EP0290812A1 - Heat-exchanger, especially for cooling cracked gas - Google Patents

Heat-exchanger, especially for cooling cracked gas Download PDF

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Publication number
EP0290812A1
EP0290812A1 EP88106015A EP88106015A EP0290812A1 EP 0290812 A1 EP0290812 A1 EP 0290812A1 EP 88106015 A EP88106015 A EP 88106015A EP 88106015 A EP88106015 A EP 88106015A EP 0290812 A1 EP0290812 A1 EP 0290812A1
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EP
European Patent Office
Prior art keywords
tube
gas
plate
chamber
plates
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP88106015A
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German (de)
French (fr)
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EP0290812B1 (en
Inventor
Peter Brücher
Helmut Lachmann
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Deutsche Babcock Borsig AG
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Borsig GmbH
Deutsche Babcock Borsig AG
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Publication of EP0290812A1 publication Critical patent/EP0290812A1/en
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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
    • F28D7/106—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 consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • F28D7/1607—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 particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • 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
    • F28F9/02—Header boxes; End plates
    • F28F9/0229—Double end plates; Single end plates with hollow spaces

Definitions

  • the invention relates to a heat exchanger, in particular for cooling cracked gas with the features of the preamble of claim 1 or 2.
  • Such heat exchangers require a construction in which the dividing walls between the heat-dissipating hot cracked gas and the high-pressure heat-absorbing cooling medium are as thin as possible to avoid thermal stresses and to achieve low wall temperatures.
  • a further requirement is the supply of cooling medium, which is sufficient at all times and under all operating conditions, to all surfaces involved in the heat exchange with a simultaneously high flow rate of the cooling medium, in particular to the horizontally arranged exchange surfaces. This high flow rate is necessary to prevent deposits of the particles contained in the cooling medium and thus overheating of the walls.
  • the invention has for its object to simplify the generic heat exchanger in such a way that the smallest possible wall thicknesses with the least possible construction costs are possible.
  • the outer tubes of the double tubes also take on a holding function in addition to the task of flow guidance by anchoring the two tube plates against one another together with the jacket.
  • the tube plates can therefore be made very thin without additional anchors, supporting or holding elements, since the high pressure loads acting on the tube plates are absorbed by the outer tube as a tensile load.
  • the outer tubes have the same wall temperature as the jacket, stresses due to differential expansions due to temperature differences in the jacket, the outer tubes and the tube plates are avoided.
  • a heat exchanger for cooling cracked gas consists of a cylindrical jacket 1, which is provided with an inlet nozzle 2 and an outlet nozzle 3 for a coolant. Boiling water is used as the cooling medium, which is fed into the interior enclosed by the jacket 1 under high pressure.
  • the jacket 1 is provided with a tube plate 4, 5 of small wall thickness.
  • a gas inlet chamber 6 is connected to the tube plates 4, 5 on one side and on the other side a gas outlet chamber 7.
  • the gas inlet chamber 6 is connected to the gas outlet chamber 7 via pipes which extend through the interior of the jacket 1.
  • Each tube is designed as a double tube, which consists of a gas-carrying inner tube 8, which is surrounded by an outer tube 9 to form an annular gap.
  • the inner tube 8 is connected to the outer tube 9 via a fitting 10 which is welded into the tube plate 4 on the side of the outer tube 9.
  • the weld seam is therefore outside of the gas flow which flows into the inner tube 8.
  • the outer tube 9 is provided at various heights with passage openings 11, the last of which is located in the immediate vicinity of the tube plate 5 lying on the gas outlet side.
  • the outer tubes 9 thus serve to guide the cooling medium and to hold the two thin-walled tube plates 4, 5.
  • two separating plates 12, 13 are arranged parallel to the tube plate 4 and are penetrated by the double tubes.
  • the two separating plates 12, 13 delimit with the jacket 1 an inflow chamber 14 into which the inlet connection 2 opens.
