EP0383173B1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
EP0383173B1
EP0383173B1 EP90102376A EP90102376A EP0383173B1 EP 0383173 B1 EP0383173 B1 EP 0383173B1 EP 90102376 A EP90102376 A EP 90102376A EP 90102376 A EP90102376 A EP 90102376A EP 0383173 B1 EP0383173 B1 EP 0383173B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
points
exchanger according
curved sections
small 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 - Lifetime
Application number
EP90102376A
Other languages
German (de)
English (en)
Other versions
EP0383173A1 (fr
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 GmbH
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 EP0383173A1 publication Critical patent/EP0383173A1/fr
Application granted granted Critical
Publication of EP0383173B1 publication Critical patent/EP0383173B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • 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
    • Y10S165/401—Shell enclosed conduit assembly including tube support or shell-side flow director
    • Y10S165/416—Extending transverse of shell, e.g. fin, baffle
    • Y10S165/423—Bar

Definitions

  • the invention relates to a heat exchanger according to the preamble of claim 1.
  • Such a heat exchanger is known from DE-A-35 43 893; a number of S-shaped profile tubes are attached between a collecting tube and a matrix deflection section.
  • the curvature of the individual profile tubes gives rise to a number of advantages over straight profile tubes.
  • this solution has the disadvantage that the individual expansion compensation of a profile tube only results in a transverse deflection with respect to the collective tube profile surrounding it at those points where the spacers of the maximum deflection points are arranged. This hinders the expansion compensation if it exceeds the play in the spacer.
  • the stringing of curve sections according to the invention results in a complete wave train over the entire length of a profile tube, which enables a controlled buckling of an entire tube or an entire tube collective of a layer in the case of relative expansions due to thermal expansions or due to impact-related expansions or compressions in relation to their external restraint.
  • the profile tubes can thus be controlled in spite of fixations fixed on both sides and a firm connection at the points of the spacers and can only expand and contract in length with slight internal stresses under the effect of temperature differences and gradients without the flow cross sections between adjacent profile tubes being changed significantly. It must be emphasized that the profile tubes are made from one piece, and the individual curve sections only represent curved sections of a profile tube.
  • the considerable advantage of the new shape of the profile tubes is that the spacers can be fixed at the points of their maximum deflection points and the intermediate points without play, whereby the collective of the profile tubes can be firmly supported against vibrations and impact forces at these points.
  • the expansion compensation is then carried out by compressing or stretching the profile tubes to the length of two abutting curve sections, ie between two fixing points each along one entire pipe section occur at least twice. For the same relative expansion there are transverse deflections which are about a factor 3 less than those of known designs.
  • the curve sections have constant radii of curvature, as a result of which the curve sections can be easily manufactured. It is advantageous if all curve sections have the same radius of curvature, which is approximately in the range of 1 to 2 times the length of the curve sections.
  • the distances between the profile tubes which are important for the flow can be kept sufficiently large in this way, even with large temperature differences.
  • the points of minimal distance between two profile tubes occur at the turning points, i.e. at the joints of two oppositely curved curve sections.
  • the curve sections have sinusoidal curves.
  • Two alternative embodiments of a sinusoidal curve are possible.
  • two curve sections together form a complete sine wave, the imaginary angular axis representing the straight-line connection of two fixing points.
  • the fixing points thus correspond to the angle 0 or 2 ⁇ , while the turning points at which two oppositely curved curve sections meet one another correspond to the angle ⁇ / 2.
  • two curve sections together form a half cosine train. That is, the imaginary angular axis is equally spaced parallel to the profile tube tangent at the two fixing points.
  • the two fixing points thus correspond to the angles 0 and ⁇ .
  • a further advantageous embodiment of the invention provides that the profile tubes have an approximately elliptical cross section, the individual curve sections being bent around the semi-axis with the lower bending resistance moment.
  • Such an elliptical cross-section enables an aerodynamically more favorable flow around the individual profile tubes.
  • a profile tube 1 is shown, which is attached by means of two attachment points 2a, 2b to two only partially drawn collecting containers 3a and 3b.
  • one of the two collecting containers 3a, 3b can also be a deflection section of a U-shaped profile tube matrix, for example.
  • a plurality of similar, regularly spaced profile tubes 4 are provided, which together with the profile tube 1 shown form a complete matrix through which a flow medium is conducted, for example, from the collecting container 3a to the collecting container 3b.
  • the fluid flow flowing inside the profile tubes 1, 4 is caused to heat exchange by a fluid flow flowing past in a cross flow, the flow direction of which is designated by 12. Usually, the fluid flow flowing within the profile tubes 1, 4 becomes thereby heats up.
  • the profile tube 1 shown in FIG. 1 essentially consists of eight curve sections 5 of equal length, which adjoin one another at the turning points 6.
  • the curve sections 5 are only differently curved areas of the integrally produced profile tube 1, d. h, there are no large number of curve sections 5 joined together, but a profile tube 1 is bent accordingly into the curve sections.
  • the curve sections 5 are alternately oppositely curved — to the left or to the right — to form a serpentine contour which is superimposed on an essentially S-shaped course.
  • the profile tube 1 has two points of maximum deflection 7a and 7b, between which an intermediate point 8 is provided which is equally distant from both points 7a, 7b.
  • two curve sections 5 are arranged so that the centers of curvature lie on alternately opposite sides of the profile tube 1, so that alternating left and right curvature is present.
  • a total of four curve sections 5 lie between the points of maximum deflection 7a and 7b.
  • the tangents 11 to the profile tube course in the points of maximum deflection 7a, 7b and in the intermediate point 8 are parallel. Furthermore, spacers 9 are provided on the points 7a, 7b and 8, with which the distances to adjacent profile tubes 4 - which are not shown in FIG. 1 for reasons of clarity - are maintained (fixing points). The tangents 11 at the attachment points 2a, 2b are also parallel to the above-mentioned tangents.
  • the curve sections 5 can have constant radii of curvature so that they can be regarded as circular sections, or they can have a sinusoidal shape.
  • the heat exchanger will be exposed to thermal expansions, and the collecting containers 3a, 3b and the spacers 9 can be fixed in place at the same time.
  • the greatest possible approach to adjacent profile tubes 4 occurs at those turning points 6 which are not at the same time fixing points 7a, 7b, 8, while due to the spacers 9 at the latter fixing points there is no change in the Distance between individual profile tubes 1.4 can be observed.
  • the radius of curvature of the curve sections 5 or the amplitude of the sinusoidal curve section 5 must be dimensioned such that the minimum distances are still so large at maximum temperature-induced expansion that the the minimum permissible flow cross-sections between adjacent profile tubes 1.4 must not be undercut.
  • the radius of curvature should be selected in the range of 3-4 cm with a length of the curve sections of 2.5 cm.
  • the profile tubes 1.4 are wider than in the side view according to FIG. 1, which is due to the fact that the profile tubes 1.4 have an approximately elliptical cross-section.
  • the inflow expediently takes place in the direction denoted by 12 and thus in the direction of the major axis of the elliptical profile tubes 1, 4.
  • the spacers 9 are attached along regularly spaced locations, both the profile tubes spaced apart in the direction of the large ellipse axis 1.4 (Fig. 2) and the profile tubes 1.4 (Fig. 1), which are spaced apart in the direction of the small axis, are kept at a defined distance.

