially through the end wall of their Jacket tube passed through and connected to a common condensate manifold. This also enables simple and cost-saving pre-assembly at the return or condensate end of the jacket and heating pipes. In addition, the structure of the heat exchanger according to the invention has the further advantage that the secondary flow and return line, as well as the steam flow line and the condensate manifold, either with one of their two or with their two line ends to the flow and return for the secondary heating medium or the common steam flow and the common condensate return can be connected. The pre-assembled and pre-assembled heat exchanger with the secondary supply and return lines, the steam supply line and the condensate manifold therefore has a wide range of connection options to the primary-side energy supply system and the secondary-side energy consumer system.

Im folgenden wird die Erfindung an einem in der Zeichnung dargestellten Ausführungsbeispiel erläutertert; die Figur 1 zeigt einen Wärmetauscher nach der Erfindung im Längsschnitt, die Figur 2 in der Draufsicht.The invention is explained below using an exemplary embodiment shown in the drawing; Figure 1 shows a heat exchanger according to the invention in longitudinal section, Figure 2 in plan view.

In der Zeichnung ist ein dampfbeheizter Wärmeübertrager für kondensatseitige Regelung der Wärmeübertragung dargestellt. Er besitzt von einem sekundären Heizmedium, insbes. Wasser, parallel durchströmte Mantelrohre 1, von welchen im Ausführungsbeispiel nur zwei vorhanden sind, die aber je nach gewünschter Wärmeübertragungsleistung auch in wesentlich größerer Anzahl vorgesehen sein können. Jedes Mantelrohr 1 ist am stromauf liegenden Ende 1'' an einen selbst nicht dargestellten Rücklauf und am stromab liegenden Ende 1' an einen ebenfalls selbst nicht dargestellten Vorlauf des sekundären Energieverbrauchersystems für das sekundäre Heizmedium in weiter unten noch näher zu beschreibender Weise angeschlossen. In jedem Mantelrohr 1 befindet sich ein Heizrohr 2 zum Durchleiten des Heizdampfes bzw. des Kondensates, wobei alle Heizrohre 2 vom Heizdampf parallel und im Gegenstrom zum sekundären Heizmedium durchströmt werden. Die Heizrohre 2 sind am stromauf liegenden Ende 2'' an einen wiederum selbst nicht dargestellten Dampfvorlauf und am stromab liegenden Ende 2' an einen ebenfalls in der Zeichnung nicht dargestellten Kondensatrücklauf des primären Energieversorgungssystems angeschlossen.In the drawing, a steam-heated heat exchanger for the condensate-side control of the heat transfer is shown. It has a secondary heating medium, in particular water, through which jacket tubes 1 flow in parallel, of which only two are present in the exemplary embodiment, but which, depending on the desired heat transfer capacity, can also be provided in a substantially larger number. Each jacket pipe 1 is connected at the upstream end 1 '' to a return line, not shown, and at the downstream end 1 'to a flow line, also not shown, of the secondary energy consumer system for the secondary heating medium in a manner to be described in more detail below. In each jacket tube 1 there is a heating tube 2 for passing the heating steam or the condensate, wherein the heating steam flows through all heating tubes 2 in parallel and in countercurrent to the secondary heating medium. The heating pipes 2 are connected at the upstream end 2 ″ to a steam supply, which is itself not shown, and at the downstream end 2 ′ to a condensate return of the primary energy supply system, also not shown in the drawing.

