EP3698048B1 - Kompressionsvorrichtung und -verfahren und kältemaschine - Google Patents

Kompressionsvorrichtung und -verfahren und kältemaschine Download PDF

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Publication number
EP3698048B1
EP3698048B1 EP18765154.2A EP18765154A EP3698048B1 EP 3698048 B1 EP3698048 B1 EP 3698048B1 EP 18765154 A EP18765154 A EP 18765154A EP 3698048 B1 EP3698048 B1 EP 3698048B1
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Prior art keywords
gas
motor
compressor
line
compressors
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EP18765154.2A
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English (en)
French (fr)
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EP3698048A1 (de
Inventor
Fabien Durand
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Air Liquide SA
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
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Air Liquide SA
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements

Definitions

  • the invention relates to a compression device and method as well as to a refrigeration machine.
  • the invention relates more particularly to a device for centrifugal compression of a working gas, in particular for a refrigeration machine, comprising several centrifugal compressors forming several successive and / or parallel compression stages and several motors for driving the compressors, the device comprising a gas circuit comprising a first inlet pipe for gas to be compressed connected to an inlet of a first compressor for conveying gas to be compressed in the first compressor, the circuit comprising a second pipe connected to an outlet of said first compressor for evacuating the gas compressed in the latter, the second pipe being connected to an inlet of a second compressor for conveying the gas which has been compressed in the first compressor into the second compressor in order to achieve a second compression, the circuit comprising a third pipe cooling unit having an upstream end connected to an outlet of at least one of the compressors and a downstream end connected to an inlet of at least one first motor for transferring a fraction of the gas compressed in said compressor into said at least one first motor in order to limit its heating.
  • a centrifugal compressor using a direct drive between the motor (electric) and the compression wheel (s) requires a flow of gas in order to evacuate the heat generated in the engine. This heat is generated mainly by the losses of the engine and by the friction of the rotor with the gas which surrounds it.
  • This cooling flow is usually injected on one side of the engine (at an inlet) and discharged on the other side (at an outlet) with a higher temperature. It can also be injected in the middle of the engine and be evacuated on both sides of the latter.
  • a more or less significant part of the heat is also usually evacuated by a heat transfer fluid circulating in a circuit surrounding the stator part of the motor (water or air or any other heat transfer fluid making it possible to cool the stator).
  • a heat transfer fluid circulating in a circuit surrounding the stator part of the motor (water or air or any other heat transfer fluid making it possible to cool the stator).
  • the gas circulating in the engine to cool it usually has the same composition as the compressed gas.
  • the motive force necessary to circulate the gas through the engine (s), is generated by one or more compression stages (that is to say by one or more of the compressors ).
  • An object of the present invention is to overcome all or part of the drawbacks of the prior art noted above.
  • the device according to the invention is essentially characterized in that the circuit comprises a fourth pipe having an upstream end connected to an outlet of the first engine to recover the gas having circulated in the first engine and a downstream end connected to an inlet of a second engine to transfer the gas therein with a view to limiting the heating of the second engine.
  • the invention also relates to a low-temperature refrigeration machine of between -100 ° C and -273 ° C comprising a working circuit containing a working fluid, the working circuit comprising a centrifugal compression device and a cooling device and expansion of the compressed gas in the compression device, the compression device conforming to any one of the characteristics above or below.
  • the invention may also relate to any alternative device or method comprising any combination of the characteristics above or below.
  • the compression device 18 shown schematically on figure 1 comprises two centrifugal compressors 1, 3 (that is to say two compressor wheels) forming two successive compression stages.
  • the two compressors 1, 3 are each driven by a respective drive motor 5, 6.
  • the compressors 1, 3 are rotated directly by their corresponding motor 5, 6.