  • the second partition plate 13 forms with the tube plate 4 an outflow chamber 15, the volume of which is several times smaller than that of the inflow chamber.
  • the volume ratio can be 1 to 4, for example.
  • the second partition plate 13 is provided with through-flow openings 16, which are each located between the double pipes.
  • the cross section of the throughflow openings 16 is dimensioned so large that a significantly higher speed of the cooling medium results in them than in the inflow chamber 14.
  • the outer tubes 9 and the fittings 10 are provided on the part lying within the outflow chamber 15 with inlet openings 17 through which the cooling medium enters the annular gap of the double tubes.
  • the cooling medium flows out of the annular gap through the passage openings 11 into the interior enclosed by the jacket 1, from which it is discharged via the outlet connection 3.
  • Within the inflow chamber 14 the cooling medium flows from a comparatively large volume at a low flow rate. As it passes through the flow openings 16, the cooling medium experiences an increase in the flow rate.
  • This principle of a low pressure loss due to low flow velocity in the inflow chamber 14 and a subsequently increased pressure loss due to higher flow velocity in the flow openings 16 in the second separating plate 13 ensures that an equal amount of cooling medium flows through all flow openings 16, regardless of whether the Flow opening 16 is located in the vicinity of the inlet nozzle 2, or is removed therefrom. This means that all double pipes are supplied with the same amount of cooling medium.
  • tubular sleeves 18 are inserted, which protrude beyond the second partition plate 13 on both sides.
  • the upwardly projecting edge of the tube sleeves 18 prevents any deposits on the separating plate 13 that are carried along by the cooling medium from being entrained.
  • the lower part of the tube sleeves 18 leads the cooling medium directly to the tube plate 4, from where it flows at high speed along the tube plate 4 to the inlet openings 17 of the double tubes.
  • the cooling medium likewise flows through these inlet openings 17 into the annular gap of the double pipes at high speed.
  • the heat exchanger shown in FIG. 3 has two end chambers 19, 20, one of which is provided with the inlet connection 2 and the other with the outlet connection 3 for the supply and discharge of the coolant.
  • the end chambers 19, 20 are connected by the double tubes formed from gas-carrying inner tube 8 and outer tube 9 and adjoin the gas inlet chamber 6 or the gas outlet chamber 7.
  • Each end chamber 19, 20 contains on the gas side one of the described tube plates 4, 5, which are connected via a side wall 21 to a second plate 22.
  • the outer tubes 9 are welded into these plates 4, 5, 22, so that the plates are anchored to one another via the outer tubes 9.
  • the outer tubes 9 are provided with inlet openings 17 and outlet openings 23 on the part lying within the end chambers 19, 20.
  • the end chamber 19 lying on the gas inlet side is divided into an inflow chamber 14 of larger volume and an inflow chamber 15 of smaller volume by a partition plate 13 provided with throughflow openings 16.
  • An overflow weir 24 is connected to the separating plate 13 and stands on the tube plate 4.
  • the cooling medium fed through the inlet nozzle 2 into the end chamber 19 enters the inflow chamber 14 via the overflow weir 24, reaches the outflow chamber 15 with increasing flow velocity, through the inlet openings 17 into the annular space of the double pipes and through the outlet openings 23 into the other end chamber 21, from where it is discharged through the outlet nozzle 3.

Abstract

Die gasführenden Rohre (8) eines zum Kühlen von Spaltgas dienenden Wärmetauschers sind von Außenrohren (9) umgeben und mit diesen verbunden. Die Außenrohre (9) sind in Rohrplatten (4, 5) eingeschweißt und dienen sowohl der Führung des Kühlmediums als auch der Verankerung der Rohrplatten (4, 5) gegeneinander, so daß diese dünnwandig ausgeführt werden können.The gas-carrying pipes (8) of a heat exchanger used to cool fission gas are surrounded by outer pipes (9) and connected to them. The outer tubes (9) are welded into tube plates (4, 5) and serve both to guide the cooling medium and to anchor the tube plates (4, 5) to one another so that they can be made thin-walled.

Description

Die Erfindung betrifft einen Wärmetauscher, insbesondere zum Kühlen von Spaltgas mit den Merkmalen des Oberbegriffes des Anspruches 1 oder 2.The invention relates to a heat exchanger, in particular for cooling cracked gas with the features of the preamble of claim 1 or 2.

