EP3183514B1 - Kühlsystem - Google Patents

Kühlsystem Download PDF

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Publication number
EP3183514B1
EP3183514B1 EP14809083.0A EP14809083A EP3183514B1 EP 3183514 B1 EP3183514 B1 EP 3183514B1 EP 14809083 A EP14809083 A EP 14809083A EP 3183514 B1 EP3183514 B1 EP 3183514B1
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EP
European Patent Office
Prior art keywords
refrigerant
outlet
evaporator
vapor
separator
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EP14809083.0A
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English (en)
French (fr)
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EP3183514A1 (de
Inventor
Charbel RAHHAL
Richard G. Lord
Jack Leon Esformes
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Carrier Corp
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Carrier Corp
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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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/06—Superheaters
    • 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
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • 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
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0012—Ejectors with the cooled primary flow at high pressure
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators

Definitions

  • the invention relates generally to a chiller system, such as air conditioning and refrigeration systems and, more particularly, to an air conditioning and refrigeration system that enables the use of immiscible oil.
  • refrigerant vapor from an evaporator is drawn in by a compressor, which then delivers the compressed refrigerant to a condenser (or a gas cooler for transcritical applications).
  • a condenser heat is exchanged between a secondary fluid, such as air or water, and the refrigerant.
  • the refrigerant typically in a liquid state passes to an expansion device, where the refrigerant is expanded to a lower pressure and temperature before being provided to the evaporator.
  • air conditioning applications heat is exchanged within the evaporator between the refrigerant and air or another secondary fluid, such as water, glycol, or brine for example, to condition the indoor air of a space.
  • the refrigerant compressor since the refrigerant compressor necessarily involves moving parts, it is typically required to provide lubrication to these parts by means of lubricating oil that is mixed with or entrained in the refrigerant passing through the compressor.
  • lubricating oil that is mixed with or entrained in the refrigerant passing through the compressor.
  • the lubricant is normally not useful within the system other than in the compressor, its presence in low concentrations in the system does not generally detract from the flow, heat transfer, and properties of the refrigerant as it passes through the system in a conventional vapor compression cycle.
  • a heat exchanger such as direct expansion and flooded heat exchangers for example, may be used as evaporators in HVAC systems.
  • the refrigerant typically surrounds the exterior of the tubes positioned within a shell and the secondary fluid to be cooled, such as water for example, flows through the tubes.
  • the secondary fluid to be cooled such as water for example
  • the refrigerant is expanded within the tubes while the chilled second fluid is circulated through the shell.
  • the typical approach temperature in a direct expansion heat exchanger is between 4°K and 6°K to ensure vapor phase at compressor suction.
  • refrigerants Due to environmental global warming potential concerns, new types of refrigerants are being considered for use in air conditioning applications. These new refrigerants include refrigerants that result in the coexistence of vapor and liquid phases through the compression process or refrigerants that have lower discharge gas temperatures and higher miscibility with lubricants compared to conventional refrigerants. Examples of these new refrigerants include, but are not limited to Hydrofluoroolefins (HFOs), and blends of HFOs and Hydrofluorocarbons (HFCs), or other refrigerants and/or refrigerant blends commonly referred to as "wet refrigerants" that have similar properties.
  • HFOs Hydrofluoroolefins
  • HFCs Hydrofluorocarbons
  • a vapor compression cooling system and method for cooling one or more microprocessors via one or more cold plates mated with the microprocessor(s).
  • Each cold plate includes an evaporator, and the cooling system is designed to operate such that the quality of the refrigerant exiting the evaporator(s) is less than 100% so as to maximize the cooling ability of the cold plate(s), i.e., to avoid dry-out of the evaporator(s).
  • a suction line heat exchanger is provided to protect the compressor of the system by increasing the quality of the refrigerant from the evaporator to at least 100% so as to provide vapor phase refrigerant to the compressor.
  • WO 2009/049096 A1 discloses a system for improving the thermal efficiency of a thermal control loop. After compression and condensation refrigerant is applied to an evaporator employs a subsidiary counter-current heat exchanger intercepting refrigerant flow to maintain the quality of the refrigerant by exchanging thermal energy between the input flow and the output flow from the evaporator.
  • the same principle is effective, with particular advantage when small connections have to be made, in systems using mixed phase media and using the concept of direct energy transfer with saturated fluid.
