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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Families Citing this family (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006003317B4 (en) 2006-01-23 2008-10-02 Alstom Technology Ltd. Tube bundle heat exchanger
US8009236B2 (en) 2006-11-01 2011-08-30 Level 3 Communications, Llc Broadcast transmission relay circuit
US7995151B2 (en) 2006-11-01 2011-08-09 Level 3 Communications, Llc Broadcast method and system
US9557119B2 (en) 2009-05-08 2017-01-31 Arvos Inc. Heat transfer sheet for rotary regenerative heat exchanger
CN101799253A (en) * 2010-03-18 2010-08-11 王子异 Heat exchanger with sealed cover plate structure
KR20130031272A (en) * 2010-04-28 2013-03-28 다이킨 고교 가부시키가이샤 Heat exchanging device and connecting tube used therein
US9200855B2 (en) * 2012-03-06 2015-12-01 Honeywell International Inc. Tubular heat exchange systems
US9127553B2 (en) * 2012-04-13 2015-09-08 General Electric Company Method, systems, and apparatuses for transition piece contouring
US9200853B2 (en) 2012-08-23 2015-12-01 Arvos Technology Limited Heat transfer assembly for rotary regenerative preheater
JP6132130B2 (en) * 2012-11-30 2017-05-24 株式会社ノーリツ Manufacturing method of heat exchanger
US10537089B2 (en) * 2013-02-06 2020-01-21 The Curators Of The University Of Missouri Waste heat recovery systems and methods for a livestock barn
DK177774B1 (en) * 2013-04-11 2014-06-23 Spx Flow Technology Danmark As HYGIENIC HEAT EXCHANGE AND METHOD FOR PREPARING A HYGIENIC HEAT EXCHANGE
US9127403B2 (en) * 2013-05-28 2015-09-08 Andritz Inc. Flash tank with flared inlet insert and method for introducing flow into a flash tank
US9752835B2 (en) 2013-06-06 2017-09-05 Honeywell International Inc. Unitary heat exchangers having integrally-formed compliant heat exchanger tubes and heat exchange systems including the same
US9764435B2 (en) 2013-10-28 2017-09-19 Honeywell International Inc. Counter-flow heat exchange systems
US10175006B2 (en) 2013-11-25 2019-01-08 Arvos Ljungstrom Llc Heat transfer elements for a closed channel rotary regenerative air preheater
US10048009B2 (en) * 2014-04-16 2018-08-14 Enterex America LLC Heat exchanger tube with concave-shaped end and method of manufacturing a heat exchanger tube with concave-shaped end
CN104370005A (en) * 2014-11-05 2015-02-25 东港市华宇精密铸造有限公司 Oil storage tank heating pipe diffuser
CN104764348B (en) * 2015-03-19 2016-10-05 南京华电节能环保设备有限公司 Air conveying solid particle heat exchanger
CN107787244B (en) * 2015-04-21 2020-11-24 Ti集团车辆系统有限责任公司 Fuel filter housing
US10094626B2 (en) 2015-10-07 2018-10-09 Arvos Ljungstrom Llc Alternating notch configuration for spacing heat transfer sheets
DE102015013517A1 (en) * 2015-10-20 2017-04-20 Borsig Gmbh Heat exchanger
AU2018205213B2 (en) 2017-01-06 2020-01-30 Bechtel Energy Inc. Branch fitting for reducing stress caused by acoustic induced vibration
CN106679467B (en) * 2017-02-28 2019-04-05 郑州大学 Shell-and-tube heat exchanger with external bobbin carriage
CN106855367B (en) * 2017-02-28 2024-01-26 郑州大学 Shell-and-tube heat exchanger with distributed inlets and outlets
KR102343408B1 (en) * 2017-11-17 2021-12-27 주식회사 엘지화학 Heat exchanger
US11519670B2 (en) 2020-02-11 2022-12-06 Airborne ECS, LLC Microtube heat exchanger devices, systems and methods
EP3964322B1 (en) * 2020-09-04 2023-01-18 ALFA LAVAL OLMI S.p.A. Device and method for restoring the tube-to-tube sheet weld joints in a shell-and-tube heat exchanger
EP4102166A1 (en) * 2021-06-08 2022-12-14 Basell Polyolefine GmbH Heat exchanger for gas phase polymerization
DE102021215093A1 (en) * 2021-12-30 2023-07-06 Robert Bosch Gesellschaft mit beschränkter Haftung Heat exchanger, water treatment plant, heat pump

Family Cites Families (198)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US682607A (en) 1899-11-22 1901-09-17 Joseph Eck Roller for calendering-machines.