Derartige Wärmetauscher erfordern eine Konstruktion, bei der die Trennwandungen zwischen dem wärmeabgebenden heißen Spaltgas und dem unter hohen Druck stehenden wärmeaufnehmenden Kühlmedium zur Vermeidung thermischer Spannungen und zur Erzielung niedriger Wandtemperaturen so dünn wie möglich sind. Eine weitere Forderung ist die jederzeit und unter allen Betriebsbedingungen ausreichende Zuführung von Kühlmedium an alle am Wärmetausch beteiligten Flächen bei gleichzeitiger ausreichend hoher Strömungsgeschwindigkeit des Kühlmediums, insbesondere an den horizontal angeordneten Austauschflächen. Diese hohe Strömungsgeschwindigkeit ist erforderlich, um Ablagerungen der im Kühlmedium enthaltenen Partikel und damit überhitzungen der Wandungen zu verhindern.Such heat exchangers require a construction in which the dividing walls between the heat-dissipating hot cracked gas and the high-pressure heat-absorbing cooling medium are as thin as possible to avoid thermal stresses and to achieve low wall temperatures. A further requirement is the supply of cooling medium, which is sufficient at all times and under all operating conditions, to all surfaces involved in the heat exchange with a simultaneously high flow rate of the cooling medium, in particular to the horizontally arranged exchange surfaces. This high flow rate is necessary to prevent deposits of the particles contained in the cooling medium and thus overheating of the walls.

Bei einem bekannten Rohrbündelwärmetauscher (DE-PS 35 33 219) zur Erfüllung dieser Forderungen ist die auf der Gaseintrittsseite angeordnete Rohrplatte dünn ausgeführt und wird über Tragfinger auf einer Tragplatte abgestützt. Das in den Wärmetauscher eingespeiste Kühlmedium wird zu einem großen Anteil durch den zwischen der dünnen Rohrplatte und der Tragplatte gebildeten Zwischenraum geführt, um auf diese Weise die dünne Rohrplatte zu kühlen. Wenn sich auch diese Konstruktion im Betrieb bewährt hat, so erfordert sie doch durch die Anordnung einer Tragplatte einen erhöhten konstruktiven Aufwand.In a known tube bundle heat exchanger (DE-PS 35 33 219) to meet these requirements, the tube plate arranged on the gas inlet side is made thin and is supported on a support plate via support fingers. A large proportion of the cooling medium fed into the heat exchanger is passed through the space formed between the thin tube plate and the support plate, in order to cool the thin tube plate in this way. Even if this construction has proven itself in operation, it requires an increased design effort due to the arrangement of a support plate.

Der Erfindung liegt die Aufgabe zugrunde, den gattungsgemäßen Wärmetauscher derart zu vereinfachen, daß geringstmögliche Wanddicken bei geringstmöglichem Bauaufwand möglich sind.The invention has for its object to simplify the generic heat exchanger in such a way that the smallest possible wall thicknesses with the least possible construction costs are possible.

Diese Aufgabe wird bei einem gattungsgemäßen Wärmetauscher durch die kennzeichnenden Merkmale des Anspruches 1 oder 2 gelöst. Vorteilhafte Ausgestaltungen der Erfindung sind in den Unteransprüchen angegeben.This object is achieved in a generic heat exchanger by the characterizing features of claim 1 or 2. Advantageous embodiments of the invention are specified in the subclaims.

