EP0130122A1 - Apparat zum Verdampfen einer Flüssigkeit durch Wärmeaustausch mit einem zweiten Fluid und Luftdestillationsanlage mit einem solchen Apparat - Google Patents

Apparat zum Verdampfen einer Flüssigkeit durch Wärmeaustausch mit einem zweiten Fluid und Luftdestillationsanlage mit einem solchen Apparat Download PDF

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Publication number
EP0130122A1
EP0130122A1 EP84401284A EP84401284A EP0130122A1 EP 0130122 A1 EP0130122 A1 EP 0130122A1 EP 84401284 A EP84401284 A EP 84401284A EP 84401284 A EP84401284 A EP 84401284A EP 0130122 A1 EP0130122 A1 EP 0130122A1
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EP
European Patent Office
Prior art keywords
liquid
passages
heat exchanger
bath
exchanger according
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
EP84401284A
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English (en)
French (fr)
Other versions
EP0130122B1 (de
EP0130122B2 (de
Inventor
Pierre Petit
Maurice Grenier
Jean-François Deschamps
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
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Application filed by Air Liquide SA, LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude filed Critical Air Liquide SA
Priority to AT84401284T priority Critical patent/ATE37229T1/de
Publication of EP0130122A1 publication Critical patent/EP0130122A1/de
Publication of EP0130122B1 publication Critical patent/EP0130122B1/de
Application granted granted Critical
Publication of EP0130122B2 publication Critical patent/EP0130122B2/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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • 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
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • 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
    • 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
    • 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
    • F25J2250/00—Details related to the use of reboiler-condensers
    • F25J2250/04—Down-flowing type boiler-condenser, i.e. with evaporation of a falling liquid film
    • 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
    • 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 the vaporization of a liquid by heat exchange with a second fluid by means of a heat exchanger of the type with vertical plates. It applies in particular to air distillation installations.
  • the liquid oxygen which is in the bottom of the low pressure column is vaporized by heat exchange with. nitrogen gas taken from the top of the medium pressure column.
  • the temperature difference between oxygen and nitrogen made necessary by the structure of the heat exchanger imposes the operating pressure of the medium pressure column. It is . It is therefore desirable for this temperature difference to be as small as possible, in order to minimize the expenses linked to the compression of the air to be treated injected into the medium pressure column.
  • the invention aims to provide means for obtaining heat exchange performance at least as good but more reliably and more economically.
  • the subject of the invention is a method for vaporizing a liquid by heat exchange with a second fluid by means of a heat exchanger comprising a parallelepipedic body formed by an assembly of parallel vertical plates defining between them a multitude of flat passages, method of the type in which the liquid is sent in a first set of passages and the second fluid in the remaining passages, characterized in that the liquid is distributed in. two stages at the upper end of the passages of said first set, over the entire horizontal length thereof, the two stages comprising a rough predistribution of the liquid over the entire length of the passages of said first assembly, then a fine distribution over the entire length of these passages of the liquid thus predistributed.
  • the liquid flow rate is adapted to permanently ensure the presence of a liquid film over practically the entire extent of all the walls contained in each of the passages of said first assembly.
  • the invention also relates to a heat exchanger intended for the implementation of such a process.
  • This exchanger is characterized in that it comprises means for predistributing the liquid leading to means for fine distribution of the liquid arranged at the upper end of each of the passages of said first assembly.
