EP3077750B1 - Échangeur de chaleur avec canal collecteur pour l'extraction d'une phase liquide - Google Patents

Échangeur de chaleur avec canal collecteur pour l'extraction d'une phase liquide Download PDF

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Publication number
EP3077750B1
EP3077750B1 EP14806185.6A EP14806185A EP3077750B1 EP 3077750 B1 EP3077750 B1 EP 3077750B1 EP 14806185 A EP14806185 A EP 14806185A EP 3077750 B1 EP3077750 B1 EP 3077750B1
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EP
European Patent Office
Prior art keywords
heat exchanger
collecting channel
medium
shell
liquid phase
Prior art date
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EP14806185.6A
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German (de)
English (en)
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EP3077750A1 (fr
Inventor
Stefan Kayser
Steffen Brenner
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Linde GmbH
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Linde GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J5/00—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants
    • F25J5/002—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger
    • F25J5/005—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger in a reboiler-condenser, e.g. within a column
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F28D21/0017—Flooded core 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
    • 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
    • F28D9/0006—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 plate-like or laminated conduits being enclosed within a pressure vessel
    • 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
    • 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
    • F28F9/005—Other auxiliary members within casings, e.g. internal filling means or sealing means
    • 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
    • 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
    • F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
    • F28D2021/0064—Vaporizers, e.g. evaporators

