EP0328044A1 - Device for positioning a work piece - Google Patents

Device for positioning a work piece Download PDF

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Publication number
EP0328044A1
EP0328044A1 EP89102075A EP89102075A EP0328044A1 EP 0328044 A1 EP0328044 A1 EP 0328044A1 EP 89102075 A EP89102075 A EP 89102075A EP 89102075 A EP89102075 A EP 89102075A EP 0328044 A1 EP0328044 A1 EP 0328044A1
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EP
European Patent Office
Prior art keywords
tubes
heat exchanger
header
tube
collecting
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
EP89102075A
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German (de)
French (fr)
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EP0328044B1 (en
Inventor
Hubert Dr. Ing. Grieb
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.)
MTU Aero Engines AG
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MTU Motoren und Turbinen Union Muenchen GmbH
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Publication of EP0328044A1 publication Critical patent/EP0328044A1/en
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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
    • F28D7/06—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 having a single U-bend
    • 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
    • F28F9/0243—Header boxes having a circular cross-section
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making
    • Y10T29/49389—Header or manifold making

Definitions

  • the invention relates to a heat exchanger with two collecting tubes arranged in parallel, which are connected to one another via a plurality of U-shaped profile tubes.
  • Such a heat exchanger as it has become known for example from DE-PS 36 35 549 and is particularly suitable for high gas temperatures and high thermal, cyclical loads, has so far been produced in that the individual components, i. H. the profile tubes and header sections are firmly connected to one another by means of soldering or welding.
  • the collecting tubes can consist of two half shells joined together or of individual shorter tube sections which are arranged one behind the other and are soldered together.
  • a disadvantage of the designs described is that, in the event of leaks, which can occur either as a result of incorrect manufacture or as a result of material fatigue, an expensive repair or even an exchange of the entire heat exchanger is often required.
  • a shock load transversely to the header tube axis unsteady inertial forces can also result in high voltage peaks at the connection points between the header tube and the profile tubes, which entails the risk of cracks and leaks, since the header tubes accommodate a large number of profile tubes.
  • As a dangerous consequence of cracks there is a local weakening of the stiffness and strength of the header pipes, which triggers a progressive increase in the local stress peaks and thus a progressive damage until breakage.
  • the object of the invention is to improve a heat exchanger of the generic type in such a way that the formation of cracks is prevented by lower loads. Furthermore, a progressive higher load should be avoided in the event of cracks. In the event of mechanical shock loading, less deformation of the header pipes and thus a lower stress level at the endangered points should be achieved.
  • the object is achieved in that the manifolds consist of a number of manifold sections which are arranged axially one behind the other in a sealing and releasable manner and are held together by a draw tube which is supported on the manifold sections and is concentrically spaced within the manifolds.
  • the manifolds By designing the manifolds as a number of manifold sections arranged one behind the other and releasably braced together, it is possible in the event of a leak in the heat exchanger to disassemble it and to replace the defective element. This enables considerably more economical manufacture and maintenance of the heat exchanger. Furthermore, the manifolds are advantageously given increased flexural rigidity by the draw tubes, as a result of which the likelihood of cracking under impact loads is reduced. The inspection of individual heat exchanger elements is also much easier than the inspection of a complete heat exchanger.
  • the draw tubes arranged concentrically within the header tubes enable the heat exchanger to be stiffened, the impact and bending loads acting on the header tubes being absorbed by the stiffening means, and the header tube wall only having to absorb the compressive and inertial forces of the profile tubes. This significantly reduces the risk of cracking.
  • the draw tubes are provided with a multiplicity of openings distributed over the surface, so that the air flowing in the header tubes can enter the profile tubes unimpeded and from the profile tubes into the other header tube.
  • the wall thickness is dimensioned so that the required rigidity or strength is given in every direction.
  • the header pipes are under increased axial compressive stress when the heat exchanger is in operation, which further reduces the risk of cracks or leaks.
  • the draw tubes have a lower coefficient of thermal expansion than the header tubes. This effect is also achieved in that the header tubes heat up more than the inner draft tubes.
  • the tensioning by means of the draw tubes is to be set so that, during stationary operation, sufficiently high compressive forces act on the end faces of the header sections and, at the same time, the tensile loads on the draw tubes remain in the range of the elastic expansion.
  • FIG. 1 shows a heat exchanger 1, the manifolds 2 and 3 of which consist of a plurality of manifold sections 5, 6 arranged one behind the other.
  • the manifolds 2 and 3 are connected to one another via a plurality of U-shaped profile tubes 21.
  • the mode of action of the heat exchanger is as follows: A cool gas flow axially enters the manifold 2. The gas flow divides and flows through the large number of U-shaped profile tubes 21 embedded in the collecting tube 2 to the collecting tube 3. The gas heats up due to the hot gas flowing in the direction indicated by 36 in cross-countercurrent flow. The heated inner gas flow combines again in the collecting pipe 3 and flows axially through the collecting pipe 3.
  • Fig. 2 shows a section of the heat exchanger 1 in cross section.
  • the collecting pipe 2, which consists of individual collecting pipe sections 5, 6, is provided at one end with a collecting pipe end section 12, through which the internally directed gas stream is supplied.
  • a closed collecting pipe end section 11 is provided at the opposite end of the collecting pipe 2.
  • a large number of profile tubes 21 are attached in the wall of the collecting tube 2 by means of soldering or welding. Between the individual header sections 5, 6 with the connected profile tubes 21, intermediate plates 37 are provided.
  • a pull tube 15 Arranged in the interior of the collecting tube 2 is a pull tube 15, which is in fitting connection with the collecting tube 2 at the abutment points 4 of two collecting tube sections 5, 6 lying axially one behind the other.
  • the draw tube 15 is connected to the manifold end sections 11, 12 at points 7, 8, a defined bracing of the draw tube 15 being set by means of screw connections (not shown).
  • the draw tube 15 In the sections of the draw tube 15, which lie opposite the profile tubes 21, the draw tube 15 is provided with a number of openings 18, which can be distributed regularly over the circumference. This enables the gas flow from the inside of the draw tube 15 to the profile tubes 21 or in the header tube 3 in reverse.
  • At the header end sections 11 and 12 are also attached end plates 38 which are arranged parallel to the intermediate plates 27.
  • the arrangement of the collecting pipe 2 and the drawing pipe 15 shown in FIG. 2 and described above is implemented analogously in the collecting pipe 3 and the drawing pipe 16.
  • the intermediate plates 37 and end plates 38 are designed so that the header sections 5 and 6 receive narrow strips 39 without profile tubes 21 on their faces, which are necessary for reasons of strength.
  • the intermediate plates 37 arranged between the header pipe sections 5, 6 and the end plates 38 are connected to one another via the edge plates 40 on the arc sides 41 of the profile tubes, the edge plates 40 simultaneously serving to guide the gas. Furthermore, the intermediate plates 37 and end plates 38 together with the edge plates 40 prevent the deflection or deformation of the profiled tubes in the event of impacts in the collecting tube axial direction, in that the deflection of the arc sides 41 in the overall direction of the collecting tube is avoided.
  • a lug 42 is attached to one of the boundary plates 40, which is held in a certain position by a counterpart 44 fastened to the housing 43 surrounding the heat exchanger 1.
  • the part of the heat exchanger 1, d. H. the sum of all profile tubes 21, intermediate tube plates 38 and end plates 39 is recorded.
  • the intermediate plates 37 and end plates 38 are divided into two in the section tube axial direction in order to account for the different thermal expansion of the top and bottom of the heat exchanger 1 and thus of the intermediate and end plates 37, 38 due to the temperature gradient in Compensate flow direction 36.
  • the edge plates 40 are also made in two parts, since they are screwed to the intermediate and end plates 37, 38. The two parts of the edge plates 40 are connected by links 45 to ensure that the gap between the two parts remains the same under all thermal conditions in view of the required seal.
  • the concentrically arranged draw tubes 15, 16 are located inside the header tubes 2, 3. These have openings 18 distributed over the circumference.
  • a shielding plate 19 is attached to the hot gas inlet-side collecting tube 3, which ensures that the hot gas flow does not act directly on the collecting tube 3 and the connections between the collecting tube 3 and profile tubes 21 on the gas inlet side. As a result, the temperature gradients on the circumference of the collecting tube 3 are considerably reduced.
  • the manifold end sections 11, 12 also serve to center the manifolds 2, 3 and are designed so that the heat exchanger 1 can expand freely in the axial direction of the manifold.
  • the attachment of the draw tube 15 to the end sections 11 and 12 is shown enlarged.
  • the draw tube 15 is screwed to the end sections 11, 12 by means of screws 23, 24, a gap 23 being provided between the draw tube 15 and the end section 11 in order to apply the tensile load to the draw tube 15.
  • This gap 23 can advantageously be almost or completely eliminated by tightening the screw 22, as a result of which a defined prestressing of the draw tube 15 can be set.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