Bei dem erfindungsgemäßen Wärmetauscher übernehmen die Außenrohre der Doppelrohre außer der Aufgabe der Strömungsführung auch eine Haltefunktion, indem sie zusammen mit dem Mantel die beiden Rohrplatten gegeneinander verankern. Die Rohrplatten können daher trotz des auf der Kühlmediumseite herrschenden hohen Druckes ohne zusätzliche Anker, Stütz- oder Halteelemente sehr dünn ausgeführt werden, da die auf die Rohrplatten wirkenden hohen Druckbelastungen von dem Außenrohr als Zugbelastung aufgenommen werden. Da die Außenrohre die gleiche Wandtemperatur wie der Mantel annehmen, werden Spannungen durch Differenzdehnungen aufgrund von Temperaturdifferenzen in dem Mantel, den Außenrohren und den Rohrplatten vermieden. Die aus der Dehnungsdifferenz zwischen dem Innenrohr und dem Außenrohr resultierenden Spannungen werden durch die Gestaltung und die Dimensionierung der Rohrendenverbindung aufgenommen, so daß die Dehnungsdifferenz nicht auf die Rohrplatten oder auf die Verbindung zwischen den Außenrohren und den Rohrplatten übertragen wird.In the heat exchanger according to the invention, the outer tubes of the double tubes also take on a holding function in addition to the task of flow guidance by anchoring the two tube plates against one another together with the jacket. Despite the high pressure prevailing on the cooling medium side, the tube plates can therefore be made very thin without additional anchors, supporting or holding elements, since the high pressure loads acting on the tube plates are absorbed by the outer tube as a tensile load. Since the outer tubes have the same wall temperature as the jacket, stresses due to differential expansions due to temperature differences in the jacket, the outer tubes and the tube plates are avoided. The stresses resulting from the difference in elongation between the inner tube and the outer tube are absorbed by the design and dimensioning of the tube end connection, so that the difference in elongation is not transmitted to the tube plates or to the connection between the outer tubes and the tube plates.

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und werden im folgenden näher erläutert. Es zeigen:

  • Fig. 1 den Längsschnitt durch einen Wärmetauscher gemäß der Erfindung
  • Fig. 2 die Einzelheit Z nach Fig. 1 und
  • Fig. 3 den Längsschnitt durch einen Wärmetauscher gemäß einer anderen Ausführungsform der Erfindung.
Two embodiments of the invention are shown in the drawing and are explained in more detail below. Show it:
  • Fig. 1 shows the longitudinal section through a heat exchanger according to the invention
  • Fig. 2 shows the detail Z of FIG. 1 and
  • Fig. 3 shows the longitudinal section through a heat exchanger according to another embodiment of the invention.

Ein Wärmetauscher zum Kühlen von Spaltgas besteht aus einem zylindrischen Mantel 1, der mit einem Eintrittsstutzen 2 und einem Austrittsstutzen 3 für ein Kühlmittel versehen ist. Als Kühlmedium dient siedendes Wasser, das unter hohem Druck in den von dem Mantel 1 umschlossenen Innenraum eingespeist wird.A heat exchanger for cooling cracked gas consists of a cylindrical jacket 1, which is provided with an inlet nozzle 2 and an outlet nozzle 3 for a coolant. Boiling water is used as the cooling medium, which is fed into the interior enclosed by the jacket 1 under high pressure.

An den beiden Enden ist der Mantel 1 mit je einer Rohrplatte 4, 5 von geringer Wanddicke versehen. An die Rohrplatten 4, 5 schließt sich auf der einen Seite eine Gaseintrittskammer 6 und auf der anderen Seite eine Gasaustrittskammer 7 an. Die Gaseintrittskammer 6 ist mit der Gasaustrittskammer 7 über Rohre verbunden, die sich durch den Innenraum des Mantels 1 erstrecken.At the two ends, the jacket 1 is provided with a tube plate 4, 5 of small wall thickness. A gas inlet chamber 6 is connected to the tube plates 4, 5 on one side and on the other side a gas outlet chamber 7. The gas inlet chamber 6 is connected to the gas outlet chamber 7 via pipes which extend through the interior of the jacket 1.

