EP0053248A2 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
EP0053248A2
EP0053248A2 EP81108203A EP81108203A EP0053248A2 EP 0053248 A2 EP0053248 A2 EP 0053248A2 EP 81108203 A EP81108203 A EP 81108203A EP 81108203 A EP81108203 A EP 81108203A EP 0053248 A2 EP0053248 A2 EP 0053248A2
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EP
European Patent Office
Prior art keywords
tube
plates
jacket
hoods
inner tubes
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.)
Withdrawn
Application number
EP81108203A
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German (de)
French (fr)
Other versions
EP0053248A3 (en
Inventor
Heribert Dr. Kuerten
Hubert Puestel
Rudi Schulz
Georg Weber
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BASF SE
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BASF SE
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Publication date
Application filed by BASF SE filed Critical BASF SE
Publication of EP0053248A2 publication Critical patent/EP0053248A2/en
Publication of EP0053248A3 publication Critical patent/EP0053248A3/en
Withdrawn legal-status Critical Current

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    • 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
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10G—CRACKING HYDROCARBON OILS; PRODUCTION OF LIQUID HYDROCARBON MIXTURES, e.g. BY DESTRUCTIVE HYDROGENATION, OLIGOMERISATION, POLYMERISATION; RECOVERY OF HYDROCARBON OILS FROM OIL-SHALE, OIL-SAND, OR GASES; REFINING MIXTURES MAINLY CONSISTING OF HYDROCARBONS; REFORMING OF NAPHTHA; MINERAL WAXES
    • C10G1/00—Production of liquid hydrocarbon mixtures from oil-shale, oil-sand, or non-melting solid carbonaceous or similar materials, e.g. wood, coal
    • C10G1/06—Production of liquid hydrocarbon mixtures from oil-shale, oil-sand, or non-melting solid carbonaceous or similar materials, e.g. wood, coal by destructive hydrogenation
    • C10G1/065—Production of liquid hydrocarbon mixtures from oil-shale, oil-sand, or non-melting solid carbonaceous or similar materials, e.g. wood, coal by destructive hydrogenation in the presence of a solvent
    • 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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates

Definitions

  • the present invention relates to a heat exchanger for use in coal hydrogenation plants at pressures from 200 to 700 bar and temperatures from 100 to 500 o C with a tube bundle arranged in a closed pressure vessel with tube-side inlet and outlet nozzles for the coal slurry and / or cycle gas, with shell-side Inlet and outlet nozzle for the heat-emitting circulating gas, in which the inner tubes are arranged between hoods closed by tube plates, and the hoods are connected by hood nozzles to the tube-side inlet and outlet nozzles for the pulp and / or the circulating gas.
  • the inner tubes have an outer diameter of 23 mm and an inner diameter of 14 mm. Under these conditions, it is possible to accommodate between 200 to 300 inner tubes arranged parallel to a tube bundle in a pressure vessel.
  • the hoods in the known designs are conical, the difference in thermal expansion between the tube bundle and the pressure vessel is absorbed by a stuffing box.
  • the known design has several disadvantages. For example, the conical hoods take up even more dead space with larger diameters than with diameters that were customary in the past.
  • the coal slurry and the cycle gas, which are guided around the pipes in the known constructions, can be of diameters. Do not distribute larger than 600 mm evenly over the entire cross-section of the jacket space.
  • baffles when driving with pulp and circulating gas around the pipes: this is disadvantageous in two respects.
  • the heat transfer coefficient becomes smaller than that of one cross flow achieved by chicane, and on the other hand the stability of the inner tubes is jeopardized by vibrations, the risk of vibrations can only be partially contained by installing inner tubes with a wall thickness of 4.5 mm and an outer diameter of 23 mm. In addition, it cannot be avoided that leaks occur on the stuffing box.
  • the hood connections are connected to the pipe-side inlet and outlet connections for the coal slurry and / or the cycle gas via weld seams.
  • a hood is arranged as an impact body at a distance of 500 to 1,000 mm from the jacket-side inlet connection.
  • the advantages achieved by the invention are, above all, that larger diameters can be used to save material. Damaged or clogged bundles can be installed and removed faster than with the previously known construction.
  • the arrangement of baffles on the jacket side increases the heat transfer and avoids the risk of vibrations of the inner tubes.
  • the installation of an expansion adapter prevents the pulp and / or circulating gas flowing on the pipe side from mixing with the circulating gas which emits heat and the jacket side.
  • FIG. 1 shows a longitudinal section through a heat exchanger according to the invention
  • FIG. 2 shows an enlarged partial view of this heat exchanger.
  • a tube bundle is arranged in a pressure vessel, consisting of a cylindrical jacket 1 with a flanged jacket hood 2, and a welded-on jacket 3, a tube bundle is arranged.
  • This tube bundle in turn consists of inner tubes 4, which are welded into tube plates 5 and 6.
  • the hoods 7 and 8 seal the coal pulp flowing on the pipe side and / or the circulating gas.
  • a hood connector 9 connects the hood 7 to the pipe-side outlet connector 11.
  • a hood connector 10 connects the hood 8 to the pipe-side inlet connector 12.
  • the welded connection between the hood connector 9, 10 and the outlet and inlet connector is shown in FIG.
  • the tube bundle contains baffle plates on the jacket side, which consist either of alternately arranged ring plates 13 and discs 14.
  • baffle plates which is not shown, but is used for horizontal heat exchangers, consists of circular sections.
  • the baffle plates are fastened with tie rods 15 to one of the two plates 5, 6.
  • the jacket 1 and the tube bundle have different wall temperatures during operation, and they also consist of materials with different coefficients of thermal expansion; therefore an expansion compensation intermediate piece 16 is installed in the hood connector 9 or 10.
  • the jacket-side inlet connector 17 is arranged so that the flow pulse is deflected with the hood 7.
  • Jacket-side inlet and outlet nozzles 18 can be rotated according to the requirements of the pipe routing as desired on a width circle of the spherical jacket hood.

