EP0019508B1 - Ensemble d'échange thermique du genre échangeur de chaleur à plaques - Google Patents

Ensemble d'échange thermique du genre échangeur de chaleur à plaques Download PDF

Info

Publication number
EP0019508B1
EP0019508B1 EP80400560A EP80400560A EP0019508B1 EP 0019508 B1 EP0019508 B1 EP 0019508B1 EP 80400560 A EP80400560 A EP 80400560A EP 80400560 A EP80400560 A EP 80400560A EP 0019508 B1 EP0019508 B1 EP 0019508B1
Authority
EP
European Patent Office
Prior art keywords
passages
exchanger
distribution
zone
plate
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
Application number
EP80400560A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0019508A1 (fr
Inventor
Maurice Grenier
Pierre Petit
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.)
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
Original Assignee
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 LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude filed Critical LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
Priority to AT80400560T priority Critical patent/ATE1684T1/de
Publication of EP0019508A1 publication Critical patent/EP0019508A1/fr
Application granted granted Critical
Publication of EP0019508B1 publication Critical patent/EP0019508B1/fr
Expired legal-status Critical Current

Links

Images

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
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/006—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the refrigerant fluid used
    • F25J1/008—Hydrocarbons
    • F25J1/0087—Propane; Propylene
    • 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
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/0002—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the fluid to be liquefied
    • F25J1/0022—Hydrocarbons, e.g. natural gas
    • 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
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0047—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle
    • F25J1/0052—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle by vaporising a liquid refrigerant stream
    • 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
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0211—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using a multi-component refrigerant [MCR] fluid in a closed vapor compression cycle
    • F25J1/0214—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using a multi-component refrigerant [MCR] fluid in a closed vapor compression cycle as a dual level refrigeration cascade with at least one MCR cycle
    • F25J1/0215—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using a multi-component refrigerant [MCR] fluid in a closed vapor compression cycle as a dual level refrigeration cascade with at least one MCR cycle with one SCR cycle
    • F25J1/0216—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using a multi-component refrigerant [MCR] fluid in a closed vapor compression cycle as a dual level refrigeration cascade with at least one MCR cycle with one SCR cycle using a C3 pre-cooling cycle
    • 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
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0257—Construction and layout of liquefaction equipments, e.g. valves, machines
    • F25J1/0262—Details of the cold heat exchange system
    • 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
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0279—Compression of refrigerant or internal recycle fluid, e.g. kind of compressor, accumulator, suction drum etc.
    • F25J1/0292—Refrigerant compression by cold or cryogenic suction of the refrigerant gas
    • 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
    • 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
    • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • 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
    • F25J2205/00—Processes or apparatus using other separation and/or other processing means
    • F25J2205/02—Processes or apparatus using other separation and/or other processing means using simple phase separation in a vessel or drum
    • 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
    • F25J2250/02—Bath type boiler-condenser using thermo-siphon effect, e.g. with natural or forced circulation or pool boiling, i.e. core-in-kettle heat exchanger
    • 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
    • F25J2290/40—Vertical layout or arrangement of cold equipments within in the cold box, e.g. columns, condensers, heat exchangers etc.
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/108—Particular pattern of flow of the heat exchange media with combined cross flow and parallel flow
    • 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
    • Y10S62/905—Column