The manifolds (2, 3) of a profiled-tube heat exchanger (1) consist of a number of manifold sections (5, 6) which are arranged axially one behind another, and are held together and tensioned by means of internally arranged tension tubes (15, 16). …<IMAGE>…

Description

Die Erfindung bezieht sich auf einen Wärmetauscher mit zwei parallel angeordneten Sammelrohren, die über eine Vielzahl von U-förmig ange­ordneten Profilrohren miteinander in Verbindung stehen.The invention relates to a heat exchanger with two collecting tubes arranged in parallel, which are connected to one another via a plurality of U-shaped profile tubes.

Ein derartiger Wärmetauscher, wie er beispielsweise aus der DE-PS 36 35 549 bekanntgeworden ist und sich besonders für hohe Gas­temperaturen und hohe thermische, zyklische Belastungen eignet, wird bisher dadurch hergestellt, daß die einzelnen Bauteile, d. h. die Profilrohre und Sammmelrohrabschnitte mittels Löten oder Schweißen fest miteinander verbunden werden. Dabei können die Sammelrohre aus zwei zusammengefügten Halbschalen oder aus einzelnen kürzeren Rohrab­schnitten bestehen, die hintereinander angeordnet miteinander verlötet werden.Such a heat exchanger, as it has become known for example from DE-PS 36 35 549 and is particularly suitable for high gas temperatures and high thermal, cyclical loads, has so far been produced in that the individual components, i. H. the profile tubes and header sections are firmly connected to one another by means of soldering or welding. The collecting tubes can consist of two half shells joined together or of individual shorter tube sections which are arranged one behind the other and are soldered together.