  • the predistribution means comprise openings, in particular a horizontal row of holes, and retaining means for forming a bath of liquid above these openings; said fine distribution means may comprise a lining, or alternatively, when said openings are made in the plates of the exchanger, a surface for spreading the jets of liquid leaving these openings.
  • the invention also relates to an air distillation installation of the double column type, in which the liquid from the bottom of the medium pressure column is brought into heat exchange relationship with the top gas of the low pressure column at means of a heat exchanger as defined above, this installation comprising supply means for supplying the liquid to said predistribution means; and means for supplying gas to the. passages of said second set.
  • FIG. 1 illustrates a possibility of installing an oxygen-nitrogen heat exchanger in an air distillation installation of the double column type.
  • This installation comprises a medium pressure column 1 at the bottom of which the air to be treated is injected, under a pressure of the order of 6 bars absolute.
  • the oxygen-enriched liquid which is collected in the tank of column 1 is sent under reflux in the middle of the height of a second column (not rearranged), called the low pressure column, which operates slightly above atmospheric pressure.
  • the nitrogen gas which is at the head of column 1 is brought into heat exchange relationship with the liquid oxygen collected in the bottom of the low pressure column; the condensed condensing nitrogen serves as reflux in column 1 and in the low pressure column, while the resulting vaporized oxygen is returned to the bottom of the low pressure column.
  • the exchanger 2 consists of a sealed envelope 3, the main height of which contains a set of parallel plates 4 of rectangular aluminum shape, with a length of the order of 1 to 1.5 m and a height of the order of 3 to 6 m, between which waves also made of aluminum are fixed by brazing.
  • the space located above the plates 4 contains a liquid oxygen bath 5 supplied by a line 6 coming from the tank of the low pressure column and provided with a pump (not shown).
  • a bath level regulator 5 which is shown diagrammatically by a level measuring tube 6A, or, as a variant, by a flow regulator.
  • a pipe 7 for returning oxygen vaporized above the bath 5 to the bottom of the low pressure column, resulting from the heat inputs at the pump and the pipes.
  • the set of plates 4 is supplied at its upper part with gaseous nitrogen by a horizontal feed box 8 which communicates by a pipe 9 with the head of the medium pressure column 1.
  • the evacuation of the condensed nitrogen takes place at the base of the plates 4 by a horizontal collecting box 10 which communicates by a pipe 11 with a guarded channel 12 disposed at the head of the column 1.
  • On the box 10 is stuck a pipe 13 for discharging incondensable rare gases.
  • a pipe 14 connects the tank of the low pressure column to the space located in the casing 3 below the plates 4. This pipe penetrates vertically into this space through the bottom point of the casing 3, and its upper end is surmounted by a conical deflector 15. From the bottom of the casing 3 also leaves a pipe 16 intended to return to the bottom of the low pressure column the excess liquid oxygen.
  • the casing 3 has a parallelepiped shape.
  • the plates 4 define a multitude of passages intended alternately for the flow of oxygen (passages 17) and for the flow of nitrogen (passages 18). Over most of their height, the passages 17 and 18 each contain a wave 19 consisting of a corrugated perforated aluminum sheet with vertical generators.
  • each nitrogen passage comprises a liquid oxygen tank 22 containing a vertical wave 23 of perforated aluminum sheet, with vertical generators, the thickness and pitch of which are clearly greater than those of waves 19.
  • the waves 23 have only a function of spacers between the plates 4, so as to allow the assembly of the exchanger by a single brazing operation.
  • the tanks 22 are open upwards to communicate with the liquid oxygen bath 5.
  • the waves 19 of the oxygen passages 17 extend downwards to the lower end of the plates 4, so that these passages are open down. These waves extend upwards to the upper edge of the bars 21, then are extended by a lining 24.
  • the latter consists of a wave of the "serrated" type which is illustrated in more detail in FIG. 6.
  • the wave 24 is an unperforated aluminum sheet with horizontal generators (so-called "hard way” arrangement with respect to the flow of liquid oxygen).
