EP3367034A1 - Échangeur thermique et procédé de distribution d'une phase liquide dans un échangeur thermique - Google Patents

Échangeur thermique et procédé de distribution d'une phase liquide dans un échangeur thermique Download PDF

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Publication number
EP3367034A1
EP3367034A1 EP17020070.3A EP17020070A EP3367034A1 EP 3367034 A1 EP3367034 A1 EP 3367034A1 EP 17020070 A EP17020070 A EP 17020070A EP 3367034 A1 EP3367034 A1 EP 3367034A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
jacket
annular channel
distributor
medium
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP17020070.3A
Other languages
German (de)
English (en)
Other versions
EP3367034B1 (fr
Inventor
Manfred Steinbauer
Christiane Kerber
Jürgen Spreemann
Christoph Seeholzer
Eva Müller
Konrad Braun
Florian Deichsel
Luis Matamoros
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.)
Linde GmbH
Original Assignee
Linde GmbH
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 Linde GmbH filed Critical Linde GmbH
Priority to EP17020070.3A priority Critical patent/EP3367034B1/fr
Priority to US15/902,386 priority patent/US20180245856A1/en
Priority to RU2018106653A priority patent/RU2018106653A/ru
Priority to CN201810155079.3A priority patent/CN108507234A/zh
Publication of EP3367034A1 publication Critical patent/EP3367034A1/fr
Application granted granted Critical
Publication of EP3367034B1 publication Critical patent/EP3367034B1/fr
Priority to CY20191101238T priority patent/CY1122362T1/el
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F28D7/024—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0066—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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates

Definitions

  • the invention relates to a wound heat exchanger for performing an indirect heat transfer between at least a first medium, which is guided in a tube bundle of the heat exchanger, and a second medium or fluid, which is guided in the shell space of the heat exchanger, and a method for distributing a liquid phase of the second medium to the tube bundle of the heat exchanger.
  • Such heat exchangers are e.g. used in LNG systems, wherein the two-phase entering refrigerant or second medium is usually divided into a pre-manifold by gravity separation in gas and liquid phase. This deposition is preferably carried out in an annular channel which extends on the shell inside in the circumferential direction of the shell. The liquid phase of the second medium / refrigerant is then fed directly into the distribution arms connected to the annular channel. From there, the distribution takes place on the tube bundle of the heat exchanger.
  • the weight of the so-called hold-up becomes very large due to the large diameter of the jacket of the heat exchanger and a process-related damming height of the liquid phase, which has a corresponding effect on the static and thus on the wall thicknesses of the heat exchanger.
  • the present invention therefore has the object to provide a heat exchanger, which is improved in terms of the aforementioned problem.
  • the tubesheet is fixed relative to the longitudinal axis above the bottoms of the distributor arms and below the annular channel on the jacket.
  • the at least one tubesheet between the annular channel and the bottoms of the distributor arms is fixed or arranged on the jacket.
  • the term "upper end portions" of the tubes refers in particular to the vertically aligned longitudinal axis of the core tube.
  • the tube bottom defined laterally on the casing is provided with a cylindrical shape Section of the jacket of the heat exchanger connected.
  • the inlet socket provided laterally on the jacket is preferably provided on or fixed to one or the cylindrical section of the jacket of the heat exchanger.
  • the heat exchanger can have a plurality of tubesheets, wherein then each upper end portions of the tubes are combined to form a plurality of groups or tube plugs, wherein the upper end portions of a group or a Rohrzopfes are then connected to an associated tube sheet or anchored in this.
  • all tube sheets are fixed relative to the longitudinal axis above the bottoms of the distributor arms and below the annular channel on the jacket.
  • the tube plates for the upper tube end sections were arranged above the annular channel.
  • the measure according to the invention advantageously reduces the required core tube length. Furthermore, by means of the configuration according to the invention, the process-related standing height can be ensured by shifting it into the distributor arms.
  • the distributor arms preferably have a comparatively small volume, so that only a correspondingly small hold-up is present. This can be achieved with advantage a weight reduction, which has a favorable effect on the static design (earthquake and wind load) of the heat exchanger.
  • the arrangement of the tube plates also allows a decoupling of the distribution system from the tube bundle and thus the subsequent installation of the distributor. As a result, the distance between the distributor arms and the tube bundle can be reduced.
  • the annular channel is now above the tube sheets / braids - no undercuts between the tube bundle and the distributor more, so that the entire distribution system can be prefabricated separately and attached to the container or jacket with a seam.
  • the core tube is arranged coaxially with respect to the jacket along the longitudinal axis. Furthermore, the tubes of the Tube bundle preferably wound on the core tube so that it can absorb or remove the load of the tubes of the tube bundle.
  • the core tube is not in flow communication with the distributor arms.
  • the annular channel is connected to the respective distributor arm via a flow path, with the respective flow path (for example downpipe or shaft, see below) extending completely outside the core tube.
  • the annular channel extends along an inner side of the jacket facing the jacket space, in particular in a plane extending perpendicular to the longitudinal axis or perpendicular to the core tube.
  • the bottoms of the distributor arms also preferably extend in a plane which runs perpendicular to the longitudinal axis of the jacket or of the core tube.
  • the annular channel is attached to the inside of the jacket, so that in particular the jacket forms an outer wall of the annular channel.
  • the distributor arms extend in each case along or against a radial direction inwards in the direction of the core tube.
  • the respective radial direction is perpendicular to the longitudinal axis of the core tube and has outwardly to the jacket.
  • the respective distributor arm is flow-connected to the annular channel via a downpipe extending along the longitudinal axis, wherein in particular the respective downpipe is attached to a bottom and / or an inner wall of the annular channel, wherein the inner wall of the Outer wall opposite or surrounded by the outer wall.
  • the respective distributor arm is closed at the top by a roof, wherein in particular, the respective downpipe connects from above to the roof of the associated distribution arm.
  • an opening may be formed in the respective roof, which is in flow communication with the respective downpipe.
  • the respective distributor arm has a degassing chimney which is in particular formed separately from the respective downpipe.
  • the respective degassing chimney preferably connects to an opening in the roof of the relevant distributor arm.
  • the respective degassing chimney to project upwards from the roof of the respective distributor arm and to extend along the longitudinal axis, with the particular degassing chimney projecting upwards from an end section of the respective distributor arm, which is arranged adjacent to the core tube ,
  • the gas or the gaseous phase of the second medium will rise inwards and follow the respective degassing chimney upwards. This has the advantage that the gas does not have to rise up against the liquid flow. Thus, the components leading down the liquid phase of the second medium can advantageously be made smaller.
  • the respective distributor arm is formed by a lower portion of a shaft which extends downwardly from the annular channel along the longitudinal axis, wherein the respective shaft has an inner wall facing the core tube, which inclined to Longitudinal axis runs, so that the respective shaft upwards (ie toward the annular channel) in cross-section, ie, in a horizontal sectional plane, tapers.
  • the downpipes (also referred to as downcomer tubes) are replaced by a distributor shaft comprising downcomers and distributor arms in combination, wherein in particular an upper portion of the respective distributor shaft, which takes over the function of a downpipe, continuously into a lower portion of the respective shaft passes, which takes over the function of a Verteilerarmes.
  • ducts with the base or the bottom of the respective distributor arm are installed, which can change the shape upwards, in particular can taper in cross section.
  • adjacent distributor arms are in fluid communication with one another via a compensation line, so that the liquid level of the liquid phase located in the distributor arms can be compensated by a flow of the liquid phase via the at least one compensation line.
  • the compensation line may in particular be a ring line interconnecting the distributor arms.
  • the invention further allows a small distance between the bottoms of the distributor arms and along a horizontal plane (or perpendicular to the longitudinal axis) extending upper side of the tube bundle, said distance may be according to one embodiment in a range of 50 mm to 500 mm, in particular 50mm to 100mm.
  • a method for distributing a liquid phase to a tube bundle of a heat exchanger is proposed, wherein the first medium is conducted into the annular channel and from there exclusively via outside of the core tube extending Flow paths is fed into the distributor arms of the main distributor and is placed from there on the tube bundle of the heat exchanger.
