EP0738862B1 - Wärmetauscher mit gelöteten Platten - Google Patents

Wärmetauscher mit gelöteten Platten Download PDF

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Publication number
EP0738862B1
EP0738862B1 EP96400764A EP96400764A EP0738862B1 EP 0738862 B1 EP0738862 B1 EP 0738862B1 EP 96400764 A EP96400764 A EP 96400764A EP 96400764 A EP96400764 A EP 96400764A EP 0738862 B1 EP0738862 B1 EP 0738862B1
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EP
European Patent Office
Prior art keywords
heat exchanger
plates
passage
exchanger according
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.)
Expired - Lifetime
Application number
EP96400764A
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English (en)
French (fr)
Other versions
EP0738862A1 (de
Inventor
Jean-Yves Lehman
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.)
Air Liquide SA
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
Original Assignee
Air Liquide SA
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
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 Air Liquide SA, LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude filed Critical Air Liquide SA
Publication of EP0738862A1 publication Critical patent/EP0738862A1/de
Application granted granted Critical
Publication of EP0738862B1 publication Critical patent/EP0738862B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J5/00—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants
    • F25J5/002—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger
    • F25J5/005—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger in a reboiler-condenser, e.g. within a column
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J5/00—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants
    • F25J5/002—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0062—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements
    • F28D9/0068—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements with means for changing flow direction of one heat exchange medium, e.g. using deflecting zones
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2270/00—Refrigeration techniques used
    • F25J2270/12—External refrigeration with liquid vaporising loop
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2290/00—Other details not covered by groups F25J2200/00 - F25J2280/00
    • F25J2290/32—Details on header or distribution passages of heat exchangers, e.g. of reboiler-condenser or plate heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2290/00—Other details not covered by groups F25J2200/00 - F25J2280/00
    • F25J2290/42—Modularity, pre-fabrication of modules, assembling and erection, horizontal layout, i.e. plot plan, and vertical arrangement of parts of the cryogenic unit, e.g. of the cold box
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0033—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for cryogenic applications
    • 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
    • Y10S62/00—Refrigeration
    • Y10S62/902—Apparatus
    • Y10S62/903—Heat exchange structure