Definitions

  • the object of the present invention is to provide construction methods more particularly suitable for an arrangement of the exchanger according to which its large dimension is arranged vertically.
  • This vertical arrangement of the exchanger has proven to be decisive in ensuring correct distribution of the various fluids (first, second, third and fourth fluids) thus allowing a strictly balanced heat transfer in the transverse direction of the exchanger.
  • said fourth passages have, in a manner known per se, active heat exchange zones with longitudinally oriented waves, the longitudinal extension is limited to clear on each side of each said active area on the one hand a wave feed distribution area, on the other hand a wave evacuation distribution area, said feed and evacuation distribution areas opening out respectively in said entry and exit windows of said fourth passages, said entry and exit windows communicating with a common phase separator means at least substantially coextensive longitudinally with said active areas.
  • the vertical arrangement of the exchanger a makes it possible to ensure more homogeneous specific heat flows between the 1st and 2nd passages on the one hand and the 3rd passages on the other hand, it however required a complete rearrangement of the 4th passages which are arranged according to the invention no longer at cross-currents, but co-extensively with respect to the circulation of the other fluids flowing in the other passages. This is why direct communication between the inputs and outputs of the passages is provided to form a phase separator. It is understood that in operation, the liquid entering the lower end circulates like a reboiler in the passages with a large excess of vaporized liquid, which ensures perfect homogeneity of the heat transfers.
  • this advantage is essentially due to the fact that the coolant here is a single constituent such as propane and not a coolant mixture as is the case in that which circulates in the first and third passages, there is therefore no variation in the composition of the liquid and vapor phases during vaporization. It is therefore possible, without degrading the thermodynamic performance of the heat exchanger, to recycle the excess of non-vaporized liquid.
  • the most economical way to carry out this operation is to do it as close as possible to the heat transfer zone concerned, for example by means of boxes which are common to the inputs and outputs.
  • these two common boxes have a cross section sufficient for an at least coarse separation of the liquid and vapor phases to occur: the largest part, for example of the order of 90% of the non-vaporized excess liquid, is thus directly recycled at the entrance to the same exchange zone and only a small part is entrained by the vapor phase which will moreover be separated later preferably in suitable collectors.
  • a liquefaction installation comprises a plate exchanger 1 formed from a stack of rectangular plates whose large dimension, or length, or height, is arranged vertically from a first high end 1a up to at a second lower end 1b while the small dimensions, or width and thickness, have horizontal extensions.
  • the inlet boxes 14 of the first passages of the refrigerant mixture 11 are connected by a pipe 60, incorporating a cooler 61 , at the outlet of a compressor 62, the inlet of which is connected by a pipe 63 to the lateral outlet boxes (35a and 35b) of the third passages 31.
  • the inlet box 34 of the passages 31 is itself connected by a line 64 incorporating an expansion valve 65 into the outlet boxes 15 of the first passages 11.
  • the refrigerant mixture comprises, for example, hydrocarbons such as methane, ethane, butane and generally nitrogen, and the particularity of the process is that the mixture refrigerant reaches the inlet boxes in a purely gaseous state 14.
  • the second passages 21 intended for gas in during treatment (generally natural gas) are supplied by their inlet boxes 24 with natural gas in gaseous state at room temperature and the low outlet boxes 25 deliver liquefied natural gas.
  • the second passages can be equipped with outlets and intermediate inlets arranged laterally to ensure the elimination of certain components of the gas during treatment.
