EP3555544B1 - Échangeur de chaleur avec dispositif mélangeur liquide/gaz à géométrie de canal améliorée - Google Patents

Échangeur de chaleur avec dispositif mélangeur liquide/gaz à géométrie de canal améliorée Download PDF

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Publication number
EP3555544B1
EP3555544B1 EP17822398.8A EP17822398A EP3555544B1 EP 3555544 B1 EP3555544 B1 EP 3555544B1 EP 17822398 A EP17822398 A EP 17822398A EP 3555544 B1 EP3555544 B1 EP 3555544B1
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EP
European Patent Office
Prior art keywords
channel
plate
mixing device
exchanger according
passages
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.)
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EP17822398.8A
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German (de)
English (en)
French (fr)
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EP3555544A1 (fr
Inventor
Philippe Grigoletto
Natacha Haik-Beraud
Sophie LAZZARINI
Jean-Marc Peyron
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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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Publication of EP3555544A1 publication Critical patent/EP3555544A1/fr
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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
    • 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
    • F28F9/0263—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry or cross-section of header box
    • 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
    • F25J1/0032—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 the feed stream itself or separated fractions from it, i.e. "internal refrigeration"
    • F25J1/0045—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 the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by vaporising a liquid return 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
    • F25J1/0243—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
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • 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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04406—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air using a dual pressure main column system
    • F25J3/04412—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air using a dual pressure main column system in a classical double column flowsheet, i.e. with thermal coupling by a main reboiler-condenser in the bottom of low pressure respectively top of high pressure 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
    • 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