Definitions

  • the present invention relates to a brazed plate heat exchanger, of the type described in the preamble of claim 1 (see for example FR-A-2 154 352).
  • Heat exchangers of this type allow perform gas condensation and / or vaporization liquids, by circulating in passages adjacent to the two-phase fluid circulation passages an auxiliary refrigerant respectively circus.
  • the two phases to be separated are sent in a free volume associated with the exchanger but distinct from the structure thereof.
  • the invention aims to ensure the phase separation by the structure of the exchanger itself, in order to simplify the realization of the whole of the device.
  • the subject of the invention is a heat exchanger of the aforementioned type, characterized by the characterizing part of claim 1.
  • the heat exchanger according to the invention may include one or more of the characteristics of claims 2 to 11.
  • the heat exchanger 1 shown in Figures 1 and 2 is of the brazed plate type. He understands essentially a parallelepipedic body made up a stack of rectangular metal plates 2 separated by spacer waves 3.
  • the latter may in particular be perforated corrugated sheets, as shown in Figure 2, or alternatively corrugated sheets with punctures on their sides waves, called “serrated waves”.
  • the dimensions of plates 2 can reach for example 6 m x 2 m.
  • the plates 2 define between them a large number of generally flat passages. These passages, in the example shown, are divided into two alternating groups: first passages 4 for upward circulation of a two-phase fluid F during vaporization, and second passages 5 for downward circulation of a circulating fluid f .
  • the two end plates extend to the high level N1.
  • the passages 4 and 5 are delimited below and on each side by closing bars which leave free rows of fluid inlet / outlet windows, which are capped by inlet boxes / outlet of generally semi-cylindrical shape.
  • a lower box 6 for fluid inlet F there is provided a side box 7 for fluid inlet f , and a side box 8 for fluid outlet f .
  • Each passage 5 is delimited upwards by an upper closing bar 9 inclined from the top point of the corresponding inlet window for the fluid f .
  • a free volume 10 is defined above this bar 9, in each passage 5, between the plates 2A and 2B which frame the latter.
  • each box 6 to 8 in each corresponding passage, an input / output distributor constituted by a set of waves some of which are oriented obliquely.
  • a distributor which is a fluid inlet distributor F in the passages 4 and a lateral fluid outlet distributor f in the passages 5.
  • a lateral inlet distributor 11 for the fluid f is located just below each upper bar 9.
  • the exchanger is completed by an upper dome 12, conventionally made from four quarter-cylinder sheets welded together at their intersections, and welded by their lower edges the along the upper edge of the two extreme 2A plates along along the other two top edges of the exchanger. These two other edges are, as we includes, consisting of upper end sections 2A plates and side closing bars.
  • a outlet 13 of the vapor phase of the fluid F is soldered to the top of the dome 12.
  • the fluid F supplied with source, in liquid form, in each passage 4 via the box 6, gradually vaporizes. He arrives at the state biphasic at level N2, where the passage section which is offered suddenly increases, substantially double. The speed of the fluid therefore decreases suddenly, which causes the liquid phase to separate, which falls by gravity.
  • the two-phase current fast going up in passage 4 results in that the liquid does not descend in this passage, but collects in cavity 10 which surmounts the bar upper 9 of the associated passage 5.
  • This bar 9 being tilted, the liquid descends along the bar and, at through liquid outlet windows provided just above the lower end of this bar, falls in a manifold 15 which covers these windows with exit.
  • the vapor phase F V of the fluid F collects in the dome 12 and is evacuated via the tube 13.
  • the increase in cross section of the passages 4 is obtained from as follows: all plates 2 are extended up to high level N1 and between levels N1 and N2, all plates have openings 16, with the exception of course of the two extreme plates.
  • the stack of plates 2 form a continuous space, which substantially doubles the section offered to the ascending two-phase fluid. Given the speed of this fluid in the passages 4, the liquid drops only in the regions above bars 9, and, by runoff, it collects in cavities 10, before being evacuated laterally as before.
  • FIG. 4 schematically represents a variant of a heat exchanger which applies to the structure of FIG. 2 as well as to that of FIG. 3, since it only relates to the means for evacuating the vapor F V.
  • the dome 12 is deleted, and the plates 2A (in the case of Figure 2) or 2 (in that of Figure 3) are extended upwards beyond the level N1.
  • this level N1 in each phase separation passage, that is to say in each of the passages delimited between the plates 2A ( Figure 2) or 2 ( Figure 3), there is an outlet distributor. 18 adapted to bring the vapor F V towards the middle zone of the passage.
  • the distributor 18 comprises two oblique waves 19, 20 which converge upwards to a median vertical wave 21 of triangular shape, having its point at the bottom. This wave 21 opens onto an upper outlet window, and all of the outlet windows are capped by an outlet box 22 of generally semi-cylindrical shape, from which the pipe 13 starts.
  • Figures 5 and 6 illustrate a possibility of adaptation of the invention to the case of a descending two-phase fluid F, for example during partial vaporization against the flow of an ascending circulating auxiliary fluid F ( Figure 6).
  • Each passage 4 is closed, at its end lower, by a lower closing bar 23 of which the upper side is sloping.
  • An intermediate plate 24 divides passage 4 into two sub-passages 25, 26 to from a space spaced from the bar 23.
  • the underpass 25 is free, while subpass 26 is closed, at the upper edge of the plate 24, by half a closing bar 27.
  • the sub-passage 26 contains a distributor of outlet 28, consisting ( Figure 5) of an oblique wave 29 and of a horizontal wave 30, the latter opening into a side half-window 31.
  • the set of half-windows is capped by an outlet box 32.
  • the two-phase fluid F is accelerated when it arrives in the sub-passage 25, then it suddenly slows down when it exceeds the lower edge of the plate 24.
  • the vapor phase F V rises in the sub-passage 26, then is evacuated via the distributor 28 and the box 32, while the liquid phase F L trickles and collects on the lower bar 23, then is discharged laterally via an outlet box 33.
  • FIG. 7 illustrates a general diagram for the purification of a gas F under pressure in a heat exchanger 1 according to the invention, by condensation of its heavy impurities.
  • the gas F circulates from bottom to top in the passages 4 of the exchanger.
  • a condensed fraction F L1 , F L2 , F L3 is withdrawn, expanded in an expansion valve 34 and returned against the current, that is to say from top to bottom, at about the same level. of the exchanger, in passages 5, to produce cold.
  • the purified gas F is returned against the current in passages 5 to recover the sensible heat.
  • Each passage 4 is subdivided into its thickness, over most of its height, by plates intermediaries 35 spaced from each other.
  • the plaque 35 lower part of two half closing bars lower 36 and, on one side (the right side in Figure 8), the half-passage which it delimits is closed by a upper closing half-bar 37, located one small distance below the top edge of the plate 35.
  • each intermediate plate 35 includes, same side, a lower half closing bar 36 and an upper closing half-bar 37, arranged analogously.
  • each passage 4 has an active part 38 (its left part in FIG. 8), for the upward circulation of fluid F, of which the thickness is half (or, alternatively, a fraction different) of the distance between the two plates 2 which delimit this passage, while it is not equal at this distance only in the regions 39 which separate the intermediate plates 35.
  • the fluid F introduced at the base of passage 4 via a distributor 40, travels at relatively high speed in zone 38 lower and then suddenly slows down in the first zone 39, then is accelerated in the second zone 38, and and so on.
  • the liquid phases successive, corresponding to increasingly impurities lighter, separate in zones 39. Due to the ascending speed of the fluid in zones 38, the liquids flow into the calm part of zones 39, that is to say in their right half, and come together in the space 41 delimited above the bars 37. These can, as before, be tilted to facilitate the lateral evacuation of liquids.
  • the spaces 42 included between each pair of half bars 36, 37 may be inactive, or else be used for the circulation of suitable fluids.