Die feste Verbindung der Bauteile mittels Löten oder Schweißen wurde bisher als erforderlich angesehen, um zu verhindern, daß im Betrieb Leckströme zwischen den wärmetauschenden Medien auftreten. Dies ist vor allem wegen der erheblichen Thermobeanspruchungen, insbesondere bei instationärem Betrieb oder wegen äußerer oder durch den Gasstrom her­vorgerufenen Schwingungen problematisch.The firm connection of the components by means of soldering or welding has hitherto been regarded as necessary in order to prevent leakage currents occurring between the heat-exchanging media during operation. This is problematic above all because of the considerable thermal stresses, in particular during unsteady operation or because of external vibrations or vibrations caused by the gas flow.

Nachteilig bei den beschriebenen Ausführungen wirkt sich aus, daß bei Undichtheiten, die entweder durch fehlerhafte Herstellung oder durch Werkstoffermüdung auftreten können, vielfach eine aufwendige Reparatur oder sogar ein Austausch des gesamten Wärmetauschers erforderlich ist. Bei Stoßbelastung quer zur Sammelrohrachse können durch instationäre Massenkräfte außerdem hohe Spannungsspitzen an den Verbindungsstellen zwischen Sammelrohr und Profilrohren auftreten, womit die Gefahr von Anrissen und damit Lecken verbunden ist, da die Sammelrohre eine große Anzahl von Profilrohren aufnehmen. Als gefährliche Folge von Anrissen tritt eine örtliche Schwächung der Steifigkeit und Festigkeit der Sammelrohre ein, wodurch ein progressives Anwachsen der örtlichen Spannungsspitzen und damit eine progressive Schädigung bis zum Bruch ausgelöst wird.A disadvantage of the designs described is that, in the event of leaks, which can occur either as a result of incorrect manufacture or as a result of material fatigue, an expensive repair or even an exchange of the entire heat exchanger is often required. In the event of a shock load transversely to the header tube axis, unsteady inertial forces can also result in high voltage peaks at the connection points between the header tube and the profile tubes, which entails the risk of cracks and leaks, since the header tubes accommodate a large number of profile tubes. As a dangerous consequence of cracks, there is a local weakening of the stiffness and strength of the header pipes, which triggers a progressive increase in the local stress peaks and thus a progressive damage until breakage.

Insbesondere bei Stößen in Richtung der Profilrohrachsen ist dies kritisch, da hier die Felder am Umfang der Sammelrohre, die zur Auf­nahme der U-förmigen Profilrohre dienen, im Bereich der höchsten Zug- und Druckspannungen liegen. In diesem Falle tritt daher aufgrund des geringen Widerstandsmoments der Sammelrohre eine rasche progressive Schädigung bei Wechsel- bzw. Stoßbeanspruchung ein. Die bei Durchbie­gung der Sammelrohre in Belastungsrichtung entstehende Stützwirkung aufgrund der Annäherung der Profilrohre auf der einen Seite spielt dabei eine untergeordnete Rolle.This is particularly critical in the case of impacts in the direction of the profile tube axes, since here the fields on the circumference of the header tubes, which serve to accommodate the U-shaped profile tubes, are in the region of the highest tensile and compressive stresses. In this case, due to the low resistance torque of the header pipes, rapid progressive damage occurs under alternating or impact loads. The support effect resulting from the deflection of the header tubes in the direction of loading due to the approach of the profile tubes on one side plays a subordinate role.

Aufgabe der Erfindung ist es, einen Wärmetauscher der gattungsgemäßen Art derart zu verbessern, daß durch geringere Belastung die Entstehung von Anrissen verhindert wird. Weiterhin soll bei Anrissen eine pro­gressive Höherbelastung vermieden werden. Bei mechanischer Stoßbela­stung soll eine geringere Deformation der Sammelrohre und damit ein niedrigeres Spannungsniveau an den gefährdeten Stellen erzielt werden.The object of the invention is to improve a heat exchanger of the generic type in such a way that the formation of cracks is prevented by lower loads. Furthermore, a progressive higher load should be avoided in the event of cracks. In the event of mechanical shock loading, less deformation of the header pipes and thus a lower stress level at the endangered points should be achieved.

Weiterhin ist es Aufgabe, weniger hohe Qualitätsanforderungen der Verbindung Profilrohre/Sammelrohre zu ermöglichen, die nunmehr sehr viel geringere mechanische Belastungen zu übertragen brauchen, d. h. in der Hauptsache dichten müssen. Schließlich soll eine vereinfachte Fertigung, Kontrolle, Inspektion, Reparatur des Wärmetauschers er­möglicht werden.Furthermore, it is an object to enable less high quality requirements for the connection of profile tubes / header tubes, which now need to transmit much lower mechanical loads. H. mainly have to write poetry. Finally, a simplified manufacture, inspection, inspection, repair of the heat exchanger should be made possible.

Erfindungsgemäß wird die Aufgabe dadurch gelöst, daß die Sammelrohre aus einer Anzahl Sammelrohrabschnitten bestehen, die axial hinterein­ander dichtend und lösbar angeordnet sind und durch je ein an den Sammelrohrabschnitten abgestütztes und konzentrisch innerhalb der Sammelrohre beabstandet angeordnetes Zugrohr zusammengehalten werden.According to the invention the object is achieved in that the manifolds consist of a number of manifold sections which are arranged axially one behind the other in a sealing and releasable manner and are held together by a draw tube which is supported on the manifold sections and is concentrically spaced within the manifolds.