US1477209A (en) * 1919-05-05 1923-12-11 George Henry De Vore Radiator for automobiles
US1429149A (en) * 1920-10-18 1922-09-12 Engineering Dev Company Heat interchanger
US1524280A (en) * 1920-11-09 1925-01-27 Ingersoll Rand Co Condenser tube terminal
GB177780A (en) 1921-04-01 1923-02-15 Armin Renyi Improvements in rolling mills for manufacturing corrugated pasteboard, sheet metal and the like
US1450351A (en) 1922-04-22 1923-04-03 Beran Albert Rolling mill for manufacturing corrugated pasteboard, sheet metal, and the like
US1894956A (en) * 1929-01-16 1933-01-24 Babcock & Wilcox Co Air heater
US2023965A (en) 1930-05-21 1935-12-10 Ljungstroms Angturbin Ab Heat transfer
US1915742A (en) 1930-11-28 1933-06-27 Manuf Generale Metallurg Sa Heat exchange apparatus
US1987798A (en) 1931-05-19 1935-01-15 Ruppricht Siegfried Thermal insulating material
US1875188A (en) 1932-01-27 1932-08-30 Sherman Products Corp Unit formed of sheet material
FR775271A (en) * 1934-05-25 1934-12-22 Cooling radiator for heat engine of motor cars or other similar applications
US2042017A (en) 1934-08-24 1936-05-26 Orchard Paper Co Decorative corrugated paper
US2313081A (en) 1937-02-02 1943-03-09 Jarvis C Marble Heat exchange
US2102936A (en) 1937-03-09 1937-12-21 David C Bailey Window glass guide
US2160677A (en) 1937-09-15 1939-05-30 Hippolyte W Romanoff Reinforced corrugated sheet
US2438851A (en) 1943-11-01 1948-03-30 Air Preheater Plate arrangement for preheaters
SE127755C1 (en) 1945-05-28 1950-03-28 Ljungstroms Angturbin Ab Element set for heat exchangers
US2940736A (en) 1949-05-25 1960-06-14 Svenska Rotor Maskiner Ab Element set for heat exchangers
US2782009A (en) 1952-03-14 1957-02-19 Gen Motors Corp Heat exchangers
US3262490A (en) 1954-04-21 1966-07-26 Chrysler Corp Process for joining metallic surfaces and products made thereby
US2796157A (en) 1956-05-18 1957-06-18 Charles R Ginsburg Structural panel construction
FR1219505A (en) * 1958-03-25 1960-05-18 Zd Y V I Elastic connection of heat exchanger tubes to the heat exchanger base
US3111982A (en) 1958-05-24 1963-11-26 Gutehoffnungshuette Sterkrade Corrugated heat exchange structures
US2983486A (en) 1958-09-15 1961-05-09 Air Preheater Element arrangement for a regenerative heat exchanger
US3019160A (en) 1959-05-11 1962-01-30 Diamond Alkali Co Haloglycoluril bactericidal compositions for disinfecting and bleaching
US3158527A (en) 1960-06-10 1964-11-24 Crown Zellerbach Corp Plaited structure and method of forming same
GB959020A (en) 1960-07-20 1964-05-27 Apv Co Ltd A new or improved heat exchanger plate
GB992413A (en) 1961-05-25 1965-05-19 Howden James & Co Ltd Improvements relating to rotary regenerative air preheaters for boiler plant
GB984719A (en) * 1962-03-13 1965-03-03 Atomic Energy Authority Uk Improvements in or relating to heat exchangers