Definitions

  • the invention relates to a heat exchanger such as in " The standards of the brazed aluminum plate-fin heat exchanger manufacturer's association (ALPEMA) ", third edition, 2010, page 67 shown in Figure 9-1. It has a shell, which encloses a jacket space, and at least one plate heat exchanger ("core”) arranged in the shell space.
  • core plate heat exchanger
  • Such a design of a heat exchanger is also called “core-in-shell” or “block-in-shell” heat exchanger.
  • a first medium which forms a bath surrounding the plate heat exchanger during operation of the heat exchanger and rises from bottom to top in the plate heat exchanger (along the vertical) (so-called thermosiphon effect), can be converted into indirect heat transfer with a second heat transfer medium Medium are brought (for example, to be liquefied gaseous phase or a liquid phase to be cooled), which is preferably performed in countercurrent or cross flow to the first medium in the plate heat exchanger.
  • a resulting gaseous phase of the first medium collects in the shell space above the plate heat exchanger and can be deducted from there.
  • at least part of the liquid phase of the first medium can be withdrawn from the jacket space via an associated outlet nozzle.
  • the liquid phase emerging at the upper end of the plate heat exchanger together with the resulting gaseous phase is returned to the bath surrounding the at least one plate heat exchanger.
  • the entire quantity of liquid of the first medium is usually introduced into the jacket space through at least one inlet connection. A portion of this liquid flows in a vertical direction down, then enters from below into the at least one plate heat exchanger and is partially evaporated there.
  • the other part namely the liquid phase of the first medium to be withdrawn from the shell space (it is preferably a process-related, controlled and largely continuous withdrawal of Liquid from the core-in-shell heat exchanger and preferably not a withdrawal of liquid from the heat exchanger for emptying the jacket space), flows in a predominantly horizontal direction to the outlet nozzle for the liquid phase of the first medium.
  • the maximum volume flow of this cross flow occurs in the region of the outlet nozzle for the liquid phase of the first medium.
  • the horizontal and the vertical flow can influence each other negatively.
  • relatively high flow velocities may occur, which may adversely affect the operation of the core-in-shell heat exchanger.
  • the required overpressure to overcome the respective element is a function of the volume flow.
  • the rule is that the higher the volume flow, the higher the overpressure must be.
  • the present invention is therefore based on the object to provide an improved heat exchanger of the type mentioned. This problem is solved by a heat exchanger with the features of claim 1.
  • a collecting duct arranged in the jacket space which has a wall which defines an interior of the collecting channel and extends longitudinally in the jacket space along a horizontal extension direction.
  • a plurality of plate heat exchangers which are used e.g. can be operated in parallel or in series.
  • Such plate heat exchangers generally have a plurality of mutually parallel plates or plates, which form a plurality of heat transfer passages for participating in the heat transfer media.
  • a preferred embodiment of a plate heat exchanger has a plurality of corrugated or folded sheets (so-called fins), which are each arranged between two parallel separator plates or plates of the plate heat exchanger, wherein the two outermost layers of the plate heat exchanger are formed by cover plates.
  • fins corrugated or folded sheets
  • cover plates cover plates
  • first heat transfer passages are open upwards and downwards along the vertical and in particular not closed by end strips so that the liquid phase of the first medium can enter the first heat transfer passages from below and exit the first heat transfer passages as a liquid or gaseous phase at the top of the plate heat exchanger can.
  • cover plates, separator plates, fins and side bars are preferably made of aluminum and are used e.g. soldered together in an oven. Via corresponding headers with nozzles media such as e.g. the second medium are introduced into or removed from the associated heat transfer passages.
  • the jacket of the heat exchanger may, in particular, have a circumferential (circular) cylindrical wall, which is preferably oriented in the case of a heat exchanger arranged as intended, so that the longitudinal axis (cylinder axis) of the wall or of the jacket extends along the horizontal.
  • the jacket preferably has mutually opposite walls connected to that wall, which extend transversely to the horizontal or longitudinal axis.
  • the collecting channel (with respect to a heat exchanger arranged as intended) is arranged in a lower region of the jacket space, for example, on an inner side of the jacket facing the inner space.
  • the collecting channel between the shell, in particular the circumferential wall of the shell, and the at least one plate heat exchanger is arranged.
  • the collecting channel is arranged along the vertical below the at least one plate heat exchanger.
  • the plate heat exchanger along the horizontal can also be arranged next to the plate heat exchanger.
  • the collecting channel is preferably along the vertical below the liquid level of the liquid phase of the first medium in the shell space arranged so that the liquid phase of the first medium is correspondingly removable with the collecting channel from the shell space.
  • the at least one plate heat exchanger is designed to cool the second medium guided in the second heat transfer passages against the first medium guided in the adjacent first heat transfer passages and / or at least partially to liquefy, so that forms a gaseous phase of the first medium, wherein the jacket space is formed for collecting the gaseous phase.