  • the device 18 comprises a gas circuit comprising a first inlet pipe 16 for gas to be compressed connected to the inlet of a first compressor 1, in order to convey gas to be compressed in the first compressor 1.
  • the circuit comprises a second pipe 14 having an upstream end connected to an outlet of said first compressor 1 for discharging the gas compressed in the latter.
  • the second pipe 14 has a downstream end connected to an inlet of the second compressor 3, for conveying the compressed gas in the first compressor 1 in the second compressor 3 with a view to performing a second compression (a second compression stage).
  • the second pipe 14 preferably comprises a member 2 for cooling the gas, for example a heat exchanger cooled by a heat transfer fluid. This makes it possible to cool the compressed gas before it enters the second compressor 3.
  • the circuit preferably comprises a member 4 for cooling the gas at the outlet of the second compressor 3 (for example an exchanger in exchange with a coolant).
  • the circuit comprises a third pipe 10 having an upstream end connected to the outlet of a compressor 1 and a downstream end connected to a first 6 of the two motors.
  • the upstream end of the third pipe 10 can be connected to the outlet of the first compressor 1 via the second pipe 14. That is to say that the third pipe 10 is connected by branch to the second pipe 14 between the first 1 and second 3 compressors.
  • the third pipe 10 takes a fraction of the compressed gas intended to supply the second compressor 3 in order to sweep (cool) the first engine.
  • This fraction can correspond to one to forty percent of the gas flow leaving the first compressor 1.
  • the third pipe 10 may comprise a valve 8 for regulating the flow rate of the gas transferred into the first motor 6 (or any other suitable member, in particular a pressure reducing member such as an orifice, turbine, Ranque tube or vortex tube, orifice , capillary).
  • a valve 8 for regulating the flow rate of the gas transferred into the first motor 6 (or any other suitable member, in particular a pressure reducing member such as an orifice, turbine, Ranque tube or vortex tube, orifice , capillary).
  • the circuit comprises a fourth pipe 12 having an upstream end connected to an outlet of the first motor 6 to recover the gas having circulated in the first motor 6 and a first downstream end connected to an inlet of a second motor 5 in order to transfer the gas therein. in order to limit the heating of the second motor 5.
  • the fourth pipe 12 comprises a gas cooling member 13 for cooling the gas between its outlet from the first engine 6 and its entry into the second engine 5.
  • this cooling member 13 comprises a heat exchanger in exchange. thermal with a cooling heat transfer fluid.
  • the cooling gas which has circulated in the second motor 5 is discharged via a fifth pipe 7 having an upstream end connected to an outlet of the second motor 5 (to recover the gas having circulated in the second motor 5 and a downstream end connected to the inlet of the first compressor 1 with a view to its compression
  • the fifth line 7 can be connected to the inlet of the first compressor 1 via the first line 16.
  • the fifth pipe 7 (and possibly the fourth pipe 12) can also be used if necessary to recover the gas coming from any leaks (at the level for example of joints located near the engines, such as rotary joints for example).
  • the fifth pipe 7 may comprise a member 9 for cooling the gas, for example a heat exchanger in thermal exchange with a coolant coolant.
  • the fourth pipe 12 may include a second downstream end connected to the fifth pipe 7 and a valve system 11 for distributing the flow of gas coming from the first motor 6 between the second motor. 5 and the fifth line 7. That is to say that the gas leaving the first motor 6 (cooling gas) can be distributed between the second motor 5 (to cool it) and the inlet of the first compressor 1. This is obtained. via two parallel lines and at least one valve 11 (and / or any other pressure reducing device: turbine, orifice, etc.).
  • the valve 11 (or equivalent) can be arranged at the terminals of the motor 6 (or motors).
  • the valve 11 (or the valves) can be a piloted control valve.
  • a bypass line from the first motor 6 can be provided (for example between the third line 10 and the fourth line) to relatively reduce the quantity of cooling gas in the first motor 6 with respect to the quantity of cooling gas. of the second motor 5.
  • a bypass pipe can be provided between the second pipe 14 (for example after the cooling member 2) and the fourth pipe (upstream or downstream of the cooling member 13).
  • a pipe system (s) and valve (s) can be provided to distribute different quantities of cooling gas between the first motor 6 and the second motor 5 as required.