  • the respective flow path is formed by a drop tube or a shaft (see also above).
  • the liquid phase in normal operation of the heat exchanger is in the respective flow path (e.g., downpipe or well), i.e. within the flow path has a specific stand height corresponding to the operation case.
  • the respective flow path e.g., downpipe or well
  • the present invention in particular a distribution system is provided in which as much as possible can be made in parallel. Furthermore, in particular the hold-up is reduced by the design according to the invention and the weight of the container is minimized. Finally, the invention allows a reduction in the distance between the bottoms of the distributor arms and the tube bundle to minimize mis-distribution of the liquid at the upper bundle end.
  • FIG. 1 shows a wound heat exchanger 1 according to the invention with a tube bundle 2, which serves to receive a first medium M1, which is to pass in an indirect heat exchange with a in a surrounding the tube bundle 2 shell space 5 liquid phase F of a second medium M2.
  • the jacket space 5 is bounded by a pressure-bearing jacket 4, which extends along a longitudinal or cylindrical axis Z, which is arranged in the ready state of the heat exchanger 1 parallel to the vertical.
  • the tube bundle 2 has a plurality of tubes 20, which in particular helically, ie helically, are wound on a core tube 3 extended along the longitudinal axis Z, which is arranged coaxially with the jacket 4 in the jacket space 5.
  • the core tube 3 takes on the load of the tube bundle 2. In the present case, for the sake of simplicity, only one tube 20 in the FIGS. 1 to 3 located.
  • a two-phase mixture or the second medium M2 is first introduced via an inlet connection 104, which is laterally formed on the cylindrical jacket 4, into an annular channel 100, which is provided on an inner side 4a of the jacket wall 5 facing the jacket space 5 Mantels revolves and is attached to this.
  • the annular channel 100 has an outer wall 103, which is formed by the jacket 4, and an inner wall 102 which is opposite the outer wall 103 in the radial direction R of the jacket 4 or tube bundle 2. Outer wall 103 and inner wall 102 are connected to each other via a bottom 101 of the annular channel 100.
  • the annular channel 100 forms a pre-distributor, in which the two-phase mixture / second medium M2 first calms down and a gaseous phase G is separated and then the liquid phase F is passed down into distributor arms 201 of the heat exchanger 1, which is the distribution of the liquid phase F of the second Take over medium M2 on the tube bundle 2.
  • the distributor arms 201 have according to FIGS. 1 and 4 in each case a bottom 202 with outlet openings 207, can flow down through the liquid phase F on the tube bundle 2.
  • the distributor arms 201 furthermore have an outer side 206 which faces the inner side 4a of the jacket 4, wherein they respectively follow the outer wall 206 along the radial direction R of the tube bundle 2 / jacket 4 extend inside to an inner wall 208, which faces the core tube 3.
  • the outer and inner walls 206, 208 are interconnected by radially extending R side walls 204, 205 of the distributor arms 201.
  • the bottoms 202 of the distributor arms 201 are arranged along the longitudinal axis Z below the annular channel 100. Between circumferentially adjacent distribution arms 201 are according to FIG. 4 Gaps 6 present, through which upper end portions of the tubes 20 are guided to tube sheets 21, which in turn laterally, ie laterally, are fixed to the jacket 4.
  • the tubesheets 21 are set relative to the longitudinal axis Z above the bottoms 202 of the distributor arms 201 and below the annular channel 100 on the jacket 4.
  • the core tube 3 is not in fluid communication with the distributor arms 201 and does not participate in the distribution of the liquid phase F.
  • the respective distributor arm 201 is flow-connected to the annular channel 100 via a respective downpipe 10, which is extended along the longitudinal axis Z.
  • the downpipes 10 in particular have a constant circular cross-section.
  • the respective distribution arm 201 is closed at the top by a roof 203, from which the respective downpipe 10 projects upwards.
  • an opening 203 a is formed in the respective roof 203, to which the respective downpipe 10 adjoins.
  • the respective roof 203 falls inwardly in the direction of the core tube 3, so that a gaseous phase G outgassing in the respective distributor arm 201 can ascend along the roof 203 into the respective downpipe 10.
  • the respective downpipe 10 thus also forms a degassing chimney here.
  • the individual downpipes 10 can according to FIG. 1 be attached to the bottom 101 and the inner wall 102 of the annular channel 100, so that the liquid phase F can flow from the annular channel 100 via an opening in the inner wall 102 and the bottom 101 in the respective downpipe 10.
  • each distributor arm 201 furthermore has a separate degassing chimney 210, which also runs parallel to the core tube 3 from an end section of the respective distributor arm 201 upwards from the roof 203, the respective roof 203 preferably rising upwards towards the respective degasification chimney 210, so that the gaseous phase along the respective roof 203 along in the associated degassing chimney 210 can ascend.
  • the respective degassing chimney 210 adjoins, in particular, an opening 203b formed in the roof 203.
  • the respective distributor arm 201 is formed by a lower portion of a shaft 11 which extends downwardly from the annular channel 100 along the longitudinal axis Z, the respective shaft 11 having an inner wall 208 facing the core tube 3 inclined to the longitudinal axis Z extends, so that the respective shaft 11 in the upper direction in cross-section, ie, with respect to a horizontal plane, tapers.
  • the respective shaft 11 is again preferably attached to the inner wall 102 or the bottom 101 of the annular channel 100, so that the liquid phase F can fall or flow via the bottom 101 / inner wall 102 into the respective shaft 11. Due to the inclined inner wall 208, the gaseous phase G can rise here along the inner wall 208 of the respective shaft 11.
  • adjacent distributor arms 201 may be connected to one another via a compensation line 209, so that the level of the liquid phase F in the distributor arms 201 can equalize.
  • the compensation line 209 may be divided into sections, each extending between two adjacent distribution arms 201.
  • the invention enables a small distance A between the bottoms 202 of the distributor arms 201 and a top surface 2a of the tube bundle 2 which is extended along a horizontal plane, wherein this distance may be, for example, in a range of 50 mm to 500 mm. Furthermore, the invention also permits a flat design in the direction of the longitudinal axis Z, whereby typical heights H of the distributor, that is from the bottom 202 of the respective distributor arm 201 to an upper edge of the annular channel 100, can be in the range from 1000 mm to 5000 mm.
  • the considered coats 4 have in the range of the distributor arms 201, for example, a diameter in the range of 1000 mm to 6000 mm.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP17020070.3A 2017-02-24 2017-02-24 Échangeur thermique et procédé de distribution d'une phase liquide dans un échangeur thermique Active EP3367034B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP17020070.3A EP3367034B1 (fr) 2017-02-24 2017-02-24 Échangeur thermique et procédé de distribution d'une phase liquide dans un échangeur thermique
US15/902,386 US20180245856A1 (en) 2017-02-24 2018-02-22 Heat exchanger and method for distributing a liquid phase in a heat exchanger
RU2018106653A RU2018106653A (ru) 2017-02-24 2018-02-22 Теплообменник и способ распределения жидкой фазы в теплообменнике
CN201810155079.3A CN108507234A (zh) 2017-02-24 2018-02-23 热交换器及用于在热交换器中分配液相的方法
CY20191101238T CY1122362T1 (el) 2017-02-24 2019-11-26 Εναλλακτης θερμοτητας και διαδικασια για την κατανομη μιας υδαρους φασης σε εναν εναλλακτη θερμοτητας