US3260511A (en) 1962-07-20 1966-07-12 Ici Ltd Water cooling towers
US3183963A (en) 1963-01-31 1965-05-18 Gen Motors Corp Matrix for regenerative heat exchangers
SE307964B (en) 1964-03-24 1969-01-27 C Munters
US3317222A (en) * 1964-04-16 1967-05-02 Cons Edison Co New York Inc Insert constructions for tubes of heat exchangers and condensers
US3373798A (en) 1965-11-19 1968-03-19 Gen Motors Corp Regenerator matrix
US3550423A (en) 1966-04-11 1970-12-29 Wood Marc Sa Method of making a sheet of material having asymmetrical folds
US3372743A (en) 1967-01-25 1968-03-12 Pall Corp Heat exchanger
GB1196562A (en) * 1967-02-17 1970-07-01 Hitachi Ltd Welded Assembly of a Tube and a Tube Sheet
US3452814A (en) * 1967-02-24 1969-07-01 Gen Electric Bell-end condenser tubes
US3542635A (en) 1968-04-05 1970-11-24 Chevron Res Corrugated thermoplastic articles
US3523058A (en) 1968-04-05 1970-08-04 Owens Illinois Inc Fabricatable stiff-when-wet corrugated paperboard
US3490523A (en) 1968-04-08 1970-01-20 Us Health Education & Welfare Transfer device
US3574103A (en) 1968-09-06 1971-04-06 Atomic Energy Commission Laminated cellular material form
US3532157A (en) 1969-01-03 1970-10-06 Gen Motors Corp Regenerator disk
US4449573A (en) 1969-06-16 1984-05-22 Svenska Rotor Maskiner Aktiebolag Regenerative heat exchangers
GB1339542A (en) 1970-03-20 1973-12-05 Apv Co Ltd Plate heat exchangers
BE788776A (en) 1970-05-07 1973-01-02 Serck Industries Ltd LIQUID COOLING DEVICE
US3674620A (en) 1970-05-25 1972-07-04 Butler Manufacturing Co Reinforced plastic panel and method of making the same
AT319672B (en) 1971-02-15 1975-01-10 Muellender Gernot Process for the production of foil sheets for lining pipe elbows
USRE28534E (en) 1971-06-07 1975-08-26 Stress oriented corrugations
US3759323A (en) 1971-11-18 1973-09-18 Caterpillar Tractor Co C-flow stacked plate heat exchanger
DE2219130C2 (en) 1972-04-19 1974-06-20 Ulrich Dr.-Ing. 5100 Aachen Regehr CONTACT BODY FOR HEAT AND / OR SUBSTANCE EXCHANGE
US3830684A (en) 1972-05-09 1974-08-20 Hamon Sobelco Sa Filling sheets for liquid-gas contact apparatus
GB1485369A (en) 1973-12-05 1977-09-08 Covrad Ltd Apparatus for shaping sheet material
SE385971B (en) 1973-12-20 1976-07-26 Svenska Flaektfabriken Ab CONTACT BODY FOR WATER AND AIR, MAINLY INTENDED FOR COOLING TOWER AND HUMIDIFIER
NO137706L (en) 1974-01-21
US3901309A (en) 1974-05-16 1975-08-26 Gen Motors Corp Regenerator disk flexible rim
CA1061653A (en) 1975-06-16 1979-09-04 Bernard J. Wallis Apparatus for forming heat exchanger strips
FR2320520A1 (en) * 1975-08-06 1977-03-04 Ferodo Sa HEAT EXCHANGER TUBE DEFLECTOR
GB1531134A (en) 1975-08-20 1978-11-01 Atomic Energy Authority Uk Methods of fabricating bodies and to bodies so fabricated
