EP0354892A1 - 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
EP0354892A1
EP0354892A1 EP89870108A EP89870108A EP0354892A1 EP 0354892 A1 EP0354892 A1 EP 0354892A1 EP 89870108 A EP89870108 A EP 89870108A EP 89870108 A EP89870108 A EP 89870108A EP 0354892 A1 EP0354892 A1 EP 0354892A1
Authority
EP
European Patent Office
Prior art keywords
fabrics
gas
tubes
metal
fluid
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
EP89870108A
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English (en)
French (fr)
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EP0354892B1 (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 present invention relates to a heat exchanger effectively using a well-known physical datum, namely that the metal wire is the best 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 present invention relates to a heat exchanger with metal wires between a gas and a fluid, formed of a set of unitary exchange panels made up of metal fabrics, characterized in that the unitary panel comprises at least two fabrics woven in metallic wires with high thermal conductivity, between which are welded at intervals metallic tubes arranged substantially parallel to each other, in which the fluid circulates, the gas preferably circulating perpendicular to the tubes.
  • the number of fabrics woven into metal wires 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 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 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 the warp threads and the 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 transfer by thermal conductivity between these wires and the tubes, 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 as a function of the characteristics of the fluid circulating in these tubes, of its flow rate and of the allowed pressure drops while respecting a speed such as to provide good heat exchange between the fluid and the wall of the metal tube.
  • the tubes are of a highly conductive material, 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 fixing means, 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 of the unitary panels and of the 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 air streams 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 allows to greatly reduce the floor space occupied.
  • the exchanger 1 consists of 3 unitary panels 2, 3 and 4, separated from each other by spacers 5 and 6.
  • the spacers formed, for example, by a suitable profile of plastic or other materials, have a thickness of a few millimeters.
  • the metal fabrics 7 and 8 of the panel 2 are welded at regular intervals to the neighboring tubes 9 and 10.
  • the metallic fabrics used are obtained by weaving metallic wires, 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 9 and 10 as well as the tubes of the other panels 3 and 4 each have flats 11 and 12.
  • 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 assemblies 13 and 14 each formed of 2 fabrics 15 and 16, 17 and 18, are welded respectively at points 19 and 20, 21 and 22, to tubes 23 and 24.
  • the fabrics are separated from each other by a space of a few millimeters.
  • the vertical axis fan 31 centered in the sheath 30 creates in the star 29, the vacuum necessary for the suction of air through the exchangers.
  • the air circuit for exchanger 26 has been indicated by arrows 32 and 33.
  • the exchangers shown diagrammatically in FIG. 3 can be of any type.
  • the arrangement of the exchangers of FIGS. 1 and 2 can be chosen.
  • the unit heat exchanger used can include from 1 to more than 10 unit panels.
  • an exchanger composed of 6 unitary panels of two fabrics, similar to those described above, gives a heat exchange coefficient close to 2.5 kW per m2 of front surface, and by degree of logarithmic difference in temperatures between gas and fluid, even for a frontal speed of the order of 1 meter per second, with a pressure drop of approximately 3 mm of water column.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
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.
BE8900622A BE1004276A6 (fr) 1989-06-08 1989-06-08 Echangeur de chaleur entre un gaz et un fluide a pouvoir d'echange thermique eleve.
BE8900622 1989-06-08

Publications (2)

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

Family

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Family Applications (1)

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)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0435842A1 (de) * 1989-12-22 1991-07-03 Société Anonyme ECONERGIE Heizverfahren mittels Wärmepumpen
ES2163339A1 (es) * 1998-07-02 2002-01-16 Van Weezel Daniel Campagne Condensador hilado.

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Citations (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
US2601973A (en) * 1949-06-25 1952-07-01 Air Preheater Layered element for heat transfer cores
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

Patent Citations (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
US2601973A (en) * 1949-06-25 1952-07-01 Air Preheater Layered element for heat transfer cores
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

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0435842A1 (de) * 1989-12-22 1991-07-03 Société Anonyme ECONERGIE Heizverfahren mittels Wärmepumpen
ES2163339A1 (es) * 1998-07-02 2002-01-16 Van Weezel Daniel Campagne Condensador hilado.

Also Published As

Publication number Publication date
DE68905402T2 (de) 1993-09-16
EP0354892B1 (de) 1993-03-17
DE68905402D1 (de) 1993-04-22

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