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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)

Claims (9)

  1. Echangeur de chaleur à deux collecteurs (3a, 3b) reliés par un grand nombre de petits tubes profilés (1, 4) écartés régulièrement, ces petits tubes (1, 4) étant cintrés en forme de S et en leurs points (7a, 7b) de déflexion maximale et en des points de fixation éloignés de façon équidistante de ces points il y a des organes d'écartement (9) qui constituent des points intermédiaires (8) fixant l'écartement des petits tubes profilés voisins, échangeur caractérisé en ce que les petits tubes profilés (1, 4) ont un nombre de segments de courbes (5) successifs et entre les points de fixation voisins (7a, 8 ; 7b, 8) on a deux segments de courbes (5) à courbure opposée et les tangentes (11) des petits tubes profilés aux points de déflexion maximale (7a, 7b) et aux points intermédiaires (8) sont sensiblement parallèles.
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que les segments de courbes (5) ont des rayons de courbure constants.
  3. Echangeur de chaleur selon la revendication 2, caractérisé en ce que chaque petit tube profilé (1) comporte huit segments de courbes (5), de façon qu'entre les points de déflexion maximale (7a, 7b) et les points de fixation (2a, 2b) sur les collecteurs (3a, 3b), d'une part, ainsi qu'au niveau du point intermédiaire (8), d'autre part, on a chaque fois deux segments de courbes (5) et les tangentes aux petits tubes profilés (11) aux points de fixation (2a, 2b) sur les collecteurs (3a, 3b) sont alignées sur les tangentes (11) aux poins intermédiaires (8) des petits tubes profilés.
  4. Echangeur de chaleur selon la revendication 2 ou 3, caractérisé en ce que le rayon de courbure correspond à 1-2 fois et de préférence à 1,6 fois la longueur du segment courbe.
  5. Echangeur de chaleur selon la revendication 1, caractérisé en ce que les segments de courbes (5) ont un tracé sinusoïdal.
  6. Echangeur de chaleur selon la revendication 5, caractérisé en ce que deux segments de courbes (5) forment par réunion une onde sinusoïdale complète (0...2π).
  7. Echangeur de chaleur selon la revendication 5, caractérisé en ce que la réunion de deux segments courbes (5) forme une demi-onde de courbe cosinus (0...π).
  8. Echangeur de chaleur selon l'une des revendications précédentes, caractérisé e ce que les petits tubes profilés (1) ont une section circulaire.
  9. Echangeur de chaleur selon l'une des revendications 1 à 7, caractérisé en ce que les petits tubes profilés (1) ont une section sensiblement elliptique et le cintrage se fait autour du demi-axe correspondant au couple résistant de cintrage le plus faible.
EP90102376A 1989-02-11 1990-02-07 Echangeur de chaleur Expired - Lifetime EP0383173B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3904140A DE3904140C1 (fr) 1989-02-11 1989-02-11
DE3904140 1989-02-11