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  • Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Wood Science & Technology (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Organic Chemistry (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Paper (AREA)

Abstract

Heat exchanger for use in coal-hydrogenation plants at pressures of 200 to 700 bar and temperatures of 100 to 500 DEG C, comprising a tube bundle, which is arranged in a closed pressure vessel, on the tube side has inlet and outlet sockets for the coal slurry and/or recycle gas, and on the jacket side has inlet and outlet sockets for the heat- dissipating recycle gas, in which the inner tubes are arranged between covers sealed by tube plates, and the covers are connected via cover sockets to the tube-side inlet and outlet sockets for the coal slurry and/or the recycle gas, having the following features: a) The pressure vessel (1) is made from low-alloy steel (2.25% Cr, 1% Mo) with wall thicknesses between 150 and 250 mm, preferably between 180 and 220 mm, with outside diameters between 1000 and 2500 mm. b) The tube bundle, consisting of the inner tubes (4) and baffle plates (13, 14), is made from an austenitic CrNi steel, the inner tubes (4) having inside diameters of 40 to 60 mm with wall thicknesses of 2 to 3 mm. c) The baffle plates consist alternately of annular plates (13) and discs or circular segments (14) with sheet thicknesses of 12 to 16 mm, and are attached to one of the tube plates (5, 6) via tiebolts (15). d) The covers (7, 8) are constructed as hemispheres. e) One of the cover sockets (9) has an expansion-compensating adaptor (15). f) The shell-side inlet and outlet sockets (17, 18) for the heat-dissipating recycle gas are arranged on the shell covers (2, 3). <IMAGE>

Description

Die vorliegende Erfindung betrifft einen Wärmeaustauscher für den Einsatz in Kohlehydrieranlagen bei Drücken von 200 bis 700 bar und Temperaturen von 100 bis 500oC mit einem in einem geschlossenen Druckbehälter angeordneten Rohrbündel mit rohrseitigen Ein- und Austrittstutzen für den Kohlebrei und/oder Kreisgas, mit mantelseitigen Ein- und Austrittstutzen für das wärmeabgebende Kreisgas, bei dem die Innenrohre zwischen durch Rohrplatten abgeschlossenen Hauben angeordnet sind, und die Hauben durch Haubenstutzen mit den rohrseitigen Ein- und Austrittstutzen für den Kohlebrei und/oder das Kreisgas verbunden sind.The present invention relates to a heat exchanger for use in coal hydrogenation plants at pressures from 200 to 700 bar and temperatures from 100 to 500 o C with a tube bundle arranged in a closed pressure vessel with tube-side inlet and outlet nozzles for the coal slurry and / or cycle gas, with shell-side Inlet and outlet nozzle for the heat-emitting circulating gas, in which the inner tubes are arranged between hoods closed by tube plates, and the hoods are connected by hood nozzles to the tube-side inlet and outlet nozzles for the pulp and / or the circulating gas.

