EP0290812B1 - Heat-exchanger, especially for cooling cracked gas - Google Patents

Heat-exchanger, especially for cooling cracked gas Download PDF

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Publication number
EP0290812B1
EP0290812B1 EP88106015A EP88106015A EP0290812B1 EP 0290812 B1 EP0290812 B1 EP 0290812B1 EP 88106015 A EP88106015 A EP 88106015A EP 88106015 A EP88106015 A EP 88106015A EP 0290812 B1 EP0290812 B1 EP 0290812B1
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Prior art keywords
tube
chamber
plate
gas
tubes
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EP88106015A
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German (de)
French (fr)
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EP0290812A1 (en
Inventor
Peter Brücher
Helmut Lachmann
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Deutsche Babcock Borsig AG
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Deutsche Babcock Borsig AG
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Priority to DE3715712A priority patent/DE3715712C1/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10Heat-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
    • F28D7/106Heat-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16Heat-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
    • F28D7/1607Heat-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02Header boxes; End plates
    • F28F9/0229Double end plates; Single end plates with hollow spaces

Description

  • Die Erfindung betrifft einen Wärmetauscher, insbesondere zum Kühlen von Spaltgas mit den Merkmalen des Oberbegriffes des Anspruches 1.The invention relates to a heat exchanger, in particular for cooling cracked gas, with the features of the preamble of claim 1.
  • 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 ist. 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 Uberhitzungen der Wandungen zu vermeiden.Such heat exchangers require a construction in which the dividing walls between the heat-dissipating hot cracked gas and the heat-absorbing cooling medium under high pressure are as thin as possible in order 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 in order to avoid deposits of the particles contained in the cooling medium and thus overheating of the walls.
  • Bei einem bekannten Rohrbündelwärmetauscher (DE-C-3 533 219) 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-C-3 533 219) to meet these requirements, the tube plate arranged on the gas inlet side is made thin and is supported by a finger on a support plate. 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 does require an increased design effort due to the arrangement of a support plate.
  • Ein weiterer bekannter Wärmetauscher zum Kühlen von heißen Gesen (GB-A-2 057 666) weist eine Gaseintrittskammer und eine Gasaustrittskammer auf, die jeweis durch eine Rohrplatte begrenzt und durch das Gas führende innere Rohre miteinander verbunden sind. Die inneren Rohre sind von äußeren Rohren umgeben, die jeweils in eine der Gasseite abgewandte Platte einer ungeteilten Endkammer zur Zuführung und Abführung eines Kühlmediums eingesetzt sind. Auf der Gaseintrittsseite ist die Endkammer in einem Abstand von der mit dem Gas in Berührung kommenden Rohrplatte angeordnet. Zwischen dieser mit einem wärmeisolierenden Material verkleideten Rohrplatte und der Endkammer sind die äußeren Rohre von Rohrabschnitten umgeben, durch die das Kühlmedium aus der Endkammer dem Ringraum zwischen den inneren und äußeren Rohren zuströmt.Another known heat exchanger for cooling hot dies (GB-A-2 057 666) has a gas inlet chamber and a gas outlet chamber, each of which is delimited by a tube plate and connected to one another by inner tubes carrying the gas. The inner tubes are surrounded by outer tubes, each of which is inserted into a plate of an undivided end chamber facing away from the gas side for supplying and removing a cooling medium. On the gas inlet side, the end chamber is arranged at a distance from the tube plate which comes into contact with the gas. Between this tube plate clad with a heat-insulating material and the end chamber, the outer tubes are surrounded by tube sections through which the cooling medium flows from the end chamber to the annular space between the inner and outer tubes.
  • Der Erfindung loiegt die Aufgabe zugrunde, den gattungsgemäßen Wärmetauscher derart zu vereinfachen, daß geringstmögliche Wanddicken bei geringstmöglichem Bauaufwand möglich sind.The invention is based on the object of simplifying the generic heat exchanger in such a way that the smallest possible wall thicknesses are possible with the least possible construction effort.