  • the fourth passages 41 (41 a, 41 b, 41 c, 41 d) are connected by their inlet-outlet boxes 44 and 45 on the one hand, part of the high tubes 66 intended to convey steam, if necessary with liquid, and low lines 67 intended to convey exclusively liquid, to a double series of lateral collectors 71 (71a, 71 b, 71 c, 71 d) and 72 (72a, 72b, 72c, 72d).
  • lateral collectors 71 and 72 are themselves connected by “steam” pipes 73 ′ and “liquid” pipes 74, each to a separator 75 (75a, 75b, 75c, 75d) in number equal to the number of types of fourth sub-passages 41, operating under different pressures (that is to say four in the drawing), a separator 75, for example the separator 75b, being connected to the outlet of the “liquid” phase of the neighboring separator at higher pressure (75a) by a connecting pipe 76 (76b, 76c, 76d) to expansion valve 77 (77b, 77c, 77d), except the head separator under the highest pressure 75a which is itself connected by a pipe 76a , incorporating an expansion valve 77a and a cooler-condenser 78 at the outlet of a multistage compressor 79 (79a, 79b, 79c, 79d) whose inputs are connected by conduits 80 (80a, 80b, 80c, 80d ) at an upper end of the
  • the distribution zones (12) and (22-23) have structures of the same type (the same is true of the distribution zone of the low outlet not shown in the first heat exchange passages 11), and it is therefore sufficient to describe the distribution area 12.
  • the inlet (14-24) or outlet (15-25) boxes are arranged at the axial end of the exchanger 1, but with a lateral offset so as to allow, on the same exchanger end, the arrangement of several inlet and / or outlet boxes.
  • the distribution zone 12 comprises two sections 12a, 12b, formed from corrugated sheet; section 12a presents waves with vertical extension, while section 12b presents parallel waves with extension inclined parallel to the direction which connects the inner edge 91 of the supply box 14 and the most distant lower corner 92 of the distribution zone 12.
  • the fluid whether in the gaseous or liquid state (but for the supply box 14, this fluid is expressly in the gaseous state) is distributed uniformly along the waves parallel from section 12a and then distributed along the parallel waves of section 12b to reach uniformly in the active heat exchange zone 16, which is itself provided with parallel waves with vertical extension, generally very tight, for obtain the maximum heat exchange effect.
  • Each distribution zone 32 has the particularity of having an inlet window 95 of the same thickness as a passage 31 of the exchanger 1 and the other dimension of which, counted according to the width of the exchanger 1, is substantially reduced by the presence outlet boxes 15 for the refrigerant mixture and 25 for the treated gas.
  • it is a two-phase fluid which passes through this supply window 95 according to arrangements which will be examined below.
  • This distribution zone 32 consists of four sections which are defined by straight lines connecting the upper corners of the zone 32 to the neighboring edges of the window 95.
  • a first section 32a located upstream in a direction of flow of the fluid, is therefore presents in the form of a triangle whose base is coextensive with the window 95 and comprises waves with vertical extension.
  • This first section 32a feeds by its two sides two intermediate sections 32b and 32c equipped with waves inclined in the direction which connects, in each section 32b or 32c, the adjacent lower edge 96 (96 ') of section 32a to the upper edge adjacent 97 '(97) of distribution area 32.
  • a fourth distribution section 32d is also in the form of a triangle, the apex of which coincides with that of section 32a and is equipped with vertically extending waves allowing the fluid from the sections 32b and 32c to be taken up to uniformly supply the set of waves with vertical extension of the active heat exchange zone 36.
  • These sections 421 and 422 (431,432) have waves with horizontal extension, which feed (or are fed respectively by) a third distribution section 423, 424 (433, 434), formed of a double subsection each formed of inclined waves converging towards the active heat exchange zone 46 for the inlet (or diverging from this exchange zone 46 for the outlet), so as to take up the fluid issuing sections 421 and 422 (or from the heat exchange zone 46 respectively) to distribute it uniformly all along the active heat exchange zone 46 (or in sections 431, 432 respectively).