Im einzelnen münden die Mantelrohre 1 mit ihrem vorlaufseitigen Rohrende 1' in einer gemeinsamen sekundären Vorlaufleitung 3 für das sekundäre Heizmedium. Die Heizrohre 2 sind vorlaufseitig durch die Mündung 4 des jeweiligen Mantelrohres 1 hindurch in die sekundäre Vorlaufleitung 3 hinein und durch deren Wandung hindurch nach außen zu einer gemeinsamen Dampfvorlaufleitung 5 geführt, die parallel zur sekundären Vorlaufleitung 3 auf deren von den Mantelrohren 1 abgewandten Seite verläuft. Die Heizrohre 2 sind in ihrem im Bereich der Mündung 4 ihres jeweiligen Mantelrohres 1 und innerhalb der sekundären Vorlaufleitung 3 selbst verlaufenden Abschnitt 6 mit möglichst geringer Wärmetauschfläche, nämlich im Ausführungsbeispiel glattwandig ausgebildet. Die Mantelrohre 1 sind im Bereich ihrer Mündung 4 in die sekundäre Vorlaufleitung 3 im Querschnitt verengt, wobei dieser verengte Mündungsbereich im einzelnen von einem kurzen axialen Verbindungsstutzen 7 und im Übergang von diesem Verbindungsstutzen 7 zum zylindrischen Teil des Mantelrohrs 1 hin von einem nach außen konvex gewölbten Schalenabschnitt 8 gebildet. Diese Verengung führt zu einer Erhöhung der Strömungsgeschwindigkeit des sekundären Heizmediums und damit zu einer guten Kühlung der den Mündungsbereich und den Querschnitt der Vorlaufleitung 3 durchsetzenden Abschnitte 6 der Heizrohre 2.Specifically, the jacket pipes 1 open with their pipe end 1 'on the flow side into a common secondary flow pipe 3 for the secondary heating medium. The heating pipes 2 are led on the flow side through the mouth 4 of the respective casing pipe 1 into the secondary flow pipe 3 and out through the wall thereof to a common steam flow pipe 5 which runs parallel to the secondary flow pipe 3 on its side facing away from the casing pipes 1. The heating tubes 2 are in the area of the mouth 4 of their respective jacket pipe 1 and within the secondary flow line 3 self-extending section 6 with the smallest possible heat exchange surface, namely in the exemplary embodiment smooth-walled. The jacket tubes 1 are narrowed in cross-section in the area of their mouth 4 into the secondary flow line 3, this narrowed mouth area in detail from a short axial connecting piece 7 and in the transition from this connecting piece 7 to the cylindrical part of the jacket pipe 1 from a convexly curved outward Shell section 8 formed. This constriction leads to an increase in the flow rate of the secondary heating medium and thus to a good cooling of the sections 6 of the heating pipes 2 passing through the mouth area and the cross section of the flow line 3.

Die Heizrohre 2 sind anschließend an ihren im Mündungsbereich der Mantelrohre 1 gerade verlaufenden und glattwandig ausgebildeten Abschnitt 6 schraubenförmig gewendelt, wobei der äußere Wendeldurchmesser gleich dem Innendurchmesser des Mantelrohres 1 ist. Im Wendelinnenraum befindet sich ein Verdrängerkörper 9, der im Ausführungsbeispiel als Rohr ausgebildet ist, das am rücklaufseitigen Ende 1'' des Mantelrohres 1 stirnseitig geschlossen, am vorlaufseitigen Ende 1' aber stirnseitig offen ist und das verhindert, daß die Strömung des sekundären Heizmediums durch den sonst freien Innenraum der Rohrwendel hindurch erfolgt. Außerdem sind die Heizrohre 2 im gewendelten Bereich als Rippenrohre mit dicht aneinander liegenden Rohrwendeln ausgebildet.The heating tubes 2 are then helically coiled on their section 6, which runs straight and has a smooth wall in the mouth region of the jacket tubes 1, the outer coil diameter being equal to the inside diameter of the jacket tube 1. In the interior of the coil there is a displacement body 9, which in the exemplary embodiment is designed as a tube, which is closed on the front side at the return-side end 1 '' of the jacket tube 1, but is open on the front side at the forward-side end 1 'and this prevents the flow of the secondary heating medium through the otherwise free interior of the coiled tubing occurs. In addition, the heating tubes 2 are formed in the coiled area as finned tubes with tube coils lying close together.