  • each horizontal or psaudo-horizontal facet 25 of the wave 24 is provided with a puncture 26 offset upwards by a quarter of a wave step.
  • the width of the punctures 26, measured along a generatrix of the wave, is of the same order as the distance which separates each of them from the two adjacent punctures situated on the same facet 25.
  • each plate 4 comprises, above the lining 24, a horizontal row of holes 27 arranged at regular intervals over the entire length of the exchanger, the holes of the successive plates being arranged at the same height but in a staggered arrangement. As a variant, these holes could moreover be provided only in every second plate.
  • the oxygen passages are closed by horizontal bars 28, arranged at the upper end of the plates 4. To avoid the risk of obstruction of certain holes 27 by waves 23, these are interrupted for a short height at the level of said holes.
  • the regulating device of the pump for supplying the exchanger 2 with liquid oxygen maintains above the plates 4 a level of the bath 5 sufficient to overcome the various pressure drops which oppose the flow of oxygen.
  • the height liquid oxygen above the plates 4 is for example of the order of 20 cm.
  • Liquid oxygen fills the reservoirs 22 and passes through the holes 27, at a flow rate defined by the passage section of the latter and by the height of liquid which overcomes it. As this height is constant in steady state, the flow of liquid oxygen is that supplied by the pump for raising this liquid.
  • the holes 27 therefore provide a rough predistribution of the liquid oxygen along the passages 17, and the liquid oxygen thus pre-distributed appears on the lining 24, which ensures a fine distribution over the entire length of each passage 17.
  • Liquid oxygen thus approaches waves 19 by flowing in a perfectly uniform manner over all the walls (waves 19 and plates 4) of the passages which are assigned to it, that is to say by forming on these walls a continuous descending film.
  • the nitrogen gas arrives in the exchanger through the box 8 and the distribution waves 20, then flows down along the passages 18. In so doing, it gradually gives off heat to the oxygen. liquid which is in the adjacent passages 17, so that the oxygen vaporizes and that, simultaneously, the nitrogen condenses.
  • the condensed nitrogen is collected in the box 10 and flows in the pipe 11 as far as the channel 12.
  • this liquid overflows from the channel and falls into reflux in the medium pressure column after a portion has been withdrawn through a pipe 11A to ensure the reflux of the low pressure column. This creates suction in the passages 17, which ensures the circulation of nitrogen.
  • the liquid oxygen flow rate is adjusted so as to guarantee an excess of liquid oxygen over the entire height of the plates 4.
  • a total vaporization of the oxygen in a region of the passages 17 would lead to this location at a concentration of acetylene dissolved in liquid oxygen, which could cause a local explosion.
  • this risk of explosion it would also result in a drop in performance of the exchanger by neutralization of the non-wetted surface. This risk is limited thanks to the high efficiency of the fine distribution ensured by the lining 24.
  • the bars 21 which limit the upper passages 18 are arranged at the upper end of the plates 4, like the bars 28.
  • the holes 27 are eliminated and replaced by vertical holes 29 drilled at regular intervals in the bars 28, all along these.
  • the liquid oxygen in the bath 5 flows through the holes 29, at a flow rate corresponding to that of the liquid oxygen pump, and is thus predistributed over the entire length of the passages 17; these liquids then fall on the lining 24 located just below (this lining has been represented ores schematically in FIG. 3).
  • the lining 24 ensures a uniform fine distribution of the liquid oxygen over the entire length of the passages 17, and this liquid then flows along the waves 19 and the corresponding walls 4.
  • the heat exchange between oxygen and nitrogen begins during the passage of liquid oxygen through the linings 24, which are at the same level as the nitrogen gas distribution waves.
  • the holes 29 of the bars 28 instead of being of a constant diameter over the entire height of these bars, can have an enlarged diameter in most of their height by a counter-bore 29A produced from the bottom.