  • inlet windows 991 and 992 at the liquid level, and the outlet windows 993 and 994 at the vapor level have different longitudinal extensions, since the “steam” outlet windows 993 and 994 are significantly longer than the “liquid” inlet windows 991 and 992, which is explained by the fact that they must allow the same quantities of fluid to pass through as the “liquid” windows 991 and 992, but in the partially vaporized state, then that these windows 991 and 992 allow the fluid to pass exclusively in the form of liquid.
  • an auxiliary refrigerant for example propane
  • propane is introduced continuously into the lateral collectors 71 and 72 by the “liquid” lines 74, and this liquid after having been distributed in the boxes 44 and 45 enter, through the windows 991 and 992 into the sections 421 and 422 of the supply distribution area 42, before being taken up by the subsections 423 and 424 for distribution, throughout the active area d 'heat exchange 46 consisting of tight waves with vertical extension.
  • the auxiliary liquid refrigerant partially vaporizes in these waves, and flows through subsections 433 and 434 of distribution zone 43, reaches sections 431 and 432 to be directed again into boxes 44 and 45, then in the lateral collectors 71 and 72.
  • the “vapor” fraction in the collectors 71 and 72 is directed (however entraining a portion of liquid which is not completely decanted) to the separators at different pressures 75a, 75b, 75c, 75d where the liquid droplets entrained are deposited with the liquid fraction in said separators.
  • the passages for the fourth fluid 41 incorporate an active heat exchange zone 146 which consists of a double trapezoid-shaped section 146a and 146b, the largest sides of which coincide and correspond to the longitudinal height. of a passage 41.
  • the “liquid” inlet sections 142a and 142b have the shape of flattened right triangles whose short sides constitute inlet windows 199a and 199a ′ for the liquid, while the outlet sections 143a and 143b have the same shape, but have outlet windows 199b and 199b 'of shapes which are clearly more elongated in the longitudinal direction.
  • the waves of sections 146a and 146b of the active heat exchange zone 46 are all vertical and these waves can have increasingly tight steps as one approaches. boxes 44 and 45, so as to offer the fluid substantially equal pressure drops despite the appreciable differences in path lengths, as is clear from the drawing.
  • the embodiment differs essentially from what is described in Figure 3 in that the inlet (142a 'and 142b') and outlet (143a 'and 143b') sections have here the shape, no longer of triangles, but of rectangular trapezoids.
  • FIG. 5 differs from FIG. 4 in that the active heat exchange zone 46a, here, a rectangular shape with a smaller longitudinal extension and inlet sections 142a "and 142b" which have the same shape as the sections 142a 'and 142b' of FIG. 4, but these sections precede two connection sections 142c 'and 142c ", adjacent to the active area 46.
  • the active heat exchange zone 46a here, a rectangular shape with a smaller longitudinal extension and inlet sections 142a "and 142b" which have the same shape as the sections 142a 'and 142b' of FIG. 4, but these sections precede two connection sections 142c 'and 142c ", adjacent to the active area 46.
  • connection sections 142c' and 142c have waves inclined so as to distribute the fluid from sections 142a "and 142b" all along the inlet of the active heat exchange zone 46, while the connection sections 143d 'and 143d "are intended to take up the fluid in the two-phase state from the output of the active heat exchange section 46 to the output sections 143a "and 143b".
  • the embodiment according to FIG. 6 differs from the embodiment according to FIG. 5 in that the inlet sections 242a “and 242b" and the connection sections 242c 'and 242c “are not symmetrical, the sections 242c" and 242b “having a greater transverse extension than sections 242c 'and 242a ", so as to distribute the liquid coming from the inlet section 242b" over a transverse length greater than half the transverse dimension of the active heat exchange zone 46. This allows an overall flow of liquid from the left to the right, which is necessary when the liquid supply is only on the left side.