  • a bypass valve 11 can advantageously be placed between the inlet and the outlet of the cooling gas of the second motor 5 in order to limit the flow of cooling gas through this second motor 5 in the event that it is is too important.
  • the mechanical power required to compress for example a flow rate of 1.26 kg / s of gaseous nitrogen having an initial pressure of 5 bars absolute and a temperature of 288 K at a pressure of 18.34 bars absolute is 188 kW.
  • This compression power can be divided into 88kW for the motor 5 which drives the first compressor 1 and 100kW for the motor 6 which drives the second compressor 3.
  • the nitrogen is compressed for example up to 8.87 bar absolute in the first centrifugal compression stage 1 having a power of 83 kW and a typical isentropic efficiency of 86%. Then this compressed gas is cooled in the heat exchanger 2.
  • Part of the gas is withdrawn via valve 8 to cool the first motor 6.
  • the rest (the main flow) is then compressed again to 18.34 bar absolute in the second compression stage 3.
  • This second compressor 3 has for example a power of 95 kW and a typical isentropic efficiency of 86%.
  • the gas is cooled in the heat exchanger 4 at the outlet of the second compressor 3.
  • the gas is then brought to the outlet 15 of the device 18.
  • Part of the nitrogen flow at the outlet of the exchanger 2 will therefore be sent through the valve 8 and the third pipe 10 to supply the first engine 6 with cooling gas.
  • the nitrogen will then escape from the first motor 6 via the fourth pipe 12 and join the exchanger 13 to be cooled to a temperature preferably close to or equal to the inlet temperature of the first compressor 1.
  • This cooling is carried out before the gas enters the second engine 5.
  • the rise in the temperature of the gas through the second motor 5 is preferably of the same order of magnitude as that through the first motor 6 (the flow rate and the power to be extracted are preferably close).
  • the cooling gas After passing through the second engine 5, the cooling gas is sent to the downstream heat exchanger 9 via the fifth pipe 7 to be cooled before returning to the inlet 16 of the first compressor 1.
  • the solution according to the invention uses the same gas flow which is put into operation. circulation to cool two engines (in series on the cooling gas circuit). This allows the necessary cooling gas flow rate to be halved.
  • the invention allows efficient cooling (thermally and energetically) of a plurality of motors of a compression device.
  • the gas used for cooling the engines could be taken from the outlet of another or more compressors other than the first compression stage.
  • the device could include more than two compressors and more than two motors.
  • expansion turbines could be included in the device.
  • one or more expansion stages can be mounted on the same motor shaft as one or more compressors.
  • cooling members 9, 13 can be omitted (their use makes it possible to improve the efficiency of the system, but the latter are not necessary).
  • valve or valves 8, 11 can advantageously be adjustable so as to control, for example, the temperature of one or more motors and / or the cooling flow rate and / or the temperature of the cooling gas.
  • these expansion members 8, 11 can, if necessary, cool the gas before it enters the engine (s).
  • these expansion devices 8, 11 can be replaced (or supplemented) by any other pressure-reducing device such as an orifice, turbine or capillary, for example.
  • the valves 8, 11 can be replaced by or associated with one or more turbines and / or Ranque tubes (vortex tube).
  • the member 8 can be located alternately on the second pipe 14, for example.
  • the member 11 can be located alternately on the first pipe 16, for example.
  • rotary joints can be used between the engine (s) 5, 6 and the compression stage (s) 1, 3 or the expansion stage (s) so that the pressure in the cavities of the engine is close to zero.
  • lowest compressor pressure i.e. the compressor inlet pressure 13. This has the consequence of lowering the friction losses between the rotor (s) and the gas because these losses are proportional to the pressure in the engine cavity. Leaks recovered from this or these seal (s) will add to the flow of cooling gas from the third line.
  • the compression device 18 may form part of a refrigeration machine at low temperature, for example between -100 ° C and -273 ° C, and comprising a working circuit 10 containing a cooling fluid. work, the work circuit comprising a centrifugal compression device 18 and a device 19 for cooling and expanding the compressed gas in the compression device 18.
  • the working gas can include all or part of: nitrogen, helium, hydrogen, neon, argon, carbon monoxide, methane, krypton, xenon, l ethane, carbon dioxide, propane, butane, oxygen.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (14)