JPS52746A (en) 1975-11-11 1977-01-06 Mitsubishi Heavy Ind Ltd Method of manufacturing gas nozzle for gas shielded welding torch
US4034135A (en) 1975-11-20 1977-07-05 Passmore Michael Edward Anthon Rigid structure
US4049855A (en) 1976-03-22 1977-09-20 Scott Douglas Cogan Boxcell core and panel
DE2616816C3 (en) 1976-04-15 1983-12-01 Apparatebau Rothemühle Brandt + Kritzler GmbH, 5963 Wenden Heating plate package for regenerative heat exchangers
SE450166B (en) 1976-05-13 1987-06-09 Munters Ab Carl ROTATING REGENERATIVE MIXTURERS CONSISTING OF FOLDED LAYERS AND SETS AND APPARATUS FOR ITS MANUFACTURING
JPS52140052A (en) * 1976-05-19 1977-11-22 Hitachi Ltd Pierced plate with tube and its manufacturing method
GB1585471A (en) 1976-08-27 1981-03-04 Redpath Dorman Long Ltd Composite decks
DE2639693A1 (en) * 1976-09-03 1978-03-09 Siegener Ag Geisweid Pressurised heat exchanger for cracked gas cooler - has tube end plates with recessed seats for reducing weld thickness
JPS6036554B2 (en) 1976-11-19 1985-08-21 アパラ−テバウ・ロ−テミュ−レ・ブラント・ウント・クリツレル Regenerative air preheater
US4061183A (en) 1977-02-16 1977-12-06 General Motors Corporation Regenerator matrix
DK142944C (en) 1977-02-24 1981-10-05 A Bendt EDGE PROTECTION ORGANIZATION
CH617357A5 (en) 1977-05-12 1980-05-30 Sulzer Ag
US4374542A (en) 1977-10-17 1983-02-22 Bradley Joel C Undulating prismoid modules
JPS6222787Y2 (en) 1977-11-30 1987-06-10
SE423143B (en) 1978-02-16 1982-04-13 Munters Ab Carl ROTOR OR SIMILAR BODY FOR MOISTURE AND / OR HEAT EXCHANGERS AND SET FOR ITS MANUFACTURING
US4363222A (en) 1979-01-19 1982-12-14 Robinair Manufacturing Corporation Environmental protection refrigerant disposal and charging system
FR2468404A1 (en) 1979-10-26 1981-05-08 Hamon Sobelco Sa RUNOFF SHEET FOR LIQUID AND GAS CONTACT PLANT FILLING DEVICE
NO144461C (en) 1979-11-02 1981-09-02 J Caspar Falkenberg CORRUGATED, TEATED STEPS FOR BUILDING ELEMENTS
JPS5675590U (en) 1979-11-12 1981-06-20
US4343355A (en) 1980-01-14 1982-08-10 Caterpillar Tractor Co. Low stress heat exchanger and method of making the same
SE444719B (en) 1980-08-28 1986-04-28 Alfa Laval Ab PLATE HEAT EXCHANGERS WITH CORRUGATED PLATES WHICH THE CORRUGATORS SUPPOSE THE ACCESSIBLE PLATES AND THE CORRUGGES IN THE STUDY AREA CONSIDERED TO REDUCE THE DISTANCE BETWEEN TWO PLATES
US4320073A (en) 1980-11-14 1982-03-16 The Marley Company Film fill sheets for water cooling tower having integral spacer structure
US5085268A (en) 1980-11-14 1992-02-04 Nilsson Sven M Heat transmission roll and a method and an apparatus for manufacturing such a roll
US4361426A (en) 1981-01-22 1982-11-30 Baltimore Aircoil Company, Inc. Angularly grooved corrugated fill for water cooling tower
JPS57154874U (en) 1981-03-20 1982-09-29
US4396058A (en) 1981-11-23 1983-08-02 The Air Preheater Company Heat transfer element assembly