  • the embodiment according to FIG. 7 differs from the embodiment according to FIG. 6 in that, not only, the inlet sections 242a ", and 242b", 242c 'and 242c "are asymmetrical in a direction which corresponds to a greater flow from left to right only in the opposite direction, but also provision has been made for the outlet sections 243a, 243b, 243d 'and 243d "to be asymmetrical, sections 243d 'and 243a before a greater transverse extension than section 243d "and 243b, which has the consequence of increasing the flow rate of non-vaporized liquid, from left to right, towards box 44, relative to the circulating flow rate to box 45.
  • This two-phase supply box 34 is formed of an envelope 101 having a substantial vertical extension and which has an opening 102 at approximately half-height, into which opens the line 64 for reintroducing low pressure refrigerant mixture.
  • a perforated plate 103 Inside the casing 101, parallel to the window 95 and at a short distance from it, is mounted a perforated plate 103 on which, and through which are mounted tubes 104 extending below of said plate 103 and up to a distance largely below the opening 102 of the pipe 64, the tubes 104 having a lower end 105, in which one or more slots 106 has advantageously been made.
  • a lining 107 is placed in the interstitial space between the distribution zone 32 and the perforated plate 103.
  • the refrigerant mixture which has just been expanded by the expansion valve 65 at the low pressure of the cycle reaches the interior of the casing 101, in which this fluid, in the two-phase state, separates into a vapor fraction 108 and a liquid fraction 109, the normal level of separation N being generally located above the slots 106.
  • the propellant effect due to the pressure acting on the surface of the liquid mass 109 ensures a rise in the liquid through the tubes 104, at the same time as an escape of the gaseous fraction through the perforations of the plate 103.
  • the two-phase mixture is thus reconstituted in a homogeneous manner, at the upper outlet of the tubes 104, in the lining 107 , which allows a uniform feeding of section 32a resp.
  • the level N of the liquid fraction 109 descends until it reaches the level of the slots 106, which then causes the escape, through the slots 106, of the tubes 104, of part of the gaseous fraction. Once the flow rate of this liquid fraction, which normally constitutes most of the two-phase fluid, is restored, the level N rises and the operation as detailed above resumes.
  • the two-phase fluid which circulates uniformly along the vertical waves of the central section 32e is taken up - when there is symmetry, that is to say when the section 32e has the shape of an isosceles triangle whose apex is axial - half by section 32f, for the other half by section 32g, output that the vertical waves of the active heat exchange zone 36 are uniformly supplied with two-phase liquid.
  • the active heat exchange zone 36 of the cooling mixture heating passages 31 is supplied by a distribution zone 32 which is identical to that which has been described in FIG. 8, but the input box 34 is here very different in nature: this input box 34 is in the form of a thick semi-cylindrical receptacle 120 mounted in relation to supply windows 121 for the area of distribution 32.
  • Each supply window 121 is closed off with a thick strip 122 in which is mounted, by screwing, a plurality of ejectors 123 having an upwardly diverging shape, the receptacle 120 having an intake orifice on which is connected the supply line 64, but unlike the previous examples, the refrigerant mixture has been, here, expanded to an intermediate pressure, such that it is formed in the receptacle 120 that a clear liquid, the final expansion s performing in é nozzles 123; the two-phase mixing is therefore done ipso-facto at the outlet of the ejectors 123 and is, by this very fact, uniformly distributed along the vertical waves of the first section 32e of the distribution area 32.
  • FIG. 11 an alternative embodiment of the supply box 34 is described as described with reference to FIG. 9.