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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 (11)

  1. Wärmetauscher mit verlöteten Platten, des Typs, der einen Stapel von Platten (2, 2A, 2B), die durch Wellen-Abstandshalter (3, 14; 17; 25, 26) getrennt sind, und eine Gesamtheit von Durchlässen (4, 5) mit im allgemeinen flacher Form, die durch diese Platten begrenzt sind, d.h. eine Reihe erster Durchlässe (4) für die Zirkulation eines zweiphasigen Fluids, wovon jeder an wenigstens einen zweiten Durchlaß (5) für die Zirkulation eines anderen Wärmemittel- oder Kältemittel-Fluids angrenzt, enthält, dadurch gekennzeichnet, daß wenigstens die ersten Durchlässe (4) an wenigstens einer Stelle auf ihrer Länge eine Durchlaßquerschnittsvergrößerung sowie Mittel (9, 10; 26, 28; 37, 41) zum Aufnehmen und Entleeren einer der beiden Phasen des zweiphasigen Fluids enthält.
  2. Wärmetauscher nach Anspruch 1 mit aufsteigender Zirkulation des zweiphasigen Fluids, dadurch gekennzeichnet, daß eine (2A) der Platten (2A, 2B), die den ersten Durchlaß (4) begrenzen, und die gegenüberliegende Platte (2A) eines benachbarten zweiten Durchlasses (5) für die Zirkulation des anderen Fluids nach oben über das obere Ende der gemeinsamen Platte (2B) dieser beiden Durchlässe (4, 5), die über den oberen Verschlußstab (9) des benachbarten zweiten Durchlasses übersteht, verlängert sind.
  3. Wärmetauscher nach Anspruch 1 mit aufsteigender Zirkulation des zweiphasigen Fluids, in dem die zweiten Durchlässe (5) nach oben durch obere Verschlußstäbe (9) begrenzt sind, dadurch gekennzeichnet, daß alle Platten (2) nach oben über die oberen Verschlußstäbe (9) verlängert sind und daß wenigstens bestimmte der Platten mit Ausnahme der äußeren Platten mit Öffnungen (16) oberhalb der Höhe dieser Verschlußstäbe versehen sind.
  4. Wärmetauscher nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß er über den Platten (2; 2A; 2) eine obere Kuppel (12) für die Aufnahme der gasförmigen Phase des zweiphasigen Fluids aufweist.
  5. Wärmetauscher nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß er an seinem oberen Ende in jedem Zwischenplattenintervall einen Dampfsammler-Ausgangsverteiler (18), der in ein Ausgangsfenster mündet, sowie einen Dampfsammelbehälter (22), der alle diese Ausgangsfenster bedeckt, aufweist.
  6. Wärmetauscher nach irgendeinem der Ansprüche 2 bis 5, dadurch gekennzeichnet, daß die oberen Verschlußstäbe (9) geneigt sind.
  7. Wärmetauscher nach Anspruch 1, dadurch gekennzeichnet, daß der erste Durchlaß (4) vor der Stelle eine Zwischenplatte (24; 35) enthält, die hier den freien Querschnitt bis zu der Stelle verengt und die mit einem Halbverschlußstab (27; 37) einen Hohlraum (26; 41) für die Aufnahme einer der beiden Phasen des zweiphasigen Fluids bildet.
  8. Wärmetauscher nach Anspruch 7 mit absteigender Zirkulation des zweiphasigen Fluids, dadurch gekennzeichnet, daß der Hohlraum (26) oben durch den Halbverschlußstab (27) begrenzt ist und unterhalb dieser einen Ausgangsverteiler (28) enthält, der seitlich in ein Dampfaustrittsfenster mündet.
  9. Wärmetauscher nach Anspruch 8, dadurch gekennzeichnet, daß die Stelle dem unteren Ende des ersten Durchlasses (4) benachbart ist und daß dieser Durchlaß an seiner Grundfläche durch einen unteren Verschlußstab (23) verschlossen ist, der insbesondere geneigt ist und sich seitlich bis zu einem Flüssigkeitsaustrittsfenster erstreckt.
  10. Wärmetauscher nach Anspruch 7 mit aufsteigender Zirkulation des zweiphasigen Fluids, dadurch gekennzeichnet, daß der Hohlraum nach oben offen ist und unten durch den Halbverschlußstab (27), der insbesondere geneigt ist, begrenzt ist.
  11. Wärmetauscher nach Anspruch 10, dadurch gekennzeichnet, daß der erste Durchlaß (4) mehrere Zwischenplatten (35) enthält, die auf seiner Länge voneinander beabstandet sind.
EP96400764A 1995-04-14 1996-04-09 Wärmetauscher mit gelöteten Platten Expired - Lifetime EP0738862B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9504553 1995-04-14
FR9504553A FR2733039B1 (fr) 1995-04-14 1995-04-14 Echangeur de chaleur a plaques brassees, et procede correspondant de traitement d'un fluide diphasique

