EP1979699A1 - Tube bundle heat exchanger - Google Patents

Tube bundle heat exchanger

Info

Publication number
EP1979699A1
EP1979699A1 EP07702370A EP07702370A EP1979699A1 EP 1979699 A1 EP1979699 A1 EP 1979699A1 EP 07702370 A EP07702370 A EP 07702370A EP 07702370 A EP07702370 A EP 07702370A EP 1979699 A1 EP1979699 A1 EP 1979699A1
Authority
EP
European Patent Office
Prior art keywords
tube
transition piece
tube plate
heat exchanger
oval
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
EP07702370A
Other languages
German (de)
French (fr)
Other versions
EP1979699B1 (en
Inventor
Jiri Jekerle
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
General Electric Technology GmbH
Original Assignee
Alstom Technology AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Alstom Technology AG filed Critical Alstom Technology AG
Publication of EP1979699A1 publication Critical patent/EP1979699A1/en
Application granted granted Critical
Publication of EP1979699B1 publication Critical patent/EP1979699B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/003—Multiple wall conduits, e.g. for leak detection
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/006—Tubular elements; Assemblies of tubular elements with variable shape, e.g. with modified tube ends, with different geometrical features
    • 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
    • F28F9/04—Arrangements for sealing elements into header boxes or end plates
    • F28F9/16—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling
    • F28F9/18—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding
    • F28F9/182—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding the heat-exchange conduits having ends with a particular shape, e.g. deformed; the heat-exchange conduits or end plates having supplementary joining means, e.g. abutments
    • 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
    • F28F9/04—Arrangements for sealing elements into header boxes or end plates
    • F28F9/16—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling
    • F28F9/18—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding
    • F28F9/185—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding with additional preformed parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/06—Fastening; Joining by welding
    • F28F2275/067—Fastening; Joining by welding by laser welding

Definitions

  • the invention relates to a tube bundle heat exchanger with tubes which are held on both sides in tube plates or oval tube collector tube plates and connected thereto by means of weld, for cooling a guided through the tubes hot gas flow through a surrounding the tubes coolant, comprising at least one gas inlet chamber from which the hot gas stream is introduced into the individual tubes and which is bounded on one side by the input tube plate or oval tube collector tube plate and at least one gas outlet chamber in which the gas flow passed through the tubes is collected and removed and on one side is limited by the output side tube plate or oval tube collector tube plate.
  • heat exchangers for the cooling of gases in numerous process engineering plants, such as.
  • gasification plants, thermal and catalytic cracking systems, steam reforming plants, etc. are usually heat exchangers, in particular shell and tube heat exchanger (cooler) used, in which the gases to be cooled flow through straight tubes and thereby the latent heat of the hot gas over the pipe wall to the surrounding medium surrounding the pipes, in particular cooling medium.
  • heat exchangers characteristic of such heat exchangers is that the gases to be cooled are often under a high pressure and a high temperature and enter the straight tubes of the heat exchanger at a high speed.
  • a high heat flux density is achieved at the tube inlet or the first tube section, which cause both a high temperature and a high thermal stress in the tubes of the heat exchanger or in the connection tube plate - tube.
  • the gas-carrying pipes are welded into the tube plates, wherein the weld between the tube plate and tube is mounted either on the outer or inner wall of the tube plate or within the tube plate opening.
  • the document DE 37 15 713 C2 has, for example a welded joint of the pipe or pipes with the outer wall of the tube plate or the oval tube header tube plate.
  • the disadvantage of this known embodiment is that the gas facing contour or surface of the transition from tube to tube plate or oval tube collector tube plate has no exact aerodynamic shape.
  • the use of an inserted sleeve is usually for several different reasons, i.a. a narrowing of the gas-side cross-section and insufficient cooling of the sleeve, undesirable.
  • the object of the present invention is to provide a tube bundle heat exchanger in which the aforementioned disadvantages are avoided or the transition from the tube plate or the oval tube header tube plate to the tubes on the gas side has a streamlined contour and on the cooling medium side and the gas side no disturbing elements are present.
  • connection of the tubes with the input tube plate or oval tube collector tube plate is formed in each case by means of a conical and / or trumpet-shaped transition piece whose cross-section decreases seen in the gas flow direction, that seen in the gas flow direction input end of the transition piece jerky is connected to the tube plate or oval tube header tube plate and the inner and outer contours of the transition piece and the Sch mentionharms Schemees to the tube plate or oval tube collector tube plate gap and edge free and straight and / or formed with an add on the outer contour radius of equal to or greater than 5 mm ,
  • the transition from tube plate or oval tube collector tube plate to the pipes is aerodynamically designed so that the entry of the gas into the tubes is highly turbulence-free and temperature peaks in the entrance area can be reduced.
  • the length Lu of the transition piece is at least 1.5 times the inner diameter di of the heat exchanger tube and / or the inner diameter Di of the transition piece at the inlet thereof at least 1.2 times the inner diameter di of the heat exchanger tube by one to achieve optimized aerodynamic transition of the tube plate or the oval tube collector tube plate to the respective heat exchanger tubes.
  • the transition piece is formed from a separate pipe part and seen in the gas flow direction output end of the transition piece is jerkily connected to the pipe by a weld.
  • a separate pipe part complicated transition pieces (for example, several different transition radii) can be made much easier and cheaper in their shape become.
  • the pipe part used as a transition piece is designed as a forging.
  • FIG. 2 shows a detail section of the transition from tube plate to tube according to detail "A" from FIG. 1,
  • FIG. 5 is a detail section of the transition of an oval tube collector tube plate to a tube.
  • FIG. 1 shows a tube bundle heat exchanger 1 shown schematically in longitudinal section.
  • Such tube bundle heat exchanger 1 are used in numerous process engineering systems, such. As gasification plants, thermal and catalytic crackers, steam reforming plants, etc., required, in which a process gas, an exhaust gas or the like. Is produced.
  • the tube bundle heat exchanger 1 is generally used for cooling the aforementioned hot gas 18, which is introduced through a line not shown in the gas inlet chamber 8 of the heat exchanger 1 and passed from here through a plurality of straight tubes 2, then in the gas outlet chamber 9 of the Heat exchanger 1 is collected and discharged by means not shown line from the heat exchanger 1.