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP17020070.3A EP3367034B1 (fr) 2017-02-24 2017-02-24 Échangeur thermique et procédé de distribution d'une phase liquide dans un échangeur thermique

Publications (2)

Publication Number Publication Date
EP3367034A1 true EP3367034A1 (fr) 2018-08-29
EP3367034B1 EP3367034B1 (fr) 2019-08-28

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Application Number Title Priority Date Filing Date
EP17020070.3A Active EP3367034B1 (fr) 2017-02-24 2017-02-24 Échangeur thermique et procédé de distribution d'une phase liquide dans un échangeur thermique

Country Status (5)

Country Link
US (1) US20180245856A1 (fr)
EP (1) EP3367034B1 (fr)
CN (1) CN108507234A (fr)
CY (1) CY1122362T1 (fr)
RU (1) RU2018106653A (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018000468A1 (de) * 2018-01-22 2019-07-25 Linde Aktiengesellschaft Gewickelter Wärmeübertrager mit Abscheider im Kernrohr
EP3719433A1 (fr) * 2019-04-02 2020-10-07 Linde GmbH Distributeur de fluide réglable d'un échangeur de chaleur enroulé permettant de réaliser des différentes charges de fluide

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2835334A1 (de) * 1978-08-11 1980-02-21 Linde Ag Gewickelter waermetauscher
DE102004040974A1 (de) * 2004-08-24 2006-03-02 Linde Ag Gewickelter Wärmetauscher
US20120261088A1 (en) * 2011-04-14 2012-10-18 Linde Aktiengesellschaft Heat exchanger with sections
EP2818821A1 (fr) * 2013-06-27 2014-12-31 Linde Aktiengesellschaft Echangeur de chaleur enroulé avec alimentation par tuyau central

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5213154A (en) * 1992-08-17 1993-05-25 Gas Research Institute Liquid desiccant regeneration system
US9587885B2 (en) * 2014-10-09 2017-03-07 Baltimore Aircoil Company, Inc. Cooling tower with indirect heat exchanger

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2835334A1 (de) * 1978-08-11 1980-02-21 Linde Ag Gewickelter waermetauscher
DE102004040974A1 (de) * 2004-08-24 2006-03-02 Linde Ag Gewickelter Wärmetauscher
US20120261088A1 (en) * 2011-04-14 2012-10-18 Linde Aktiengesellschaft Heat exchanger with sections
EP2818821A1 (fr) * 2013-06-27 2014-12-31 Linde Aktiengesellschaft Echangeur de chaleur enroulé avec alimentation par tuyau central

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018000468A1 (de) * 2018-01-22 2019-07-25 Linde Aktiengesellschaft Gewickelter Wärmeübertrager mit Abscheider im Kernrohr
EP3719433A1 (fr) * 2019-04-02 2020-10-07 Linde GmbH Distributeur de fluide réglable d'un échangeur de chaleur enroulé permettant de réaliser des différentes charges de fluide
EP3719434A1 (fr) * 2019-04-02 2020-10-07 Linde GmbH Distributeur de fluide réglable d'un échangeur de chaleur enroulé permettant de réaliser des différentes charges de fluide

Also Published As

Publication number Publication date
CN108507234A (zh) 2018-09-07
US20180245856A1 (en) 2018-08-30
RU2018106653A (ru) 2019-08-22
CY1122362T1 (el) 2020-11-25
EP3367034B1 (fr) 2019-08-28

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