Durch die Ausbildung der Sammelrohre als einer Anzahl hintereinander angeordneter und lösbar miteinander verspannter Sammelrohrabschnitte ist es möglich, im Fall einer Leckstelle im Wärmetauscher diesen zu demontieren und das fehlerhafte Element zu ersetzen. Dadurch ist eine erheblich wirtschaftlichere Herstellung und Wartung des Wärmetauschers möglich Weiterhin erhalten die Sammelrohre durch die Zugrohre vor­teilhafterweise eine vergrößerte Biegesteifigkeit, wodurch die Anriß­wahrscheinlichkeit bei Stoßbelastungen reduziert ist. Auch ist die Inspektion einzelner Wärmetauscherelemente wesentlich einfacher, als die Inspektion eines kompletten Wärmetauschers.By designing the manifolds as a number of manifold sections arranged one behind the other and releasably braced together, it is possible in the event of a leak in the heat exchanger to disassemble it and to replace the defective element. This enables considerably more economical manufacture and maintenance of the heat exchanger. Furthermore, the manifolds are advantageously given increased flexural rigidity by the draw tubes, as a result of which the likelihood of cracking under impact loads is reduced. The inspection of individual heat exchanger elements is also much easier than the inspection of a complete heat exchanger.

Durch die konzentrisch innerhalb der Sammelrohre angeordneten Zugrohre wird eine Versteifung des Wärmetauschers ermöglicht, wobei die auf die Sammelrohre wirkenden Stoß- und Biegebelastungen durch das Verstei­fungsmittel aufgenommen werden, und die Sammelrohrwand nur noch die Druckkräfte und Trägheitskräfte der Profilrohre aufnehmen muß. Hier­durch ist die Gefahr von Rißbildung erheblich vermindert.The draw tubes arranged concentrically within the header tubes enable the heat exchanger to be stiffened, the impact and bending loads acting on the header tubes being absorbed by the stiffening means, and the header tube wall only having to absorb the compressive and inertial forces of the profile tubes. This significantly reduces the risk of cracking.

Durch die Aufnahme der bei Stößen in Richtung der Profilrohrachse an den Sammelrohren auftretenden Biegebelastung wird deren Durchbiegung und damit das Spannungsniveau in den Sammelrohrwandungen - insbeson­dere in den Feldern zur Aufnahme der Profilrohre - durch die Zugrohre vorgegeben bzw. auf niedrigem Niveau gehalten.By absorbing the bending load that occurs on the manifolds in the direction of the profile tube axis, their deflection and thus the stress level in the manifold walls - in particular in the fields for receiving the profile tubes - is predetermined by the draw tubes or kept at a low level.

Treten aufgrund örtlich hoher thermischer oder mechanischer Belastung, vor allem in den Feldern zur Aufnahme der Profilrohre, Anrisse auf, so tritt dadurch keine Schädigung des Gesamtsystems ein, da bei der ge­wählten Ausführung durch die Anrisse örtliche Spannungen abgebaut werden, so daß eine gewisse Beruhigung eintritt.If cracks occur due to locally high thermal or mechanical loads, especially in the fields for receiving the profile tubes, this does not damage the overall system, since in the selected version, local stresses are reduced by the cracks, so that a certain calming occurs .

Dies hat weiter den Vorteil, daß bei vorgegebener, auch bei Anrissen nicht weiter erhöhter örtlicher Belastung im kritischen Bereich der Sammelrohre eine wesentliche Verlängerung der Lebensdauer der Sammel­rohre unter mechanisch/thermischer Belastung erreicht wird. Zugleich ist von Vorteil, daß die Verbindung zwischen Sammelrohren und Profil­rohren, die vorzugsweise durch Löten erfolgt, nicht mehr dieselbe festigkeitstechnische Qualität zu haben braucht wie bei einer Lösung, bei der die Sammelrohre zugleich die gesamte Biegebeanspruchung aufzu­nehmen haben.This has the further advantage that, with a given local load in the critical area of the header pipes, which is not increased even when cracks occur, a substantial extension of the service life of the header pipes under mechanical / thermal load is achieved. At the same time, it is advantageous that the connection between the collecting pipes and the profiled pipes, which is preferably done by soldering, no longer needs to have the same strength-technical quality as in a solution in which the collecting pipes have to absorb the entire bending stress at the same time.

Vorzugsweise sind die Zugrohre mit einer Vielzahl von über der Oberfläche verteilter Durchbrüche versehen, so daß die in den Sammel­rohren strömende Luft ungehindert aus dem einen Sammelrohr in die Profilrohre und aus den Profilrohren in das andere Sammelrohr eintre­ten kann. Dabei ist die Wandstärke so bemessen, daß die erforderliche Steifigkeit bzw. Festigkeit in jeder Stoßrichtung gegeben ist.Preferably, the draw tubes are provided with a multiplicity of openings distributed over the surface, so that the air flowing in the header tubes can enter the profile tubes unimpeded and from the profile tubes into the other header tube. The wall thickness is dimensioned so that the required rigidity or strength is given in every direction.