Jedes Rohr ist als Doppelrohr ausgebildet, das aus einem gasführenden Innenrohr 8 besteht, das unter Bildung eines Ringspaltes von einem Außenrohr 9 umgeben ist. Das Innenrohr 8 ist mit dem Außenrohr 9 über ein Formstück 10 verbunden, das auf der Seite des Außenrohres 9 in die Rohrplatte 4 eingeschweißt ist. Die Schweißnaht liegt deshalb außerhalb des Gasstromes, welcher in das Innenrohr 8 einströmt. Das Außenrohr 9 ist in verschiedenen Höhen mit Durchtrittsöffnungen 11 versehen, deren letzte sich in unmittelbarer Nähe des auf der Gasaustrittsseite liegenden Rohrplatte 5 befindet. Die Außenrohre 9 dienen damit der Führung des Kühlmediums und der Halterung der beiden dünnwandigen Rohrplatten 4, 5.Each tube is designed as a double tube, which consists of a gas-carrying inner tube 8, which is surrounded by an outer tube 9 to form an annular gap. The inner tube 8 is connected to the outer tube 9 via a fitting 10 which is welded into the tube plate 4 on the side of the outer tube 9. The weld seam is therefore outside of the gas flow which flows into the inner tube 8. The outer tube 9 is provided at various heights with passage openings 11, the last of which is located in the immediate vicinity of the tube plate 5 lying on the gas outlet side. The outer tubes 9 thus serve to guide the cooling medium and to hold the two thin-walled tube plates 4, 5.

Um die auf der Gaseintrittsseite liegende Rohrplatte 4 wirksam zu kühlen, sind parallel zu der Rohrplatte 4 zwei Trennbleche 12, 13 angeordnet, die von den Doppelrohren durchdrungen sind. Die beiden Trennbleche 12, 13 begrenzen mit dem Mantel 1 eine Einströmkammer 14, in die der Eintrittsstutzen 2 mündet. Das zweite Trennblech 13 bildet mit der Rohrplatte 4 eine Ausströmkammer 15, deren Volumen um ein Mehrfaches geringer ist als das der Einströmkammer. Das Volumenverhältnis kann zum Beispiel 1 zu 4 betragen.In order to effectively cool the tube plate 4 lying on the gas inlet side, two separating plates 12, 13 are arranged parallel to the tube plate 4 and are penetrated by the double tubes. The two separating plates 12, 13 delimit with the jacket 1 an inflow chamber 14 into which the inlet connection 2 opens. The second partition plate 13 forms with the tube plate 4 an outflow chamber 15, the volume of which is several times smaller than that of the inflow chamber. The volume ratio can be 1 to 4, for example.

Das zweite Trennblech 13 ist mit Durchströmöffnungen 16 versehen, die sich jeweils zwischen den Doppelrohren befinden. Der Querschnitt der Durchströmöffnungen 16 ist so groß bemessen, daß sich in ihnen eine deutlich höhere Geschwindigkeit des Kühlmediums ergibt als in der Einströmkammer 14.The second partition plate 13 is provided with through-flow openings 16, which are each located between the double pipes. The cross section of the throughflow openings 16 is dimensioned so large that a significantly higher speed of the cooling medium results in them than in the inflow chamber 14.

Die Außenrohre 9 bzw. die Formstücke 10 sind auf dem innerhalb der Ausströmkammer 15 liegenden Teil mit Eintrittsöffnungen 17 versehen, durch die das Kühlmedium in den Ringspalt der Doppelrohre eintritt. Aus dem Ringspalt strömt das Kühlmedium durch die Durchtrittsöffnungen 11 in den von dem Mantel 1 umschlossenen Innenraum, aus dem es über den Austrittsstutzen 3 abgeführt wird. Innerhalb der Einströmkammer 14 von vergleichsweise großem Volumen strömt das Kühlmedium mit geringer Strömungsgeschwindigkeit. Bei dem Durchtritt durch die Durchströmöffnungen 16 erfährt das Kühlmedium eine Erhöhung der Strömungsgeschwindigkeit. Durch dieses Prinzip eines niedrigen Druckverlustes infolge niedriger Strömungsgeschwindigkeit in der Einströmkammer 14 und eines anschließend erhöhten Druckverlustes infolge höherer Strömungsgeschwindigkeit in den Durchströmöffnungen 16 im zweiten Trennblech 13 wird sichergestellt, daß durch alle Durchströmöffnungen 16 eine gleich große Menge Kühlmedium strömt, unabhängig davon, ob sich die Durchströmöffnung 16 in der Nähe des Eintrittsstutzens 2 befindet, oder davon entfernt ist. Dadurch werden alle Doppelrohre mit der gleichen Menge Kühlmedium versorgt.The outer tubes 9 and the fittings 10 are provided on the part lying within the outflow chamber 15 with inlet openings 17 through which the cooling medium enters the annular gap of the double tubes. The cooling medium flows out of the annular gap through the passage openings 11 into the interior enclosed by the jacket 1, from which it is discharged via the outlet connection 3. Within the inflow chamber 14 the cooling medium flows from a comparatively large volume at a low flow rate. As it passes through the flow openings 16, the cooling medium experiences an increase in the flow rate. This principle of a low pressure loss due to low flow velocity in the inflow chamber 14 and a subsequently increased pressure loss due to higher flow velocity in the flow openings 16 in the second separating plate 13 ensures that an equal amount of cooling medium flows through all flow openings 16, regardless of whether the Flow opening 16 is located in the vicinity of the inlet nozzle 2, or is removed therefrom. This means that all double pipes are supplied with the same amount of cooling medium.