US4409274A (en) 1982-02-24 1983-10-11 Westvaco Corporation Composite material
US4501318A (en) 1982-09-29 1985-02-26 Hebrank William H Heat recovery and air preheating apparatus
SE8206809L (en) 1982-11-30 1984-05-31 Sven Melker Nilsson VERMEVEXLARE
US4518544A (en) 1983-01-20 1985-05-21 Baltimore Aircoil Company, Inc. Serpentine film fill packing for evaporative heat and mass exchange
US4472473A (en) 1983-07-01 1984-09-18 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Curved cap corrugated sheet
DK8404709A (en) 1983-10-05 1985-04-06
US4512389A (en) 1983-12-19 1985-04-23 The Air Preheater Company, Inc. Heat transfer element assembly
EP0150913A2 (en) 1984-02-01 1985-08-07 General Motors Corporation Roller tooling for forming corrugated strip
US4553458A (en) 1984-03-28 1985-11-19 The Air Preheater Company, Inc. Method for manufacturing heat transfer element sheets for a rotary regenerative heat exchanger
US4605996A (en) 1985-03-12 1986-08-12 Crown Creative Industries Knock down lamp shade
US4676934A (en) 1985-09-27 1987-06-30 Jaeger Products, Inc. Structured WV packing elements
US4668443A (en) 1985-11-25 1987-05-26 Brentwood Industries, Inc. Contact bodies
DE3541887A1 (en) * 1985-11-27 1987-06-04 Krupp Koppers Gmbh HEAT EXCHANGER FOR COOLING SOLIDS CONTAINING GASES
JPS62158996A (en) * 1985-12-28 1987-07-14 Kawasaki Heavy Ind Ltd Shell and tube type heat exchanger
ATA177787A (en) 1986-08-04 1991-08-15 Mueanyagfel Dolgozo Vall SPHERICAL OR CIRCULAR FILLING ELEMENT MADE OF PLASTIC WITH CENTRAL FLOW OPENING FOR DISORDERED FILLINGS OF BIOLOGICAL DRIP BODIES
GB2195953A (en) 1986-10-06 1988-04-20 Ciba Geigy Ag Laminated panel having a stainless steel foil core
GB8625126D0 (en) 1986-10-20 1986-11-26 Raychem Sa Nv Heat recoverable article
US4950430A (en) 1986-12-01 1990-08-21 Glitsch, Inc. Structured tower packing
US4791773A (en) 1987-02-02 1988-12-20 Taylor Lawrence H Panel construction
SE459672B (en) 1987-02-16 1989-07-24 Plannja Ab PROFILED PLATE FOR BUILDING END
US4744410A (en) 1987-02-24 1988-05-17 The Air Preheater Company, Inc. Heat transfer element assembly
SE455883B (en) 1987-02-27 1988-08-15 Svenska Rotor Maskiner Ab KIT OF TRANSFER TRANSFER PLATES, WHICH THE DOUBLE LOADERS OF THE PLATES HAVE A SPECIFIC INBOUND ORIENTATION
US4769968A (en) 1987-03-05 1988-09-13 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Truss-core corrugation for compressive loads
US4974656A (en) 1987-03-25 1990-12-04 Verosol Usa Inc. Shade and method for the manufacture thereof
SE458806B (en) 1987-04-21 1989-05-08 Alfa Laval Thermal Ab PLATE HEAT EXCHANGER WITH DIFFERENT FLOW RESISTANCE FOR MEDIA
DE3715713C1 (en) * 1987-05-12 1988-07-21 Borsig Gmbh Heat exchanger in particular for cooling cracked gases
JPS63293174A (en) * 1987-05-25 1988-11-30 Ito Horo Kogyo Kk Perforated type calcination disk