  1. Vorrichtung zur Zentrifugalkompression eines Arbeitsgases, insbesondere für eine Kältemaschine, umfassend mehrere Zentrifugalkompressoren (1, 3), die mehrere aufeinanderfolgende und/oder parallele Kompressionsstufen bilden, und mehrere Motoren (5, 6) zum Antrieb der Kompressoren (1,3), wobei die Vorrichtung einen Gaskreislauf umfasst, der eine erste Leitung (16) für den Einlass von zu komprimierendem Gas umfasst, die mit einem Einlass eines ersten Kompressors (1) verbunden ist, um zu komprimierendes Gas in den ersten Kompressor (1) zu leiten, wobei der Kreislauf eine zweite Leitung (14) umfasst, die mit einem Auslass des ersten Kompressors (1) verbunden ist, um das darin komprimierte Gas abzuleiten, wobei die zweite Leitung (14) mit einem Einlass eines zweiten Kompressors (3) verbunden ist, um das Gas, das im ersten Kompressor (1) komprimiert wurde, für eine zweite Kompression in den zweiten Kompressor (3) zu leiten, wobei der Kreislauf eine dritte Leitung (10) zum Kühlen umfasst, deren stromaufwärtiges Ende mit einem Auslass zumindest eines der Kompressoren (1, 3) verbunden ist und dessen stromabwärtiges Ende mit einem Einlass zumindest eines ersten Motors (6) verbunden ist, um einen Teil des im Kompressor (1) komprimierten Gases in den zumindest einen ersten Motor (6) zu leiten, um dessen Erwärmung zu begrenzen,
    dadurch gekennzeichnet, dass der Kreislauf eine vierte Leitung (12) umfasst, deren stromaufwärtiges Ende mit einem Auslass des ersten Motors (6) verbunden ist, um das Gas, das im ersten Motor (6) zirkuliert ist, aufzunehmen, und deren stromabwärtiges Ende mit einem Einlass eines zweiten Motors (5) verbunden ist, um das Gas dorthin zu leiten, um eine Erwärmung des zweiten Motors (5) zu begrenzen.
  2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass die vierte Leitung (12) ein Element (13) zum Kühlen des Gases zwischen seinem Auslass aus dem ersten Motor (6) und seinem Einlass in den zweiten Motor (5) umfasst.
  3. Vorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Kreislauf eine fünfte Leitung (7) umfasst, deren stromaufwärtiges Ende mit einem Auslass des zweiten Motors (5) verbunden ist, um das Gas, das im zweiten Motor (5) zirkuliert ist, aufzunehmen, und deren stromabwärtiges Ende mit dem Einlass des ersten Kompressor (1) für dessen Verdichtung verbunden ist.
  4. Vorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass die fünfte Leitung (7) ein Element (9) zum Kühlen des Gases umfasst.
  5. Vorrichtung nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass die vierte Leitung (12) ein zweites stromabwärtiges Ende aufweist, das mit der fünften Leitung (7) verbunden ist.
  6. Vorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass sie ein System (11) aus Leitung(en) und Ventil(en) zum Verteilen der Kühlgasmengen auf den ersten Motor (6) und den zweiten Motor (5) umfasst.
  7. Vorrichtung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass die zweite Leitung (14) ein Element (2) zum Kühlen des Gases umfasst.
  8. Vorrichtung nach Anspruch 7, dadurch gekennzeichnet, dass das Kühlelement (2) der zweiten Leitung (14) einen Wärmetauscher umfasst, der durch ein Wärmeträgermedium gekühlt wird.
  9. Vorrichtung nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass der Kreislauf ein Element (4) zum Kühlen des Gases an einem Auslass (15) des zweiten Kompressors (3) umfasst.
  10. Vorrichtung nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass die dritte Leitung (10) ein Ventil (8) zur Regelung des Durchsatzes des in den ersten Motor (6) geleiteten Gases umfasst.
  11. Vorrichtung nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, dass sie zumindest einen Motor, der einen oder mehrere Kompressoren antreibt, und zumindest einen Motor, der mit einer oder mehreren Expansionsturbinen gekoppelt ist, umfasst.
  12. Vorrichtung nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, dass sie eine oder mehrere Drehverbindungen zwischen dem bzw. den Motoren (5, 6) und dem bzw. den Kompressoren (1, 3) oder einer bzw. mehreren Expansionsstufen aufweist, so dass der Druck in den Hohlräumen des Motors bzw. der Motoren nahe dem niedrigsten Druck des Kompressors (1), d. h. dem Einlassdruck des Kompressors (1), ist.
  13. Maschine zum Kühlen auf Tieftemperatur zwischen - 100 °C und -273 °C, umfassend einen Arbeitskreislauf, der ein Arbeitsfluid enthält, wobei der Arbeitskreislauf eine Zentrifugalkompressionsvorrichtung (18) und eine Vorrichtung (19) zum Kühlen und Expandieren des in der Kompressionsvorrichtung (18) komprimierten Gases umfasst, dadurch gekennzeichnet, dass die Kompressionsvorrichtung (18) einem der Ansprüche 1 bis 12 entspricht.
  14. Verfahren zur Zentrifugalkompression eines Arbeitsgases, insbesondere für eine Kältemaschine, unter Verwendung mehrerer Zentrifugalkompressoren (1, 3), die mehrere aufeinanderfolgende und/oder parallele Kompressionsstufen bilden, und mehrerer Motoren (5, 6) zum Antrieb der Kompressoren (1, 3), wobei die Kompressoren (1, 3) direkt von den Motoren (5, 6) in Drehung versetzt werden, wobei das Verfahren Folgendes umfasst:
    - einen Schritt der Kompression eines Arbeitsgases in einem ersten Kompressor (1) und anschließend in einem zweiten Kompressor (3), die in Reihe oder parallel angeordnet sind,
    - einen Schritt der Entnahme eines Teils des komprimierten Gases, das aus zumindest einem der Kompressoren (1) austritt, und des Zirkulierens dieses entnommenen Gases in einem ersten Motor (6) für dessen Kühlung,
    dadurch gekennzeichnet, dass es einen Schritt der Kühlung des Gases, das zur Kühlung des ersten Motors (6) gedient hat, und anschließend einen Schritt des Zirkulierenes des gekühlten Gases in einem zweiten Motor (5) für dessen Kühlung umfasst.
EP18765154.2A 2017-10-16 2018-08-01 Kompressionsvorrichtung und -verfahren und kältemaschine Active EP3698048B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1701076A FR3072428B1 (fr) 2017-10-16 2017-10-16 Dispositif et procede de compression et machine de refrigeration
PCT/FR2018/051975 WO2019077212A1 (fr) 2017-10-16 2018-08-01 Dispositif et procédé de compression et machine de réfrigération