Es ist bekannt, Wärmeaustauscher von 600 mm Durchmesser und Rohrbündellängen von 18 m zu bauen. Die Innenrohre haben einen Außendurchmesser von 23 mm und einen Innendurchmesser von 14 mm. Unter diesen Voraussetzungen ist es möglich, zwischen 200 bis 300 parallel zu einem Rohrbündel angeordnete Innenrohre in einem Druckbehälter unterzubringen. Die Hauben bei den bekannten Ausführungen sind kegelförmig, die Wärmedehnungsdifferenz zwischen Rohrbündel und Druckbehälter wird über eine Stopfbüchse aufgenommen. Die bekannte Bauweise hat verschiedene Nachteile. So beanspruchen die kegelförmigen Hauben bei größeren Durchmessern noch mehr toten Raum als bei früher üblichen Durchmessern. Der Kohlebrei und das Kreisgas, die bei den bekannten Konstruktionen um die Rohre geführt werden, lassen sich bei Durchmessern . größer als 600 mm nicht mehr gleichmäßig über den ganzen Querschnitt des Mantelraumes verteilen.It is known to build heat exchangers with a diameter of 600 mm and tube bundle lengths of 18 m. The inner tubes have an outer diameter of 23 mm and an inner diameter of 14 mm. Under these conditions, it is possible to accommodate between 200 to 300 inner tubes arranged parallel to a tube bundle in a pressure vessel. The hoods in the known designs are conical, the difference in thermal expansion between the tube bundle and the pressure vessel is absorbed by a stuffing box. The known design has several disadvantages. For example, the conical hoods take up even more dead space with larger diameters than with diameters that were customary in the past. The coal slurry and the cycle gas, which are guided around the pipes in the known constructions, can be of diameters. Do not distribute larger than 600 mm evenly over the entire cross-section of the jacket space.

Bei der Fahrweise mit Kohlebrei und Kreisgas um die Rohre ist, wie sich gezeigt hat, der Einbau von Schikanen nicht möglich: dies ist in zweifacher Hinsicht nachteilig. Einmal wird die Wärmeübergangszahl kleiner als bei einer durch Schikane erzielten Querströmung, und zum anderen ist die Stabilität der Innenrohre durch Schwingungen gefährdet, die Schwingungsgefahr kann nur zum Teil durch den Einbau von Innenrohren mit 4,5 mm Wanddicke bei einem Außendurchmesser von 23 mm eingedämmt werden. Außerdem ist nicht zu vermeiden, daß an der Stopfbüchse Undichtigkeiten auftreten.As has been shown, it is not possible to install baffles when driving with pulp and circulating gas around the pipes: this is disadvantageous in two respects. First, the heat transfer coefficient becomes smaller than that of one cross flow achieved by chicane, and on the other hand the stability of the inner tubes is jeopardized by vibrations, the risk of vibrations can only be partially contained by installing inner tubes with a wall thickness of 4.5 mm and an outer diameter of 23 mm. In addition, it cannot be avoided that leaks occur on the stuffing box.

Es war daher die Aufgabe der vorliegenden Erfindung, einen Wärmeaustauscher für den Einsatz in Kohlehydrieranlagen anzugeben, der zum einen materialsparend für Kohlebrei- und Kreisgasdurchsätze bis über 5·105 kg h-1, zum anderen reparaturfreundlich ausgelegt ist.It was therefore the object of the present invention to provide a heat exchanger for use in coal hydrogenation plants which, on the one hand, is designed to save material for coal pulp and cycle gas throughputs of up to 5 · 10 5 kg h -1 and , on the other hand, is easy to repair.

Diese Aufgabe wird erfindungsgemäß gelöst durch die Kombination folgender Merkmale:

  • a) Der Druckbehälter ist aus niedriglegiertem Stahl (2,25 % Cr, 1 % Mo) mit Wanddicken zwischen 150 und 250 mm, gefertigt; bei Außendurchmessern zwischen -1 000 und 2 500 mm.
  • b) Das Rohrbündel, bestehend aus den Innenrohren und Schikaneblechen ist aus einem austenitischen CrNi-Stahl gefertigt, wobei die Innenrohre (4) Innendurchmesser von 40 bis 60 mm, bei Wanddicken von 2 bis 3 mm aufweisen.
  • c) Die Schikanebleche bestehen abwechselnd aus Ringblechen und Scheiben mit Blechdicken von 12 bis 16 mm und sind an einer Rohrplatte über Zuganker befestigt.
  • d) Die Hauben mit Wanddicken von 20 bis 40 mm sind als Halbkugeln ausgebildet.
  • e) Einer der Haubenstutzen weist ein Dehnungsausgleich-Zwischenstück auf.
  • f) Die mantelseitigen Ein- und Austrittstutzen für das wärmegebende Kreisgas sind an den Mantelhauben angeordnet.
This object is achieved according to the invention by combining the following features:
  • a) The pressure vessel is made of low-alloy steel (2.25% Cr, 1% Mo) with wall thicknesses between 150 and 250 mm; for outside diameters between -1,000 and 2,500 mm.
  • b) The tube bundle, consisting of the inner tubes and baffle plates is made of an austenitic CrNi steel, the inner tubes (4) having an inner diameter of 40 to 60 mm, with wall thicknesses of 2 to 3 mm.
  • c) The baffle plates alternately consist of ring plates and discs with plate thicknesses of 12 to 16 mm and are attached to a tube plate via tie rods.
  • d) The hoods with wall thicknesses of 20 to 40 mm are designed as hemispheres.
  • e) One of the hood socket has a Dehnungsausgleic h -Zwischenstück.
  • f) The jacket-side inlet and outlet nozzles for the heat-generating circulating gas are arranged on the jacket hoods.

Gemäß einer bevorzugten Ausführungsform der Erfindung sind die Haubenstutzen mit den rohrseitigen Ein- und Austrittstutzen für den Kohlebrei und/oder das Kreisgas über Schweißnähte verbunden.According to a preferred embodiment of the invention, the hood connections are connected to the pipe-side inlet and outlet connections for the coal slurry and / or the cycle gas via weld seams.

Gemäß einer weiteren Ausführungsform der Erfindung ist eine Haube als Prallkörper im Abstand von 500 bis 1 000 mm vom mantelseitigen Eintrittstutzen angeordnet. Die mit der Erfindung erzielten Vorteile bestehen vor allen Dingen darin, daß mit größeren Durchmessern zugleich materialsparend gebaut werden kann. Ein- und Ausbau beschädigter oder verstopfter Bündel ist schneller möglich als bei der bisher bekannten Konstruktion. Die Anordnung mantelseitiger Schikanen erhöht den Wärmeübergang und vermeidet die Gefahr von Schwingungen der Innenrohre. Durch den Einbau eines Dehnungszwischenstückes wird ausgeschlossen, daß rohrseitig strömender Kohlebrei und/oder Kreisgas sich mit dem wärmeabgebenden, mantelseitig strömenden Kreisgas vermischen. Durch die Ausführung der Hauben als Halbkugeln wird gegenüber der spitzwinkligen, kegelförmigen Haube Druckbehälterraum gespart.According to a further embodiment of the invention, a hood is arranged as an impact body at a distance of 500 to 1,000 mm from the jacket-side inlet connection. The advantages achieved by the invention are, above all, that larger diameters can be used to save material. Damaged or clogged bundles can be installed and removed faster than with the previously known construction. The arrangement of baffles on the jacket side increases the heat transfer and avoids the risk of vibrations of the inner tubes. The installation of an expansion adapter prevents the pulp and / or circulating gas flowing on the pipe side from mixing with the circulating gas which emits heat and the jacket side. By designing the hoods as hemispheres, pressure vessel space is saved compared to the acute-angled, conical hood.

Die Erfindung wird nachstehend anhand der Zeichnungen näher erläutert. Es zeigen Figur 1 einen Längsschnitt durch einen Wärmeaustauscher gemäß der Erfindung, Figur 2 eine vergrößerte Teilansicht dieses Wärmeaustauschers.The invention is explained below with reference to the drawings. FIG. 1 shows a longitudinal section through a heat exchanger according to the invention, FIG. 2 shows an enlarged partial view of this heat exchanger.

In einem Druckbehälter, bestehend aus einem zylindrischen Mantel 1 mit einer angeflanschten Mantelhaube 2, sowie einer angeschweißten Mantelhaube 3 ist ein Rohrbündel angeordnet. Dieses Rohrbündel besteht seinerseits aus Innenrohren 4, die in Rohrplatten 5 und 6 eingeschweißt sind. Die Hauben 7 und 8 dichten den rohrseitig strömenden Kohlebrei und/oder das Kreisgas ab. Ein Haubenstutzen 9 verbindet die Haube 7 mit dem rohrseitigen Austrittstutzen 11. Ein Haubenstutzen 10 verbindet die Haube 8 mit dem rohrseitigen Eintrittstutzen 12. Die Schweißverbindung zwischen den Haubenstutzen 9, 10 und Aus- und Eintrittstutzen ist in Figur 2 dargestellt. Das Rohrbündel enthält mantelseitig Schikanebleche, die entweder aus abwechselnd angeordneten Ringblechen 13 und Scheiben 14 bestehen.In a pressure vessel, consisting of a cylindrical jacket 1 with a flanged jacket hood 2, and a welded-on jacket 3, a tube bundle is arranged. This tube bundle in turn consists of inner tubes 4, which are welded into tube plates 5 and 6. The hoods 7 and 8 seal the coal pulp flowing on the pipe side and / or the circulating gas. A hood connector 9 connects the hood 7 to the pipe-side outlet connector 11. A hood connector 10 connects the hood 8 to the pipe-side inlet connector 12. The welded connection between the hood connector 9, 10 and the outlet and inlet connector is shown in FIG. The tube bundle contains baffle plates on the jacket side, which consist either of alternately arranged ring plates 13 and discs 14.

Eine andere Ausführungsform der Schikanebleche, die nicht dargestellt ist, jedoch bei liegenden Wärmeaustauschern angewendet wird, besteht aus Kreisabschnitten.Another embodiment of the baffle plates, which is not shown, but is used for horizontal heat exchangers, consists of circular sections.

Die Schikanebleche sind mit Zugankern 15 an einer der beiden Platten 5, 6 befestigt. Der Mantel 1 und das Rohrbündel haben im Betrieb unterschiedliche Wandtemperaturen, außerdem bestehen sie aus Werkstoffen mit unterschiedlichen Wärmeausdehnungskoeffizienten; deswegen ist ein Dehnungsausgleich-Zwischenstück 16 im Haubenstutzen 9 oder 10 eingebaut. Der mantelseitige Eintrittstutzen 17 wird so angeordnet, daß der Strömungsimpuls mit der Haube 7 abgelenkt wird. Mantelseitige Ein- und Austrittstutzen 18 können entsprechend den Erfordernissen der Rohrleitungsführung beliebig auf einem Breitenkreis der kugelförmigen Mantelhaube gedreht werden.The baffle plates are fastened with tie rods 15 to one of the two plates 5, 6. The jacket 1 and the tube bundle have different wall temperatures during operation, and they also consist of materials with different coefficients of thermal expansion; therefore an expansion compensation intermediate piece 16 is installed in the hood connector 9 or 10. The jacket-side inlet connector 17 is arranged so that the flow pulse is deflected with the hood 7. Jacket-side inlet and outlet nozzles 18 can be rotated according to the requirements of the pipe routing as desired on a width circle of the spherical jacket hood.

Claims (3)

1. Wärmeaustauscher für den Einsatz in Kohlehydrieranlagen bei Drücken von 200 bis 700 bar und Temperaturen von 100 bis 500°C mit einem in einem geschlossenen Druckbehälter angeordneten Rohrbündel, mit rohrseitigem Ein-und Austrittstutzen für den Kohlebrei und/oder Kreisgas, mit mantelseitigen Ein- und Austrittstutzen für das wärmeabgebende Kreisgas, bei dem die Innenrohre zwischen durch Rohrplatten abgeschlossenen Hauben angeordnet sind, und die Hauben durch Haubenstutzen mit den rohrseitigen Ein- und Austrittstutzen für den Kohlebrei und/oder das Kreisgas verbunden sind, gekennzeichnet durch die Kombination folgender Merkmale: a) Der Druckbehälter (1) ist aus niedriglegiertem Stahl (2,25 % Cr, 1 % Mo) mit Wanddicken zwischen 150 und 250 mm, vorzugsweise zwischen 180 und 220 mm, gefertigt; bei Außendurchmessern zwischen 1 000 und 2 500 mm. b) Das Rohrbündel, bestehend aus den Innenrohren(4) und Schikaneblechen (13, 14) ist aus einem austenitischen CrNi-Stahl gefertigt, wobei die Innenrohre (4) Innendurchmesser von 40 bis 60 mm bei Wanddicken von 2 bis 3 mm aufweisen. c) Die Schikanebleche bestehen abwechselnd aus Ringblechen (13) und Scheiben oder Kreisabschnitten (14) mit Blechdicken von 12 bis 16 mm und sind an einer der Rohrplatten (5, 6) über Zuganker (15) befestigt. d) Die Hauben (7, 8) sind als Halbkugeln ausgebildet. e) Einer der Haubenstutzen (9) weist ein Dehnungsausgleich-Zwischenstück (16) auf. f) Die mantelseitigen Ein- und Austrittstutzen (17, 18) für das wärmeabgebende Kreisgas sind an den Mantelhauben (2, 3) angeordnet. 1. Heat exchanger for use in coal hydrogenation plants at pressures from 200 to 700 bar and temperatures from 100 to 500 ° C with a tube bundle arranged in a closed pressure vessel, with inlet and outlet connections on the tube side for the coal pulp and / or cycle gas, with jacket-side inlet and outlet connections for the heat-emitting cycle gas, in which the inner tubes are arranged between hoods closed by tube plates, and the hoods are connected by hood nozzles to the tube-side inlet and outlet nozzles for the coal pulp and / or the cycle gas, characterized by the combination of the following features: a) The pressure vessel (1) is made of low-alloy steel (2.25% Cr, 1% Mo) with wall thicknesses between 150 and 250 mm, preferably between 180 and 220 mm; for outside diameters between 1 000 and 2 500 mm. b) The tube bundle, consisting of the inner tubes (4) and baffle plates (13, 14) is made of an austenitic CrNi steel, the inner tubes (4) having an inner diameter of 40 to 60 mm with wall thicknesses of 2 to 3 mm. c) The baffle plates alternately consist of ring plates (13) and disks or circular sections (14) with plate thicknesses of 12 to 16 mm and are attached to one of the tube plates (5, 6) via tie rods (15). d) The hoods (7, 8) are designed as hemispheres. e) One of the hood sockets (9) has an expansion compensation intermediate piece (16). f) The jacket-side inlet and outlet nozzles (17, 18) for the heat-emitting circulating gas are arranged on the jacket hoods (2, 3). 2. Wärmeaustauscher nach Anspruch l, dadurch gekennzeichnet, daß die Haubenstutzen (9, 10) mit den rohrseitigen Ein-und Austrittstutzen (11, 12) für den Kohlebrei und/oder das Kreisgas über Schweißnähte verbunden sind.2. Heat exchanger according to claim l, characterized in that the hood connector (9, 10) with the pipe-side inlet and outlet connector (11, 12) for the coal pulp and / or the cycle gas are connected via welds. 3. Wärmeaustauscher nach Anspruch 1 und 2, dadurch gekennzeichnet, daß eine der Hauben (7) als Prallkörper im Abstand von 500 bis 1 000 mm vom mantelseitigen Eintrittstutzen (17) angeordnet ist.3. Heat exchanger according to claim 1 and 2, characterized in that one of the hoods (7) is arranged as a baffle body at a distance of 500 to 1,000 mm from the jacket-side inlet connector (17).
EP81108203A 1980-11-28 1981-10-12 Heat exchanger Withdrawn EP0053248A3 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3044902 1980-11-28
DE19803044902 DE3044902A1 (en) 1980-11-28 1980-11-28 HEAT EXCHANGER

Publications (2)

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EP0053248A2 true EP0053248A2 (en) 1982-06-09
EP0053248A3 EP0053248A3 (en) 1982-11-24

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EP (1) EP0053248A3 (en)
JP (1) JPS57117787A (en)
AU (1) AU7794981A (en)
DE (1) DE3044902A1 (en)
ZA (1) ZA818241B (en)

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FR2939058A1 (en) * 2008-12-03 2010-06-04 Air Liquide Welding metal tube on metal structure comprising opening, comprises positioning tube around opening located in wall of structure so that inner side of tube is in fluid communication with opening, and welding tube to wall of structure
US10684077B2 (en) 2015-04-24 2020-06-16 Hexsol Italy Srl Tube-nest heat exchanger with improved structure
CN112013037A (en) * 2020-08-31 2020-12-01 东风商用车有限公司 Heat radiation structure of clutch housing
CN112105515A (en) * 2018-03-23 2020-12-18 摩丁制造公司 High pressure tolerant liquid-to-refrigerant heat exchanger

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DE10312788A1 (en) 2003-03-21 2004-09-30 Behr Gmbh & Co. Kg Exhaust gas heat exchanger and sealing device for exhaust gas heat exchanger
CN117646838B (en) * 2024-01-29 2024-04-05 无锡佳龙换热器股份有限公司 Inner and outer tube flexible joint for double-pipe heat exchanger

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FR2345665A1 (en) * 1976-03-22 1977-10-21 Kraftwerk Union Ag STEAM GENERATOR FOR PRESSURIZED WATER NUCLEAR REACTORS

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BE449817A (en) *
DE962171C (en) * 1953-12-12 1957-04-18 Basf Ag Heat exchanger
FR87777E (en) * 1964-04-16 1966-02-11 Schmidt Sche Heissdampf temperature exchanger, in particular for cooling gas coming out of cracking or other
DE1263969B (en) * 1965-03-19 1968-03-21 Hoesch Ag Impact distributor for a shot spray system
DE2341808A1 (en) * 1973-05-29 1975-01-02 Fbm Cost Mecc Spa Heat exchanger construction with butt welded end plates - uses expansion joint on outer casing and temporary tube elongation
DE2330015A1 (en) * 1973-06-13 1975-01-09 Uhde Gmbh Friedrich Synthesis gas cooler has composite tubes - alkali resistant internally and of boiler steel externally
FR2345665A1 (en) * 1976-03-22 1977-10-21 Kraftwerk Union Ag STEAM GENERATOR FOR PRESSURIZED WATER NUCLEAR REACTORS

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KR100773680B1 (en) * 2000-05-16 2007-11-05 킴벌리-클라크 월드와이드, 인크. Presentation and bonding of garment side panels
EP1712867A1 (en) * 2005-04-08 2006-10-18 Balcke-Dürr GmbH Process to join a tube with a tube plate
FR2939058A1 (en) * 2008-12-03 2010-06-04 Air Liquide Welding metal tube on metal structure comprising opening, comprises positioning tube around opening located in wall of structure so that inner side of tube is in fluid communication with opening, and welding tube to wall of structure
US10684077B2 (en) 2015-04-24 2020-06-16 Hexsol Italy Srl Tube-nest heat exchanger with improved structure
CN112105515A (en) * 2018-03-23 2020-12-18 摩丁制造公司 High pressure tolerant liquid-to-refrigerant heat exchanger
CN112105515B (en) * 2018-03-23 2023-10-24 摩丁制造公司 High pressure tolerant liquid-to-refrigerant heat exchanger
CN112013037A (en) * 2020-08-31 2020-12-01 东风商用车有限公司 Heat radiation structure of clutch housing

Also Published As

Publication number Publication date
EP0053248A3 (en) 1982-11-24
AU7794981A (en) 1982-06-03
DE3044902A1 (en) 1982-07-08
ZA818241B (en) 1983-07-27
JPS57117787A (en) 1982-07-22

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