  • the at least one plate heat exchanger is formed so that the first medium rises during operation of the heat exchanger in the at least one plate heat exchanger, namely in designated first or second heat transfer passages of the at least one plate heat exchanger, in particular the at least one plate heat exchanger to is formed to lead the second medium in the second heat transfer passages in countercurrent or in cross flow to the first medium.
  • the collection channel for withdrawing the liquid phase of the first medium is flow-connected to an outlet nozzle, which is arranged in particular on an underside of the jacket, so that the liquid phase of the first medium can be withdrawn via those outlet nozzle from the collection channel.
  • the collecting channel can also be connected in a flow-conducting manner with a plurality of, for example two or three, outlet nozzles, which are preferably distributed over the length of the collecting channel.
  • the collection channel extends along an extension direction which is aligned parallel to the longitudinal axis (cylinder axis) of the shell or along the horizontal, and thereby preferably transversely to said extension direction (longitudinal axis) an eg tubular (in particular circular) or, for example, has an angular, in particular rectangular cross-section.
  • the collecting duct extends at least over 60%, 70%, 80% or 90% of the length of the heat exchanger along the extension direction, preferably over the entire length of the jacket space of the heat exchanger along the extension direction.
  • the collecting channel further comprises a wall which encloses an interior of the collecting channel, in which the liquid phase can flow to said outlet nozzle.
  • that portion of that wall of the collecting channel which points towards an underside of the heat exchanger or points downwards along the vertical is referred to as the lower side of the collecting channel, and the opposite region of the wall of the collecting channel facing the upper side of the heat exchanger accordingly provides
  • the top and bottom of the collecting channel are preferably interconnected by along the longitudinal axis of the shell extending side walls of the collecting channel.
  • the front side of the collecting channel is preferably limited by opposing end faces, each connecting the top, the bottom and the side walls together.
  • the front side of the collecting channel can also be designed open.
  • a variant of the invention further provides that one or more of the aforementioned areas of the wall of the collecting channel are formed by the jacket of the heat exchanger.
  • the underside of the collecting channel or the underside of the wall of the collecting channel is formed by the jacket of the heat exchanger.
  • the side walls and end faces are therefore attached to the jacket corresponding to the jacket space.
  • the collecting channel preferably has at least one inlet opening, particularly preferably a plurality of inlet openings, which is or are formed in particular on the upper side of the collecting channel and possibly on the opposite side walls of the collecting channel.
  • the inlet openings formed on the upper side of the collecting channel are preferably slit-shaped, whereas inlet openings provided on the side walls preferably have a circular contour (for example bores).
  • the distances of adjacent inlet openings in particular the distances of the top or on the side walls provided inlet openings, to remove the respective end face of the collecting channel. That is, the two adjacent entrance openings, which are located closer to one of the end faces of the collecting channel, preferably have a smaller distance from each other along the direction of extension of the collecting channel than two adjacent inlet openings, which are arranged towards the center of the collecting channel (with respect to the extension direction).
  • the number, distribution, size and / or shape of the inlet openings are selected so that the velocity field of the liquid phase of the first medium in the collecting channel is preferably uniform. In particular, so that the flow in the adjacent shell space should be influenced as little negative.
  • the cross-sectional area (and optionally contour) of the collecting channel in a plane perpendicular to the extension direction of the collecting channel is selected such that sets a preferably uniform velocity field of the liquid phase of the first medium in the collecting channel. In particular, so that the flow in the adjacent shell space should be influenced as little negative.
  • This is preferably supported by an enlargement / enlargement of the cross section of the collecting channel towards the outlet nozzle and / or by a defined arrangement, shape and size of the inlet openings on the collecting channel.
  • the outlet nozzle opens centrally into the collecting channel or interior of the collecting channel.
  • the heat exchanger may have a plurality of arranged in the shell space, inventive collecting channels, which are in flow communication with the outlet nozzle or in each case with one or more outlet nozzle.
  • the positions, dimensions and orientations of these collection channels are preferably chosen so that the velocity field of the liquid phase of the first medium in the respective collection channel is preferably uniform.
  • the sheath can of course also have a plurality of outlet stubs, which may be connected to a collecting channel as described above or possibly to a plurality of collecting channels of the type described above.
  • the inlet openings in particular the inlet openings on the side walls of the collecting channel have a defined distance along the vertical to the inside of the jacket on the underside of the jacket. This allows the limitation of the liquid withdrawal, e.g. in the event of a plant standstill or interruption of the inlet flow (i.e., a defined residual quantity remains in the shell space).
