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EP0354892B1 - Wärmeaustauscher zwischen einem Gas und einer Flüssigkeit mit erhöhten thermischen Austauschfähigkeiten - Google Patents

Wärmeaustauscher zwischen einem Gas und einer Flüssigkeit mit erhöhten thermischen Austauschfähigkeiten Download PDF

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Publication number
EP0354892B1
EP0354892B1 EP19890870108 EP89870108A EP0354892B1 EP 0354892 B1 EP0354892 B1 EP 0354892B1 EP 19890870108 EP19890870108 EP 19890870108 EP 89870108 A EP89870108 A EP 89870108A EP 0354892 B1 EP0354892 B1 EP 0354892B1
Authority
EP
European Patent Office
Prior art keywords
gas
tubes
fluid
heat exchanger
grids
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
EP19890870108
Other languages
English (en)
French (fr)
Other versions
EP0354892A1 (de
Inventor
Vincent Thillaye Du Boullay
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.)
SOCIETE ANONYME ECONERGIE
Original Assignee
Econergie SA
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
Priority claimed from BE8800885A external-priority patent/BE1002337A6/fr
Priority claimed from BE8900622A external-priority patent/BE1004276A6/fr
Application filed by Econergie SA filed Critical Econergie SA
Publication of EP0354892A1 publication Critical patent/EP0354892A1/de
Application granted granted Critical
Publication of EP0354892B1 publication Critical patent/EP0354892B1/de
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
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/122—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and being formed of wires