In vorteilhafter Ausbildung stehen die Sammelrohre bei Betrieb des Wärmetauschers unter erhöhter axialer Druckspannung, wodurch die Ge­fahr von Anrissen bzw. Leckagen weiter vermindert wird. Vorzugsweise besitzen zu diesem Zweck die Zugrohre einen geringeren Wärmedehnungs­koeffizienten als die Sammelrohre. Diese Wirkung wird zudem dadurch erreicht, daß die Sammelrohre sich mehr aufheizen als die innen lie­genden Zugrohre.In an advantageous embodiment, the header pipes are under increased axial compressive stress when the heat exchanger is in operation, which further reduces the risk of cracks or leaks. Preferably For this purpose, the draw tubes have a lower coefficient of thermal expansion than the header tubes. This effect is also achieved in that the header tubes heat up more than the inner draft tubes.

Die Verspannung mittels der Zugrohre ist dabei so einzustellen, daß bei stationärem Betrieb genügend hohe Druckkräfte an den Stirnflächen der Sammelrohrabschnitte wirken und gleichzeitig bei instätionaren Bedingungen an den Zugrohren die Zugbelastungen im Bereich der elastischen Dehnung bleiben.The tensioning by means of the draw tubes is to be set so that, during stationary operation, sufficiently high compressive forces act on the end faces of the header sections and, at the same time, the tensile loads on the draw tubes remain in the range of the elastic expansion.

Die Erfindung wird nachfolgend anhand der beigefügten Zeichnungen wei­ter erläutert. Dabei zeigt:

  • Fig. 1 eine Schrägansicht des demontierten Wärmetauschers,
  • Fig. 2 einen Axialschnitt durch ein Sammelrohr,
  • Fig. 3 einen Querschnitt eines Wärmetauschers.
  • Fig. 4a ein Detailschnitt der Zugrohrbefestigung,
  • Fig. 4b die zweite Zugrohrbefestigung im Schnitt.
The invention is further explained below with reference to the accompanying drawings. It shows:
  • 1 is an oblique view of the disassembled heat exchanger,
  • 2 shows an axial section through a manifold,
  • Fig. 3 shows a cross section of a heat exchanger.
  • 4a is a detail section of the draw tube attachment,
  • Fig. 4b, the second draw tube attachment in section.

In Fig. 1 ist ein Wärmetauscher 1 gezeigt, dessen Sammelrohre 2 und 3 aus mehreren hintereinander angeordneten Sammelrohrabschnitten 5,6 bestehen. Die Sammelrohre 2 und 3 sind über eine Vielzahl U-förmig gebogener Profilröhrchen 21 miteinander verbunden. Die Wirkungsweise des Wärmetauschers ist folgende: Ein kühler Gasstrom tritt axial in das Sammelrohr 2 ein. Der Gasstrom teilt sich auf und durchfließt die Vielzahl der in dem Sammelrohr 2 eingelassenen U-förmig gekrümmten Profilröhrchen 21 zum Sammelrohr 3. Dabei erhitzt sich das Gas auf­grund des außen in der mit 36 angedeuteten Richtung im Kreuz-Gegen­strom anfließenden Heißgases. Der erwärmte innere Gasstrom vereinigt sich wieder im Sammelrohr 3 und fließt durch das Sammelrohr 3 axial ab.1 shows a heat exchanger 1, the manifolds 2 and 3 of which consist of a plurality of manifold sections 5, 6 arranged one behind the other. The manifolds 2 and 3 are connected to one another via a plurality of U-shaped profile tubes 21. The mode of action of the heat exchanger is as follows: A cool gas flow axially enters the manifold 2. The gas flow divides and flows through the large number of U-shaped profile tubes 21 embedded in the collecting tube 2 to the collecting tube 3. The gas heats up due to the hot gas flowing in the direction indicated by 36 in cross-countercurrent flow. The heated inner gas flow combines again in the collecting pipe 3 and flows axially through the collecting pipe 3.

Fig. 2 zeigt einen Ausschnitt des Wärmetauschers 1 im Querschnitt. Dabei ist das aus einzelnen Sammelrohrabschnitten 5,6 bestehende Sammelrohr 2 an einem Ende mit einem Sammelrohrendabschnitt 12 verse­hen, durch den der innen geleitete Gasstrom zugeführt wird. Am entge­gengesetzten Ende des Sammelrohres 2 ist ein verschlossener Sammel­rohrendabschnitt 11 vorgesehen. In der Wand des Sammelrohres 2 sind eine Vielzahl von Profilröhrchen 21 mittels Löten oder Schweißen ange­bracht. Zwischen den einzelnen Sammelrohrabschnitten 5,6 mit den ver­bundenen Profilröhrchen 21 sind Zwischenplatten 37 vorgesehen.Fig. 2 shows a section of the heat exchanger 1 in cross section. The collecting pipe 2, which consists of individual collecting pipe sections 5, 6, is provided at one end with a collecting pipe end section 12, through which the internally directed gas stream is supplied. At the opposite end of the collecting pipe 2, a closed collecting pipe end section 11 is provided. A large number of profile tubes 21 are attached in the wall of the collecting tube 2 by means of soldering or welding. Between the individual header sections 5, 6 with the connected profile tubes 21, intermediate plates 37 are provided.