  • FIG. 5 shows that similar holes can also be obtained by perforating the upper core 30 of U-shaped profiles constituting the bars 28.
  • the advantage of these two embodiments lies in the fact that the useful part of the holes 29, which defines the liquid oxygen passage section is short and therefore less subject to the appearance of blockages or undesirable vaporization.
  • the vaporized oxygen is evacuated from below at the same time as the excess liquid oxygen.
  • the vaporized oxygen is free to escape both from the top and from the bottom.
  • the exchanger of FIG. 6 is identical to that of FIG. 2 from the bottom of the plates 4 to the level of the upper edge of the bars 21 which limit the nitrogen passages 18 above.
  • each plate 4 has a horizontal row of holes 31. Above these, the. plates 4 extend over a significant height, up to a level higher than that of the free surface of the liquid oxygen bath 5.
  • waves - spacers 32 with vertical generators similar to the waves 23 in FIG. 2.
  • a free space 33 is provided at the holes 31, above waves 19, and this space is overcome, from bottom to top by the lining 24 previously described, by a bar 28 with holes 29 similar to those of FIG. 3, and by a wave-spacer 34 similar to waves 32 but with generators horizontal.
  • the bath 5 is supplied laterally by a supply box 35 located above the box 8 and opening into the spaces occupied by the waves 34.
  • the bars 36 which close the passages 17 on this side of oxygen extend upward only up to the level of the upper edge of the bars 28.
  • the heat exchanger illustrated in FIG. 7 differs from that of FIG. 2 only in the way in which the oxygen is distributed and evacuated.
  • the lining 24 is eliminated; the jets of liquid oxygen 37 leaving the holes 27 strike the plate 4 opposite and spread over the latter.
  • the spacing and the diameter of these holes are chosen so that the sheets of parabolic shape thus formed meet in a continuous sheet a little above the heat exchange waves 19.
  • the predistribution of oxygen is still provided by the holes 27, while its fine distribution is provided by the plates 4 themselves.
  • This distribution method is particularly simple and has the advantage of not creating a significant obstacle to the evacuation of the oxygen vaporized from the top of the passages 17, as shown.
  • the lower end of the passages 17 can then be either closed and provided with means for collecting the excess liquid oxygen, or open to also allow the gaseous oxygen the possibility of being evacuated from below.
  • the areas for spreading the jets can be provided on additional plates 39 attached to the plates 4.
  • the exchanger region located above the bars 21 does not require any waves.
  • waves 23 made of strong sheet metal and with large pitch can be used as spacers, these ecant waves interrupted at the level of the holes 27 and in the areas of spreading of the jets.
  • FIG. 8 there is shown in the passages 17 a wave 23 in two parts, respectively above and below the holes 27, with a striated zone 40. Opposite these holes and another striated zone 41 between the wave 23 and wave 19. This figure 8 also shows that such waves 23 allow the simultaneous installation of additional plates 39.
  • holes 27 can be provided in all the plates 4, with of course a suitable offset, in order to supply each passage 17 with two layers of liquid oxygen.
  • the nitrogen circuit is conventional. It can therefore be replaced by other known types of nitrogen circuits, in particular by those described in the FR patent. 78.20.757 of the plaintiff.
  • one or more heat exchangers according to the invention can be installed inside a double air distillation column whose low pressure column is superimposed on the medium pressure column.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Heat Treatment Of Water, Waste Water Or Sewage (AREA)
EP84401284A 1983-06-24 1984-06-21 Apparat zum Verdampfen einer Flüssigkeit durch Wärmeaustausch mit einem zweiten Fluid und Luftdestillationsanlage mit einem solchen Apparat Expired - Lifetime EP0130122B2 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84401284T ATE37229T1 (de) 1983-06-24 1984-06-21 Apparat zum verdampfen einer fluessigkeit durch waermeaustausch mit einem zweiten fluid und luftdestillationsanlage mit einem solchen apparat.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8310472 1983-06-24
FR8310472A FR2547898B1 (fr) 1983-06-24 1983-06-24 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