In die Durchströmöffnungen 16 sind Rohrhülsen 18 eingesetzt, die nach beiden Seiten das zweite Trennblech 13 überragen. Der nach oben überstehende Rand der Rohrhülsen 18 verhindert das Mitreißen eventuell auf dem Trennblech 13 befindlicher, vom Kühlmedium mitgeführter Ablagerungen. Der untere Teil der Rohrhülsen 18 führt das Kühlmedium direkt zur Rohrplatte 4, von wo es mit hoher Geschwindigkeit entlang der Rohrplatte 4 zu den Eintrittsöffnungen 17 der Doppelrohre strömt. Durch diese Eintrittsöffnungen 17 strömt das Kühlmedium ebenfalls mit hoher Geschwindigkeit in den Ringspalt der Doppelrohre.In the flow openings 16, tubular sleeves 18 are inserted, which protrude beyond the second partition plate 13 on both sides. The upwardly projecting edge of the tube sleeves 18 prevents any deposits on the separating plate 13 that are carried along by the cooling medium from being entrained. The lower part of the tube sleeves 18 leads the cooling medium directly to the tube plate 4, from where it flows at high speed along the tube plate 4 to the inlet openings 17 of the double tubes. The cooling medium likewise flows through these inlet openings 17 into the annular gap of the double pipes at high speed.

Der in Fig. 3 dargestellte Wärmetauscher weist zwei Endkammern 19, 20 auf, von denen eine mit dem Eintrittsstutzen 2 und die andere mit dem Austrittsstutzen 3 für die Zuführung und die Abführung des Kühlmittels versehen ist. Die Endkammern 19, 20 sind durch die aus gasführendem Innenrohr 8 und Außenrohr 9 gebildeten Doppelrohre verbunden und schließen sich an die Gaseintrittskammer 6 bzw. an die Gasaustrittskammer 7 an. Jede Endkammer 19, 20 enthält auf der Gasseite eine der beschriebenen Rohrplatten 4, 5, die über eine Seitenwand 21 mit einer zweiten Platte 22 verbunden sind. In diese Platten 4, 5, 22 sind die Außenrohre 9 eingeschweißt, so daß die Platten über die Außenrohre 9 gegeneinander verankert sind. Die Außenrohre 9 sind auf dem innerhalb der Endkammern 19, 20 liegenden Teil mit Eintrittsöffnungen 17 und Austrittsöffnungen 23 versehen.The heat exchanger shown in FIG. 3 has two end chambers 19, 20, one of which is provided with the inlet connection 2 and the other with the outlet connection 3 for the supply and discharge of the coolant. The end chambers 19, 20 are connected by the double tubes formed from gas-carrying inner tube 8 and outer tube 9 and adjoin the gas inlet chamber 6 or the gas outlet chamber 7. Each end chamber 19, 20 contains on the gas side one of the described tube plates 4, 5, which are connected via a side wall 21 to a second plate 22. The outer tubes 9 are welded into these plates 4, 5, 22, so that the plates are anchored to one another via the outer tubes 9. The outer tubes 9 are provided with inlet openings 17 and outlet openings 23 on the part lying within the end chambers 19, 20.

