EP0199321B1 - Wärmetauscher - Google Patents

Wärmetauscher Download PDF

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Publication number
EP0199321B1
EP0199321B1 EP86105461A EP86105461A EP0199321B1 EP 0199321 B1 EP0199321 B1 EP 0199321B1 EP 86105461 A EP86105461 A EP 86105461A EP 86105461 A EP86105461 A EP 86105461A EP 0199321 B1 EP0199321 B1 EP 0199321B1
Authority
EP
European Patent Office
Prior art keywords
matrix
heat exchanger
exchanger according
boundary
hot gas
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.)
Expired
Application number
EP86105461A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0199321A1 (de
Inventor
Klaus Dipl.-Ing. Hagemeister
Bernhard Dr. Wöhrl
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
Original Assignee
MTU Motoren und Turbinen Union Muenchen GmbH
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 MTU Motoren und Turbinen Union Muenchen GmbH filed Critical MTU Motoren und Turbinen Union Muenchen GmbH
Publication of EP0199321A1 publication Critical patent/EP0199321A1/de
Application granted granted Critical
Publication of EP0199321B1 publication Critical patent/EP0199321B1/de
Expired legal-status Critical Current

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Classifications

    • 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
    • F28F9/005—Other auxiliary members within casings, e.g. internal filling means or sealing means
    • 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels

Definitions

  • a heat exchanger is known with a central air tube containing separate compressed air ducts, of which a substantially U-shaped heat exchanger tube matrix projects on both sides against a hot gas flow and is designed in a cross-counterflow design.
  • a perforated plate holding the matrix and movably guided along rails of the housing is also intended to form a hot gas bulkhead opposite the entire arcuate matrix deflection area; consequently, in the known case, the entire arcuate matrix deflection area (also referred to as “air deflection chamber”) is excluded from the heat exchange process; in other words, a not inconsiderable part of the available matrix volume for the heat exchange process remains completely unused in favor of expansion compensation measures.
  • the cross-countercurrent matrix which consists essentially of U-shaped matrix tube brackets, is intended to communicate on the one hand with two separate compressed air ducts and, on the other hand, an arcuate one Have deflection area; the deflection area is to be surrounded on the outside by a boundary guide wall of the hot gas housing at a distance; furthermore, in the known case, a shell arranged between a matrix guide wall should at least partially cover the outer deflection area on the hot gas side; in the present known case, however, the shell is to be firmly connected to the adjacent profile tube bends of the matrix, e.g. Example, be soldered so that the spring-anchored shell or anchored via a deformable profile strip on the housing can only extend into the curved boundary baffle together with the outer peripheral matrix tube brackets.
  • a turbine blade is known as a thermally highly stressed component, which - seen from the inside out - consists of a metallic blade core containing cooling channels, a metal felt sheathing the latter and covering the cooling channels, as well as a ceramic infiltrated one and onto the Metal felt applied ceramic thermal barrier coating should be formed as the outermost blade sheath.
  • the primary aim is to ensure the shortest possible heat dissipation to the coolant with a low coolant requirement; due to the interposition of the metal felt, thermal expansion differences between the core (metal) and sheath (ceramic) should also be controllable in the known case in such a way that the sheath is not exposed to impermissibly high material stresses.
  • the invention has for its object to eliminate the disadvantages mentioned and to provide a heat exchanger according to the type mentioned, in which the relative movements of the individual profile tubes with each other and between the latter and the hot gas housing structure surrounding the matrix can be controlled and at the same time in particular the arcuate outer profile edge area of the Matrix can be largely included in the heat exchange process without jeopardizing the homogeneity of the hot gas side outflow area at the matrix outlet.
  • the sealing element according to the invention is thus able to compensate for the relative movements of the individual matrix pipe brackets caused by different temperatures, vibrations or elastic deflections, and at the same time consistently shut off the undesired, previously defined hot gas leakage gap, in such a way that the outer marginal one Matrix deflection area can be included in the heat exchange process in the context of the hot gas main flow direction.
  • the marginal pipe bracket can freely penetrate into the metal felt mat or contract or stretch differently, which is why the resilient support of the mat via the sheet metal on the housing has an extremely advantageous effect.
  • a particularly advantageous embodiment of the invention results from claim 6, for. B. in combination with the design and arrangement of the relevant gas inflow passage according to claim 3; Accordingly, it is possible to allow the hot gas to flow in the transverse matrix direction (cross flow) in the outer matrix deflection area, with the result of an increased degree of heat exchange in the arc area and a homogenization of the pressure, mass flow and speed differences of the hot gas flow that are otherwise present in such known heat exchangers the straight-leg parts of the U-shaped pipe bracket and its pipe bend parts.
  • the heat exchanger illustrated in FIGS. 1 and 2 consists of a first compressed air guide 15 designed as a collecting pipe, a second compressed air guide 16 running essentially parallel to it, also designed as a collecting pipe, and a pipe matrix 1 around which hot gases G flow, which inlet side for the supply of a working medium to be heated, e.g. B. compressed air (arrow D) to the first manifold and for the discharge of the heated compressed air (arrow D ') is connected on the outlet side to the second manifold.
  • a working medium to be heated e.g. B. compressed air (arrow D) to the first manifold and for the discharge of the heated compressed air (arrow D ')
  • the tube matrix 1 consists of U-shaped matrix tube brackets 2, which project laterally from both header tubes (compressed air ducts) 15, 16 and protrude transversely to the hot gas flow direction G, the outer deflection area of which is surrounded by a boundary guide wall 3, which has the wall structure of a housing 12 for the inlet and outlet side the hot gas duct is connected.
  • the tube matrix 1 thus consists of a field of spaced adjacent to one another and - viewed as a cross-section - nested matrix tube brackets 2 arranged essentially uniformly spatially offset from one another (see also FIG. 11).
  • the two pipe guides for the separate supply of compressed air into the pipe matrix or compressed air discharge from the pipe matrix could also be integrated in a common header pipe, as is known from US Pat. No. 3,746,083.
  • the above-mentioned hot gas partial leakage flow A would receive a relatively large excess of speed compared to the hot gas main flow G, which could lead to mixed turbulence when it flows back into the main flow G leaving the matrix and thus also to non-uniformities in the heat exchange process.
  • FIG. 4 represents the distance between the matrix tube bracket 2 and the housing 12 or the boundary guide wall in the cold state and b the relevant required distance in the hot state, which has the disadvantages described above Heat exchange process comes up, but on the other hand must be strictly adhered to, for. B. to prevent abrasive movements of the matrix on the housing or on the boundary guide wall 3, these abrasive movements such. B. may be the cause of operational matrix vibrations (intermittent driving).
  • said distance a (FIG. 4) must be taken into account structurally in order to be able to ensure operationally induced differential expansions of the matrix tube brackets 2 or always to ensure that the latter can be freely stretched relative to the housing or the boundary guide wall 3.
  • Fig. 5 embodies variable relative movement possibilities of three matrix pipe brackets 2, 2 ', 2 "with each other, which are on the one hand in a lateral offset c of the pipe bracket 2, on the other hand in a matrix longitudinal direction away from the boundary guide wall 3 offset d of the tubular bracket 2' and z. B. in a directed against the boundary baffle 3, extending in the matrix longitudinal offset e of the tube bracket 2 ".
  • the hot gas leak gap (hot gas minimum leak gap b- FIG. 3) located between the outer deflection area of the matrix 1 and the adjacent boundary guide wall 3 (FIG. 4) be blocked off directly by at least one flexible, elastic sealing element 17.
  • this sealing element 17 it is first possible to keep the heat losses correspondingly low; in other words, the lossy hot gas leakage component A according to FIG. 1 is avoided, i. that is, the hot gas main flow G experiences only in the U-shaped matrix deflection area a forced by the sealing element 17, laterally swinging flow course G ', which at the same time an unobstructed, almost complete flow of hot gas around the matrix tube bracket, e.g. B. 2, so also in the outer edge region of the matrix 1.
  • Another task of the sealing element 17 is to record the different temperature expansions between the tube bracket 2 and the cooled or insulated housing 12, as previously explained with reference to FIG. 4.
  • the tubular brackets 2, 2 ', 2 "(FIG. 5) experience relative movements with respect to one another as a result of different temperatures, vibrations or elastic deflections.
  • the sealing element 17 is intended to be able to accommodate these different movements, as was also explained previously in FIG. 5 by way of example are.
  • This sealing element 17 (FIG. 3) should be able to partially or essentially enclose the outer deflection region of the matrix 1, as shown, or else completely.
  • the sealing element 17 is designed as a flexible, made of elastic metal felt (metal felt) mat.
  • the metal felt mat adapts to the relative movements of the individual matrix tube brackets 2, 2 ', 2 "of the matrix 1, which are mentioned by way of example in FIG. 5, and is also capable of absorbing or strongly damping vibrations of the matrix tube brackets concerned, ie in the manner of a" Vibration damping pads •.
  • the boundary guide wall 3 can be lined with thermal insulation 18, at least including the associated hot gas upstream and downstream wall structures of the housing 12 on the side facing the matrix 1 or the sealing element 17, in order to keep the housing 12 as cool as possible, and thus not to be exposed to any significant thermal expansions due to hot gas.
  • the sealing element 17, as a metal felt mat is covered on the side facing away from the tubular bracket matrix 1 by means of a thin sheet 19 and is resiliently fastened to the housing 12 in a manner which will be explained in more detail later; the sheet 19 can be arranged opposite the boundary baffle 3 or its insulation 18 while leaving an arcuate gas inflow passage 20 which is blocked off at the downstream end by a section of the sheet 19 bent outwards as a resilient seal 21; this section of the sheet 19 can be fixed to the housing 12 or to the boundary guide wall 3, for. B. by means of a screw connection 22.
  • the dashed contour of the sheet 19 embodies the thermal compensation according to the invention as a result of this spring-elastic seal-shut-off combination.
  • FIG. 9 further clarifies that the gas inflow passage 20 should be designed to branch off part of the hot gases G directed against the matrix 1 in the main flow direction.
  • a foil can also be provided instead of the sheet 19 (FIGS. 9 and 9).
  • individual sections of the sheet 19 or the film can also be connected to the metal felt mat by soldering, folding or in a clamp-like manner.
  • the cover plate 19 or the film with perforations Chen 23, 24, 25 is provided, which communicate with the gas inflow passage 20 and through which (23, 24, 25) the outer deflection area of the matrix 1 can flow around in the transverse direction via the sealing element 17 designed as a metal felt mat.
  • the sealing element 17 designed as a metal felt mat.
  • the arrows F indicate the hot gas flow from the gas inflow passage 20, through the metal felt mat and over the pipe bracket 2, which is in each case at the edge here.
  • the sealing element 17 designed as a metal felt mat has at the contact zone for the directly adjacent tube brackets 2 of the matrix deflection area corresponding to the upstream profile contour according to pre-profiled formations 26.
  • the openings 23, 24, 25 can be dimensioned and distributed locally in such a way that a differential gas pressure which is always present during operation counteracts a load-dependent, sealing contact pressure of the metal felt mat encased by the sheet 19 or a foil the adjacent arc sections of the tubular bracket 2 exercises.
  • the metal felt mat with the perforated outer sheet 19 or the foil for the hot gas offers a resistance which can be adjusted by varying the opening area, the resulting pressure difference exerts a contact pressure in the direction of the pipe bracket.
  • This contact force increases the sealing effect.
  • the contact pressure depends on the load.
  • this heat exchanger e.g. B. in a vehicle gas turbine
  • the sealing effect is increased and the pipe bracket package stabilized due to increased contact pressure as a result of higher differential pressure Ap at higher engine speed.
  • the main direction of hot gas flow is designated by G in FIG. 9, and the hot gas flow portions which split off and flow through the sealing gas element 17 formed as a metal felt mat are designated by F.
  • the separate compressed air ducts 15, 16 are each formed by separate manifolds 29, 30.
  • a single manifold 31 for receiving two separate compressed air ducts 15, 16 may be formed, as is illustrated in a heat exchanger according to FIG. 10, the mode of operation of which with respect to the remaining reference numerals 1, D, D ', G with FIG. 1 is identical.
  • the individual pipe brackets 2 of the matrix 1 should preferably be aerodynamically optimized, lancet or lenticular hollow profile bodies in cross section, each of which has two inner compressed air channels 8 ', 9' separated from one another by a central transverse web 7 '. have a triangular, tapering in the sense of the upstream and downstream ends tapering.
  • the individual profile rows of the matrix tube brackets 2 interlock spatially, ensuring the permissible hot gas blockage.

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)
EP86105461A 1985-04-20 1986-04-21 Wärmetauscher Expired EP0199321B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3514379 1985-04-20
DE19853514379 DE3514379A1 (de) 1985-04-20 1985-04-20 Waermetauscher

Publications (2)

Publication Number Publication Date
EP0199321A1 EP0199321A1 (de) 1986-10-29
EP0199321B1 true EP0199321B1 (de) 1988-06-15

Family

ID=6268730

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86105461A Expired EP0199321B1 (de) 1985-04-20 1986-04-21 Wärmetauscher

Country Status (4)

Country Link
US (1) US4735260A (enrdf_load_stackoverflow)
EP (1) EP0199321B1 (enrdf_load_stackoverflow)
JP (1) JPS61243281A (enrdf_load_stackoverflow)
DE (2) DE3514379A1 (enrdf_load_stackoverflow)

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US4755331A (en) * 1986-12-02 1988-07-05 Evapco, Inc. Evaporative heat exchanger with elliptical tube coil assembly
DE3642506A1 (de) * 1986-12-12 1988-06-23 Mtu Muenchen Gmbh Gasturbinenanlage
DE3726058A1 (de) * 1987-08-06 1989-02-16 Mtu Muenchen Gmbh Waermetauscher fuer gase stark unterschiedlicher temperaturen, insbesondere in kreuz-gegenstrom-bauweise
US4874041A (en) * 1987-10-19 1989-10-17 Combustion Engineering, Inc. Bar support shim and method
DE3935960C2 (de) * 1989-10-27 1994-06-23 Mtu Muenchen Gmbh Einrichtung zur abdichtenden Überbrückung eines Spaltes zwischen zwei in drei Raumrichtungen verschiebbaren Bauteilen
DE4118777C2 (de) * 1991-06-07 2002-04-18 Mtu Aero Engines Gmbh Gasturbinentriebwerk mit Wärmetauscher
DE19533902C2 (de) * 1995-09-13 1999-12-09 Metallgesellschaft Ag Wärme- und Korrosionsschutz der inneren Gefäßwand eines Wärmetauschers
DE19905429A1 (de) * 1999-02-10 2000-08-17 Eisenmann Kg Maschbau Reaktor zur Durchführung einer katalytischen, mit einer Wärmetönung verbundenen Reaktion an Substanzen, die in einer Gasströmung enthalten sind
US6474408B1 (en) 2000-08-31 2002-11-05 Honeywell International Inc. Heat exchanger with bypass seal allowing differential thermal expansion
US6465110B1 (en) * 2000-10-10 2002-10-15 Material Sciences Corporation Metal felt laminate structures
US6918598B2 (en) * 2002-04-02 2005-07-19 Honeywell International, Inc. Hot air seal
US6974634B2 (en) * 2003-11-05 2005-12-13 Material Sciences Corporation Metal felt laminates
WO2007009640A1 (de) * 2005-07-22 2007-01-25 Linde Aktiengesellschaft Gewickelter wärmetauscher mit antidröhnwänden
CN101400959B (zh) * 2006-03-16 2010-09-29 贝洱两合公司 用于汽车的热交换器
EP1936311B1 (de) * 2006-12-23 2013-10-02 Joachim Schult Kompaktplattenwärmeübertrager
JP2009002239A (ja) * 2007-06-21 2009-01-08 T Rad Co Ltd Ｅｇｒクーラ
BE1017737A3 (nl) * 2007-08-24 2009-05-05 Atlas Copco Airpower Nv Warmtewisselaar en afdekplaat daarbij toegepast.
US20110277473A1 (en) * 2010-05-14 2011-11-17 Geoffrey Courtright Thermal Energy Transfer System
EP2660530B1 (en) * 2010-12-27 2017-08-30 Rinnai Corporation Latent heat exchanger and hot water supply device
US9541197B2 (en) 2011-06-01 2017-01-10 General Electric Company Seal system and method of manufacture
DE102011080474A1 (de) 2011-08-05 2013-02-07 Behr Gmbh & Co. Kg Wärmetauscheranordnung
DE102012204121A1 (de) * 2012-03-15 2013-09-19 Mahle International Gmbh Ladeluftkühleinrichtung
DE102013201465A1 (de) * 2013-01-30 2014-07-31 Eberspächer Exhaust Technology GmbH & Co. KG Wärmetauscher einer Brennkraftmaschine
CN107003089B (zh) * 2014-10-03 2018-12-07 达纳加拿大公司 具有自保持旁通密封的换热器
US10184727B2 (en) 2016-05-16 2019-01-22 Hamilton Sundstrand Corporation Nested loop heat exchanger
RU2647942C1 (ru) * 2017-05-05 2018-03-21 Виталий Григорьевич Барон Теплообменный аппарат

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Also Published As

Publication number Publication date
JPH037871B2 (enrdf_load_stackoverflow) 1991-02-04
JPS61243281A (ja) 1986-10-29
US4735260A (en) 1988-04-05
DE3514379A1 (de) 1986-10-23
EP0199321A1 (de) 1986-10-29
DE3660324D1 (en) 1988-07-21
DE3514379C2 (enrdf_load_stackoverflow) 1988-11-17

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