  • the semi-cylindrical receptacle 120 intended to receive the free liquid at pressure intermediate, but the. ejectors 123 are here arranged in a regularly distributed manner in a support plate 124 which extends over the entire surface of the exchanger 1, but at a short distance beyond this exchanger, and between the plate 124 and the windows free 125 of the cooling mixture heating passages 31 is provided a grating 126 for distributing the two-phase fluid at the entrance to sections 32e of all distribution areas 32.
  • FIGS. 13, 14 and 15 another alternative embodiment of the two-phase supply of the conduits for heating the refrigerant mixture 31 is described.
  • the supply box 34 comprises a receptacle 151 extending over the entire depth of the exchanger 1 and into which opens, after separation into a separator 150 and via line 64, a free liquid 152.
  • the passages 31 are here arranged side by side, two by two, and, in the interval between two pairs of passages 31, is formed a steam passage 51 which extends over a short terminal length of the exchanger on the side of its lower end or second end, which further limits the longitudinal extension of the cooling passages of the treated gas 21.
  • the separation between the passages 51 on the one hand, and 11 and 21 on the other hand, is ensured by spacers of sealing 52.
  • the passages 51 are closed by bars 53, and it can be seen that the intermediate wall plates 54 between each passage 51 and each passage 31 are perforated according to inclined slots (or holes) 56, evenly distributed.
  • the outlets of the cooling mixture cooling passages 11 and the outlets of the cooling ganz treated cooling passage are here arranged laterally at the exchanger, as indicated in 57 for the refrigerant mixture passages 11, or in 58 for cooling gas cooling passages.
  • the evacuating distribution zone has been simplified in that it provides for the evacuation of the entire refrigerant mixture on one side of the exchanger, towards the box 57 by the distribution zone 59, while the evacuation of the treated gas is carried out entirely on the other side towards the box 58 of the exchanger.
  • outlet boxes 57 and 58 are staggered longitudinally, so as to provide a free space for the arrangement of an inlet box 60 associated with a distribution area 61, for the vapor phase which comes from the separator 150, while the liquid 152 is drawn off in a tank in this same separator 150.
  • the vapor which enters the passages 51 undergoes a certain pressure drop in the ports 56, so that the level of liquid N, which is established in the passages 51 is lower than the level of liquid N 2 which is established in the cooling mixture heating passages 31.
  • the vapor therefore engages uniformly in the slots 56 and is thus distributed in the liquid.
  • the essential advantage of this arrangement is that the two-phase mixing is carried out just upstream of the heat exchange zone between the cooling conduits for the refrigerant mixture 11 and for the treated gas 21.
  • the treated gas passages 21 here extend over the entire length of the exchanger 1 and the outlet box 25 is then disposed at the end of the exchanger.
  • the treated gas passages 21 lead to an end outlet box 25.
  • an ejector is here formed of two parts fixed to the plate 122, namely an upstream part 131 pierced with a passage 132 of diameter d and a downstream portion 133 pierced with a passage 134 of diameter D.
  • the transverse surface of the passage D is equal to 1.5 to 5 times the transverse surface of the passage d, advantageously from 2 to 4 and preferably of the order of 3. This arrangement allows flexibility of adjustment making it possible to have a constant expansion pressure downstream for flow rates varying within wide limits, for example from 40% to 120% with also very different upstream pressures.
  • FIG. 19 is an alternative embodiment of FIG. 18 where the passages 132 ′ and 134 ′ are made directly in the plate 122.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Separation By Low-Temperature Treatments (AREA)
EP80400560A 1979-05-18 1980-04-25 Ensemble d'échange thermique du genre échangeur de chaleur à plaques Expired EP0019508B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT80400560T ATE1684T1 (de) 1979-05-18 1980-04-25 Thermische austauschvorrichtung nach art eines plattenwaermeaustauschers.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR7912727 1979-05-18
FR7912727A FR2456924A2 (fr) 1979-05-18 1979-05-18 Ensemble d'echange thermique du genre echangeur de chaleur a plaques