  • Diese Aufgabe wird bei einem gattungsgemäßen Wärmetauscher erfindungsgemäß durch die kennzeichenden Merkmale des Anspruches 1 gelöst. Vorteilhafte Ausgestaltungen der Erfindung sind in den Unteransprüchen angegeben.This object is achieved according to the invention in a generic heat exchanger by the characterizing features of claim 1. 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 the 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 serves as the cooling medium, which is fed under high pressure into the interior enclosed by the jacket 1.
  • 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. The tube plates 4, 5 are followed by a gas inlet chamber 6 on one side and a gas outlet chamber 7 on the other side. 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 shaped piece 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 with passage openings 11 at different heights, 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.Around the pipe on the gas inlet side plate 4 to cool effectively, two partition plates 12, 13 are arranged parallel to the tube plate 4, which 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 or the fittings 10 are provided on the part lying inside 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 from 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 of comparatively large volume, the cooling medium flows 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 partition 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. As a result, 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 by a partition plate 13 provided with throughflow openings 16 into an inflow chamber 14 of larger volume and an inflow chamber 15 of smaller volume. 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. Heat exchanger in particular for the cooling of fission gas, consisting of a gas entry chamber (6) and a gas exit chamber (7), which are connected one with the other by gas-conducting tubes (8) and each bounded by a respective tube plate (4, 5) penetrated by the tubes (8), wherein at least the tube plate (4) at the gas entry side together with a second plate (12, 22) bounds an end chamber (19) for the conduction of coolant and each gas-conducting tube (8) is surrounded with the formation of an annular gap by an outer tube (9) welded in the tube plate (4) and connected with the tube (8), characterised thereby, that the outer tubes (9) are additionally welded into the second plates (12, 22) and/orthe tube plate (5) at the gas exit side, that the tube plates (4,5) and the second plates (12,22) are thin-walled, that the end chamber (19) is divided by a metal partition plate (18), which is arranged parallelly tothe tube plate (4) and provided with passage openings (16), into an inflow chamber (14), which is bounded by the second plate (12, 22) and provided with the entry nipple (2), and an outflow chamber (15) bounded by the tube plate (4), that the volume of the inflow chamber (14) is several times greater than that of the outflow chamber (15) and that the outer tubes (9) are provided with entry openings (17) on the part lying within the outflow chamber (15).
2. Heat exchanger according to claim 1, characterised thereby, that the tube plate (5) on the gas exit side together with a second plate (22) bounds an end chamber (20) for the discharge of the coolant.
3. Heat exchanger according to claim 1, characterised thereby, that the tube plates (4, 5) are connected with a jacket (1), which encloses the tubes (8) and is provided with an entry nipple (2) and an exit nipple (3), for the formation of an internal space flowed through by the coolant and that the outer tubes (9) are provided with passage openings (11) on the part lying within the interior space.
4. Heat exchanger according to claim 1, characterised thereby, that the cross-section of all throughflow openings (16) is so dimensioned by comparison with the cross-section of the inflow chamber (14) that an increase in the speed of flow of the coolant results.
5. Heat exchanger according to claim 1 or 4, characterised thereby, that tube sleeves (18), which project beyond the second metal partition plate (13) at both sides, are inserted into the throughflow openings (16) of the metal partition plate (13).
EP88106015A 1987-05-12 1988-04-15 Heat-exchanger, especially for cooling cracked gas Expired - Lifetime EP0290812B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE3715712 1987-05-12
DE3715712A DE3715712C1 (en) 1987-05-12 1987-05-12 Heat exchanger especially for cooling cracked gas

Publications (2)

Publication Number Publication Date
EP0290812A1 EP0290812A1 (en) 1988-11-17
EP0290812B1 true EP0290812B1 (en) 1991-01-02

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EP (1) EP0290812B1 (en)
JP (1) JP2722076B2 (en)
DE (2) DE3715712C1 (en)

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JP2722076B2 (en) 1998-03-04
JPS63297994A (en) 1988-12-05
US4848449A (en) 1989-07-18
EP0290812A1 (en) 1988-11-17
DE3715712C1 (en) 1988-07-21
DE3861347D1 (en) 1991-02-07

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