Publications (2)

Publication Number Publication Date
EP0738862A1 EP0738862A1 (de) 1996-10-23
EP0738862B1 true EP0738862B1 (de) 1999-12-01

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP96400764A Expired - Lifetime EP0738862B1 (de) 1995-04-14 1996-04-09 Wärmetauscher mit gelöteten Platten

Country Status (6)

Country Link
US (1) US5682945A (de)
EP (1) EP0738862B1 (de)
JP (1) JPH0979769A (de)
CN (1) CN1160185A (de)
DE (1) DE69605347T2 (de)
FR (1) FR2733039B1 (de)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19605500C1 (de) * 1996-02-14 1997-04-17 Linde Ag Vorrichtung und Verfahren zum Verdampfen einer Flüssigkeit
GB2316478A (en) * 1996-08-20 1998-02-25 Imi Marston Ltd Liquefaction heat exchanger
US5775129A (en) * 1997-03-13 1998-07-07 The Boc Group, Inc. Heat exchanger
US6179051B1 (en) 1997-12-24 2001-01-30 Delaware Capital Formation, Inc. Distributor for plate heat exchangers
FR2786858B1 (fr) * 1998-12-07 2001-01-19 Air Liquide Echangeur de chaleur
FR2796137B1 (fr) * 1999-07-07 2001-09-14 Air Liquide Vaporiseur-condenseur a bain a plaques brasees et son application a un appareil de distillation d'air
US6832647B2 (en) * 2002-04-02 2004-12-21 Modine Manufacturing Company Integrated condenser/separator for fuel cell exhaust gases
DE10302708A1 (de) * 2003-01-23 2004-07-29 Behr Gmbh & Co. Kg Vorrichtung zum Austausch von Wärme
SE524938C2 (sv) * 2003-02-03 2004-10-26 Ep Technology Ab Värmeväxlare och metod för att torka ett fuktigt medium
US10209015B2 (en) * 2009-07-17 2019-02-19 Lockheed Martin Corporation Heat exchanger and method for making

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3992168A (en) * 1968-05-20 1976-11-16 Kobe Steel Ltd. Heat exchanger with rectification effect
BE789479A (fr) * 1971-10-01 1973-03-29 Air Liquide Echangeur de chaleur et sa mise en oeuvre
US3797565A (en) * 1971-11-22 1974-03-19 United Aircraft Prod Refrigerated gas dryer
DE2222269C2 (de) * 1972-05-06 1984-05-24 Kobe Steel, Ltd., Kobe, Hyogo Rieselkolonne zum Rektifizieren von Flüssigkeiten
US4132587A (en) * 1977-05-23 1979-01-02 Ecodyne Corporation Evaporator
US4249595A (en) * 1979-09-07 1981-02-10 The Trane Company Plate type heat exchanger with bar means for flow control and structural support
FR2547898B1 (fr) * 1983-06-24 1985-11-29 Air Liquide Procede et dispositif pour vaporiser un liquide par echange de chaleur avec un deuxieme fluide, et leur application a une installation de distillation d'air
FR2690231B1 (fr) * 1992-04-17 1994-06-03 Air Liquide Echangeur de chaleur a ruissellement et installation de distillation d'air comportant un tel echangeur.

Also Published As

Publication number Publication date
US5682945A (en) 1997-11-04
CN1160185A (zh) 1997-09-24
JPH0979769A (ja) 1997-03-28
DE69605347T2 (de) 2000-05-11
EP0738862A1 (de) 1996-10-23
FR2733039B1 (fr) 1997-07-04
FR2733039A1 (fr) 1996-10-18
DE69605347D1 (de) 2000-01-05

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