Definitions

  • the invention relates to a heat exchanger according to the preamble of claim 1.
  • a heat exchanger is known according to FR-A-793 344.
  • the present invention effectively uses a well-known physical datum, namely that the metallic wire is the best heat convector between a gas and a solid, since it constitutes almost entirely a leading edge.
  • devices using these methods require air velocities circulating between these plates or between these fins, sufficiently high to obtain a satisfactory exchange coefficient between gases and tubes.
  • the object of the present invention is to economically solve, by a simple technical arrangement, heat exchange problems which are difficult to solve by the use of existing techniques, thanks to the particularly efficient characteristics of exchangers with woven wire cloths.
  • the subject of the present invention is a heat exchanger between a gas and a fluid formed by one or more unitary exchange panels made up of fabrics woven from metal wires with high thermal conductivity, between which metal tubes are arranged at intervals. substantially parallel to each other, in which the fluid circulates, characterized in that the unitary panel comprises two sets of at least two fabrics, the gas preferably flowing perpendicular to the fabrics; the fabrics of the same assembly are spaced between the welding points in contact with the tubes.
  • the number of fabrics woven into metal wires forming the assemblies may include two, three or more fabrics.
  • the unitary panel can thus comprise two sets of 2 or 3 or more fabrics, woven into metallic wires between which metallic tubes are welded at intervals.
  • the number of fabrics to be used per set will be limited to 2 or 3 fabrics and preferably two fabrics for reasons of construction and optimization of a methodical exchange.
  • the fabrics are spaced a few millimeters apart, for example 3 mm.
  • the chosen gas is generally air, which does not exclude the use of other gases or vapors.
  • the fluid circulating in the tubes is a liquid or a gas, and can result from a change of state liquid / gas or gas / liquid, the latter fluids having a very good coefficient of heat exchange with the interior wall of the tube.
  • the fluids used include in particular water, saline or other solutions, solvents, heat transfer liquids, etc.
  • the unitary panel comprises two sets of at least two fabrics of metal wires with high thermal conductivity, of any structure and nature, for example of copper. These wires have a diameter between 0.1 and 3 millimeters, and generally between 0.2 and 2 millimeters. In addition, the diameters of warp threads and weft threads can be different.
  • the size of the mesh of the canvas is the result of a compromise specific to each application, between a dense structure of the fabrics to multiply the leading edges of the wires, and a sufficient opening of the mesh, to reduce to an economic level the pressure drop during the passage of gas through the fabrics.
  • the metal wires of the fabrics perpendicular to the tubes are preferably of a larger diameter than the wires parallel to the tubes.
  • wires are the best convectors; they are suitable for wires parallel to the tubes.
  • wires perpendicular to the tubes must have a sufficient diameter to ensure the transfer by thermal conductivity between these wires and the tubes, of the enthalpy received or emitted by the wires constituting the fabrics.
  • the wires perpendicular to the tubes are designated by warp yarns and the wires parallel to the tubes by weft yarns. It is obvious that a reverse arrangement could be adopted without departing from the scope of the present invention.
  • the contact surfaces between wires are increased by rolling the fabrics, so as to pass from a point contact to a contact of the meniscus type between the two wires.
  • This enlarged contact promotes heat transfer between weft and warp threads, and makes it possible to obtain a higher overall heat exchange coefficient of the unitary panel.
  • This rolling is carried out under a load such that only the contact surfaces between wires are increased, and it does not in any way modify the profile of the wires between the contact surfaces.
  • the diameter of the tubes must be chosen according to the characteristics of the fluid circulating in these tubes, its flow rate and the allowed pressure drops, while respecting a speed such as to provide a good heat exchange between the fluid and the wall of the metal tube. .
  • the tubes are of a material with high thermal conductivity, for example copper, and they are preferably arranged at regular intervals. They preferably have two flats parallel to each other on which the wire cloths are welded. By welding, we also understand any other means of fixing, for example brazing, bonding, etc.
  • the interval between the tubes depends on the diameter of the warp threads and the permissible temperature differences between gas and fluid.
  • the tubes are arranged substantially parallel to one another and spaced 1 to 10 cm apart, the diameter of the warp threads being chosen as a function of this deviation.
  • the tubes are partially flattened by any known method so as to present two parallel flats with one another, intended to ensure an effective connection between fabrics and tubes, both for a satisfactory solidity of the panel, and for a good transfer to the tubes of the enthalpy collected or emitted by the threads of the fabrics.
  • the unitary panels can have very variable dimensions and are generally of rectangular or square section.
  • the exchangers of the claimed type comprise a single panel or are formed by assembly of unitary panels the number of which can even exceed 10, depending on the magnitude of the temperature gradient to be ensured in a methodical exchange against the current between the gas and the circulating fluid. in the tubes.
  • the texture of the fabrics of the successive panels can be different to adapt to the evolution of the heat transfer to be ensured during the passage of the gas through the exchanger.
  • This spacing is generally constant, but it is not excluded to possibly vary it.
  • the gas stream is preferably introduced perpendicularly to the panels by ducts of section generally identical to that of the exchanger; the same arrangement is adopted at the outlet of the exchanger.
  • the collectors or sheets in the case of connections between the ends of the tubes of successive panels, serve as ducts on two of the four sides of the exchanger; the collectors are in direct contact with the fabrics at the end of the tubes.
  • a flexible spacer is mounted between the sheet and the metal fabrics so as to allow the differential expansion of the panels.
  • a deposit or a surface treatment of any type may be applied to the constituent elements of the exchanger formed by unitary panels and collectors.
  • the metal mesh heat exchangers of the claimed type are grouped in a star.
  • the panels of the exchangers are arranged vertically, and the exchangers are assembled in a star around a central air intake duct.
  • the thermal powers to be evacuated can reach several tens of megawatts, which implies the use of large frontal surfaces.
  • the exchangers described above are grouped in pairs around a central duct which unites the veins of air collected between the two faces of the branches of the star.
  • one or more fans installed in the duct above the star create the vacuum necessary for the passage of the air current through metal fabric exchangers of the type claimed.
  • the underside of the star is fully closed as well as the upper part of each branch located around the sheath.
  • the speed of the fan (s) must be adjustable so as to limit the consumption of electricity according to weather conditions.
  • the reverse arrangement with lower chimney allows the enthalpy of the air to be captured by a fluid to be heated.
  • the most important advantage is certainly the maintenance of a high heat exchange coefficient even at low front speed of the gas perpendicular to the wire mesh.
  • This characteristic makes it possible to limit the speed of the gas to a level sufficient to ensure the flow of enthalpy given to the gas (in the case of air coolers) or extracted from the gas (in the case of gas coolers) during its passage through the fabric exchanger. metallic.
  • metal mesh heat exchangers are significantly more compact and lighter than the finned tube heat exchangers usually used in industry, and the star arrangement makes it possible to greatly reduce the floor space occupied.
  • FIGS. 1 and 2 The present invention will be better understood using FIGS. 1 and 2.
  • FIG. 1 represents a unitary panel formed by 2 sets of 2 metallic fabrics between which are welded at intervals, metallic tubes arranged substantially parallel to each other, in which the fluid circulates.
  • Figure 2 shows a plan view of a set of 24 exchangers arranged in pairs in the 12 branches of a star.
  • the unitary panel 1 comprises the assemblies 2 and 3 each formed of 2 metallic fabrics 4 and 5, 6 and 7, which are welded respectively at points 8 and 9, 10 and 11, to the tubes 12 and 13.
  • the two assemblies 2 and 3 are welded at regular intervals to the neighboring tubes 12 and 13.
  • the metallic fabrics used are obtained by weaving metallic threads, for example copper, with a diameter of 0.3 mm in weft and 0.6 mm in warp.
  • the tubes with a diameter of 5 mm are arranged parallel to each other and spaced apart, for example 3 cm.
  • the metal tubes 12 and 13 have flats at the welding points 8 and 9, 10 and 11.
  • the flats were obtained by any known means such as a partial flattening of the tube, or directly in manufacture from a profiled die.
  • the flats of the tubes used in the example presented in FIG. 1 have a width of approximately 3 mm.
  • the fabrics are separated from each other by a space of a few millimeters.
  • the vertical axis fan 20 centered in the sheath 19 creates in the star 18 the vacuum necessary for the suction of air through the exchangers.
  • the air circuit for exchanger 15 has been indicated by arrows 21 and 22.
  • the exchangers shown diagrammatically in FIG. 2 can be of any type.
  • they can be made up of unitary panels 1 of FIG. 1, which are assembled so as to create a staggered arrangement of the metal tubes of the successive panels.
  • the unit heat exchanger used can include from 1 to more than 10 unit panels.