Publications (3)

Publication Number Publication Date
EP0130122A1 true EP0130122A1 (de) 1985-01-02
EP0130122B1 EP0130122B1 (de) 1988-09-14
EP0130122B2 EP0130122B2 (de) 1994-04-06

Family

ID=9290142

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84401284A Expired - Lifetime EP0130122B2 (de) 1983-06-24 1984-06-21 Apparat zum Verdampfen einer Flüssigkeit durch Wärmeaustausch mit einem zweiten Fluid und Luftdestillationsanlage mit einem solchen Apparat

Country Status (14)

Country Link
US (1) US4599097A (de)
EP (1) EP0130122B2 (de)
JP (1) JPS6017601A (de)
KR (1) KR850000658A (de)
AT (1) ATE37229T1 (de)
AU (1) AU566656B2 (de)
BR (1) BR8403038A (de)
CA (1) CA1245627A (de)
DE (1) DE3474059D1 (de)
ES (1) ES533634A0 (de)
FR (1) FR2547898B1 (de)
IN (1) IN160739B (de)
PT (1) PT78780A (de)
ZA (1) ZA844598B (de)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0303492A2 (de) * 1987-08-14 1989-02-15 The BOC Group plc Flüssiggasboiler
FR2665755A1 (fr) * 1990-08-07 1992-02-14 Air Liquide Appareil de production d'azote.
EP0501471A2 (de) * 1991-03-01 1992-09-02 Air Products And Chemicals, Inc. Siedeverfahren und Wärmetauscher zur Verwendung in diesem Verfahren
EP0546947A1 (de) * 1991-12-11 1993-06-16 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Indirekter Plattenwärmetauscher
EP0566435A1 (de) * 1992-04-17 1993-10-20 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Rieselwärmetauscher und Lufttrennungseinrichtung mit einem solchen Wärmetauscher
EP0695921A1 (de) * 1994-08-05 1996-02-07 Praxair Technology, Inc. Abwärtsströmender dünner Wärmetauscher für kryogene Rektifikation
EP0699884A1 (de) 1994-08-29 1996-03-06 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Sauerstoffherstellungsverfahren und Einrichtung durch kryogene Destillation
FR2774755A1 (fr) * 1998-02-09 1999-08-13 Air Liquide Condenseur a plaques brasees perfectionne et son application aux doubles colonnes de distillation d'air
FR2786858A1 (fr) 1998-12-07 2000-06-09 Air Liquide Echangeur de chaleur
FR2957142A1 (fr) * 2010-03-08 2011-09-09 Air Liquide Echangeur de chaleur
EP2508830A1 (de) * 2004-10-25 2012-10-10 ConocoPhillips Company Vertikale Wärmetauscherkonfiguration für Flüssigerdgasanlage
CN102792116A (zh) * 2010-03-08 2012-11-21 乔治洛德方法研究和开发液化空气有限公司 热交换器
CN105066745A (zh) * 2015-08-03 2015-11-18 中冶焦耐工程技术有限公司 一种酸汽冷凝器
WO2016124748A1 (fr) 2015-02-06 2016-08-11 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Echangeur de chaleur comprenant un dispositif de distribution de liquide frigorigene
WO2016166473A1 (fr) 2015-04-16 2016-10-20 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Échangeur de chaleur présentant des éléments de microstructure et unité de séparation comprenant un tel échangeur de chaleur
EP3653983A1 (de) * 2018-11-13 2020-05-20 Linde Aktiengesellschaft Plattenwärmetauscher, verfahren zum betreiben eines plattenwärmetauschers und verfahren zum herstellen eines plattenwärmetauschers
EP3462119B1 (de) 2013-04-30 2021-03-31 Hamilton Sundstrand Corporation Integrierter verteiler eines wärmetauschers