  • liquid withdrawal can also be achieved by a corresponding arrangement of the collecting channel in the jacket space, for example by the collecting channel is arranged at a defined height above the underside of the shell.
  • each inlet opening can be provided with vortex breakers, which prevent the formation or intensification of vertebrae.
  • each inlet opening can be configured individually.
  • the velocity field in the core-in-shell heat exchanger can be better controlled by the solution according to the invention.
  • the neutrraum or shell space is better utilized in its overall size.
  • smaller jacket sizes can be achieved.
  • the deducted Liquid can be selectively removed from areas of the original or shell space in which little liquid flows for the purpose of partial evaporation in the plate heat exchanger in the vertical direction downwards. This prevents in particular that the currents influence each other negatively.
  • the collecting duct is a non-pressure-bearing component and must therefore meet only low requirements for wall thickness, material and manufacturing.
  • its cross-sectional shape can be freely designed without affecting its strength.
  • the positions of the liquid nozzles of the core-in-shell heat exchanger are more variable.
  • the outlet nozzle can be arranged on the underside of the jacket in the middle or at the edge. As a result, the construction of the surrounding components is less restricted.
  • FIG. 1 shows in connection with the Figures 2 and 3 a heat exchanger 1, which has a transverse, (circular) cylindrical shell 2, which has a jacket space 3 of the heat exchanger 1 limited.
  • the jacket 2 in this case has a circumferential, cylindrical wall 14, which is delimited by two opposing walls 15 frontally.
  • a plate heat exchanger 4 is arranged, which has a plurality of parallel heat transfer passages.
  • the plate heat exchanger 4 has a plurality of e.g. corrugated or folded sheets (so-called fins), which are each arranged between two flat partition plates or plates of the plate heat exchanger 4.
  • fins e.g. corrugated or folded sheets
  • the two outermost layers are formed by cover plates of the plate heat exchanger 4; towards the sides are provided between each two adjacent partition plates or separating and cover plates.
  • the shell space 3 is filled during operation of the heat exchanger 1 via a provided on an upper side 8 of the shell 2 inlet nozzle 60 with a first medium F1.
  • This inlet flow into the heat exchanger 1 is usually two-phase, but can only be liquid.
  • the liquid phase L1 of the first medium F1 then forms a bath surrounding the plate heat exchanger 4, the gaseous phase G1 of the first medium F1 accumulating above the liquid phase L1 in an upper region 34 of the jacket space 3.
  • the liquid phase L1 of the first medium F1 can ascend in associated first heat transfer passages of the plate heat exchanger 4 and is partly through indirect heat transfer by a second medium to be cooled F2, which is performed in cross flow to the first medium F1 in associated second heat transfer passages of the plate heat exchanger evaporated.
  • the resulting gaseous phase G1 of the first medium F1 can emerge at an upper end of the plate heat exchanger 4 and rises in the shell space 3 of the heat exchanger 1, from where it can be withdrawn via corresponding outlet nozzle 40 on the top 8 of the shell 2.
  • a part of the liquid phase L1 circulates in the shell space 3, wherein that part is conveyed in the plate heat exchanger 4 in the first heat transfer passages from bottom to top and then flows outside the plate heat exchanger 4 in the shell space 3 back down.
  • the second medium F2 is passed through a suitable inlet port O in the plate heat exchanger 4 and after passing through the associated second heat transfer passages via an outlet port O 'cooled or liquefied withdrawn from the plate heat exchanger 4.
  • a box-shaped collecting channel 5 is arranged on an inner side 2 a of the jacket 2 facing the jacket space 3, which extends along an extension direction 7.
  • the collecting channel 5 is designed, in particular, longitudinally extended and accordingly has a greater extent along the direction of extent 7 than transversely to that direction of extent 7.
  • the collecting channel 5 has a wall W which delimits an interior I of the collecting channel 5, through which the liquid phase L1 of the first medium F1 is withdrawn from the jacket space 3.
  • the wall W has in detail an upper side 9 and two side walls 11 extending therefrom, which extend along the extension direction 7 and are connected to one another via a bottom 9 (bottom side) 10 of the collecting channel 5 which is formed by the jacket 2 ,
  • the collecting channel 5 or its wall W has two end faces 11a, 11b, which lie opposite one another along the extension direction 7.
  • the collecting channel 5 is further connected to an outlet nozzle 6 of the jacket 2, which opens at the bottom 10 of the collecting channel 5 into the collecting channel 5, so that the liquid via the inlet openings 12, 13 into the interior I of the collecting channel 5 liquid phase L1 of the first Medium F1 can be withdrawn from the collection channel 5 via the outlet nozzle 6.
  • the outlet nozzle 6 is preferably arranged centrally along the direction of extent 7 on the collecting channel 5, the upper side 9 of the collecting channel 5 preferably having two outlet sections 6 towards the rising portions 9a, 9b, which preferably meet above the outlet nozzle 6.
  • the cross-section of the collecting channel 5 preferably widens (widens) in each case from the end faces 11a, 11b of the collecting channel 5, starting in the direction of the outlet nozzle 6 in order to obtain in the collecting channel 5 as homogeneous as possible a velocity field of the liquid phase L1 of the first medium F1.
  • the flow of the liquid phase L1 in the adjacent shell space 3 should thus be influenced as negatively as possible.

Claims (15)

  1. Echangeur de chaleur (1) assurant un transfert indirect de chaleur entre un premier fluide (F1) et un deuxième fluide (F2) et présentant :
    une enveloppe (2) qui présente un espace enveloppé (3) qui reprend une phase liquide (L1) du premier fluide (F1) et
    au moins un échangeur de chaleur (4) à plaques qui présente des premiers passages de transfert de chaleur reprenant le premier fluide (F1) ainsi que des deuxièmes passages de transfert de chaleur reprenant le deuxième fluide (F2), de telle sorte que de la chaleur puisse être transférée indirectement entre les deux fluides (F1, F2),
    l'échangeur de chaleur (4) à plaques étant disposé dans l'espace enveloppé (3) de telle sorte qu'il puisse être entouré par une phase liquide (L1) du premier fluide (F1) située dans l'espace enveloppé (3), caractérisé en ce que
    un canal de collecte (5) est prévu dans l'espace enveloppé (3) pour extraire la phase liquide (L1) du premier fluide (F1) hors de l'espace enveloppé (3), le canal de collecte (5) présentant une paroi (W) qui définit un espace intérieur (I) du canal de collecte (5) et dont l'extension longitudinale s'étend dans une direction horizontale (7) dans l'espace enveloppé (3).
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que le canal de collecte (5) est disposé dans une partie inférieure (33) de l'espace enveloppé (3).
  3. Echangeur de chaleur selon les revendications 1 ou 2, caractérisé en ce que le canal de collecte (5) est disposé en dessous du ou des échangeurs de chaleur (4) à plaques ou à côté du ou des échangeurs de chaleur (4) à plaques et en particulier entre l'enveloppe (2) et le ou les échangeurs de chaleur (4) à plaques.
  4. Echangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que l'espace enveloppé (3), en particulier une partie supérieure (34) de l'espace enveloppé (3), est configuré pour collecter une phase gazeuse (G1) du premier fluide (F1) qui est formée en particulier lors du transfert de chaleur indirect entre les deux fluides (F1, F2).
  5. Echangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que le ou les échangeurs de chaleur (4) à plaques sont configurés de telle sorte que le premier fluide (F1) remonte dans le ou les échangeurs de chaleur (4) à plaques lorsque l'échangeur de chaleur (1) est en fonctionnement, le ou les échangeurs de chaleur (4) à plaques étant configurés pour guider le deuxième fluide (F2) dans le ou les échangeurs de chaleur (4) à plaques à contre-courant ou à courants croisés par rapport au premier fluide (F1).
  6. Echangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que plusieurs échangeurs de chaleur (4) à plaques sont disposés dans l'espace enveloppé (3).
  7. Echangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que le canal de collecte (5), en particulier l'espace intérieur (I) du canal de collecte (5), est relié à une tubulure de sortie (6) prévue sur l'enveloppe (2) de telle sorte que la phase liquide (L1) du premier fluide (F1) puise être extraite hors de l'espace enveloppé (3) par le canal de collecte (5) et l'intermédiaire de la tubulure de sortie (6).
  8. Echangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que la paroi (W) du canal de collecte (5) s'étend le long du côté inférieur (16) de l'enveloppe (2).
  9. Echangeur de chaleur selon les revendications 7 et 8, caractérisé en ce que la tubulure de sortie (6) débouche au milieu de l'espace intérieur (I) du canal de collecte (5) dans la direction d'extension (7).
  10. Echangeur de chaleur selon la revendication 7 et selon les revendications 8 ou 9, caractérisé en ce que l'espace intérieur (I) du canal de collecte (5) présente dans la direction transversale par rapport à la direction d'extension (7) une section transversale qui s'agrandit en direction de la tubulure de sortie (6) de telle sorte que le champ de vitesse (v) de la phase liquide (L1) du premier fluide (F1) soit aussi régulier que possible dans le canal de collecte (5) et en particulier également que l'écoulement de phase liquide (L1) du premier fluide (F1) dans l'espace enveloppé (3) adjacent soit influencé négativement aussi peu que possible.
  11. Echangeur de chaleur selon l'une des revendications 1 à 10, caractérisé en ce que la paroi (W) du canal de collecte (5) présente un côté supérieur (9) et un côté inférieur (10) opposé, le côté supérieur (9) et le côté inférieur (10) étant reliés l'un à l'autre par des parois latérales (11) mutuellement opposées de la paroi (W) du canal de collecte (5).
  12. Echangeur de chaleur selon l'une des revendications 1 à 11, caractérisé en ce qu'une partie de la paroi (W) du canal de collecte (5), en particulier le côté inférieur (10) de la paroi (W), est formée par l'enveloppe (2).
  13. Echangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que le canal de collecte (5) présente au moins une ouverture d'entrée et en particulier plusieurs ouvertures d'entrée (12, 13) configurées pour permettre l'entrée de la phase liquide (L1) du premier fluide (F1) dans le canal de collecte (5), l'ouverture de sortie ou les ouvertures de sortie (12, 13) étant formées dans la paroi (W), en particulier dans le côté supérieur (9) et/ou dans les parois latérales (11) du canal de collecte (5), le nombre, la répartition, la taille et/ou la forme des ouvertures d'entrée (12, 13) du canal de collecte (5) étant sélectionnés de telle sorte que le champ de vitesse (v) de la phase liquide (L1) du premier fluide (F1) soit aussi régulier que possible dans le canal de collecte (5) et en particulier également que l'écoulement de phase liquide (L1) du premier fluide (F1) dans l'espace enveloppé (3) adjacent soit influencé négativement aussi peu que possible.
  14. Echangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que l'enveloppe (2) présente une paroi cylindrique (14) qui s'étend transversalement à la direction d'extension (7) et qui relie l'une à l'autre deux parois frontales (15) de l'enveloppe (2).
  15. Echangeur de chaleur selon les revendications 7 et 14, caractérisé en ce que la tubulure de sortie (6) est disposée sur la paroi périphérique (14) de l'enveloppe (2) et en particulier dans une partie inférieure (16) de la paroi (14) de l'enveloppe (2).
EP14806185.6A 2013-12-05 2014-12-02 Échangeur de chaleur avec canal collecteur pour l'extraction d'une phase liquide Active EP3077750B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP14806185.6A EP3077750B1 (fr) 2013-12-05 2014-12-02 Échangeur de chaleur avec canal collecteur pour l'extraction d'une phase liquide