Am stromauf liegenden Ende 1'' sind die Mantelrohre 1 durch je einen seitlich angesetzten Stutzen 10 an eine neben den Mantelrohren 1 verlaufende gemeinsame sekundäre Rücklaufleitung 11 für das sekundäre Heizmedium angeschlossen. Mit dieser Rücklaufleitung 11 erfolgt der Anschluß aller Mantelrohre 1 an den gemeinsamen Rücklauf des gekühlten sekundären Heizmediums aus dem sekundären Energieverbrauchersystem, wobei dieser Anschluß wahlweise an einem der beiden Enden der Rücklaufleitung 11 oder an beiden Leitungsenden erfolgen kann. Auch der Anschluß des sekundären Vorlaufs des Energieverbrauchersystems erfolgt über die allen Mantelrohren 1 gemeinsame sekundäre Vorlaufleitung 3, wobei der Anschluß wiederum an einem der beiden Enden dieser Vorlaufleitung 3 oder an ihren beiden Enden gleichzeitig vorgenommen werden kann. Die kondensatseitigen Enden 2' der Heizrohre 2 sind jeweils axial durch die Stirnwand ihres Mantelrohres 1 hindurchgeführt und mit einer gemeinsamen Kondensatsammelleitung 12 verbunden, die in im einzelnen in der Figur nicht dargestellter Weise an den Kondensatrücklauf des primären Energieversorgungssystems anzuschließen ist.At the upstream end 1 ″, the jacket pipes 1 are connected by a laterally attached connector 10 to a common secondary return line 11 running next to the jacket pipes 1 for the secondary heating medium. With this return line 11, all jacket pipes 1 are connected to the common return of the cooled secondary heating medium from the secondary energy consumer system, this connection being able to be made either at one of the two ends of the return line 11 or at both line ends. The secondary flow of the energy consumer system is also connected via the secondary flow line 3 common to all the casing pipes 1, the connection again being able to be carried out at one of the two ends of this flow line 3 or at both ends thereof. The condensate-side ends 2 'of the heating tubes 2 are each guided axially through the end wall of their casing tube 1 and connected to a common condensate manifold 12 which is to be connected to the condensate return of the primary energy supply system in a manner not shown in the figure.

Claims (9)

Dampfbeheizter Wärmeübertrager, insbes. für kondensatseitige Regelung der Wärmeübertragung, mit einem ein dampfbeheiztes Heizsystem aufweisenden, vom sekundären Heizmedium durchströmten Gehäuse, das am stromauf liegenden Ende an einen Rücklauf und am stromab liegenden Ende an einen Vorlauf für das sekundäre Heizmedium anschließbar ist, und mit vom Heizdampf parallel und im Gegenstrom zum sekundären Heizmedium durchströmten Heizrohren (2), die am stromauf liegenden Ende (2'') an einen Dampfvorlauf und am stromab liegenden Ende (2') an einen Kondensatrücklauf angeschlossen sind, dadurch gekennzeichnet, daß das Gehäuse aus einer Reihe von vom sekundären Heizmedium parallel durchströmten Mantelrohren (1) besteht, in denen je eines der Heizrohre (2) angeordnet ist, daß die Mantelrohre (1) mit ihrem vorlaufseitigen Rohrende (1') in einer gemeinsamen sekundären Vorlaufleitung (3) für das sekundäre Heizmedium münden, und daß die Heizrohre (1) vorlaufseitig durch die Mündung (4) des jeweiligen Mantelrohres (1) hindurch in die sekundäre Vorlaufleitung (3) hinein und durch deren Wandung hindurch nach außen zum gemeinsamen Dampfvorlauf geführt sind.Steam-heated heat exchanger, in particular for condensate-side control of heat transfer, with a housing which has a steam-heated heating system and through which the secondary heating medium flows, which can be connected to a return at the upstream end and to a flow for the secondary heating medium at the downstream end, and with the Heating steam in parallel and in countercurrent to the secondary heating medium through which heating pipes (2) are connected, which are connected to a steam supply at the upstream end (2 '') and to a condensate return at the downstream end (2 '), characterized in that the housing consists of a Row of jacket tubes (1) through which the secondary heating medium flows in parallel, in each of which one of the heating tubes (2) is arranged such that the jacket tubes (1) with their inlet-side tube end (1 ') in a common secondary inlet line (3) for the secondary Heating medium open, and that the heating pipes (1) on the flow side through the M invention (4) of the respective casing tube (1) are guided in the secondary flow line (3) and out through the wall of which passes outwardly to the common vapor flow. Wärmetauscher nach Anspruch 1, dadurch gekennzeichnet, daß die Heizrohre (2) im Bereich der Mündung (4) des Mantelrohres (1) in die sekundäre Vorlaufleitung (3) und innerhalb der sekundären Vorlaufleitung (3) selbst eine möglichst geringe Wärmetauschfläche aufweisen, insbes. glattwandig sind.Heat exchanger according to claim 1, characterized in that the heating pipes (2) in the area of the mouth (4) of the casing pipe (1) into the secondary flow line (3) and within the secondary flow line (3) themselves have the smallest possible heat exchange area, in particular are smooth-walled. Wärmetauscher nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Mantelrohre (1) im Bereich ihrer Mündung (4) in die sekundäre Vorlaufleitung (3) im Querschnitt verengt sind.Heat exchanger according to claim 1 or 2, characterized in that the jacket tubes (1) are narrowed in cross section in the region of their mouth (4) into the secondary flow line (3). Wärmetauscher nach Anspruch 3, dadurch gekennzeichnet, daß der verengte Mündungsbereich des Mantelrohres (1) von einem kurzen axialen Verbindungsstutzen (7) gebildet ist, in den das Mantelrohr (1) mit einem nach außen konvex gewölbten Schalenabschnitt (8) übergeht.Heat exchanger according to claim 3, characterized in that the narrowed mouth region of the casing tube (1) is formed by a short axial connecting piece (7) into which the casing tube (1) merges with a shell section (8) which is convexly curved outwards. Wärmetauscher nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß parallel zur sekundären Vorlaufleitung (3) auf ihrer von den Mantelrohren (1) abgewandten Seite eine Dampfvorlaufleitung (5) verläuft, an welche die quer durch die sekundäre Vorlaufleitung (3) hindurch geführten Heizrohre (2) angeschlossen sind.Heat exchanger according to one of claims 1 to 4, characterized in that a steam flow line (5) runs parallel to the secondary flow line (3) on its side facing away from the jacket pipes (1), to which the steam flow line leads through the secondary flow line (3) Heating pipes (2) are connected. Wärmetauscher nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die Heizrohre (2) in den Mantelrohren (1) mit Abstand von deren Mündung (4) in die sekundäre Vorlaufleitung (3) schraubenförmig gewendelt sind, wobei der äußere Wendeldurchmesser gleich dem Innendurchmesser des Mantelrohres (1) und im Wendelinnenraum ein Verdrängerkörper (9) angeordnet ist.Heat exchanger according to one of claims 1 to 5, characterized in that the heating pipes (2) in the casing pipes (1) are helically wound at a distance from their mouth (4) into the secondary flow line (3), the outer spiral diameter being equal to the inner diameter the casing tube (1) and a displacer (9) is arranged in the interior of the coil. Wärmetauscher nach Anspruch 6, dadurch gekennzeichnet, daß die Heizrohre (2) im gewendelten Bereich als Rippenrohre mit dicht aneinander liegenden Rohrwendeln ausgebildet sind.Heat exchanger according to claim 6, characterized in that the heating tubes (2) in the coiled area as finned tubes with closely coiled tube coils are trained. Wärmetauscher nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daR die Mantelrohre (1) am stromauf liegenden Ende (1'') durch je einen seitlich angesetzten Stutzen (10) an eine neben den Mantelrohren (1) verlaufende gemeinsame sekundäre Rücklaufleitung (11) für das sekundäre Heizmedium angeschlossen sind, und daß die kondensatseitigen Enden (2') der Heizrohre (2) jeweils axial durch die Stirnwand ihres Mantelrohres (1) hindurchgeführt und mit einer gemeinsamen Kondensatsammelleitung (12) verbunden sind.Heat exchanger according to one of claims 1 to 7, characterized in that the jacket pipes (1) at the upstream end (1 '') each have a side connection piece (10) to a common secondary return line (11) running next to the jacket pipes (1) ) are connected for the secondary heating medium, and that the condensate-side ends (2 ') of the heating tubes (2) are each guided axially through the end wall of their jacket tube (1) and are connected to a common condensate manifold (12). Wärmetauscher nach den Ansprüchen 1 bis 8, dadurch gekennzeichnet, daR die sekundäre Vor- und Rücklaufleitung (3, 11) ebenso wie die Dampfvorlaufleitung (5) und die Kondensatsammelleitung (12) wahlweise mit jeweils einem ihrer beiden oder mit ihren beiden Leitungsenden an den Vor- und Rücklauf für das sekundäre Heizmedium bzw. an den gemeinsamen Dampfvorlauf und den gemeinsamen Kondensatrücklauf anschließbar sind.Heat exchanger according to claims 1 to 8, characterized in that the secondary supply and return line (3, 11) as well as the steam supply line (5) and the condensate manifold (12) optionally with one of their two or with their two line ends at the front - And return for the secondary heating medium or to the common steam flow and the common condensate return can be connected.
EP94105670A 1993-06-02 1994-04-13 Steam-heated heat exchanger Expired - Lifetime EP0627607B1 (en)