NZ224766A (en) 1987-05-26 1990-04-26 John Leslie Graham Mcnab Cooling tower pack
JP2670512B2 (en) 1988-04-25 1997-10-29 エービービー株式会社 Heat transfer element plate stack
US4906510A (en) 1988-07-20 1990-03-06 Adolph Coors Company Method and apparatus for forming a hinge for laminated corrugated material
JPH0730213Y2 (en) * 1988-11-17 1995-07-12 川崎重工業株式会社 Heat exchanger
US5314738A (en) 1989-03-10 1994-05-24 Hiroo Ichikawa Reinforced composite corrugate body
DE3913731A1 (en) * 1989-04-26 1990-10-31 Borsig Gmbh HEAT EXCHANGER FOR COOLING FUSE GAS
US4930569A (en) 1989-10-25 1990-06-05 The Air Preheater Company, Inc. Heat transfer element assembly
US5150520A (en) * 1989-12-14 1992-09-29 The Allen Group Inc. Heat exchanger and method of assembly thereof
US4981732A (en) 1990-02-20 1991-01-01 Charles Hoberman Reversibly expandable structures
US5150596A (en) 1991-07-11 1992-09-29 General Motors Corporation Heat transfer fin with dammed segments
DE4122949A1 (en) 1991-07-11 1993-01-14 Rothemuehle Brandt Kritzler HEATING SHEET PACKAGE FOR REGENERATIVE HEAT EXCHANGER AND METHOD AND DEVICE FOR PRODUCING PROFILE SHEETS FOR SUCH HEATING SHEET PACKAGES
ATA166091A (en) 1991-08-23 1996-02-15 Faigle Heinz Kg FILLING BODY
US5337592A (en) 1992-08-20 1994-08-16 Paulson Wallace S Non-stretch bending of sheet material to form cyclically variable cross-section members
US5308677A (en) 1992-09-04 1994-05-03 Douglas Renna Package stuffing
US5333482A (en) 1992-10-30 1994-08-02 Solar Turbines Incorporated Method and apparatus for flattening portions of a corrugated plate
EP0671963B1 (en) 1992-12-01 1998-10-07 Sulzer Chemtech AG Nested packing for an exchange column
ES2137977T3 (en) 1993-03-10 2000-01-01 Sulzer Chemtech Ag ORDERLY FILLING OF COLUMN.
US5598930A (en) 1995-07-20 1997-02-04 Advanced Wirecloth, Inc. Shale shaker screen
FR2705445B1 (en) 1993-05-18 1995-07-07 Vicarb Sa Plate heat exchanger.
US5318102A (en) 1993-10-08 1994-06-07 Wahlco Power Products, Inc. Heat transfer plate packs and baskets, and their utilization in heat recovery devices
US5380579A (en) 1993-10-26 1995-01-10 Accurate Tool Company, Inc. Honeycomb panel with interlocking core strips
JP3450067B2 (en) 1993-12-07 2003-09-22 千代田化工建設株式会社 Heat exchanger for combustion apparatus, regenerator for heat exchanger, and method for preheating oxidant for combustion
DE4343825A1 (en) * 1993-12-22 1995-06-29 Behr Gmbh & Co Pipe-floor connection for a heat exchanger
TW259725B (en) * 1994-04-11 1995-10-11 Mitsubishi Heavy Ind Ltd
DK44194A (en) 1994-04-15 1995-10-16 Rasmussen Kann Ind As Deformable sheet material, in particular for roofing purposes, and method of making such material
FR2721313B1 (en) 1994-06-17 1996-07-19 Atochem Elf Sa Process for the production of alkyl acrylates by direct esterification.