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP13005656 2013-12-05
EP14806185.6A EP3077750B1 (fr) 2013-12-05 2014-12-02 Échangeur de chaleur avec canal collecteur pour l'extraction d'une phase liquide
PCT/EP2014/003208 WO2015082061A1 (fr) 2013-12-05 2014-12-02 Échangeur de chaleur muni d'un canal collecteur pour l'extraction d'une phase liquide

Publications (2)

Publication Number Publication Date
EP3077750A1 EP3077750A1 (fr) 2016-10-12
EP3077750B1 true EP3077750B1 (fr) 2018-02-21

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EP (1) EP3077750B1 (fr)
JP (1) JP6509223B2 (fr)
KR (1) KR102232165B1 (fr)
CN (1) CN105980803A (fr)
AU (1) AU2014359786B2 (fr)
CA (1) CA2931254C (fr)
ES (1) ES2666137T3 (fr)
MX (1) MX2016006814A (fr)
RU (1) RU2669991C1 (fr)
TR (1) TR201807001T4 (fr)
WO (1) WO2015082061A1 (fr)

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KR101969581B1 (ko) 2016-11-17 2019-08-13 주식회사 엘지화학 올레핀계 단량체의 회수 장치
JP2023500762A (ja) 2019-11-15 2023-01-11 リンデ ゲゼルシャフト ミット ベシュレンクテル ハフツング 断熱を有する移行部品

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EP3077750A1 (fr) 2016-10-12
JP2016539308A (ja) 2016-12-15
CA2931254C (fr) 2022-01-04
AU2014359786A1 (en) 2016-06-09
KR20160094422A (ko) 2016-08-09
CN105980803A (zh) 2016-09-28
WO2015082061A1 (fr) 2015-06-11
US10443947B2 (en) 2019-10-15
CA2931254A1 (fr) 2015-06-11
RU2669991C1 (ru) 2018-10-17
JP6509223B2 (ja) 2019-05-08
ES2666137T3 (es) 2018-05-03
MX2016006814A (es) 2016-09-07
KR102232165B1 (ko) 2021-03-24
US20160290731A1 (en) 2016-10-06
AU2014359786B2 (en) 2019-02-28
TR201807001T4 (tr) 2018-06-21

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