  • the tubes 2, through which an indirect heat exchange takes place with a surrounding the tubes 2 cooling medium 19, are each spaced from each other between two tube plates 3, 4 or oval tube-collector tube plates 5, 6 and with these fixed and gas-tight - usually welded - connected.
  • the inlet side end 16 of the transition piece 10 seen in the gas flow direction is jerkily connected to the tube plate 3 or oval tube header tube plate 5 and the inner and outer contours 1 1, 12 of the transition piece 10 and the Sch relieharms Schemees 13 to the tube plate 3 or oval tube collector tube plate 5 gap. and edge-free as well as straight and / or with an attaching to the outer contour 12 radius, which is at least 5 mm formed.
  • the inventive design of the transition of tube plate 3 and of oval tube header tube plate 5 on the tube 2 an aerodynamic contour 1 1, 12 creates both on the gas-contacting as well as on the coolant-contacting side of the tubes 2, the transition piece 10 and the tube plate 3 or oval tube collector tube plate 5, which at any point has a column, an edge or an angular transition. All transitions including the weld connection region 13 on the inner and outer contour 1 1, 12 are therefore according to the invention either straight or flat and / or formed with a radius.
  • the transition piece 10 is, for example, mechanically expanded end 16 of the tube 2.
  • the weld joint region 13 between tube 2 and tube plate 3, 5th forms.
  • Figure 3 and 4 has a transition piece 10, which consists of a separate tube member 15 and is usually easier to manufacture, since the tube member 15 is compared to the entire tube 2 is much shorter and thus easier to handle.
  • a further weld seam 22 is required, which forms the weld joint region 14 between the pipe 2 and the pipe part 15.
  • This weld joint region 14 is advantageously formed either on the inner as well as on the outer contour 1 1, 12 either straight or flat and / or with a radius, i. the area 14 is edge and gap free.
  • the transition pieces 10 according to the figures 2 to 5 have at its input end 16, based on the outer contour 12 of the transition pieces 10, for example, a radius R 1 of 5 mm.
  • a further radius R 2 of, for example, 60 mm follows this, whereas in the transition piece 10 according to FIG. 4 the first radius is followed by a conical constriction with a subsequent radius of, for example, 20 mm.
  • the inner contour 1 1 of the transition pieces 10 according to Figures 2 and 5 then has corresponding radii, which are greater by the wall thickness s of the transition piece 10.
  • the transition between the two wall thicknesses s and t is within the weld connection area 13 According to the invention either straight or flat and / or formed with a radius.
  • a different wall thickness t of the tube plate 3, 5 with respect to the wall thickness s of the tube 2 can be compensated according to Figures 3 and 4 with a designed as a tubular member 15 transition piece 10 by the respective wall thicknesses at the tube ends of the tubular member 15 to the wall thicknesses t and s the tube plate 3, 5 and the tube 2 are adjusted. That is, seen in the gas flow direction, within the pipe section 15, the wall thickness t is continuously reduced or increased to the wall thickness s.
  • the tube part 15 may advantageously be formed as a forged piece.
  • the length L 1 of the transition piece 10 is advantageously 1.5 times the inner diameter di of the tube 2 and the inner diameter Di of the transition piece 10 directly at the entry into the transition piece 10 is advantageously 1.2 times the inner diameter di of the tube 2.
  • FIG. 4 instead of a trumpet-shaped transition piece 10 has a cone-shaped transition piece 10, which in turn is formed from a separate tube part 15. Again, the pipe member 15 is connected by two welds 7, 22 with the tube plate 3 and the tube 2.
  • FIG. 5 shows a shell-and-tube heat exchanger 1 with double tubes 2, 21, in which the cooling medium 19 circulates in the annular cross-section between inner tube 2 and outer tube 21.
  • the cooling medium 19 leading outer tubes 21 of the otherwise, and as shown in Figure 1 required heat exchanger outer jacket 23 is unnecessary.
  • the cooling medium 1 9 is supplied to and removed from the space inside the outer jacket 23 and the tube plates 3, 5 and A 1 6, the cooling medium 19 according to FIG. 5 is fed by means of oval tube collectors 20. or dissipated.
  • the compound of the transition piece 10 according to the invention takes place in this case with the oval tube collector tube plate. 5

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Lubricants (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)

Abstract

A tube bundle heat exchanger has tubes which are held at each side in tube plates or oval-tube collecting-tube plates and are connected to these in each case by means of a weld seam. The connection of the tubes to the inlet-side tube plate or oval-tube collecting-tube plate is formed in each case by means of a conical and/or trumpet-shaped transition piece. The cross section of the transition piece reduces as viewed in the gas flow direction in such a way that the inlet-side end, as viewed in the gas flow direction, of the transition piece is connected in a buttjoint to the tube plate or oval-tube collecting-tube plate. The inner and outer contours of the transition piece and of the welded connection region are formed without gaps and comers to the tube plate or oval tube collecting-tube plate and so as to be straight and/or with a radius, measured from the outer contour, of at least 5 mm.

Description

Beschreibungdescription
Rohrbündel-WärmetαuscherTubular Wärmetαuscher
Die Erfindung bezieht sich auf einen Rohrbündel-Wärmetauscher mit Rohren, die beidseitig in Rohrplatten oder Ovalrohr-Sammlerrohrplatten gehalten und mit diesen jeweils mittels Schweißnaht verbunden sind, zum Abkühlen eines durch die Rohre geleiteten heißen Gasstromes durch ein die Rohre umgebendes Kühlmittel, aufweisend wenigstens eine Gaseintrittskammer, von der aus der heiße Gasstrom in die einzelnen Rohre eingeleitet wird und die an einer Seite durch die eingangsseitige Rohrplatte oder Ovalrohr-Sammlerrohrplatte begrenzt ist und wenigstens eine Gasaustrittskammer, in der der durch die Rohre hindurchgeleitete Gasstrom gesammelt und abgeführt wird und die an einer Seite durch die ausgangsseitige Rohrplatte oder Ovalrohr- Sammlerrohrplatte begrenzt ist.The invention relates to a tube bundle heat exchanger with tubes which are held on both sides in tube plates or oval tube collector tube plates and connected thereto by means of weld, for cooling a guided through the tubes hot gas flow through a surrounding the tubes coolant, comprising at least one gas inlet chamber from which the hot gas stream is introduced into the individual tubes and which is bounded on one side by the input tube plate or oval tube collector tube plate and at least one gas outlet chamber in which the gas flow passed through the tubes is collected and removed and on one side is limited by the output side tube plate or oval tube collector tube plate.