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Publication Number Publication Date
EP3698048A1 EP3698048A1 (de) 2020-08-26
EP3698048B1 true EP3698048B1 (de) 2021-10-20

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US (1) US11384768B2 (de)
EP (1) EP3698048B1 (de)
JP (1) JP7234225B2 (de)
KR (1) KR102503137B1 (de)
CN (1) CN111212981B (de)
AU (1) AU2018350938B2 (de)
CA (1) CA3079027A1 (de)
DK (1) DK3698048T3 (de)
ES (1) ES2903562T3 (de)
FR (1) FR3072428B1 (de)
WO (1) WO2019077212A1 (de)

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US11384768B2 (en) 2022-07-12
KR102503137B1 (ko) 2023-02-22
KR20190042463A (ko) 2019-04-24
ES2903562T3 (es) 2022-04-04
JP2020537075A (ja) 2020-12-17
AU2018350938A1 (en) 2020-05-21
FR3072428B1 (fr) 2019-10-11
AU2018350938B2 (en) 2023-12-07
CN111212981A (zh) 2020-05-29
JP7234225B2 (ja) 2023-03-07
US20200240437A1 (en) 2020-07-30
FR3072428A1 (fr) 2019-04-19
CN111212981B (zh) 2022-11-01
DK3698048T3 (da) 2022-01-10
EP3698048A1 (de) 2020-08-26
CA3079027A1 (en) 2019-04-25
WO2019077212A1 (fr) 2019-04-25

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