Im inneren des Sammelrohres 2 ist ein Zugrohr 15 angeordnet, das an den Stoßstellen 4 zweier axial hintereinander liegender Sammelrohr­abschnitte 5,6 in Paßverbindung mit dem Sammelrohr 2 steht. Das Zug­rohr 15 ist an den Stellen 7,8 mit den Sammelrohrendabschnitten 11,12 verbunden, wobei eine definierte Verspannung des Zugrohres 15 mittels nicht dargestellter Schraubverbindungen einzustellen ist. In den Ab­schnitten des Zugrohres 15, die den Profilrohren 21 gegenüberliegen, ist das Zugrohr 15 mit einer Anzahl Durchbrüche 18 versehen, die regelmäßig über dem Umfang verteilt sein können. Hierdurch wird die Gasströmung aus dem Inneren des Zugrohres 15 zu den Profilröhrchen 21 bzw. im Sammelrohr 3 umgekehrt ermöglicht. An den Sammelrohrend­ abschnitten 11 und 12 sind ferner Endplatten 38 befestigt, die paral­lel zu den Zwischenplatten 27 angeordnet sind. Die in Fig. 2 dar­gestellte und oben beschriebene Anordnung von Sammelrohr 2 und Zug­rohr 15 ist analog im Sammelrohr 3 und Zugrohr 16 realisiert.Arranged in the interior of the collecting tube 2 is a pull tube 15, which is in fitting connection with the collecting tube 2 at the abutment points 4 of two collecting tube sections 5, 6 lying axially one behind the other. The draw tube 15 is connected to the manifold end sections 11, 12 at points 7, 8, a defined bracing of the draw tube 15 being set by means of screw connections (not shown). In the sections of the draw tube 15, which lie opposite the profile tubes 21, the draw tube 15 is provided with a number of openings 18, which can be distributed regularly over the circumference. This enables the gas flow from the inside of the draw tube 15 to the profile tubes 21 or in the header tube 3 in reverse. At the header end sections 11 and 12 are also attached end plates 38 which are arranged parallel to the intermediate plates 27. The arrangement of the collecting pipe 2 and the drawing pipe 15 shown in FIG. 2 and described above is implemented analogously in the collecting pipe 3 and the drawing pipe 16.

Die Zwischenplatten 37 und Endplatten 38 sind so ausgeführt, daß die Sammelrohrabschnitte 5 und 6 an ihren Stirnseiten schmale Streifen 39 ohne Profilröhrchen 21 erhalten, die aus Festigkeitsgründen notwendig sind.The intermediate plates 37 and end plates 38 are designed so that the header sections 5 and 6 receive narrow strips 39 without profile tubes 21 on their faces, which are necessary for reasons of strength.

Die zwischen den Sammelrohrabschnitten 5,6 angeordneten Zwischenplat­ten 37 sowie die Endplatten 38 werden miteinander uber die Beran­dungsbleche 40 an den Bogenseiten 41 der Profilrohre miteinander verbunden, wobei die Berandungsbleche 40 gleichzeitig der Gasführung dienen. Weiterhin verhindern die Zwischenplatten 37 und Endplatten 38 zusammen mit den Berandungsblechen 40 bei Stößen in Sammelrohraxial­richtung die Auslenkung bzw. Deformation der Profilrohre, in dem die Auslenkung der Bogenseiten 41 in Sammelrohrachsrichtung insgesamt vermieden wird. Hierzu ist an einem der Berandungsbleche 40 eine Nase 42 angebracht, die durch ein an dem Wärmetauscher 1 umgebenden Gehäuse 43 befestigtes Gegenstück 44 in einer bestimmten Lage gehalten wird. Damit wird der bei Stößen in Sammelrohraxialrichtung gegenüber De­formationen anfällige Teil des Wärmetauschers 1, d. h. die Summe aller Profilrohre 21, Zwischenrohrplatten 38 und Endplatten 39 festgehalten.The intermediate plates 37 arranged between the header pipe sections 5, 6 and the end plates 38 are connected to one another via the edge plates 40 on the arc sides 41 of the profile tubes, the edge plates 40 simultaneously serving to guide the gas. Furthermore, the intermediate plates 37 and end plates 38 together with the edge plates 40 prevent the deflection or deformation of the profiled tubes in the event of impacts in the collecting tube axial direction, in that the deflection of the arc sides 41 in the overall direction of the collecting tube is avoided. For this purpose, a lug 42 is attached to one of the boundary plates 40, which is held in a certain position by a counterpart 44 fastened to the housing 43 surrounding the heat exchanger 1. Thus, the part of the heat exchanger 1, d. H. the sum of all profile tubes 21, intermediate tube plates 38 and end plates 39 is recorded.

Die Zwischenplatten 37 und Endplatten 38 sind, wie in Fig. 3 gezeigt, in Profilrohrachsrichtung zwei geteilt, um die unterschiedliche Wärmedehnung der Ober- und Unterseite des Wärmetauschers 1 und damit der Zwischen- und Endplatten 37,38 aufgrund des Temperaturgefälles in Anströmrichtung 36 auszugleichen. Die Berandungsbleche 40 sind eben­falls zweiteilig ausgefuhrt, da diese mit den Zwischen- und Endplatten 37,38 verschraubt sind. Die beiden Teile der Berandungsbleche 40 sind durch Lenker 45 verbunden, um sicherzustellen, daß der Spalt zwischen den beiden Teilen mit Rücksicht auf die erforderliche Dichtung unter allen thermischen Bedingungen gleich bleibt.The intermediate plates 37 and end plates 38, as shown in FIG. 3, are divided into two in the section tube axial direction in order to account for the different thermal expansion of the top and bottom of the heat exchanger 1 and thus of the intermediate and end plates 37, 38 due to the temperature gradient in Compensate flow direction 36. The edge plates 40 are also made in two parts, since they are screwed to the intermediate and end plates 37, 38. The two parts of the edge plates 40 are connected by links 45 to ensure that the gap between the two parts remains the same under all thermal conditions in view of the required seal.