Families Citing this family (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2649192A1 (fr) * 1989-06-30 1991-01-04 Inst Francais Du Petrole Procede et dispositif de transfert simultane de matiere et de chaleur
FR2650379B1 (fr) * 1989-07-28 1991-10-18 Air Liquide Appareil de vaporisation-condensation pour double colonne de distillation d'air, et installation de distillation d'air comportant un tel appareil
USRE36435E (en) * 1989-07-28 1999-12-14 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Vaporization-condensation apparatus for air distillation double column, and air distillation equipment including such apparatus
JPH0336401U (de) * 1989-08-11 1991-04-09
US5233839A (en) * 1991-03-13 1993-08-10 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Process for operating a heat exchanger
FR2733039B1 (fr) * 1995-04-14 1997-07-04 Air Liquide Echangeur de chaleur a plaques brassees, et procede correspondant de traitement d'un fluide diphasique
US5730209A (en) * 1995-04-28 1998-03-24 Air Products And Chemicals, Inc. Defrost and liquid distribution for plate-fin heat exchangers
GB9515492D0 (en) * 1995-07-28 1995-09-27 Aitken William H Apparatus for combined heat and mass transfer
GB2302044A (en) * 1995-06-12 1997-01-08 William Harrold Aitken Liquid-vapour contact apparatus
US5667643A (en) * 1995-12-18 1997-09-16 The Boc Group, Inc. Heat exchanger and double distillation column
US5699671A (en) * 1996-01-17 1997-12-23 Praxair Technology, Inc. Downflow shell and tube reboiler-condenser heat exchanger for cryogenic rectification
US5709264A (en) * 1996-03-18 1998-01-20 The Boc Group, Inc. Heat exchanger
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GB9705889D0 (en) * 1997-03-21 1997-05-07 Boc Group Plc Heat exchange method and apparatus
US6186223B1 (en) 1998-08-27 2001-02-13 Zeks Air Drier Corporation Corrugated folded plate heat exchanger
US6244333B1 (en) 1998-08-27 2001-06-12 Zeks Air Drier Corporation Corrugated folded plate heat exchanger
JP4592125B2 (ja) * 1998-10-05 2010-12-01 大陽日酸株式会社 流下液膜式凝縮蒸発器
ES2204380T3 (es) * 1999-03-17 2004-05-01 Linde Aktiengesellschaft Dispositivo y procedimiento para descomponer una mezcla gaseosa a baja temperatura.
FR2798599B1 (fr) * 1999-09-21 2001-11-09 Air Liquide Vaporiseur-condenseur a thermosiphon et installation de distillation d'air correspondante
FR2807826B1 (fr) 2000-04-13 2002-06-14 Air Liquide Echangeur vaporisateur-condenseur du type a bain
FR2793548A1 (fr) 2000-07-21 2000-11-17 Air Liquide Vaporiseur-condenseur a plaques fonctionnant en thermosiphon, et double colonne de distillation d'air comportant un tel vaporiseur-condenseur
US6349566B1 (en) 2000-09-15 2002-02-26 Air Products And Chemicals, Inc. Dephlegmator system and process
FR2891901B1 (fr) * 2005-10-06 2014-03-14 Air Liquide Procede de vaporisation et/ou de condensation dans un echangeur de chaleur
JP4704928B2 (ja) * 2006-02-15 2011-06-22 大陽日酸株式会社 熱交換型蒸留装置
JP4818044B2 (ja) * 2006-09-28 2011-11-16 三洋電機株式会社 熱交換器の製造方法
US8161771B2 (en) 2007-09-20 2012-04-24 Praxair Technology, Inc. Method and apparatus for separating air
FR2938904B1 (fr) * 2008-11-24 2012-05-04 Air Liquide Echangeur de chaleur
CN102650492A (zh) * 2012-05-10 2012-08-29 西安交通大学 空分板翅型降膜式冷凝蒸发器
CN102650491B (zh) * 2012-05-10 2013-10-16 西安交通大学 空分板翅型膜式主冷液体分布器
CN105546935A (zh) * 2016-02-05 2016-05-04 江苏建筑职业技术学院 空分膜式主冷液体分布器
FR3065795B1 (fr) 2017-04-27 2019-06-14 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Echangeur de chaleur a jonction d'ondes amelioree, installation de separation d'air associee et procede de fabrication d'un tel echangeur
DE102018005505A1 (de) * 2018-07-11 2020-01-16 Linde Aktiengesellschaft Wärmeübertrager mit Block als Fallfilmverdampfer und Verfahren zur indirekten Wärmeübertragung
US11774189B2 (en) * 2020-09-29 2023-10-03 Air Products And Chemicals, Inc. Heat exchanger, hardway fin arrangement for a heat exchanger, and methods relating to same

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Cited By (32)