Publications (2)

Publication Number Publication Date
EP0383173A1 EP0383173A1 (fr) 1990-08-22
EP0383173B1 true EP0383173B1 (fr) 1993-04-28

Family

ID=6373895

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90102376A Expired - Lifetime EP0383173B1 (fr) 1989-02-11 1990-02-07 Echangeur de chaleur

Country Status (5)

Country Link
US (1) US5058663A (fr)
EP (1) EP0383173B1 (fr)
JP (1) JPH02233991A (fr)
DE (1) DE3904140C1 (fr)
ES (1) ES2040520T3 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6250379B1 (en) * 1994-05-17 2001-06-26 Hde Metallwerk Gmbh High-speed capillary tube heat exchanger
US20040069470A1 (en) * 2002-09-10 2004-04-15 Jacob Gorbulsky Bent-tube heat exchanger
CN103307813B (zh) * 2013-07-05 2016-08-17 丹佛斯微通道换热器（嘉兴）有限公司 换热器及其成形方法
EP4306786A3 (fr) * 2022-07-15 2024-04-03 RTX Corporation Échangeur de chaleur pour aéronef

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB394864A (en) * 1931-10-30 1933-07-06 Bbc Brown Boveri & Cie Improvements in and relating to surface condensers
FR732163A (fr) * 1932-02-23 1932-09-14 Perfectionnement aux condenseurs à surface et appareils analogues, comportant des tubes fixés rigidement à leurs deux extrémités
CH223395A (de) * 1940-10-17 1942-09-15 Oerlikon Maschf Wärmeaustauscher.
US2519084A (en) * 1945-03-13 1950-08-15 Westinghouse Electric Corp Shell and tube heat exchanger having zig-zag tubes
US3042379A (en) * 1959-06-29 1962-07-03 Bell & Gossett Co Condensers
US3212570A (en) * 1963-08-28 1965-10-19 Trane Co Heat exchanger
US3336974A (en) * 1965-05-05 1967-08-22 United Aircraft Corp Serpentine tube boiler
SU399709A1 (ru) * 1967-05-20 1973-10-03 Теплообменный элемент
US3605872A (en) * 1968-08-15 1971-09-20 Wiegand Apparatebau Gmbh Method of causing a liquid to flow in a stream of annular cross section
US3989105A (en) * 1972-02-22 1976-11-02 Georges Trepaud Heat exchanger
US3848430A (en) * 1973-09-13 1974-11-19 Trane Co Absorption refrigeration machine with second stage generator
FR2266866A2 (en) * 1974-04-03 1975-10-31 Trepaud Georges Heat exchanger with tube bundle - having tubes each shaped in wave-form and having supports preventing axial rotation
FR2293684A2 (fr) * 1974-12-05 1976-07-02 Trepaud Georges Echangeur de chaleur a faisceau tubulaire
DE2535075A1 (de) * 1975-08-06 1977-02-24 Lass Geb Friedewald Eva Durchlauf- misch- heiz- oder kuehlaggregat
JPS539322A (en) * 1976-07-12 1978-01-27 Kyowa Hakko Kogyo Co Ltd Analgesics
FR2355191A1 (fr) * 1976-06-16 1978-01-13 Creusot Loire Dispositif de maintien d'une nappe de tubes a l'interieur d'une enceinte
US4573528A (en) * 1981-01-08 1986-03-04 Georges Trepaud Heat exchangers with clusters of straight or corrugated tubes, especially to systems for supporting the tubes at fixed and movable axial levels
FR2540984A1 (fr) * 1983-02-11 1984-08-17 Trepaud Pierre Appareil echangeur de chaleur, notamment generateur de vapeur
DE3329202A1 (de) * 1983-08-12 1985-02-21 MTU Motoren- und Turbinen-Union München GmbH, 8000 München Profilrohr-waermetauscher
DE3401567A1 (de) * 1984-01-18 1985-07-25 MTU Motoren- und Turbinen-Union München GmbH, 8000 München Rohrverteileranordnung eines waermetauschers
DE3543893A1 (de) * 1985-12-12 1987-06-25 Mtu Muenchen Gmbh Waermetauscher

Also Published As

Publication number Publication date
JPH02233991A (ja) 1990-09-17
US5058663A (en) 1991-10-22
ES2040520T3 (es) 1993-10-16
DE3904140C1 (fr) 1990-04-05
EP0383173A1 (fr) 1990-08-22

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