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

Claims (7)

  1. Wärmeaustauscher für den Wärmeaustausch zwischen einem Gas und einem Fluid, aus einer oder mehreren Austausch-Einheitsplatten, die Gewebe aus Drähten mit hoher Wärmeleitfähigkeit umfassen. und zwischen denen in Abständen im wesentlichen parallel zueinander angeordnete Metallrohre angeschweißt sind, in denen das Fluid strömt, dadurch gekennzeichnet, daß die Einheitsplatte zwei Einheiten aus mindestens zwei Geweben umfaßt; und die Gewebe derselben Einheit zwischen den Schweißpunkten auf den Rohren einen gewissen Abstand voneinander aufweisen.
  2. Wärmeaustauscher für den Wärmeaustausch zwischen einem Gas und einem Fluid, gemäß Anspruch 1, dadurch gekennzeichnet, daß die Einheitsplatte zwei Einheiten mit 2 oder 3 Geweben umfaßt.
  3. Wärmeaustauscher für den Wärmeaustausch zwischen einem Gas und einem Fluid, gemäß Anspruch 1 und 2, dadurch gekennzeichnet, daß die Gewebedrähte mit hoher Wärmeleitfähigkeit aus Kupfer sind und einen Durchmesser zwischen 0,1 und 3 mm haben.
  4. Wärmeaustauscher für den Wärmeaustausch zwischen einem Gas und einem Fluid, gemäß Anspruch 1 bis 3, dadurch gekennzeichnet, daß die zu den Rohren senkrechten Drähte der Gewebe einen größeren Durchmesser als die zu den Rohren parallelen Drähte haben.
  5. Wärmeaustauscher für den Wärmeaustausch zwischen einem Gas und einem Fluid, gemäß Anspruch 1 bis 4, dadurch gekennzeichnet, daß die Kontaktflächen zwischen den Drähten durch Walzen der Gewebe vergrößert sind.
  6. Wärmeaustauscher für den Wärmeaustausch zwischen einem Gas und einem Fluid, gemäß Anspruch 1 bis 5, dadurch gekennzeichnet, daß die Metallrohre in gleichmäßigen Abständen angeordnet sind und zwei zueinander parallele, halbflache Schienen aufweisen, auf die die Drahtgewebe aufgeschweißt sind.
  7. Einheit, aus Wärmeaustauschern für den Wärmeaustausch zwischen einem Gas und einem Fluid gemäß Anspruch 1 bis 6, dadurch gekennzeichnet, daß die als Kühltürme verwendeten Wärmeaustauscher in vertikaler Richtung sternförmig um einen Luftansaugkanal herum und unter einem Luftansaugkanal angeordnet sind.
EP19890870108 1988-07-29 1989-07-07 Wärmeaustauscher zwischen einem Gas und einer Flüssigkeit mit erhöhten thermischen Austauschfähigkeiten Expired - Lifetime EP0354892B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
BE8800885 1988-07-29
BE8800885A BE1002337A6 (fr) 1988-07-29 1988-07-29 Echangeur de chaleur entre un gaz et un fluide a pouvoir d'echange thermique eleve.
BE8900622 1989-06-08
BE8900622A BE1004276A6 (fr) 1989-06-08 1989-06-08 Echangeur de chaleur entre un gaz et un fluide a pouvoir d'echange thermique eleve.

Publications (2)

Publication Number Publication Date
EP0354892A1 EP0354892A1 (de) 1990-02-14
EP0354892B1 true EP0354892B1 (de) 1993-03-17

Family

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Application Number Title Priority Date Filing Date
EP19890870108 Expired - Lifetime EP0354892B1 (de) 1988-07-29 1989-07-07 Wärmeaustauscher zwischen einem Gas und einer Flüssigkeit mit erhöhten thermischen Austauschfähigkeiten

Country Status (2)

Country Link
EP (1) EP0354892B1 (de)
DE (1) DE68905402T2 (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE1003595A5 (fr) * 1989-12-22 1992-04-28 Econergie Sa Procede de chauffage par pompes a chaleur.
ES2163339B1 (es) * 1998-07-02 2003-02-16 Van Weezel Daniel-Mau Campagne Condensador hilado.
DE102010034019A1 (de) 2010-08-11 2012-02-16 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Wärmeübertrager, Verfahren zu dessen Herstellung und dessen Verwendung

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR793344A (fr) * 1934-10-24 1936-01-22 échangeur thermique
NL83716C (de) * 1949-06-25
FR2428224A2 (fr) * 1978-06-06 1980-01-04 Martel Catala & Cie Ets Perfectionnements aux faisceaux tubulaires et a leur procede de fabrication
AT379019B (de) * 1981-07-01 1985-11-11 Kuprian Systembau Ges M B H Waermetauscher

Also Published As

Publication number Publication date
DE68905402T2 (de) 1993-09-16
DE68905402D1 (de) 1993-04-22
EP0354892A1 (de) 1990-02-14

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