JPH0824670A (en) 1994-07-11 1996-01-30 Usui Internatl Ind Co Ltd Metallic honeycomb body for purifying exhaust gas
JPH08101000A (en) 1994-09-30 1996-04-16 Hisaka Works Ltd Plate-type heat exchanger
USH1621H (en) 1995-01-31 1996-12-03 The United States Of America As Represented By The Secretary Of The Navy Offset corrugated panel with curved corrugations for increased strength
US5609942A (en) 1995-03-13 1997-03-11 The United States Of America As Represented By The Secretary Of The Navy Panel having cross-corrugated sandwich construction
DE29505064U1 (en) 1995-03-25 1996-07-25 Heerklotz, Siegfried, Dipl.-Ing., 49143 Bissendorf Flat cushion body
JPH093590A (en) 1995-06-21 1997-01-07 Nippon Steel Corp Oxide dispersion strengthened ferritic heat resistant steel sheet and its production
US5600928A (en) 1995-07-27 1997-02-11 Uc Industries, Inc. Roof vent panel
SE513642C2 (en) * 1996-03-29 2000-10-16 Valeo Engine Cooling Ab Heat exchanger and methods of making such
JP3451160B2 (en) 1996-04-17 2003-09-29 株式会社 日立インダストリイズ Plate heat exchanger
JPH09296994A (en) 1996-04-30 1997-11-18 Sanden Corp Heat exchanger
US5792539A (en) 1996-07-08 1998-08-11 Oceaneering International, Inc. Insulation barrier
US5803158A (en) 1996-10-04 1998-09-08 Abb Air Preheater, Inc. Air preheater heat transfer surface
US5836379A (en) 1996-11-22 1998-11-17 Abb Air Preheater, Inc. Air preheater heat transfer surface
DE19652999C2 (en) 1996-12-19 1999-06-24 Steag Ag Heat storage block for regenerative heat exchangers
JPH10328861A (en) * 1997-05-29 1998-12-15 Kawasaki Steel Corp Laser lap welding method
US5979050A (en) 1997-06-13 1999-11-09 Abb Air Preheater, Inc. Air preheater heat transfer elements and method of manufacture
US5899261A (en) 1997-09-15 1999-05-04 Abb Air Preheater, Inc. Air preheater heat transfer surface
FR2771025B1 (en) 1997-11-17 2000-01-28 Air Liquide CORRUGATED STRIP FOR CROSS-CORRUGATED TRIM AND ITS APPLICATION TO ON-BOARD DISTILLATION COLUMNS
DE69928590T2 (en) 1998-03-23 2006-08-03 Calsonic Kansei Corp. Embossing roller for thin metal plates as a catalyst carrier
JPH11287588A (en) * 1998-03-31 1999-10-19 Isuzu Motors Ltd Egr cooler
JPH11294986A (en) 1998-04-10 1999-10-29 Furukawa Electric Co Ltd:The Heat transfer tube having grooved inner surface
DE19833004A1 (en) * 1998-07-22 2000-01-27 Borsig Gmbh Heat exchanger for cooling a hot process gas
US6019160A (en) 1998-12-16 2000-02-01 Abb Air Preheater, Inc. Heat transfer element assembly
JP2000213425A (en) * 1999-01-20 2000-08-02 Hino Motors Ltd Egr cooler
US6280824B1 (en) 1999-01-29 2001-08-28 3M Innovative Properties Company Contoured layer channel flow filtration media
US6516871B1 (en) 1999-08-18 2003-02-11 Alstom (Switzerland) Ltd. Heat transfer element assembly
ATE254751T1 (en) 1999-09-15 2003-12-15 Brentwood Ind Inc CONTACT BODY AND METHOD AND DEVICE FOR PRODUCING SAME
US6478290B2 (en) 1999-12-09 2002-11-12 Praxair Technology, Inc. Packing for mass transfer column
SE513927C2 (en) 2000-02-11 2000-11-27 Sven Melker Nilsson Method of folding metal foil and foil packages of such foil
US6212907B1 (en) 2000-02-23 2001-04-10 Praxair Technology, Inc. Method for operating a cryogenic rectification column
GB0023427D0 (en) 2000-09-23 2000-11-08 Smiths Industries Plc Apparatus
JP3650910B2 (en) 2001-08-06 2005-05-25 株式会社ゼネシス Heat transfer part and heat transfer part forming method
JP2003080083A (en) 2001-09-14 2003-03-18 Calsonic Kansei Corp Metallic catalyst support