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DE4318240A DE4318240C2 (en) 1993-06-02 1993-06-02 Steam heated heat exchanger
DE4318240 1993-06-02

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EP0627607A3 EP0627607A3 (en) 1996-03-20
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DE10303570A1 (en) * 2003-01-30 2004-08-12 Helmut Bälz GmbH Heat exchanger installation for e.g. heat transfer stations, has heat exchanger units that are connected to channels within pylon and are attached around pylon
CN107869927A (en) * 2017-03-21 2018-04-03 山东大学 A kind of non-condensable gas pipe heat exchanger of constant-current stabilizer length change
CN107869924A (en) * 2017-03-21 2018-04-03 山东大学 A kind of shell-and-tube heat exchanger of the condensable multitube constant-current stabilizer of vapour phase
CN107869926A (en) * 2017-03-21 2018-04-03 山东大学 The condensable gas heat exchanger that a kind of constant-current stabilizer size tapers into
CN107869925A (en) * 2017-03-21 2018-04-03 山东大学 A kind of shell-and-tube heat exchanger of the multitube constant-current stabilizer containing on-condensible gas
CN107894178A (en) * 2017-03-21 2018-04-10 山东大学 A kind of constant-current stabilizer spacing becomes the heat exchanger of big condensable gas
CN107966051A (en) * 2017-04-21 2018-04-27 青岛金玉大商贸有限公司 A kind of condensable porous type constant-current stabilizer heat exchanger of spacing change
CN107966052A (en) * 2017-04-21 2018-04-27 青岛金玉大商贸有限公司 Condensable porous current stabilizer heat exchanger with variable length
CN107966050A (en) * 2017-04-21 2018-04-27 青岛金玉大商贸有限公司 A kind of porous type constant-current stabilizer heat exchanger containing on-condensible gas
CN107966053A (en) * 2017-04-21 2018-04-27 青岛金玉大商贸有限公司 A kind of condensable porous type constant-current stabilizer heat exchanger
CN107976094A (en) * 2017-04-21 2018-05-01 青岛金玉大商贸有限公司 A kind of non-condensable gas porous type constant-current stabilizer heat exchanger of length change
CN107976093A (en) * 2017-04-21 2018-05-01 青岛金玉大商贸有限公司 A kind of non-condensable gas porous type constant-current stabilizer heat exchanger of spacing change