Publications (2)

Publication Number Publication Date
EP0019508A1 EP0019508A1 (fr) 1980-11-26
EP0019508B1 true EP0019508B1 (fr) 1982-10-20

Family

ID=9225645

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80400560A Expired EP0019508B1 (fr) 1979-05-18 1980-04-25 Ensemble d'échange thermique du genre échangeur de chaleur à plaques

Country Status (6)

Country Link
US (1) US4330308A (enrdf_load_stackoverflow)
EP (1) EP0019508B1 (enrdf_load_stackoverflow)
JP (1) JPS55155195A (enrdf_load_stackoverflow)
AT (1) ATE1684T1 (enrdf_load_stackoverflow)
DE (1) DE3060964D1 (enrdf_load_stackoverflow)
FR (1) FR2456924A2 (enrdf_load_stackoverflow)

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2499226B1 (fr) * 1981-02-05 1985-09-27 Air Liquide Procede et installation de liquefaction d'un gaz
FR2685071B1 (fr) * 1991-12-11 1996-12-13 Air Liquide Echangeur de chaleur indirect du type a plaques.
DE69328612T2 (de) * 1992-12-25 2000-08-31 Idemitsu Petrochemical Co., Ltd. Polyolefinharz und dieses Harz enthaltende Zusammensetzung
FR2718836B1 (fr) * 1994-04-15 1996-05-24 Maurice Grenier Echangeur de chaleur perfectionné à plaques brasées.
EP0723125B1 (en) * 1994-12-09 2001-10-24 Kabushiki Kaisha Kobe Seiko Sho Gas liquefying method and plant
FR2733823B1 (fr) * 1995-05-04 1997-08-01 Packinox Sa Echangeur thermique a plaques
US5558748A (en) * 1995-05-12 1996-09-24 Basf Corporation Plate-type distillation/condensation apparatus and method of use
FR2751402B1 (fr) * 1996-07-19 1998-10-09 Packinox Sa Installation d'echange thermique entre au moins trois fluides
US6044902A (en) * 1997-08-20 2000-04-04 Praxair Technology, Inc. Heat exchange unit for a cryogenic air separation system
FR2774755B1 (fr) * 1998-02-09 2000-04-28 Air Liquide Condenseur a plaques brasees perfectionne et son application aux doubles colonnes de distillation d'air
JP3100371B1 (ja) * 1999-04-28 2000-10-16 春男 上原 蒸発器
FR2797942B1 (fr) * 1999-08-24 2001-11-09 Air Liquide Vaporiseur-condenseur et installation de distillation d'air correspondante
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
FR2812935B1 (fr) * 2000-08-08 2002-10-18 Air Liquide Echangeur thermique a blocs echangeurs multiples a ligne d'alimentation en fluide a distribution uniforme, et vaporiseur-condenseur comportant un tel echangeur
US6349566B1 (en) 2000-09-15 2002-02-26 Air Products And Chemicals, Inc. Dephlegmator system and process
DE10137103A1 (de) * 2001-07-30 2003-02-13 Linde Ag Mehrstöckiger Kondensator-Verdampfer
US7353864B2 (en) * 2005-12-23 2008-04-08 Hamilton Sundstrand Corporation Apparatus for reducing thermal fatigue in heat exchanger cores
US7779899B2 (en) * 2006-06-19 2010-08-24 Praxair Technology, Inc. Plate-fin heat exchanger having application to air separation
DE102011106004A1 (de) 2010-08-06 2012-02-09 Linde Aktiengesellschaft Plattenwärmetauscher mit Zwei-Phasen-Zuspeisung
CN102654376A (zh) * 2012-04-20 2012-09-05 苏州制氧机有限责任公司 一种主换热器中板翅式热交换器斜边空气抽口装置
CN102654375A (zh) * 2012-04-20 2012-09-05 苏州制氧机有限责任公司 一种主换热器中板翅式热交换器空气抽口装置
JP6623244B2 (ja) * 2018-03-13 2019-12-18 株式会社神戸製鋼所 再液化装置
US10982898B2 (en) 2018-05-11 2021-04-20 Air Products And Chemicals, Inc. Modularized LNG separation device and flash gas heat exchanger
US12013194B2 (en) * 2019-04-29 2024-06-18 Hamilton Sundstrand Corporation Asymmetric cross counter flow heat exchanger
FR3099557B1 (fr) 2019-08-01 2021-07-30 Air Liquide Procédé de liquéfaction de gaz naturel avec circulation améliorée d’un courant réfrigérant mixte
FR3099563B1 (fr) * 2019-08-01 2021-07-30 Air Liquide Echangeur de chaleur avec configuration de passages et structures d’échange thermique améliorées
FR3099560B1 (fr) 2019-08-01 2021-07-02 Air Liquide Procédé de liquéfaction de gaz naturel avec injection améliorée d’un courant réfrigérant mixte
FR3099559B1 (fr) 2019-08-01 2021-07-16 Air Liquide Procédé de liquéfaction de gaz naturel avec configuration d’échangeur améliorée

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1925480U (de) 1962-04-19 1965-10-14 Mannesmann Meer Ag Transportables, montagefertiges teilstueck fuer foerderbruecken.
DE1152432B (de) * 1962-04-21 1963-08-08 Linde Eismasch Ag Platten-Kondensator-Verdampfer, insbesondere fuer Gas- und Luftzerleger
JPS4936109B1 (enrdf_load_stackoverflow) * 1965-11-15 1974-09-27
FR2008887B1 (enrdf_load_stackoverflow) * 1968-05-20 1973-12-07 Kobe Steel Ltd
US3587731A (en) * 1968-07-22 1971-06-28 Phillips Petroleum Co Plural refrigerant tray type heat exchanger
FR2053109A7 (en) * 1969-07-23 1971-04-16 British Oxygen Co Ltd Distributors for gas/liquid mixture over - heat exchanger inlet surface
DE2206620B2 (de) * 1972-02-11 1981-04-02 Linde Ag, 6200 Wiesbaden Anlage zum Verflüssigen von Naturgas
DE2438443C2 (de) * 1974-08-09 1984-01-26 Linde Ag, 6200 Wiesbaden Verfahren zum Verflüssigen von Erdgas
FR2384221A1 (fr) * 1977-03-16 1978-10-13 Air Liquide Ensemble d'echange thermique du genre echangeur a plaques