Im Inneren der Sammelrohre 2,3 liegen die konzentrisch angeordneten Zugrohre 15,16. Diese weisen über dem Umfang verteilte Durchbrüche 18 auf.The concentrically arranged draw tubes 15, 16 are located inside the header tubes 2, 3. These have openings 18 distributed over the circumference.

Am heißgaseintrittsseitigen Sammelrohr 3 ist ein Abschirmblech 19 angebracht, das dafür sorgt, daß der heiße Gasstrom das Sammelrohr 3 sowie die Verbindungen zwischen Sammelrohr 3 und Profilrohren 21 auf der Gaseintrittsseite nicht direkt beaufschlagt. Hierdurch werden die Temperaturgradienten am Umfang des Sammelrohres 3 erheblich reduziert. Die Sammelrohrendabschnitte 11,12 dienen ferner der Zentrierung der Sammelrohre 2,3 und sind so ausgebildet, daß sich der Wärmetauscher 1 in Sammelrohraxialrichtung frei dehnen kann.A shielding plate 19 is attached to the hot gas inlet-side collecting tube 3, which ensures that the hot gas flow does not act directly on the collecting tube 3 and the connections between the collecting tube 3 and profile tubes 21 on the gas inlet side. As a result, the temperature gradients on the circumference of the collecting tube 3 are considerably reduced. The manifold end sections 11, 12 also serve to center the manifolds 2, 3 and are designed so that the heat exchanger 1 can expand freely in the axial direction of the manifold.

In Fig. 4a und 4b ist die Befestigung des Zugrohres 15 an den End­abschnitten 11 bzw. 12 vergrößert dargestellt. Das Zugrohr 15 ist dabei mittels Schrauben 23, 24 an den Endabschnitten 11, 12 ange­schraubt, wobei zur Aufbringung der Zugbelastung auf das Zugrohr 15 ein Spalt 23 zwischen Zugrohr 15 und Endabschnitt 11 vorgesehen ist. Dieser Spalt 23 kann vorteilhafterweise fast oder ganz durch Anziehen der Schraube 22 beseitigt werden, wodurch sich eine definierte Vor­spannung des Zugrohres 15 einstellen läßt.4a and 4b, the attachment of the draw tube 15 to the end sections 11 and 12 is shown enlarged. The draw tube 15 is screwed to the end sections 11, 12 by means of screws 23, 24, a gap 23 being provided between the draw tube 15 and the end section 11 in order to apply the tensile load to the draw tube 15. This gap 23 can advantageously be almost or completely eliminated by tightening the screw 22, as a result of which a defined prestressing of the draw tube 15 can be set.

Claims (5)

1. Wärmetauscher mit zwei parallel angeordneten Sammelrohren, die über eine Vielzahl von U-förmig angeordneten Profilrohren miteinander in Verbindung stehen, dadurch gekennzeichnet, daß die Sammelrohre (2,3) aus einer Anzahl Sammelrohrabschnitte (5,6) bestehen, die axial hintereinander dichtend und lösbar angeordnet sind und durch je ein an den Sammelrohrabschnitten (11,12) abgestütztes und kon­zentrisch innerhalb der Sammelrohre (2,3) beabstandet angeordnetes Zugrohr (15,16) zusammengehalten werden.1. Heat exchanger with two parallel collecting tubes, which are connected to each other via a plurality of U-shaped profile tubes, characterized in that the collecting tubes (2, 3) consist of a number of collecting tube sections (5, 6) which seal axially one behind the other and are arranged detachably and are held together by a pulling tube (15, 16), which is supported on the collecting tube sections (11, 12) and is concentrically spaced within the collecting tubes (2, 3). 2. Wärmetauscher nach Anspruch 1, dadurch gekennzeichnet, daß die Zugrohre (16,15) mit einer Vielzahl von über der Oberfläche ver­teilten Durchbrüche (18) versehen sind.2. Heat exchanger according to claim 1, characterized in that the draw tubes (16, 15) are provided with a plurality of openings (18) distributed over the surface. 3. Wärmetauscher nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß jedes Zugrohr (15,16) an den Stoßstellen (4) zweier axial hinter­einander liegender Sammelrohrabschnitte (5,6) in Paßverbindung mit dem Sammelrohr (2,3) steht.3. Heat exchanger according to claim 1 or 2, characterized in that each draw tube (15, 16) at the abutment points (4) of two axially consecutive header sections (5, 6) is in register with the header (2, 3). 4. Wärmetauscher nach Anspruch 1, dadurch gekennzeichnet, daß zwi­schen den einzelnen Sammelrohrabschnitten (5,6) Zwischenplat­ten (37) vorgesehen sind.4. Heat exchanger according to claim 1, characterized in that intermediate plates (37) are provided between the individual header sections (5,6). 5. Wärmetauscher nach Anspruch 1 bis 4, dadurch gekennzeichnet, daß die Zugrohre (16, 15) einen geringeren Wärmedehnungskoeffizienten haben als die Sammelrohre (2, 3).5. Heat exchanger according to claim 1 to 4, characterized in that the draw tubes (16, 15) have a lower coefficient of thermal expansion than the header tubes (2, 3).
EP89102075A 1988-02-10 1989-02-07 Device for positioning a work piece Expired - Lifetime EP0328044B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3803947A DE3803947A1 (en) 1988-02-10 1988-02-10 HEAT EXCHANGER
DE3803947 1988-02-10

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EP0328044A1 true EP0328044A1 (en) 1989-08-16
EP0328044B1 EP0328044B1 (en) 1991-08-28

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EP89102075A Expired - Lifetime EP0328044B1 (en) 1988-02-10 1989-02-07 Device for positioning a work piece

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US (1) US4940084A (en)
EP (1) EP0328044B1 (en)
JP (1) JP2678046B2 (en)
BR (1) BR8900566A (en)
CA (1) CA1305959C (en)
DE (1) DE3803947A1 (en)
ES (1) ES2025342B3 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2677404A1 (en) * 1991-06-07 1992-12-11 Mtu Muenchen Gmbh DEVICE FOR ASSEMBLING A GAS TURBINE ENGINE WITH A HEAT RECOVERY EXCHANGER.

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3911257C2 (en) * 1989-04-07 1994-05-26 Mtu Muenchen Gmbh Heat exchanger
US5177865A (en) * 1989-05-05 1993-01-12 Mtu Motoren-Und Turbinen-Union Method for making heat exchanger having at least two collecting pipes
DE3914773C2 (en) * 1989-05-05 1994-03-03 Mtu Muenchen Gmbh Heat exchanger with at least two header pipes
US5623987A (en) * 1992-08-04 1997-04-29 Ergenics, Inc. Modular manifold gas delivery system
DE10236380A1 (en) * 2002-08-08 2004-03-04 Mtu Aero Engines Gmbh Recuperative exhaust gas heat exchanger for gas turbine drive has collection tube with closed end fastened radially and axially to turbine housing
US6786202B2 (en) * 2002-09-24 2004-09-07 Caterpillar Inc Hydraulic pump circuit
DE102006021436A1 (en) * 2006-05-09 2007-11-15 Mtu Aero Engines Gmbh Gas turbine engine
JP5651991B2 (en) * 2010-05-10 2015-01-14 富士通株式会社 RADIATOR AND ELECTRONIC DEVICE HAVING THE SAME
US11092384B2 (en) * 2016-01-14 2021-08-17 Hamilton Sundstrand Corporation Thermal stress relief for heat sinks

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB277656A (en) * 1926-09-17 1928-05-10 Jules Basin Improvements in radiators for heating buildings
FR669324A (en) * 1929-02-07 1929-11-14 Sheet metal heating radiator
US3689972A (en) * 1970-11-19 1972-09-12 Modine Mfg Co Method of fabricating a heat exchanger
GB2078361A (en) * 1980-06-24 1982-01-06 Delanair Ltd Heat exchangers and heat exchanger headers

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE214188C (en) *
US916640A (en) * 1908-03-23 1909-03-30 Robert Warg Steam-radiator.
GB134277A (en) * 1918-10-24 1919-10-24 John Melville James Improvements in or relating to Radiators for Cooling Fluids.
DE730039C (en) * 1935-12-11 1943-01-06 Getefo Ges Fuer Tech Fortschri Radiators for aircraft and motor vehicles
FR859510A (en) * 1939-05-22 1940-12-20 Chausson Usines Sa Advanced radiator
DE1928146U (en) 1965-09-03 1965-12-02 H & K Moll O H G ROUND STAND FOR SETTING UP FOLDERS OD. DGL. DEPOSIT CONTAINERS.
DE1928146A1 (en) * 1968-06-06 1969-12-11 Delaney Gallay Ltd Heat exchanger
US3605882A (en) * 1968-07-02 1971-09-20 Ass Eng Ltd Heat exchangers
DE3543893A1 (en) * 1985-12-12 1987-06-25 Mtu Muenchen Gmbh HEAT EXCHANGER
DE3635549C1 (en) * 1986-10-20 1988-03-03 Mtu Muenchen Gmbh Heat exchanger

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB277656A (en) * 1926-09-17 1928-05-10 Jules Basin Improvements in radiators for heating buildings
FR669324A (en) * 1929-02-07 1929-11-14 Sheet metal heating radiator
US3689972A (en) * 1970-11-19 1972-09-12 Modine Mfg Co Method of fabricating a heat exchanger
GB2078361A (en) * 1980-06-24 1982-01-06 Delanair Ltd Heat exchangers and heat exchanger headers

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN, Band 10, Nr. 189 (M-494)[2245], 3. Juli 1986; & JP-A-61 31 892 (SHOWA ALUM CORP.) 14-02-1986 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2677404A1 (en) * 1991-06-07 1992-12-11 Mtu Muenchen Gmbh DEVICE FOR ASSEMBLING A GAS TURBINE ENGINE WITH A HEAT RECOVERY EXCHANGER.

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BR8900566A (en) 1989-10-10
DE3803947C2 (en) 1990-03-01
ES2025342B3 (en) 1992-03-16
CA1305959C (en) 1992-08-04
JP2678046B2 (en) 1997-11-17
DE3803947A1 (en) 1989-08-24
US4940084A (en) 1990-07-10
EP0328044B1 (en) 1991-08-28
JPH01318891A (en) 1989-12-25

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