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DE1150695B (en) * 1958-03-17 1963-06-27 Clarke Chapman Ltd Heat exchanger with several parallel jacket pipes through which the heating medium flows and which contain helical pipe coils
EP0105847A2 (en) * 1982-10-04 1984-04-18 FERROLI INDUSTRIE RISCALDAMENTO S.p.A. Water-gas heat exchanger, in particular for centralized heating systems and sanitary water systems
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Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10303570A1 (en) * 2003-01-30 2004-08-12 Helmut Bälz GmbH Heat exchanger installation for e.g. heat transfer stations, has heat exchanger units that are connected to channels within pylon and are attached around pylon
DE10303570B4 (en) * 2003-01-30 2007-02-01 Helmut Bälz GmbH Heat exchanger device for generating hot or hot water
CN107869927A (en) * 2017-03-21 2018-04-03 山东大学 A kind of non-condensable gas pipe heat exchanger of constant-current stabilizer length change
CN107869924A (en) * 2017-03-21 2018-04-03 山东大学 A kind of shell-and-tube heat exchanger of the condensable multitube constant-current stabilizer of vapour phase
CN107869926A (en) * 2017-03-21 2018-04-03 山东大学 The condensable gas heat exchanger that a kind of constant-current stabilizer size tapers into
CN107869925A (en) * 2017-03-21 2018-04-03 山东大学 A kind of shell-and-tube heat exchanger of the multitube constant-current stabilizer containing on-condensible gas
CN107894178A (en) * 2017-03-21 2018-04-10 山东大学 A kind of constant-current stabilizer spacing becomes the heat exchanger of big condensable gas
CN107894178B (en) * 2017-03-21 2019-02-12 山东大学 A kind of heat exchanger for the condensable steam that constant-current stabilizer spacing becomes larger
CN107966052A (en) * 2017-04-21 2018-04-27 青岛金玉大商贸有限公司 Condensable porous current stabilizer heat exchanger with variable length
CN107966050A (en) * 2017-04-21 2018-04-27 青岛金玉大商贸有限公司 A kind of porous type constant-current stabilizer heat exchanger containing on-condensible gas
CN107966053A (en) * 2017-04-21 2018-04-27 青岛金玉大商贸有限公司 A kind of condensable porous type constant-current stabilizer heat exchanger
CN107976094A (en) * 2017-04-21 2018-05-01 青岛金玉大商贸有限公司 A kind of non-condensable gas porous type constant-current stabilizer heat exchanger of length change
CN107976093A (en) * 2017-04-21 2018-05-01 青岛金玉大商贸有限公司 A kind of non-condensable gas porous type constant-current stabilizer heat exchanger of spacing change
CN107966051A (en) * 2017-04-21 2018-04-27 青岛金玉大商贸有限公司 A kind of condensable porous type constant-current stabilizer heat exchanger of spacing change
CN107966053B (en) * 2017-04-21 2019-03-08 青岛金玉大商贸有限公司 A kind of condensable porous type constant-current stabilizer heat exchanger
CN107966052B (en) * 2017-04-21 2019-03-08 青岛金玉大商贸有限公司 Condensable porous current stabilizer heat exchanger with variable length
CN107976093B (en) * 2017-04-21 2019-03-29 青岛金玉大商贸有限公司 A kind of non-condensable gas porous type constant-current stabilizer heat exchanger of spacing variation
CN107966051B (en) * 2017-04-21 2019-04-02 青岛金玉大商贸有限公司 A kind of condensable porous type constant-current stabilizer heat exchanger of spacing variation

Also Published As

Publication number Publication date
DK0627607T3 (en) 1999-02-08
EP0627607B1 (en) 1998-09-30
DE59406993D1 (en) 1998-11-05
ATE171776T1 (en) 1998-10-15
EP0627607A3 (en) 1996-03-20
DE4318240C2 (en) 1998-05-20
DE4318240A1 (en) 1994-12-08

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