Die auf der Gaseintrittsseite liegende Endkammer 19 ist durch ein mit Durchströmöffnungen 16 versehenes Trennblech 13 in eine Einströmkammer 14 von größerem Volumen und eine Anströmkammer 15 von geringerem Volumen aufgeteilt. Mit dem Trennblech 13 ist ein überlaufwehr 24 verbunden, das auf der Rohrplatte 4 aufsteht. Das durch den Eintrittsstutzen 2 in die Endkammer 19 eingespeiste Kühlmedium tritt über das Überlaufwehr 24 in die Einströmkammer 14 ein, gelangt unter Erhöhung der Strömungsgeschwindigkeit in die Ausströmkammer 15, durch die Eintrittsöffnungen 17 in den Ringraum der Doppelrohre und durch die Austrittsöffnungen 23 in die andere Endkammer 21, von wo aus es durch den Austrittsstutzen 3 abgeführt wird.The end chamber 19 lying on the gas inlet side is divided into an inflow chamber 14 of larger volume and an inflow chamber 15 of smaller volume by a partition plate 13 provided with throughflow openings 16. An overflow weir 24 is connected to the separating plate 13 and stands on the tube plate 4. The cooling medium fed through the inlet nozzle 2 into the end chamber 19 enters the inflow chamber 14 via the overflow weir 24, reaches the outflow chamber 15 with increasing flow velocity, through the inlet openings 17 into the annular space of the double pipes and through the outlet openings 23 into the other end chamber 21, from where it is discharged through the outlet nozzle 3.

Wenn auch die Erfindung vorstehend an Spaltgaskühlern stehender Bauart erläutert ist, so kann die Erfindung auch auf liegend angeordnete Spaltgaskühler angewendet werden.Even though the invention has been explained above on standing gas coolers, the invention can also be applied to lying gas coolers arranged horizontally.

Claims (5)