Definitions

  • the present invention relates to a heat exchanger comprising series of passages for each of the fluids to be placed in a heat exchange relationship, the exchanger comprising at least one mixing device configured to distribute at least one two-phase liquid / gas mixture in a series of passages
  • An exchanger according to the preamble of claim 1 is known from the document FR 2 563 620 A1 .
  • the present invention can be applied to a heat exchanger which vaporizes at least one flow of liquid-gas mixture, in particular a flow of mixture with several constituents, for example a mixture of hydrocarbons, by heat exchange with at least one other fluid, for example natural gas.
  • the technology commonly used for an exchanger is that of brazed aluminum plate and fin exchangers, which make it possible to obtain very compact devices offering a large exchange surface.
  • These exchangers comprise plates between which are inserted heat exchange waves, formed of a succession of fins or wave legs, thus constituting a stack of vaporization passages and condensation passages, some intended to vaporize refrigerant and the like to condense a circulating gas. Heat exchange between fluids can take place with or without phase change.
  • the sizing of the exchanger is calculated by assuming a uniform distribution of the phases, and therefore a single end of vaporization temperature of the liquid phase, equal to the dew point temperature of the mixture.
  • the end of vaporization temperature will depend on the proportion of liquid phase and gas phase in the passages.
  • the temperature profile of the refrigerant will therefore vary according to the passages, or even vary within the same passage. Due to this non-uniform distribution, it may then happen that the circulating fluid (s) in exchange relation with the two-phase mixture have a temperature at the outlet of the exchanger higher than that expected, which consequently degrades the performance. of the heat exchanger.
  • the document FR-A-2563620 describes such an exchanger in which a grooved bar is inserted in the series of passages intended to channel the two-phase mixture.
  • This mixing device has separate inlets for a liquid phase and a gas phase opening into a common mixing volume provided with an outlet for distributing the liquid-gas mixture to the heat exchange zone.
  • the liquid phase supplying the mixing device is then inevitably in a heat exchange situation with the circulating fluid (s) circulating in the adjacent passages of the other series of passages. This can cause the start of vaporization of the liquid phase even within the corresponding inlets, thereby leading to an unequal distribution of the two phases of the mixture in certain passages of the series as well as in certain zones within the same passage.
  • one solution would be to install the mixing device in a zone of the exchanger in which no other fluid is circulating. It would then be necessary to place the mixing device at one end of the exchanger, free of any means of discharge or supply of fluid, which would require restructuring the exchanger as a whole and would necessarily lead to an increase in its size. In addition, such a solution does not allow the introduction of the two-phase mixture in the middle of the exchanger, which may be desirable in cases where the specificities of the process require it.
  • the object of the present invention is to resolve all or part of the above-mentioned problems, in particular by proposing a heat exchanger in which the distribution of the liquid and gas phases of a mixture is as uniform as possible, and this without complicating any excessively the structure of the exchanger, nor increase its size.
  • the present invention can be applied to a heat exchanger which vaporizes at least one flow of liquid-gas mixture, in particular a flow of mixture with several constituents, for example a mixture of hydrocarbons, by heat exchange with at least one. other fluid, for example natural gas.
  • natural gas refers to any composition containing hydrocarbons including at least methane. This includes a "crude” composition (prior to any treatment or washing), as well as any composition that has been partially, substantially or fully treated for the reduction and / or elimination of one or more compounds, including, but not limited to. limit, sulfur, carbon dioxide, water, mercury and some heavy and aromatic hydrocarbons.
  • FIGS. 1 and 2 illustrate a heat exchanger 1 according to an embodiment of the invention comprising a stack of plates 2a, 2b, 2c ... which extend in two dimensions, in a longitudinal direction z and a lateral direction y.
  • the plates 2a, 2b, 2c ... are arranged parallel one above the other with spacing and thus form a plurality of passages for fluids in indirect heat exchange relation via said plates.
  • the lateral direction is represented therein orthogonal to the longitudinal direction z and parallel to the plates 2a, 2b, 2c ....
  • each passage has a parallelepipedal and flat shape.
  • the gap between two successive plates is small compared to the length and width of each successive plate.
  • the exchanger 1 may include a number of plates greater than 20, or even greater than 100, defining between them a first series of passages 10 for channeling at least one refrigerant F1, and a second series of passages 20 (not visible on the Figure 1 ) to channel at least one circulating fluid F2, the flow of said fluids taking place generally in the longitudinal direction z.
  • the passages 10 of the first series can be arranged, in whole or in part, alternating or adjacent to all or part of the passages 20 of the second series.
  • the exchanger 1 comprises distribution and evacuation means 43, 52 configured to distribute the various fluids selectively in the passages 10, 20, as well as to evacuate said fluids from said passages 10, 20.
  • the sealing of the passages 10, 20 along the edges of the plates 2a, .. is generally ensured by lateral and longitudinal sealing strips 4 fixed to the plates 2a, ...
  • the lateral sealing strips 4 do not block off not completely the passages 10, 20 but advantageously leave fluid inlet and outlet openings located in the diagonally opposite corners of the passages.
  • the openings of the passages 10 of the first series are arranged in coincidence one above the other, while the openings of the passages 20 of the second series are arranged at the opposite corners.
  • the openings placed one above the other are united respectively in semi-tubular collectors 40, 45, 50, 55, through which the distribution and evacuation of the fluids take place.
  • the semi-tubular collectors 50, 45 are used for the introduction of fluids into the exchanger 1 and the semi-tubular collectors 40, 55 are used for the evacuation of these fluids out of the exchanger 1.
  • the supply manifold of one of the fluids and the discharge manifold of the other fluid are located at the same end of the exchanger, the fluids F1, F2 thus circulating in counter-current in exchanger 1.
  • the refrigerant and circulating fluids can also circulate in co-current, the means for supplying one of the fluids and the means for discharging the other fluid then being located at opposite ends of the 'exchanger 1.
  • the longitudinal direction is oriented vertically when the exchanger 1 is in operation.
  • the refrigerant F1 flows generally vertically and in the upward direction.
  • Other directions and direction of flow of the fluids F1, F2 can of course be envisaged, without departing from the scope of the present invention.
  • one or more refrigerants F1 and one or more circulating fluids F2 of different types can flow within passages 10, 20 of the first and second series of the same exchanger.
  • the distribution and evacuation means 43, 52 advantageously comprise distribution waves 44, 51, 54, arranged between two successive plates 2a, 2b, ... in the form of corrugated sheets, which extend from the openings d entry and exit.
  • the distribution waves 44, 51, 54 ensure the uniform distribution and the recovery of the fluids over the entire width of the passages 10, 20.
  • the passages 10, 20 advantageously comprise heat exchange structures arranged between the plates 2a, 2b, .... These structures have the function of increasing the heat exchange surface area of the exchanger.
  • the heat exchange structures are in contact with the fluids circulating in the passages and transfer heat flows by conduction to the adjacent plates, to which they can be fixed by brazing, which increases the mechanical resistance of the exchanger.
  • the heat exchange structures also have a function of spacers between the plates, in particular during assembly by brazing the exchanger and to prevent any deformation of the plates during the use of fluids under pressure. They also ensure the guidance of the fluid flows in the passages of the exchanger.
  • these structures comprise heat exchange waves 11 which advantageously extend along the width and the length of the passages 10, 20, parallel to the plates, in the extension of the distribution waves 44, 51, 54 along the length of the passages 10, 20.
  • the passages 10, 20 of the exchanger thus have a main part of their length constituting the actual heat exchange part, which is lined with a heat exchange structure, said main part being bordered by distribution parts furnished with distribution waves 44, 51, 54.
  • the Figure 1 illustrates a passage 10 of the first series 1 configured to distribute a refrigerant F1 in the form of a two-phase liquid-gas mixture.
  • the refrigerant F1 is separated in a separator device 6 into a gas phase 61 and a liquid phase 62 introduced separately into the exchanger 1 via a side manifold 30 and the manifold 50.
  • the two phases 61, 62 are then mixed with each other by means of a mixing device 3 arranged in the passage 10 and shown schematically on the Figure 1 .
  • several passages 10, or even all of the passages 10 of the first series include a mixing device 3.
  • the Figure 2 is a schematic sectional view, in a plane parallel to the longitudinal direction z and perpendicular to the lateral direction y, of the heat exchanger of the Figure 1 . It shows a stack of passages 10, 20 of the first and second series, mixing devices 3 being arranged in two passages 10.
  • the mixing device 3 advantageously consists of a bar, or rod, housed in a passage 10 and which preferably extends in the section of passage 10 over almost all, if not all, of the height of passage 10, so that the mixing device is in contact with each plate 2a, 2b forming passage 10.
  • the mixing device 3 is advantageously fixed to the adjacent plates 2a and 2b by brazing.
  • the mixing device 3 may have, parallel to the longitudinal direction z, a first dimension comprised between 20 and 200 mm and, parallel to the lateral direction y, a second dimension comprised between 100 and 1,400 mm.
  • the mixing device 3 is delimited in particular by a first surface 3a arranged facing a first plate 2a of the exchanger and a second surface 3b arranged facing a second plate 2b.
  • the second plate 2b forms, with a third plate 2c, the adjacent passage 20.
  • the first and second surfaces 3a, 3b preferably extend generally parallel, that is to say parallel or almost parallel, to the first and second plates 2a and 2b respectively.
  • the mixing device 3 is advantageously of generally parallelepipedal shape.
  • the first and second surfaces 3a, 3b are generally planar but can locally have recesses forming fluid channels, as explained below.
  • the mixer device 3 comprises at least a first channel 31 for channeling a gas phase 61 of the refrigerant F1, the direction of flow of the fluid being symbolized by the arrow 61.
  • the longitudinal section of the second channel 32 decreases towards the second surface 3b.
  • the longitudinal section of the second channel 32, or of an opening of said channel means the section of the channel measured parallel to the second surface 3b, that is to say according to section planes of said channel parallel to the second plate 3b.
  • the first channel 31 extends in the longitudinal direction z and the second channel 32 extends in the lateral direction y.
  • the longitudinal section of the second channel 32 then decreases in the direction represented by the arrow x.
  • the contact surface between the liquid phase 62 and the part of the second plate 2b extending at the level of the mixing device 3 is reduced, which makes it possible to greatly reduce the heat exchanges that can take place between the circulating fluid F2 flowing in the adjacent passage 20 and the liquid phase 62 of the refrigerant F1.
  • the two phases of the mixture are thus distributed as homogeneously as possible within the passages for the two-phase mixture, as well as between the different passages for the two-phase mixture.
  • This solution has the advantages of being easy to implement, of not modifying the size of the exchanger and of not complicating its structure.
  • the longitudinal channel 31 and the second channel 32 are in fluid communication via at least one orifice 34 arranged between the first channel 31 and the second channel 32.
  • the orifice 34 comprises an inlet 342 opening into the second channel 32 and a outlet 341 opening into the first channel 31.
  • One or more orifices 34 may be arranged along the y direction.
  • the longitudinal section of the second channel 32 decreases from the inlet 342 of the orifice 34 towards the second surface 3b.
  • the mixing of the liquid 62 and gas 61 phases takes place generally downstream of the outlet 341 and the two-phase liquid / gas mixture is distributed out of the mixing device through one or more passages 33.
  • the channels 31, 32 and / or the passages 33 may open out at the level of the end faces 35, 36 of the mixing device 3, or recessed towards the interior of the device 3 with respect to said faces 35, 36.
  • the first and second channels 31, 32 are of elongate shape, their length being great compared to their width.
  • the first and second channels 31, 32 pass through the mixing device 3 right through.
  • the second channel 32 extends over almost all, or even all of the width of the passage 10, measured in the lateral direction y.
  • At least one passage 10 of the first series is defined between a first plate 2a and a second plate 2b, the first plate 2a also defining an adjacent passage 20 of the second series immediately adjacent to the passage 10 considered.
  • a mixing device 3 is arranged in the passage 10 of the first series considered.
  • the first channel 31 is formed from a recess formed within the mixing device 3.
  • the first channel 31 may be formed from a recess formed within the mixing device 3 and opening out at the level of the first surface 3a.
  • the second channel 32 is formed from a recess formed within the mixing device 3.
  • the recess forming the second channel 32 opens at the level of the second surface 3b.
  • the second channel 32 then comprises a second open end 321 located at the level of the second surface 3b.
  • the second channel 32 is formed by a blind internal recess.
  • the Figures 3A to 6 illustrate mixing devices 3 comprising a single second channel 32.
  • the device 3 can also advantageously comprise several lateral channels 32 following one another along the longitudinal direction z.
  • the mixing device 3 can comprise one or more longitudinal channels 31.
  • the Figure 3B illustrates a device 3 comprising a row of longitudinal channels 31 succeeding one another along the lateral direction y.
  • the longitudinal channels 31 extend substantially parallel to each other.
  • the first longitudinal channels 31 are advantageously arranged between the second channel 32 and the first surface 3a.
  • the second channel 32 advantageously comprises a first end 322 located at the level of the inlet 342 of the orifice 34 and a second end 321 located on the side of the second surface 3b.
  • the longitudinal section of the second channel 32 decreases so that the ratio between the longitudinal section of the second channel 32 measured at the level of the second end 321 and the longitudinal section of the second channel 32 measured at level of the first end 322 is between 0 and 0.8, preferably between 0.2 and 0.8.
  • Such dimensioning makes it possible to minimize the heat exchanges between the liquid circulating in the second channel 32 and the adjacent fluids.
  • a ratio of longitudinal sections of second channel 32 equal to 0 corresponds to a second channel 32 whose cross section is triangular in shape.
  • the ratio between the longitudinal section of the opening 321 and the width of the second channel 32 measured at the level of the first end 322, or bottom 322, is between 0.2 and 0 , 8.
  • the longitudinal section of the second channel 32 can gradually decrease towards the second surface 3b.
  • the cross section of the second channel 32 is at least partly of frustoconical shape converging towards the second surface 3b.
  • the reduction in the longitudinal section of the second channel 32 can be caused by a lateral constriction 324 of said second channel 32 towards the second surface 3b.
  • the term “constriction” is understood to mean a sudden reduction in the width of the second channel 32, typically a reduction such as the section ratio. longitudinal values defined above is between 0.2 and 0.8, this reduction occurring over a distance typically less than 4 mm, in the direction of the second surface 3b.
  • the constriction 324 takes place in a substantially symmetrical fashion.
  • the constriction is such that the second channel 32 has an inverted T-shaped section, as illustrated in the figures.
  • the second channel 32 can comprise side walls 323 arranged perpendicularly to the bottom 322 and said bottom 322 can be arranged parallel to the longitudinal direction z.
  • Figure 3B remains applicable for a representation of the mixing device 3 in a plane perpendicular to that of the Figures 5 or 6 .
  • the mixing device 3 further comprises a third channel 37 for channeling the gas phase 61 of the refrigerant F1, said third channel 37 extending in the longitudinal direction z, between the second channel 32 and the second surface 3b.
  • this third channel 37 makes it possible to further minimize the heat exchanges between the liquid circulating in the second channel 32 and the fluids circulating in the adjacent passages. This in fact makes it possible to create a gas barrier which acts as a thermal insulator between the second channel and the second plate 2b.
  • the first channel 31 and the third channel 37 may be of distinct or identical shape and number.
  • the opening 321 of the second channel 32 advantageously opens into the third channel 37.
  • the mixing device 3 comprises at least two passages 33 for the two-phase liquid / gas mixture.
  • the exchanger according to the invention is mainly described in the case where the passages 10, 20 extend in the longitudinal direction z, the first channel 31 extending in the longitudinal direction z and the second channel 32 s' extending in a lateral direction y orthogonal to the longitudinal direction z.
  • the reverse is also possible, that is to say a first channel 31 extending in the lateral direction y and a second channel 32 extending in the longitudinal direction z.
  • the lateral y and longitudinal z directions may also not be mutually orthogonal.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (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)
EP17822398.8A 2016-12-16 2017-12-12 Échangeur de chaleur avec dispositif mélangeur liquide/gaz à géométrie de canal améliorée Active EP3555544B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1662581A FR3060721B1 (fr) 2016-12-16 2016-12-16 Echangeur de chaleur avec dispositif melangeur liquide/gaz a geometrie de canal amelioree
PCT/FR2017/053505 WO2018109352A1 (fr) 2016-12-16 2017-12-12 Échangeur de chaleur avec dispositif mélangeur liquide/gaz à géométrie de canal améliorée

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EP3555544A1 EP3555544A1 (fr) 2019-10-23
EP3555544B1 true EP3555544B1 (fr) 2021-02-24

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US (1) US20200109894A1 (ja)
EP (1) EP3555544B1 (ja)
JP (1) JP7019696B2 (ja)
CN (1) CN110234952B (ja)
FR (1) FR3060721B1 (ja)
RU (1) RU2743818C2 (ja)
WO (1) WO2018109352A1 (ja)

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FR3103543B1 (fr) * 2019-11-21 2021-10-22 Air Liquide Echangeur de chaleur avec agencement de dispositifs mélangeurs améliorant la distribution d’un mélange diphasique

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DE3415807A1 (de) * 1984-04-27 1985-10-31 Linde Ag, 6200 Wiesbaden Waermetauscher
RU2005973C1 (ru) * 1990-11-05 1994-01-15 Западно-Сибирский научно-исследовательский и проектно-конструкторский институт технологии глубокого разведочного бурения Теплообменник
CN1236271C (zh) * 2002-12-30 2006-01-11 西安交通大学 低温两相流气液均匀分配板翅式相变换热器
US9151540B2 (en) * 2010-06-29 2015-10-06 Johnson Controls Technology Company Multichannel heat exchanger tubes with flow path inlet sections
CN202382638U (zh) * 2011-12-08 2012-08-15 杭州中泰深冷技术股份有限公司 用于铝制板翅式热交换器的液体均布器
CN103983138A (zh) * 2014-05-16 2014-08-13 杭州杭氧股份有限公司 一种铝制板翅式换热器大气量两相流均布装置
CN203928851U (zh) * 2014-05-16 2014-11-05 杭州杭氧股份有限公司 铝制板翅式换热器大气量两相流均布装置
CN105486106A (zh) * 2015-12-29 2016-04-13 无锡佳龙换热器股份有限公司 一种天然气气液均布换热装置
CN205784010U (zh) * 2016-07-05 2016-12-07 天津商业大学 一种抽气式板翅式换热器

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Also Published As

Publication number Publication date
FR3060721B1 (fr) 2019-08-16
EP3555544A1 (fr) 2019-10-23
RU2019120798A (ru) 2021-01-11
CN110234952B (zh) 2021-06-08
CN110234952A (zh) 2019-09-13
RU2019120798A3 (ja) 2021-01-12
RU2743818C2 (ru) 2021-02-26
JP2020514654A (ja) 2020-05-21
JP7019696B2 (ja) 2022-02-15
WO2018109352A1 (fr) 2018-06-21
FR3060721A1 (fr) 2018-06-22
US20200109894A1 (en) 2020-04-09

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