Für die Kühlung von Gasen in zahlreichen verfahrenstechnischen Anlagen, wie z. B. Vergasungsanlagen, thermischen und katalytischen Spaltanlagen, Dampfreformierungs- anlagen etc., werden in der Regel Wärmetauscher, insbesondere Rohrbündel- Wärmetauscher (Kühler), eingesetzt, in den die zu kühlenden Gase durch gerade Rohre strömen und dabei die latente Wärme des heißen Gases über die Rohrwand an das die Rohre umgebende Medium, insbesondere Kühlmedium, abgeben. Charakteristisch für derartige Wärmetauscher ist es, dass die zu kühlenden Gase oft unter einem hohen Druck und einer hohen Temperatur stehen und in die geraden Rohre des Wärmetauschers mit einer hohen Geschwindigkeit eintreten. Dadurch wird am Rohreintritt bzw. dem ersten Rohrabschnitt eine hohe Wärmestromdichte erreicht, die sowohl eine hohe Temperatur als auch eine hohe Wärmespannung in den Rohren des Wärmetauschers bzw. in der Verbindung Rohrplatte - Rohr verursachen.For the cooling of gases in numerous process engineering plants, such as. As gasification plants, thermal and catalytic cracking systems, steam reforming plants, etc., are usually heat exchangers, in particular shell and tube heat exchanger (cooler) used, in which the gases to be cooled flow through straight tubes and thereby the latent heat of the hot gas over the pipe wall to the surrounding medium surrounding the pipes, in particular cooling medium. Characteristic of such heat exchangers is that the gases to be cooled are often under a high pressure and a high temperature and enter the straight tubes of the heat exchanger at a high speed. As a result, a high heat flux density is achieved at the tube inlet or the first tube section, which cause both a high temperature and a high thermal stress in the tubes of the heat exchanger or in the connection tube plate - tube.
Bei Wärmetauschern gemäß dem Stand der Technik werden die gasführenden Rohre in die Rohrplatten eingeschweißt, wobei die Schweißnaht zwischen Rohrplatte und Rohr entweder an der Außen- oder Innenwand der Rohrplatte oder innerhalb der Rohrplattenöffnung angebracht ist. Die Druckschrift DE 37 15 713 C2 weist beispielsweise eine Schweißverbindung des Rohres bzw. der Rohre mit der Außenwand der Rohrplatte bzw. der Ovalrohr-Sammlerrohrplatte auf.In heat exchangers according to the prior art, the gas-carrying pipes are welded into the tube plates, wherein the weld between the tube plate and tube is mounted either on the outer or inner wall of the tube plate or within the tube plate opening. The document DE 37 15 713 C2 has, for example a welded joint of the pipe or pipes with the outer wall of the tube plate or the oval tube header tube plate.
Der Nachteil dieser bekannten Ausführung besteht darin, dass die dem Gas zugewandte Kontur bzw. Oberfläche des Überganges von Rohr zu Rohrplatte bzw. Ovalrohr-Sammlerrohrplatte keine exakte aerodynamische Form aufweist. Die Verwendung einer eingesteckten Hülse ist in der Regel aus mehreren unterschiedlichen Gründen, u.a. eine Einengung des gasseitigen Querschnittes sowie eine unzureichende Kühlung der Hülse, unerwünscht. Darüber hinaus kann auf der Kühlmediumseite der Rohrplatten - Rohr Verbindung ein Spalt vorkommen, der zu einer wasserseitigen Korrosion führt, oder die Rohrplatten - Rohr Verbindung kann eine Ecke aufweisen, in der eine unerwünschte Spannungskonzentration auftritt.The disadvantage of this known embodiment is that the gas facing contour or surface of the transition from tube to tube plate or oval tube collector tube plate has no exact aerodynamic shape. The use of an inserted sleeve is usually for several different reasons, i.a. a narrowing of the gas-side cross-section and insufficient cooling of the sleeve, undesirable. In addition, there may be a gap on the cooling medium side of the tube plate tube connection that results in water side corrosion, or the tube plate tube connection may have a corner where undesirable stress concentration occurs.
Die Aufgabe der vorliegenden Erfindung besteht darin, einen Rohrbündel- Wärmetauscher zu schaffen, bei dem die vorgenannten Nachteile vermieden werden bzw. der Übergang von der Rohrplatte bzw. der Ovalrohr-Sammlerrohrplatte zu den Rohren auf der Gasseite eine strömungsgünstige Kontur aufweist sowie auf der Kühlmediumseite und der Gasseite keine störenden Elemente vorhanden sind.The object of the present invention is to provide a tube bundle heat exchanger in which the aforementioned disadvantages are avoided or the transition from the tube plate or the oval tube header tube plate to the tubes on the gas side has a streamlined contour and on the cooling medium side and the gas side no disturbing elements are present.
Die vorstehend genannte Aufgabe wird durch die kennzeichnenden Merkmale des Patentanspruches 1 gelöst. Die Lösung sieht dabei vor, dass die Verbindung der Rohre mit der eingangseitigen Rohrplatte oder Ovalrohr-Sammlerrohrplatte jeweils mittels eines konus- und/oder trompetenförmigen Übergangsstückes gebildet ist, dessen Querschnitt sich in Gasströmungsrichtung gesehen verringert, dass das in Gasströmungsrichtung gesehen eingangseitige Ende des Übergangsstückes stoßartig mit der Rohrplatte oder Ovalrohr-Sammlerrohrplatte verbunden ist und die Innen- und Außenkonturen des Übergangstückes und des Schweißverbindungsbereiches zur Rohrplatte oder Ovalrohr-Sammlerrohrplatte spalt- und kantenfrei sowie gerade und/oder mit einem an der Außenkontur ansetzenden Radius von gleich oder größer 5 mm ausgebildet sind.The above object is solved by the characterizing features of claim 1. The solution provides that the connection of the tubes with the input tube plate or oval tube collector tube plate is formed in each case by means of a conical and / or trumpet-shaped transition piece whose cross-section decreases seen in the gas flow direction, that seen in the gas flow direction input end of the transition piece jerky is connected to the tube plate or oval tube header tube plate and the inner and outer contours of the transition piece and the Schweißverbindungsbereiches to the tube plate or oval tube collector tube plate gap and edge free and straight and / or formed with an add on the outer contour radius of equal to or greater than 5 mm ,
Vorteilhafte Ausgestaltungen der Erfindung sind den Unteransprüchen zu entnehmen. Durch die erfindungsgemäße Lösung wird ein Rohrbündel-Wärmetauscher geschaffen, der die nachfolgenden Vorteile aufweist:Advantageous embodiments of the invention can be found in the dependent claims. The solution according to the invention provides a shell-and-tube heat exchanger which has the following advantages:
Durch die Vermeidung von vorstehenden Kanten sowie Spalten an der Verbindungsstelle zwischen den Rohren und der Rohrplatte bzw. der Ovalrohr- Sammlerrohrplatte werden einerseits Verwirbelungen des Gas- sowie des Kühlmediums vermieden und andererseits Korrosion unterbunden, Der Übergang von Rohrplatte bzw. Ovalrohr-Sammlerrohrplatte zu den Rohren ist aerodynamisch ausgebildet, so dass der Eintritt des Gases in die Rohre in höchstem Maße verwirbelungsfrei verläuft und Temperaturspitzen im Eingangsbereich abgebaut werden können.By avoiding protruding edges and gaps at the junction between the tubes and the tube plate or the Ovalrohr- collector tube plate turbulence of the gas and the cooling medium are avoided on the one hand and on the other hand prevented corrosion, the transition from tube plate or oval tube collector tube plate to the pipes is aerodynamically designed so that the entry of the gas into the tubes is highly turbulence-free and temperature peaks in the entrance area can be reduced.
In vorteilhafter Ausgestaltung beträgt die Länge Lü des Übergangsstückes mindestens das 1 ,5-fache des Innendurchmessers di des Wärmetauscher-Rohres und/oder der Innendurchmesser Di des Übergangsstückes an dessen Eintritt mindestens das 1 ,2- fache des Innendurchmessers di des Wärmetauscher-Rohres um einen optimierten aerodynamischen Übergang der Rohrplatte bzw. der Ovalrohrsammler-Rohrplatte zu den jeweiligen Wärmetauscher-Rohren zu erzielen.In an advantageous embodiment, the length Lu of the transition piece is at least 1.5 times the inner diameter di of the heat exchanger tube and / or the inner diameter Di of the transition piece at the inlet thereof at least 1.2 times the inner diameter di of the heat exchanger tube by one to achieve optimized aerodynamic transition of the tube plate or the oval tube collector tube plate to the respective heat exchanger tubes.
Zweckmäßig ist es, das Übergangsstück am in Gasströmungsrichtung gesehen eingangsseitigen Ende des Rohres mechanisch aufzuweiten. Durch diese Maßnahme wird lediglich an einem Teil - dem Rohr - gefertigt und der Arbeitsprozess zur Herstellung des erfindungsgemäßen Übergangstückes lässt sich vereinfachen und abkürzen.It is expedient to mechanically expand the transition piece on the input side of the pipe, viewed in the gas flow direction. By this measure, only at one part - the tube - manufactured and the work process for the production of the transition piece according to the invention can be simplified and abbreviate.
Bei einer vorteilhaften Ausgestaltung der Erfindung ist das Übergangsstück aus einem gesonderten Rohrteil gebildet und das in Gasströmungsrichtung gesehen ausgangseitige Ende des Übergangsstückes stoßartig mit dem Rohr durch eine Schweißnaht verbunden. Durch die Verwendung eines gesonderten Rohrteiles können auch in ihrer Form komplizierte Übergangstücke (beispielsweise mehrere unterschiedliche Übergangsradien) wesentlich einfacher und kostengünstiger hergestellt werden. Zweckmäßig ist es bei dieser Ausgestaltung der Erfindung, die Innen- und Außenkonturen des Schweißverbindungs-bereiches zwischen Übergangsstück und Rohr spalt- und kantenfrei sowie gerade und/oder mit einem Radius gleich oder größer 5 mm auszubilden. Durch diese Maßnahme wird eine aerodynamische Form am Eintritt des Gases in die Rohre erzielt.In an advantageous embodiment of the invention, the transition piece is formed from a separate pipe part and seen in the gas flow direction output end of the transition piece is jerkily connected to the pipe by a weld. By using a separate pipe part complicated transition pieces (for example, several different transition radii) can be made much easier and cheaper in their shape become. It is expedient in this embodiment of the invention, the inner and outer contours of the weld joint area between transition piece and pipe gap and edge free and straight and / or with a radius equal to or greater than 5 mm form. By this measure, an aerodynamic shape is achieved at the inlet of the gas into the tubes.
In besonders vorteilhafter Weise sind die Innen- und Außen konturen des Übergangstückes und des Schweißverbindungsbereiches zur Rohrplatte oder Ovalrohr- Sammlerrohrplatte und zum Rohr spalt- und kantenfrei sowie gerade und/oder mit einem Radius gleich oder größer 2 mm ausgebildet.In a particularly advantageous manner, the inner and outer contours of the transition piece and the Schweißverbindungsbereiches to the tube plate or Ovalrohr- collector tube plate and the pipe gap and edge free and straight and / or formed with a radius equal to or greater than 2 mm.
In zweckmäßigerweise ist das als Übergangstück eingesetzte Rohrteil als Schmiedestück ausgebildet.Conveniently, the pipe part used as a transition piece is designed as a forging.
Nachstehend sind Ausführungsbeispiele der Erfindung an Hand der Zeichnung und der Beschreibung näher erläutert.Embodiments of the invention with reference to the drawings and the description are explained in more detail below.
Es zeigt:It shows:
Fig. 1 einen Längsschnitt durch einen Rohrbündel-Wärmetauscher,1 shows a longitudinal section through a tube bundle heat exchanger,
Fig. 2 einen Detailschnitt des Überganges von Rohrplatte zu Rohr gemäß Einzelheit „A" aus Figur 1 ,2 shows a detail section of the transition from tube plate to tube according to detail "A" from FIG. 1,
Fig. 3 wie Figur 2, jedoch alternative Ausführung,3 as Figure 2, but alternative embodiment,
Fig. 4 wie Figur 2, jedoch alternative Ausführung,4 as Figure 2, but alternative embodiment,
Fig. 5 einen Detailschnitt des Überganges einer Ovalrohr-Sammlerrohrplatte zu einem Rohr. Figur 1 zeigt einen Rohrbündel-Wärmetαuscher 1 schematisch dargestellt im Längsschnitt. Derartige Rohrbündel-Wärmetauscher 1 werden in zahlreichen verfahrenstechnischen Anlagen, wie z. B. Vergasungsanlagen, thermischen und katalytischen Spaltanlagen, Dampfreformierungsanlagen etc., benötigt, in denen ein Prozessgas, ein Abgas oder dgl. produziert wird. Der Rohrbündel-Wärmetauscher 1 dient in der Regel zum Kühlen des vorgenannten heißen Gases 18, das durch eine nicht dargestellte Leitung in die Gaseintrittskammer 8 des Wärmetauschers 1 eingeführt und von hier durch eine Vielzahl von geraden Rohren 2 hindurchgeleitet wird, anschließend in der Gasaustrittskammer 9 des Wärmetauschers 1 gesammelt und mittels nicht dargestellter Leitung aus dem Wärmetauscher 1 abgeführt wird. Die Rohre 2, durch die ein indirekter Wärmetausch mit einem die Rohre 2 umgebenden Kühlmedium 19 stattfindet, sind dabei jeweils voneinander beabstandet zwischen zwei Rohrplatten 3, 4 bzw. Ovalrohr-Sammlerrohrplatten 5, 6 angeordnet und mit diesen fest und gasdicht - in der Regel verschweißt - verbunden.Fig. 5 is a detail section of the transition of an oval tube collector tube plate to a tube. FIG. 1 shows a tube bundle heat exchanger 1 shown schematically in longitudinal section. Such tube bundle heat exchanger 1 are used in numerous process engineering systems, such. As gasification plants, thermal and catalytic crackers, steam reforming plants, etc., required, in which a process gas, an exhaust gas or the like. Is produced. The tube bundle heat exchanger 1 is generally used for cooling the aforementioned hot gas 18, which is introduced through a line not shown in the gas inlet chamber 8 of the heat exchanger 1 and passed from here through a plurality of straight tubes 2, then in the gas outlet chamber 9 of the Heat exchanger 1 is collected and discharged by means not shown line from the heat exchanger 1. The tubes 2, through which an indirect heat exchange takes place with a surrounding the tubes 2 cooling medium 19, are each spaced from each other between two tube plates 3, 4 or oval tube-collector tube plates 5, 6 and with these fixed and gas-tight - usually welded - connected.
Um am Eintritt des heißen Gases 18 von der Gaseintrittskammer 8 in die jeweiligen Wärmetauscher-Rohre 2 die auftretenden Wärmespannungen an der in Gasströmungsrichtung gesehen eingangseitigen Rohrplatte 3, 5 und dem eingangseitigen Ende 16 der Rohre 2 möglichst gering zu halten, wird erfindungsgemäß die Verbindung der Rohre 2 mit der eingangseitigen Rohrplatte 3 (siehe Figuren 2 bis 4) oder Ovalrohr-Sammlerrohrplatte 5 (siehe Figur 5) jeweils mittels eines konus- und/oder trompetenförmigen Übergangsstückes 10 gebildet, dessen Querschnitt sich in Gasströmungsrichtung (siehe Pfeil) gesehen verringert. Ferner wird das in Gasströmungsrichtung gesehen eingangseitige Ende 16 des Übergangsstückes 10 stoßartig mit der Rohrplatte 3 oder Ovalrohr-Sammlerrohrplatte 5 verbunden und die Innen- und Außenkonturen 1 1 , 12 des Übergangstückes 10 und des Schweißverbindungsbereiches 13 zur Rohrplatte 3 oder Ovalrohr-Sammlerrohrplatte 5 spalt- und kantenfrei sowie gerade und/oder mit einem an der Außenkontur 12 ansetzenden Radius, der wenigstens 5 mm beträgt, ausgebildet.In order to minimize the occurrence of thermal stresses at the entrance of the hot gas 18 from the gas inlet chamber 8 in the respective heat exchanger tubes 2 on the input side tube plate 3, 5 and the input end 16 of the tubes 2, the connection of the tubes according to the invention 2 with the input-side tube plate 3 (see FIGS. 2 to 4) or oval tube collector tube plate 5 (see FIG. 5), each being formed by means of a conical and / or trumpet-shaped transition piece 10 whose cross-section is reduced in the gas flow direction (see arrow). Furthermore, the inlet side end 16 of the transition piece 10 seen in the gas flow direction is jerkily connected to the tube plate 3 or oval tube header tube plate 5 and the inner and outer contours 1 1, 12 of the transition piece 10 and the Schweißverbindungsbereiches 13 to the tube plate 3 or oval tube collector tube plate 5 gap. and edge-free as well as straight and / or with an attaching to the outer contour 12 radius, which is at least 5 mm formed.
Das heißt, dass die erfindungsgemäße Ausbildung des Überganges von Rohrplatte 3 bzw. von Ovalrohr-Sammlerrohrplatte 5 auf das Rohr 2 eine aerodynamische Kontur 1 1 , 12 sowohl an der gasberührten als auch an der kϋhlmediumberührten Seite der Rohre 2, des Übergangstückes 10 und der Rohrplatte 3 bzw. Ovalrohr- Sammlerrohrplatte 5 schafft, die an keiner Stelle eine Spalte, eine Kante oder einen eckigen Übergang aufweist. Sämtliche Übergänge einschließlich des Schweißverbindungsbereiches 13 an der Innen- sowie Außenkontur 1 1 , 12 sind demnach erfindungsgemäß entweder gerade bzw. plan und/oder mit einem Radius ausgebildet.That is, the inventive design of the transition of tube plate 3 and of oval tube header tube plate 5 on the tube 2 an aerodynamic contour 1 1, 12 creates both on the gas-contacting as well as on the coolant-contacting side of the tubes 2, the transition piece 10 and the tube plate 3 or oval tube collector tube plate 5, which at any point has a column, an edge or an angular transition. All transitions including the weld connection region 13 on the inner and outer contour 1 1, 12 are therefore according to the invention either straight or flat and / or formed with a radius.
Gemäß Figur 2 und 5 ist das Übergangsstück 10 das beispielsweise mechanisch aufgeweitete Ende 16 des Rohres 2. Bei dieser Ausbildung ist lediglich eine Schweißnaht 7 zwischen Rohr 2 und Rohrplatte 3 bzw. 5 erforderlich, die den Schweißverbindungsbereich 13 zwischen Rohr 2 und Rohrplatte 3, 5 bildet. Figur 3 und 4 weist ein Übergangsstück 10 auf, das aus einem gesonderten Rohrteil 15 besteht und in der Regel einfacher zu fertigen ist, da das Rohrteil 15 gegenüber dem gesamten Rohr 2 wesentlich kürzer ist und somit auch leichter zu bearbeiten ist. Zur kopfseitigen Verbindung des in Gasströmungsrichtung gesehen ausgangseitigen Ende 1 7 des Rohrteiles 15 ist eine weitere Schweißnaht 22 erforderlich, die den Schweißverbindungsbereich 14 zwischen Rohr 2 und Rohrteil 15 bildet. Dieser Schweißverbindungsbereich 14 ist sowohl an der Innen- wie auch an der Außenkontur 1 1 , 12 vorteilhaft entweder gerade bzw. plan und/oder mit einem Radius ausgebildet, d.h. der Bereich 14 ist kanten- und spaltfrei ausgeführt.According to Figure 2 and 5, the transition piece 10 is, for example, mechanically expanded end 16 of the tube 2. In this embodiment, only one weld 7 between tube 2 and tube plate 3 and 5 is required, the weld joint region 13 between tube 2 and tube plate 3, 5th forms. Figure 3 and 4 has a transition piece 10, which consists of a separate tube member 15 and is usually easier to manufacture, since the tube member 15 is compared to the entire tube 2 is much shorter and thus easier to handle. For the head-side connection of the output side of the pipe part 15, as seen in the gas flow direction, a further weld seam 22 is required, which forms the weld joint region 14 between the pipe 2 and the pipe part 15. This weld joint region 14 is advantageously formed either on the inner as well as on the outer contour 1 1, 12 either straight or flat and / or with a radius, i. the area 14 is edge and gap free.
Die Übergangstücke 10 gemäß der Figuren 2 bis 5 weisen an ihrem eingangseitigen Ende 16, bezogen auf die Außenkontur 12 der Übergangsstücke 10, beispielhaft einen Radius R1 von 5 mm auf. Gemäß der Figuren 2, 3 und 5 schließt sich daran ein weiterer Radius R2 von beispielsweise 60 mm an, wogegen sich beim Übergangstück 10 gemäß der Figur 4 dem ersten Radius eine konusförmige Verengung mit einem anschließenden Radius von beispielsweise 20 mm anschließt. Die Innenkontur 1 1 der Übergangsstücke 10 gemäß der Figuren 2 und 5 weist dann entsprechend Radien auf, die um die Wandstärke s des Übergangstückes 10 größer sind. Entspricht die Wandstärke t der Rohrplatte 3, 5 nicht der Wandstärke s des Rohres 2, dann ist der Übergang zwischen den beiden Wandstärken s und t innerhalb des Schweißverbindungsbereiches 13 erfindungsgemäß entweder gerade bzw. plan und/oder mit einem Radius ausgebildet. Eine abweichende Wandstärke t der Rohrplatte 3, 5 gegenüber der Wandstärke s des Rohres 2 kann gemäß der Figuren 3 und 4 mit einem als Rohrteil 15 ausgebildeten Übergangstück 10 ausgeglichen werden, indem die jeweiligen Wandstärken an den Rohrenden des Rohrteiles 15 an die Wandstärken t und s der Rohrplatte 3, 5 sowie des Rohres 2 angepasst sind. D.h., dass sich, in Gasströmungsrichtung gesehen, innerhalb des Rohrstückes 15 die Wandstärke t kontinuierlich auf die Wandstärke s verringert bzw. vergrößert. Das Rohrteil 15 kann dabei vorteilhaft als Schmiedestück ausgebildet sein.The transition pieces 10 according to the figures 2 to 5 have at its input end 16, based on the outer contour 12 of the transition pieces 10, for example, a radius R 1 of 5 mm. According to FIGS. 2, 3 and 5, a further radius R 2 of, for example, 60 mm follows this, whereas in the transition piece 10 according to FIG. 4 the first radius is followed by a conical constriction with a subsequent radius of, for example, 20 mm. The inner contour 1 1 of the transition pieces 10 according to Figures 2 and 5 then has corresponding radii, which are greater by the wall thickness s of the transition piece 10. If the wall thickness t of the tube plate 3, 5 does not correspond to the wall thickness s of the tube 2, then the transition between the two wall thicknesses s and t is within the weld connection area 13 According to the invention either straight or flat and / or formed with a radius. A different wall thickness t of the tube plate 3, 5 with respect to the wall thickness s of the tube 2 can be compensated according to Figures 3 and 4 with a designed as a tubular member 15 transition piece 10 by the respective wall thicknesses at the tube ends of the tubular member 15 to the wall thicknesses t and s the tube plate 3, 5 and the tube 2 are adjusted. That is, seen in the gas flow direction, within the pipe section 15, the wall thickness t is continuously reduced or increased to the wall thickness s. The tube part 15 may advantageously be formed as a forged piece.
Die Länge Lü des Übergangstückes 10 beträgt vorteilhaft das 1 ,5-fache des Innendurchmessers di des Rohres 2 und der Innendurchmesser Di des Übergangsstückes 10 direkt am Eintritt in das Übergangsstück 10 beträgt vorteilhaft das 1 ,2-fache des Innendurchmessers di des Rohres 2.The length L 1 of the transition piece 10 is advantageously 1.5 times the inner diameter di of the tube 2 and the inner diameter Di of the transition piece 10 directly at the entry into the transition piece 10 is advantageously 1.2 times the inner diameter di of the tube 2.
Figur 4 weist beispielhaft anstelle eines trompetenförmigen Übergangstückes 10 ein konusförmiges Übergangsstück 10 auf, das wiederum aus einem gesonderten Rohrteil 15 gebildet wird. Auch hier wird das Rohrteil 15 durch zwei Schweißnähte 7, 22 mit der Rohrplatte 3 sowie dem Rohr 2 verbunden.By way of example, FIG. 4 instead of a trumpet-shaped transition piece 10 has a cone-shaped transition piece 10, which in turn is formed from a separate tube part 15. Again, the pipe member 15 is connected by two welds 7, 22 with the tube plate 3 and the tube 2.
Figur 5 zeigt einen Rohrbündel-Wärmetauscher 1 mit Doppelrohren 2, 21 auf, bei denen das Kühlmedium 19 im kreisringförmigen Querschnitt zwischen Innenrohr 2 und Außenrohr 21 zirkuliert. Durch die, das Kühlmedium 19 führende, Außenrohre 21 wird der ansonsten, und wie in Figur 1 dargestellt, erforderliche Wärmetauscher- Außenmantel 23 entbehrlich. Während bei dem in Figur 1 dargestellten Wärmetauscher 1 das Kühlmedium 1 9 dem Raum innerhalb des Außenmantels 23 und der Rohrplatten 3, 5 sowie A1 6 zu- und abgeführt wird, wird das Kühlmedium 19 gemäß der Figur 5 mittels Ovalrohr-Sammler 20 zu- bzw. abgeführt. Die Verbindung des erfindungsgemäßen Übergangstückes 10 erfolgt in diesem Fall mit der Ovalrohr- Sammlerrohrplatte 5.FIG. 5 shows a shell-and-tube heat exchanger 1 with double tubes 2, 21, in which the cooling medium 19 circulates in the annular cross-section between inner tube 2 and outer tube 21. By, the cooling medium 19 leading outer tubes 21 of the otherwise, and as shown in Figure 1, required heat exchanger outer jacket 23 is unnecessary. While in the heat exchanger 1 shown in FIG. 1, the cooling medium 1 9 is supplied to and removed from the space inside the outer jacket 23 and the tube plates 3, 5 and A 1 6, the cooling medium 19 according to FIG. 5 is fed by means of oval tube collectors 20. or dissipated. The compound of the transition piece 10 according to the invention takes place in this case with the oval tube collector tube plate. 5
Als Kühlmedium 19 kann Wasser eingesetzt werden, das durch die Wärmezufuhr zum Teil oder ganz verdampft wird. Bezugszeichenliste:As a cooling medium 19, water can be used, which is partially or completely evaporated by the heat supply. LIST OF REFERENCE NUMBERS
1 Rohrbündel-Wärmetαuscher1 tube bundle heat exchanger
2 Rohr2 pipe
3 Rohrplatte, eingangseitig3 tube plate, input side
4 Rohrplatte, ausgangseitig4 tube plate, output side
5 Ovalrohr-Sammlerrohrplatte, eingangseitig ό Ovalrohr-Sammlerrohrplatte, ausgangseitig5 Oval tube collector tube plate, input side ό Oval tube collector tube plate, output side
7 Schweißnaht7 weld
8 Gaseintrittskammer8 gas inlet chamber
9 Gasaustrittskammer9 gas outlet chamber
10 Übergangstück10 transition piece
1 1 Innenkontur1 1 inner contour
12 Außen kontur12 outer contour
13 Schweißverbindungsbereich13 weld joint area
14 Schweißverbindungsbereich14 weld joint area
15 Rohrteil15 pipe part
16 Eingangseitiges Ende des Übergangstückes bzw. des Rohres 1 7 Ausgangseitiges Ende des Übergangstückes bzw. Rohrteiles16 input side end of the transition piece or the pipe 1 7 output side end of the transition piece or pipe part
18 Gas18 gas
1 9 Kühlmedium1 9 cooling medium
20 Ovalrohr-Sammler20 oval tube collectors
21 Außenrohr21 outer tube
22 Schweißnaht22 weld
23 Mantel 23 coat

Claims

Pαtentα nsprüche Pαtentα claims
1 . Rohrbündel-Wärmetαuscher mit Rohren ( 2 ), die beidseitig in Rohrplatten ( 3, 4 ) oder Ovalrohr-Sammlerrohrplatten ( 5, ό ) gehalten und mit diesen jeweils mittels Schweißnaht ( 7 ) verbunden sind, zum Abkühlen eines durch die Rohre ( 2 ) geleiteten heißen Gasstromes ( 18 ) durch ein die Rohre ( 2 ) umgebendes Kühlmittel ( 19 ), aufweisend wenigstens eine Gaseintrittskammer ( 8 ), von der aus der heiße Gasstrom ( 18 ) in die einzelnen Rohre ( 2 ) eingeleitet wird und die an einer Seite durch die eingangsseitige Rohrplatte ( 3 ) oder Ovalrohr-Sammlerrohrplatte ( 5 ) begrenzt ist und wenigstens eine Gasaustrittskammer ( 9 ), in der der durch die Rohre ( 2 ) hindurchgeleitete Gasstrom { 18 ) gesammelt und abgeführt wird und die an einer Seite durch die ausgangsseitige Rohrplatte ( 4 ) oder Ovalrohr-Sammlerrohrplatte ( 6 ) begrenzt ist, dadurch gekennzeichnet, dass die Verbindung der Rohre ( 2 ) mit der eingangseitigen Rohrplatte ( 3 ) oder Ovalrohr-Sammlerrohrplatte ( 5 ) jeweils mittels eines konus- und/oder trompetenförmigen Übergangsstückes ( 10 ) gebildet ist, dessen Querschnitt sich in Gasströmungsrichtung gesehen verringert, dass das in Gasströmungsrichtung gesehen eingangseitige Ende ( l ό ) des Übergangsstückes ( 10 ) stoßartig mit der Rohrplatte ( 3 ) oder Ovalrohr- Sammlerrohrplatte ( 5 ) verbunden ist und die Innen- und Außenkonturen ( 1 1 , 12 ) des Übergangstückes ( 10 ) und des Schweißverbindungsbereiches ( 13 ) zur Rohrplatte ( 3 ) oder Ovalrohr- Sammlerrohrplatte ( 5 ) spalt- und kantenfrei sowie gerade und/oder mit einem an der Außenkontur ( 12 ) ansetzenden Radius ( R ) von wenigstens 5 mm ausgebildet sind.1 . Tube bundle heat exchanger with tubes (2) which are held on both sides in tube plates (3, 4) or oval tube collector tube plates (5, ό) and connected to them by means of weld seams (7) for cooling one through the tubes (2) hot gas stream (18) through a coolant (19) surrounding the tubes (2), comprising at least one gas inlet chamber (8) from which the hot gas stream (18) is introduced into the individual tubes (2) and through at one side the input-side tube plate (3) or oval tube collector tube plate (5) is limited and at least one gas outlet chamber (9) in which the through the tubes (2) passed gas stream {18) is collected and discharged and on one side through the output side tube plate (4) or oval tube header tube plate (6) is limited, characterized in that the connection of the tubes (2) with the input-side tube plate (3) or oval tube header tube plate (5) respectively s is formed by means of a conical and / or trumpet-shaped transition piece (10) whose cross-section decreases seen in the gas flow direction, that seen in the gas flow direction input end (l ό) of the transition piece (10) jerky with the tube plate (3) or oval tube Collector tube plate (5) is connected and the inner and outer contours (1 1, 12) of the transition piece (10) and the Schweißverbindungsbereiches (13) to the tube plate (3) or Ovalrohr- collector tube plate (5) gap and edge free and straight and / or are formed with a on the outer contour (12) attaching radius (R) of at least 5 mm.