Also Published As

Publication number Publication date
JPS55155195A (en) 1980-12-03
EP0019508A1 (fr) 1980-11-26
DE3060964D1 (en) 1982-11-25
FR2456924A2 (fr) 1980-12-12
US4330308A (en) 1982-05-18
JPH0154639B2 (enrdf_load_stackoverflow) 1989-11-20
ATE1684T1 (de) 1982-11-15

Similar Documents

Publication Publication Date Title
EP0019508B1 (fr) Ensemble d'échange thermique du genre échangeur de chaleur à plaques
EP0546947B1 (fr) Echangeur de chaleur indirect du type à plaques
EP0130122B2 (fr) Dispositif pour vaporiser un liquide par échange de chaleur avec un deuxième fluide et installation de distillation d'air comprenant un tel dispositif
FR2718836A1 (fr) Echangeur de chaleur perfectionné à plaques brasées.
EP3479044B1 (fr) Echangeur de chaleur comprenant un dispositif de distribution d'un melange liquide/gaz
FR2563620A1 (fr) Echangeur de chaleur du type a plaques
EP3830511B1 (fr) Procede d'echange de chaleur
EP0566435B1 (fr) Echangeur de chaleur à ruissellement et installation de distillation d'air comportant un tel échangeur
FR2684437A1 (fr) Echangeur de chaleur, notamment pour reacteurs hypersoniques, comportant un entretoisement pour les tubes de sa matrice.
EP1179724B1 (fr) Echangeur thermique à blocs échangeurs multiples à ligne d'alimentation en fluide à distribution uniforme, et vaporiseur-condenseur comportant un tel échangeur
FR2571837A1 (fr) Appareil de rechauffage de fluide
EP1088578A1 (fr) Vaporiseur-condenseur à thermosiphon et installation de distillation d'air correspondante
EP0738862B1 (fr) Echangeur de chaleur à plaques brasées
EP0058106A2 (fr) Procédé et installation de liquéfaction d'un gaz
EP0507649B1 (fr) Procédé de vaporisation d'un liquide, échangeur de chaleur pour sa mise en oeuvre, et application à une installation de distillation d'air à double colonne
FR2515803A1 (fr) Echangeur de chaleur comportant un faisceau de tubes paralleles pouvant etre sollicite par de l'air, notamment pour la climatisation de l'habitacle d'un vehicule automobile
EP0553340B1 (fr) Echangeur a plaques
EP1230522B1 (fr) Vaporiseur-condenseur et installation de distillation d'air correspondante
FR3099563A1 (fr) Echangeur de chaleur avec configuration de passages et structures d’échange thermique améliorées
EP4078065B1 (fr) Dispositif mélangeur favorisant une distribution homogène d'un mélange diphasique, installation d'échange de chaleur et procédé de mélange associé
FR3103543A1 (fr) Echangeur de chaleur avec agencement de dispositifs mélangeurs améliorant la distribution d’un mélange diphasique
FR2718835A1 (fr) Echangeur de chaleur à plaques brasées.
FR3151082A3 (fr) Procédé de fabrication d’un échangeur comprenant des passages dotés d’au moins un organe de support et échangeur fabriqué par un tel procédé
WO2020174172A1 (fr) Méthode de fabrication d'un appareil d'échange de chaleur et de matière
BE419055A (enrdf_load_stackoverflow)

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): AT BE CH DE FR GB IT LU NL SE

17P Request for examination filed
GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Designated state(s): AT BE CH DE FR GB IT LU NL SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19821020

Ref country code: NL

Effective date: 19821020

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 19821020

REF Corresponds to:

Ref document number: 1684

Country of ref document: AT

Date of ref document: 19821115

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3060964

Country of ref document: DE

Date of ref document: 19821125

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Effective date: 19821201

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19830430

Ref country code: LI

Effective date: 19830430

Ref country code: CH

Effective date: 19830430

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19960311

Year of fee payment: 17

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 19960318

Year of fee payment: 17

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19960319

Year of fee payment: 17

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19960325

Year of fee payment: 17

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19970425

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Effective date: 19970430

BERE Be: lapsed

Owner name: L' AIR LIQUIDE S.A. POUR L'ETUDE ET L'EXPLOITATION

Effective date: 19970430

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19970425

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19971231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19980101

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT