EP0228581B1 - Wärmetauscher - Google Patents

Wärmetauscher Download PDF

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Publication number
EP0228581B1
EP0228581B1 EP86116618A EP86116618A EP0228581B1 EP 0228581 B1 EP0228581 B1 EP 0228581B1 EP 86116618 A EP86116618 A EP 86116618A EP 86116618 A EP86116618 A EP 86116618A EP 0228581 B1 EP0228581 B1 EP 0228581B1
Authority
EP
European Patent Office
Prior art keywords
deflection
heat exchanger
exchanger according
plates
profiled
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
EP86116618A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0228581A1 (de
Inventor
Klaus Hagemeister
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 EP0228581A1 publication Critical patent/EP0228581A1/de
Application granted granted Critical
Publication of EP0228581B1 publication Critical patent/EP0228581B1/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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • 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
    • F28D7/08—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 otherwise bent, e.g. in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements
    • 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
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/355—Heat exchange having separate flow passage for two distinct fluids
    • Y10S165/40—Shell enclosed conduit assembly
    • Y10S165/427—Manifold for tube-side fluid, i.e. parallel
    • Y10S165/436—Bent conduit assemblies

Definitions

  • a heat exchanger known from US-A-2,819,883 shows that it is known per se to want to design the overall matrix in the form of a semicircular tube which is embedded between two plates and ensures deflection of a fluid.
  • the priority is to create an operationally stable pressure welding connection along the outer plate edges.
  • the invention is based on the object of specifying a heat exchanger according to the preamble of patent claim 1, which has a comparatively high degree of heat exchange, in particular with regard to the normally critical arc or deflection area of the matrix, and at the same time, in particular with regard to expected vibration and shock loads, a reliable operation Bracket and support of the profile tube ends enables.
  • the outer deflection section of the matrix of the profile tube heat exchanger is formed from deflection chambers embedded between plates, in which the fluid (compressed air) emerging from the orthogonally outward profile tubes of a tube layer or row is collected and with the orthogonal mixing and heat exchange internally directed profile tube layer or row is supplied.
  • the spacers and / or other shaped bodies or shapes applied along the inner chamber wall can be designed as aerodynamic baffles to increase the degree of heat exchange.
  • the plates do not have to be smooth-walled, but can e.g. B. be wave-shaped or relief-like, so that they are able to respond to thermal deformations and distortions largely soft and stable.
  • these corrugations and relief structures can also be designed to improve the heat transfer and thus to increase the degree of heat exchange.
  • the contours of the plates can be correlated with one another while maintaining the chamber-side wall spacing as well as the mutual hot gas-side wall spacing.
  • Fig. 1 illustrates a cross-counterflow design tubular heat exchanger; this has two manifolds 1, 2 arranged parallel to one another.
  • a profile tube matrix projecting laterally on both sides from the collecting lines 1, 2 is designated by 3.
  • the outer deflection section 4 is designed as a plate heat exchanger which will be explained in more detail later.
  • the profile tube matrix 3 shown schematically in FIG. 1 protrudes transversely from the two manifolds 1, 2 against a main hot gas flow H.
  • compressed air D to be preheated flows into the manifold 1 on one side, is fed from there to the relevant rows of profile tubes 8 of the upper matrix block (D,), then deflected via the compressed air deflection chambers 5 contained in the outer deflection section 4 (D 2 ), so that it can now flow in the opposite flow direction into the lower matrix block containing the relevant profile tube rows 9 (D 3 ), from which it can then flow out into the lower manifold 2 in the heated state, in order to then finally a suitable consumer, e.g. B. the combustion chamber of a gas turbine engine to be supplied (D 4 ).
  • a suitable consumer e.g. B. the combustion chamber of a gas turbine engine to be supplied (D 4 ).
  • the outer deflection section 4 protrudes against a lateral housing wall 10 which supports the guiding of hot gas portions H 'in the latter (4).
  • the relevant plates 6, 7 are along their outer surfaces - see also z. B. Figs. 3 and 4 - flows around from the hot gas portions H '.
  • FIG. 1 there are only relatively large spacing gaps A for the hot gas flow H 'between the plates 6, 7, which are shown here relatively large.
  • the entire outer deflection section 4 of the matrix 3 can also be included in a targeted, homogeneous heat exchange process which provides the required heat exchange surfaces.
  • the contours K, K '(FIG. 1) characterize the U-shaped matrix arch end region made of individual profile tubes which is customary in the context of the prior art.
  • FIG. 1 it is assumed that the profile tube matrix sections shown broken off in FIG. 1, right, can of course be connected to the left according to a matrix deflection section according to the invention as a plate concept along with relevant housing sheathing according to FIG. 1.
  • the adjacent housing wall 10 ′ is curved.
  • brush seals 14, 15 are designed to compensate for movement and are arranged on the housing wall 10 '. The bristles of the brush seals 14, 15 always nestle tightly against the relevant end gaps (A) for the hot gas (FIG.
  • FIG. 4 explains in the way of the cut-open plate-chamber section the form-fitting and fluid-tight gripping possibility provided from the local plate bulges 21, 22 and - formation of the profile tube rows 8 and 9 of the matrix 3 that open locally into the relevant compressed-air deflection chamber 5.
  • FIG. 5 embodies a deflection chamber configuration in which spacers designed as deflection aids primarily define the chamber throughflow cross section at discrete locations between two adjacent plates 6, 7 (FIG. 1, 3 or 4), e.g. B. pin 23 or baffles 24 or straight guide elements 25 are provided.
  • FIG. 6 a flow deflection that is as homogeneous as possible, with the primary avoidance of a pronounced separation zone in the critical inner deflection area already mentioned in FIG. 5 - between the two rows of profile pipes 8, 9 in the compressed air deflection chamber - is sought; by means of appropriate plate contouring, e.g. B.
  • the compressed air deflection chamber - seen from left to right from the inlet to the outlet side - should be curved in such a curved manner that they are from a first substantially continuous inwardly curved chamber portion T, of, downstream of an inner Umlenkbogenendes U, expands greater on a side bulged chamber part T cross-section, the bulged chamber portion T of is then to the Druckbuchumlenkhunt spilling out on an inwardly retracted KammerteiiT a , whose cross-section on the outlet side is essentially identical to the cross-section on the inflow side of the profile row 8 in T.
  • the subject matter of the invention is not limited to designing all deflection aids or guide plates or aerodynamic baffles at the same time as spacers; it can therefore be provided only partially radially protruding into the compressed air deflection chamber, applied to one or both plates 6, 7 or sheet metal forms as aerodynamic baffles to increase the degree of heat exchange and as deflection aids.
  • the plates 6, 7 forming the deflection chambers 5 can be equipped on the hot gas and / or compressed air side by means of thermal deformations to compensate and / or to increase the degree of heat exchange by contouring.
  • the contours in question should be designed to be correlated with one another while maintaining the chamber-side wall spacing (e.g. chamber 5, FIG. 4) and the hot gas flow-through wall or plate spacing gap A (FIG. 1).
  • a further design of the heat exchanger includes the possibility of combining corrugated configurations according to FIG. 7 or 8 with the deflection chamber concept according to FIG. 5 or z.
  • 9 embodies a concept in which a plurality of channel-shaped deflection chambers which are fluidically separated from one another are arranged between two plates 6, 7 of the matrix deflection section 4; the number of channel-shaped deflection chambers is matched to the number of tubes of a matrix profile row 8 or 9 opening into it; 9, the channel-shaped deflection chambers are formed between mutual half-profile formations 28, 29 of the two adjacent plates 6, 7 in each case.
  • B. provide two fluidically separated channel-shaped deflection chambers and z. B. to open two tubes of a row of matrix tubes in each deflection chamber.
  • channel-shaped deflection chambers communicating with one another in a fluidic manner can also be provided.
  • FIG. 10 illustrates a profile which is advantageously usable in a further embodiment and has a lenticular or lancet-shaped hollow profile in cross section, that is to say an aerodynamically optimized profile which tapered in the direction of the hot gas flow H upstream and downstream on the flow side for the respective profile tube rows 8 and 9 of the matrix 3 (FIG . 1).
  • the lancet tube with its periodically changing curve shape is pushed far less from its position.
  • the leading and trailing edges also experience different thermal longitudinal expansions, following the law of the curve shape, they are homologous to one another in a distortion state that twists the lancet-shaped pipe cross sections. Only slight thermal stresses are built up, so that the profile tube remains essentially in the plane of its curve and hardly bends in the direction of the higher temperature.

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)
EP86116618A 1985-12-12 1986-11-29 Wärmetauscher Expired EP0228581B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3543893 1985-12-12
DE19853543893 DE3543893A1 (de) 1985-12-12 1985-12-12 Waermetauscher

Publications (2)

Publication Number Publication Date
EP0228581A1 EP0228581A1 (de) 1987-07-15
EP0228581B1 true EP0228581B1 (de) 1989-05-03

Family

ID=6288254

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86116618A Expired EP0228581B1 (de) 1985-12-12 1986-11-29 Wärmetauscher

Country Status (4)

Country Link
US (1) US4809774A (enrdf_load_stackoverflow)
EP (1) EP0228581B1 (enrdf_load_stackoverflow)
JP (1) JPH0697144B2 (enrdf_load_stackoverflow)
DE (1) DE3543893A1 (enrdf_load_stackoverflow)

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3735846A1 (de) * 1987-10-23 1989-05-03 Mtu Muenchen Gmbh Verfahren zur herstellung einer rohrbodenstruktur eines waermetauschers
DE3803947A1 (de) * 1988-02-10 1989-08-24 Mtu Muenchen Gmbh Waermetauscher
DE3803948A1 (de) * 1988-02-10 1989-08-24 Mtu Muenchen Gmbh Waermetauscher
DE3840460A1 (de) * 1988-12-01 1990-06-07 Mtu Muenchen Gmbh Waermetauscher
DE3904140C1 (enrdf_load_stackoverflow) * 1989-02-11 1990-04-05 Mtu Muenchen Gmbh
DE3914774A1 (de) * 1989-05-05 1990-11-08 Mtu Muenchen Gmbh Waermetauscher
DE4029010C1 (enrdf_load_stackoverflow) * 1990-09-13 1992-01-16 Mtu Muenchen Gmbh
DE4139104C1 (enrdf_load_stackoverflow) * 1991-11-28 1993-05-27 Mtu Muenchen Gmbh
US5309637A (en) * 1992-10-13 1994-05-10 Rockwell International Corporation Method of manufacturing a micro-passage plate fin heat exchanger
DE4315256A1 (de) * 1993-05-07 1994-11-10 Mtu Muenchen Gmbh Einrichtung zur Verteilung sowie Zu- und Abführung eines Kühlmittels an einer Wand eines Turbo-, insbesondere Turbo-Staustrahltriebwerks
JP4574783B2 (ja) * 2000-03-07 2010-11-04 株式会社豊田自動織機 水素吸蔵合金タンク
FI113695B (fi) * 2001-10-09 2004-05-31 Vahterus Oy Hitsattu levyrakenteinen lämmönvaihdin
JP4868354B2 (ja) * 2006-02-27 2012-02-01 三洋電機株式会社 冷凍サイクル装置
CN101874192B (zh) * 2007-07-23 2012-04-18 东京滤器株式会社 板层积式热交换器
DE102010019241A1 (de) * 2010-05-03 2011-11-03 Benteler Automobiltechnik Gmbh Verfahren zur Herstellung eines Wärmetauscherrohres und Wärmetauscher
GB201120008D0 (en) * 2011-11-21 2012-01-04 Rolls Royce Plc Heat exchanger
JP6055232B2 (ja) * 2012-08-10 2016-12-27 株式会社Uacj 冷却プレートおよび冷却装置
KR102175003B1 (ko) 2012-10-16 2020-11-05 더 아벨 파운데이션, 인크. 매니폴드를 포함한 열교환기
US10314315B2 (en) * 2015-02-03 2019-06-11 Lbc Bakery Equipment, Inc. Convection oven with linear counter-flow heat exchanger
US11092384B2 (en) * 2016-01-14 2021-08-17 Hamilton Sundstrand Corporation Thermal stress relief for heat sinks
CN105744805A (zh) * 2016-04-15 2016-07-06 周哲明 一种多通道组合水冷板
EP4306786A3 (en) * 2022-07-15 2024-04-03 RTX Corporation Aircraft heat exchanger

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11661A (en) * 1854-09-12 Surface-condenser for marine engines
US1782380A (en) * 1927-04-23 1930-11-18 Bell & Gossett Co Unrestricted-return water heater
FR656643A (fr) * 1928-06-29 1929-05-10 Aéro-économiseur à tuyaux
US1953302A (en) * 1932-05-25 1934-04-03 William D Johnston Heat conserver
GB537421A (en) * 1938-11-30 1941-06-23 Cherry Burrell Corp Improvements in or relating to heat exchange devices and method of making the same
US2819883A (en) * 1954-08-25 1958-01-14 Metal Specialty Company Pressure-welded tubing turn
US3112793A (en) * 1960-03-04 1963-12-03 Ind Co Kleinewefers Konst Pipe recuperator
DE1601114A1 (de) * 1967-03-04 1970-05-21 Piero Pasqualini Herstellungs- und Montagesystem fuer Sammlerkoepfe von Gegenstromwasserkondensatoren und mit diesem System hergestellte Erzeugnisse
US3601186A (en) * 1970-04-17 1971-08-24 Clay D Smith Modular header systems
JPS4824412B1 (enrdf_load_stackoverflow) * 1970-07-16 1973-07-20
SE374942B (enrdf_load_stackoverflow) * 1971-11-04 1975-03-24 Motoren Werke Mannheim Ag
US4202405A (en) * 1972-09-25 1980-05-13 Hudson Products Corporation Air cooled condenser
CA1117520A (en) * 1980-06-27 1982-02-02 Bozo Dragojevic Heat exchange assembly
DE3242845C2 (de) * 1982-11-19 1986-03-20 MTU Motoren- und Turbinen-Union München GmbH, 8000 München Wärmetauscher für Gase stark unterschiedlicher Temperaturen

Also Published As

Publication number Publication date
DE3543893A1 (de) 1987-06-25
JPH0697144B2 (ja) 1994-11-30
DE3543893C2 (enrdf_load_stackoverflow) 1988-01-28
JPS62142989A (ja) 1987-06-26
US4809774A (en) 1989-03-07
EP0228581A1 (de) 1987-07-15

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