2. Rohrbündel-Wärmetauscher nach Anspruch 1 , dadurch gekennzeichnet, dass die Länge ( Lü ) des Übergangsstückes ( 10 ) mindestens das 1 ,5-fache des Innendurchmessers ( di ) des Rohres ( 2 ) beträgt. 2. tube bundle heat exchanger according to claim 1, characterized in that the length (Lü) of the transition piece (10) is at least 1.5 times the inner diameter (di) of the tube (2).
3. Rohrbündel-Wärmetαuscher nach Anspruch 1 , dadurch gekennzeichnet, dass der Innendurchmesser ( Di ) des Übergangsstückes ( 10 ) in Gasströmungsrichtung gesehen an dessen Eintritt mindestens das 1 ,2-fache des Innendurchmessers ( di ) des Rohres ( 2 ) beträgt.3. Rohrbündel-Wärmetauschus according to claim 1, characterized in that the inner diameter (Di) of the transition piece (10) seen in the gas flow direction at the inlet at least 1.2 times the inner diameter (di) of the tube (2).
4. Rohrbündel-Wärmetauscher nach Anspruch 1 , dadurch gekennzeichnet, dass das Übergangsstück ( 10 ) durch eine mechanische Aufweitung am in Gasströmungsrichtung gesehen eingangseitigen Ende ( 16 ) des Rohres ( 2 ) gebildet ist.4. tube bundle heat exchanger according to claim 1, characterized in that the transition piece (10) by a mechanical expansion on the input side in the gas flow direction seen end (16) of the tube (2) is formed.
5. Rohrbündel-Wärmetauscher nach Anspruch 1 , dadurch gekennzeichnet, dass das Übergangsstück ( 10 ) aus einem gesonderten Rohrteil ( 15 ) gebildet ist und das in Gasströmungsrichtung gesehen ausgangseitige Ende ( 17 ) des Übergangsstückes ( 10 ) stoßartig mit dem Rohr ( 2 ) durch eine Schweißnaht ( 22 ) verbunden ist.5. tube bundle heat exchanger according to claim 1, characterized in that the transition piece (10) from a separate tube part (15) is formed and seen in the gas flow direction output end (17) of the transition piece (10) jerky with the tube (2) a weld (22) is connected.
6. Rohrbündel-Wärmetauscher nach Anspruch 5, dadurch gekennzeichnet, dass die Innen- und Außenkonturen ( 1 1 , 12 ) des Schweißverbindungsbereiches ( 14 ) zwischen Übergangsstück ( 10 ) und Rohr ( 2 ) spalt- und kantenfrei sowie gerade und/oder mit einem an der Außenkontur ( 12 ) ansetzenden Radius ( R ) von wenigstens 5 mm ausgebildet sind.6. tube bundle heat exchanger according to claim 5, characterized in that the inner and outer contours (1 1, 12) of the Schweißverbindungsbereiches (14) between transition piece (10) and tube (2) gap-free and edge-free and straight and / or with a on the outer contour (12) attaching radius (R) of at least 5 mm are formed.
7. Rohrbündel-Wärmetauscher nach einem der vorgenannten Ansprüche, dadurch gekennzeichnet, dass die Innen- und Außenkonturen ( 1 1 , 12 ) des Übergangstückes ( 10 ) und des Schweißverbindungsbereiches ( 13, 14 ) zur Rohrplatte ( 3 ) oder Ovalrohr-Sammlerrohrplatte ( 5 ) und zum Rohr ( 2 ) spalt- und kantenfrei sowie gerade und/oder mit einem an der Außenkontur ( 12 ) ansetzenden Radius ( R ) von wenigstens 2 mm ausgebildet sind.7. tube bundle heat exchanger according to one of the preceding claims, characterized in that the inner and outer contours (1 1, 12) of the transition piece (10) and the Schweißverbindungsbereiches (13, 14) to the tube plate (3) or oval tube-collector tube plate (5 ) and the tube (2) gap-free and free of edges and straight and / or with a on the outer contour (12) attaching radius (R) of at least 2 mm are formed.
8. Rohrbündel-Wärmetauscher nach einem der vorgenannten Ansprüche, dadurch gekennzeichnet, dass das Rohrteil ( 15 ) als Schmiedestück ausgebildet ist. 8. tube bundle heat exchanger according to one of the preceding claims, characterized in that the tubular part (15) is designed as a forging.
EP07702370A 2006-01-23 2007-01-19 Tube bundle heat exchanger Active EP1979699B1 (en)

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US9534850B2 (en) 2017-01-03
JP2009524004A (en) 2009-06-25
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AU2007207217A1 (en) 2007-07-26
US20090065185A1 (en) 2009-03-12
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EP1979699B1 (en) 2009-04-01
ZA200806306B (en) 2009-05-27
CN101371097B (en) 2011-10-05
ATE427470T1 (en) 2009-04-15
CN101371097A (en) 2009-02-18
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DK1979699T3 (en) 2009-06-29
AU2007207217B2 (en) 2010-04-29

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