JP4055411B2 (en) 2001-12-11 2008-03-05 アルストム テクノロジー リミテッド Manufacturing method of heat transfer element in rotary regenerative heat exchanger
US20030178173A1 (en) 2002-03-22 2003-09-25 Alstom (Switzerland) Ltd. Heat transfer surface for air preheater
JP4207184B2 (en) 2002-08-30 2009-01-14 株式会社ティラド Plate type heat exchanger and manufacturing method thereof
FR2848292B1 (en) 2002-12-05 2005-03-04 Packinox Sa THERMAL EXCHANGER PLATE AND PLATE HEAT EXCHANGER
DE10304814C5 (en) 2003-02-06 2009-07-02 Emitec Gesellschaft Für Emissionstechnologie Mbh Method and tool for producing structured sheet metal layers; The catalyst support body
US6764532B1 (en) 2003-03-03 2004-07-20 General Motors Corporation Method and apparatus for filtering exhaust particulates
US6730008B1 (en) 2003-04-16 2004-05-04 Shih Wen Liang Differential shaft for a strip-producing machine
TWI267337B (en) 2003-05-14 2006-11-21 Inventor Prec Co Ltd Heat sink
US7347351B2 (en) * 2004-08-18 2008-03-25 The Boeing Company Apparatus and system for unitized friction stir welded structures and associated method
US7555891B2 (en) 2004-11-12 2009-07-07 Board Of Trustees Of Michigan State University Wave rotor apparatus
EP1812688B1 (en) 2004-11-12 2016-04-13 Board of Trustees of Michigan State University Composite turbomachine impeller and method of manufacture
US8323778B2 (en) 2005-01-13 2012-12-04 Webb Alan C Environmentally resilient corrugated building products and methods of manufacture
US20070017664A1 (en) * 2005-07-19 2007-01-25 Beamer Henry E Sheet metal pipe geometry for minimum pressure drop in a heat exchanger
GB2429054A (en) 2005-07-29 2007-02-14 Howden Power Ltd A heating surface element
DE102006003317B4 (en) 2006-01-23 2008-10-02 Alstom Technology Ltd. Tube bundle heat exchanger
FR2899430B1 (en) 2006-04-11 2010-03-19 Kuhn Sa MOWER-CONDITIONER CONDITIONER ROLLER, METHOD FOR MANUFACTURING SUCH ROLLER, AND MOWER-CONDITIONER EQUIPPED WITH SUCH ROLLER
DE102006032861A1 (en) 2006-07-14 2008-01-17 Emitec Gesellschaft Für Emissionstechnologie Mbh Production of openings in a metal foil and honeycomb body produced therewith for the treatment of exhaust gas
DE102006035958A1 (en) 2006-08-02 2008-02-07 Klingenburg Gmbh Rotary heat exchanger
CN101210780B (en) 2006-12-30 2010-10-20 卡特彼勒公司 Cooling system with non-parallel cooling radiating flange
SE532714C2 (en) 2007-12-21 2010-03-23 Alfa Laval Corp Ab Plate heat exchanger device and plate heat exchanger
US9557119B2 (en) 2009-05-08 2017-01-31 Arvos Inc. Heat transfer sheet for rotary regenerative heat exchanger
US8622115B2 (en) 2009-08-19 2014-01-07 Alstom Technology Ltd Heat transfer element for a rotary regenerative heat exchanger
DE102010030781A1 (en) 2010-06-30 2012-01-05 Sgl Carbon Se Heat exchanger plate, thus provided plate heat exchanger and method for producing a plate heat exchanger
US9644899B2 (en) 2011-06-01 2017-05-09 Arvos, Inc. Heating element undulation patterns
US9200853B2 (en) 2012-08-23 2015-12-01 Arvos Technology Limited Heat transfer assembly for rotary regenerative preheater
US10175006B2 (en) 2013-11-25 2019-01-08 Arvos Ljungstrom Llc Heat transfer elements for a closed channel rotary regenerative air preheater

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2007082515A1 *

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WO2007082515A1 (en) 2007-07-26
US20170074593A1 (en) 2017-03-16
JP2009524004A (en) 2009-06-25
DK1979699T3 (en) 2009-06-29
EP1979699B1 (en) 2009-04-01
ZA200806306B (en) 2009-05-27

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