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Publication number Priority date Publication date Assignee Title
EP0303492A3 (de) * 1987-08-14 1989-08-09 The BOC Group plc Flüssiggasboiler
US5014773A (en) * 1987-08-14 1991-05-14 The Boc Group Plc Liquefied gas boilers
EP0303492A2 (de) * 1987-08-14 1989-02-15 The BOC Group plc Flüssiggasboiler
FR2665755A1 (fr) * 1990-08-07 1992-02-14 Air Liquide Appareil de production d'azote.
EP0501471A2 (de) * 1991-03-01 1992-09-02 Air Products And Chemicals, Inc. Siedeverfahren und Wärmetauscher zur Verwendung in diesem Verfahren
EP0501471A3 (en) * 1991-03-01 1992-12-09 Air Products And Chemicals, Inc. Boiling process and a heat exchanger for use in the process
US5333683A (en) * 1991-12-11 1994-08-02 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Indirect heat exchanger
EP0546947A1 (de) * 1991-12-11 1993-06-16 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Indirekter Plattenwärmetauscher
FR2685071A1 (fr) * 1991-12-11 1993-06-18 Air Liquide Echangeur de chaleur indirect du type a plaques.
EP0566435A1 (de) * 1992-04-17 1993-10-20 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Rieselwärmetauscher und Lufttrennungseinrichtung mit einem solchen Wärmetauscher
US5321954A (en) * 1992-04-17 1994-06-21 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Streaming heat exchanger and apparatus for air distillation comprising such an exchanger
FR2690231A1 (fr) * 1992-04-17 1993-10-22 Air Liquide Echangeur de chaleur à ruissellement et installation de distillation d'air comportant un tel échangeur.
EP0695921A1 (de) * 1994-08-05 1996-02-07 Praxair Technology, Inc. Abwärtsströmender dünner Wärmetauscher für kryogene Rektifikation
EP0699884A1 (de) 1994-08-29 1996-03-06 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Sauerstoffherstellungsverfahren und Einrichtung durch kryogene Destillation
FR2774755A1 (fr) * 1998-02-09 1999-08-13 Air Liquide Condenseur a plaques brasees perfectionne et son application aux doubles colonnes de distillation d'air
US6189338B1 (en) 1998-02-09 2001-02-20 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Brazed-plates condenser and its application to double air-distillation columns
EP1008826A1 (de) * 1998-12-07 2000-06-14 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Fallstrom-Verdampfer und Luftzerlegungsvorrichtung
FR2786858A1 (fr) 1998-12-07 2000-06-09 Air Liquide Echangeur de chaleur
EP2508830A1 (de) * 2004-10-25 2012-10-10 ConocoPhillips Company Vertikale Wärmetauscherkonfiguration für Flüssigerdgasanlage
CN102792116B (zh) * 2010-03-08 2015-04-08 乔治洛德方法研究和开发液化空气有限公司 热交换器
WO2011110772A3 (fr) * 2010-03-08 2011-11-10 L'Air Liquide, Société Anonyme pour l'Etude et l'Exploitation des Procédés Georges Claude Echangeur de chaleur
WO2011110772A2 (fr) * 2010-03-08 2011-09-15 L'Air Liquide, Société Anonyme pour l'Etude et l'Exploitation des Procédés Georges Claude Echangeur de chaleur
CN102792116A (zh) * 2010-03-08 2012-11-21 乔治洛德方法研究和开发液化空气有限公司 热交换器
FR2957142A1 (fr) * 2010-03-08 2011-09-09 Air Liquide Echangeur de chaleur
EP3462119B1 (de) 2013-04-30 2021-03-31 Hamilton Sundstrand Corporation Integrierter verteiler eines wärmetauschers
WO2016124748A1 (fr) 2015-02-06 2016-08-11 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Echangeur de chaleur comprenant un dispositif de distribution de liquide frigorigene
FR3032521A1 (fr) * 2015-02-06 2016-08-12 Air Liquide Echangeur de chaleur comprenant un dispositif de distribution de liquide frigorigene
WO2016166473A1 (fr) 2015-04-16 2016-10-20 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Échangeur de chaleur présentant des éléments de microstructure et unité de séparation comprenant un tel échangeur de chaleur
FR3035202A1 (fr) * 2015-04-16 2016-10-21 Air Liquide Echangeur de chaleur presentant des elements de microstructure et unite de separation comprenant un tel echangeur de chaleur
CN107660265A (zh) * 2015-04-16 2018-02-02 乔治洛德方法研究和开发液化空气有限公司 包括微结构元件的热交换器以及包括这种热交换器的分离单元
CN105066745A (zh) * 2015-08-03 2015-11-18 中冶焦耐工程技术有限公司 一种酸汽冷凝器
EP3653983A1 (de) * 2018-11-13 2020-05-20 Linde Aktiengesellschaft Plattenwärmetauscher, verfahren zum betreiben eines plattenwärmetauschers und verfahren zum herstellen eines plattenwärmetauschers

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Publication number Publication date
EP0130122B1 (de) 1988-09-14
KR850000658A (ko) 1985-02-28
FR2547898A1 (fr) 1984-12-28
CA1245627A (fr) 1988-11-29
ES8600489A1 (es) 1985-09-16
PT78780A (fr) 1984-07-01
US4599097A (en) 1986-07-08
ZA844598B (en) 1985-02-27
AU2956384A (en) 1985-01-31
AU566656B2 (en) 1987-10-29
JPH0531042B2 (de) 1993-05-11
BR8403038A (pt) 1985-05-28
FR2547898B1 (fr) 1985-11-29
DE3474059D1 (en) 1988-10-20
ES533634A0 (es) 1985-09-16
ATE37229T1 (de) 1988-09-15
EP0130122B2 (de) 1994-04-06
IN160739B (de) 1987-08-01
JPS6017601A (ja) 1985-01-29

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