1. Wärmetauscher, insbesondere zum Kühlen von Spaltgas, bestehend aus einer Gaseintrittskammer (6) und einer Gasaustrittskammer (8), die durch gasführende Rohre (8) miteinander verbunden und durch jeweils eine von den Rohren (8) durchdrungene Rohrplatte (4, 5) begrenzt sind, wobei die Rohrplatten (4, 5) mit einem die Rohre umschließenden, mit einem Eintrittsstutzen (2) und einem Austrittsstutzen (3) versehenen Mantel (1) zur Bildung eines von dem Kühlmedium durchflossenen Innenraumes verbunden sind, dadurch gekennzeichnet, daß jedes gasführende Rohr (8) unter Bildung eines Ringspaltes von einem Durchtrittsöffnungen (11) aufweisenden Außenrohr (9) umgeben und mit diesem verbunden ist, daß das Außenrohr (9) in die Rohrplatte (4, 5) eingeschweißt ist und daß beide Rohrplatten (4, 5) dünnwandig sind.1. Heat exchanger, in particular for cooling cracked gas, consisting of a gas inlet chamber (6) and a gas outlet chamber (8) which are connected to one another by gas-carrying pipes (8) and by a tube plate (4, 5) penetrated by the tubes (8). are limited, the tube plates (4, 5) being connected to a jacket (1) which surrounds the tubes and has an inlet connector (2) and an outlet connector (3) to form an interior through which the cooling medium flows, characterized in that each gas-carrying pipe (8), forming an annular gap, is surrounded by an outer pipe (9) having through openings (11) and connected to it, that the outer pipe (9) is welded into the pipe plate (4, 5) and that both pipe plates (4, 5) are thin-walled. 2. Wärmetauscher, insbesondere zum Kühlen von Spaltgas, bestehend aus einer Gaseintrittskammer (6) und einer Gasaustrittskammer (7), die durch gasführende Rohre (8) miteinander verbunden und durch jeweils eine von den Rohren durchdrungene Rohrplatte (4, 5) begrenzt sind, wobei die Rohrplatten (4, 5) mit jeweils einer zweiten Platte (22) zur Bildung von Endkammern (19, 20) für die Zuführung und Abführung eines Kühlmediums verbunden sind, dadurch gekennzeichnet, daß jedes gasführende Rohr (8) unter Bildung eines Ringspaltes von einem Außenrohr (9) umgeben und mit diesem verbunden ist, daß das Außenrohr (9) in die Rohrplatten (4, 5) und die zweiten Platten (22) eingeschweißt ist und daß die Platten (4, 5, 22) dünnwandig sind.2. heat exchanger, in particular for cooling cracked gas, consisting of a gas inlet chamber (6) and a gas outlet chamber (7), which are connected to one another by gas-carrying pipes (8) and are each delimited by a pipe plate (4, 5) penetrated by the pipes, wherein the tube plates (4, 5) are each connected to a second plate (22) to form end chambers (19, 20) for the supply and discharge of a cooling medium, characterized in that each gas-carrying tube (8) forms an annular gap from surrounded and connected to an outer tube (9) that the outer tube (9) is welded into the tube plates (4, 5) and the second plates (22) and that the plates (4, 5, 22) are thin-walled. 3. Wärmetauscher nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß in einem Abstand von der auf der Gaseintrittsseite liegenden Rohrplatte (4) ein mit Durchströmöffnungen (16) versehenes Trennblech (13) zur Bildung einer Ausströmkammer (15) angeordnet ist, daß das Außenrohr (9) auf dem innerhalb der Ausströmkammer (15) liegenden Teil mit Eintrittsöffnungen (17) versehen ist, daß auf der der Rohrplatte (4) abgewandten Seite des Trennbleches (13) eine Einströmkammer (14) gebildet ist, in die der Eintrittsstutzen (2) mündet und deren Volumen um ein Mehrfaches größer ist als das der Ausströmkammer (15).3. Heat exchanger according to claim 1 or 2, characterized in that at a distance from the tube plate lying on the gas inlet side (4) with a flow openings (16) provided separating plate (13) for forming an outflow chamber (15) is arranged that the outer tube (9) on the part located within the outflow chamber (15) is provided with inlet openings (17) that on the side of the separating plate (13) facing away from the tube plate (4) an inflow chamber (14) is formed, into which the inlet nozzle (2 ) opens out and its volume is several times larger than that of the outflow chamber (15). 4. Wärmetauscher nach Anspruch 3, dadurch gekennzeichnet, daß der Querschnitt aller Durchströmöffnungen (16) im Vergleich zu dem Querschnitt der Einströmkammer (14) so bemessen ist, daß sich eine Erhöhung der Strömungsgeschwindigkeit des Kühlmediums ergibt.4. Heat exchanger according to claim 3, characterized in that the cross section of all flow openings (16) compared to the cross section of the inflow chamber (14) is dimensioned such that there is an increase in the flow rate of the cooling medium. 5. Wärmetauscher nach Anspruch 3 oder 4, dadurch gekennzeichnet, daß in die Durchströmöffnungen (16) des zweiten Trennbleches (13) Rohrhülsen (18) eingesetzt sind, die das Trennblech (13) nach beiden Seiten hin überragen.5. Heat exchanger according to claim 3 or 4, characterized in that in the flow openings (16) of the second partition plate (13) tubular sleeves (18) are inserted which protrude beyond the partition plate (13) on both sides.
EP88106015A 1987-05-12 1988-04-15 Heat-exchanger, especially for cooling cracked gas Expired - Lifetime EP0290812B1 (en)

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DE3715712A DE3715712C1 (en) 1987-05-12 1987-05-12 Heat exchanger especially for cooling cracked gas
DE3715712 1987-05-12

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EP0290812B1 EP0290812B1 (en) 1991-01-02

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Also Published As

Publication number Publication date
DE3861347D1 (en) 1991-02-07
DE3715712C1 (en) 1988-07-21
JP2722076B2 (en) 1998-03-04
JPS63297994A (en) 1988-12-05
EP0290812B1 (en) 1991-01-02
US4848449A (en) 1989-07-18

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