  • EP 0 626 443 A1 discloses a ammonia refrigeration unit.
  • a refrigerator working fluid composition comprises an ammonia refrigerant and a lubricating oil which has a remarkably good compatibility therewith.
  • the refrigerating unit comprises circulating the above composition in a circulatory cycle and constituting a refrigeration or heat pump cycle.
  • the method of lubricating an ammonia refrigerant compressor comprises the use of a lubricating oil comprising one or more ether compounds.
  • DE 10 344 590 A1 describes an air conditioning equipment for motor vehicle.
  • the equipment has a refrigerating circuit including a collector filled with liquefied carbon dioxide.
  • the collector is connected to a jet pump, by a connecting unit, for sucking a part of carbon dioxide from the collector and directly injecting into an evaporator.
  • the carbon dioxide is removed from the collector by the unit for directly supplying the evaporator, without being sucked by a compressor.
  • An independent claim is also included for a method of controlling an air conditioning equipment
  • Document DE 10 344 590 A1 represents the closest prior art to the present invention.
  • a heat exchanger for refrigeration compression cycle in vehicle air conditioning has an internal heat exchanger fixed to one end of a radiator.
  • the internal heat exchanger has the passages for the high pressure refrigerant closer to the radiator than the passages for the low pressure refrigerant.
  • the heat exchanger is mounted in the vehicle so that the radiator receives more cooling air than the internal heat exchanger.
  • a chiller system according to the invention is claimed in independent claim 1.
  • Optional features are claimed in the dependent claims.
  • the refrigerant may have a low global warming potential.
  • the refrigerant may include at least one of a Hydrofluoroolefin (HFO) and an HFO blend.
  • HFO Hydrofluoroolefin
  • the chiller system includes a lubrication system having an oil separator arranged generally downstream from the compressor.
  • the oil separator is configured to supply oil separated from the refrigerant to one or more moving components of the compressor.
  • the oil is an immiscible oil.
  • the chiller system includes a refrigerant to refrigerant heat exchanger fluidly coupled to the vapor compression circuit and the efficiency circuit.
  • the refrigerant to refrigerant heat exchanger is configured to convert the vapor refrigerant provided from an outlet of the separator into a superheated vapor.
  • a refrigerant R is configured to circulate through the chiller system 20 such that the refrigerant R absorbs heat when evaporated at a low temperature and pressure and releases heat when condensed at a higher temperature and pressure.
  • the refrigerant has a low global warming potential, such as a Hydrofluoroolefin (HFO) or an HFO blend refrigerant for example.
  • HFO Hydrofluoroolefin
  • HFO blend refrigerant for example.
  • the compressor 25 receives refrigerant vapor from the evaporator 40 and compresses it to a higher temperature and pressure, with the relatively hot vapor then passing to the condenser 30 where it is cooled and condensed to a liquid state by a heat exchange relationship with a cooling medium, such as air or water for example.
  • the liquid refrigerant R then passes from the condenser 30 to an expansion valve 35, wherein the refrigerant R is expanded to a low temperature two phase liquid/vapor state as it passes to the evaporator 40.
  • low pressure vapor then returns to the compressor 25 where the cycle is repeated.
  • the compressor 25, condenser 30, expansion device 35 and evaporator 40 form a vapor compression circuit.
  • the evaporator 40 is a direct expansion heat exchanger. As illustrated in FIG. 2 , which shows an embodiment not being part of the invention but being helpful to understand the invention, the evaporator 40 includes a connected first shell 100a and second shell 100b, and a coupled first plurality of tubes 105a and second plurality of tubes 105b, arranged within each of the shells 100a, 100b, respectively.
  • the evaporator 40 includes a connected first shell 100a and second shell 100b, and a coupled first plurality of tubes 105a and second plurality of tubes 105b, arranged within each of the shells 100a, 100b, respectively.
  • embodiments having any number of shells 100a, 100b are within the scope of the invention, as long as these embodiments furthermore comprise all features of appended independent claim 1.
  • the shells are fluidly coupled to one another and the tubes 105a, 105b within each respective shell 105a, 105 are fluidly coupled.
  • a plurality of large baffles 107 and small baffles 109 generally receive and support the tubes 105a, 105b to maintain the position of the tubes 105a, 105b along the length of the shell 100a, 100b.
  • the large baffle 107 is configured to receive each of the plurality of tubes 105a, 105b within a shell 100a, 100b and the small baffle 109 is configured to receive only a portion, such as a central portion for example, of the plurality of tubes 105a, 105b within a shell 100a, 100b.
  • the refrigerant of the chiller system 20 is configured to pass from an inlet header 110, through the one or more plurality of tubes 105b, 105a, and out an outlet header 115.
  • a heating medium such as water for example, is pumped into the interior 120 of the shell 100 via an inlet 125, through the one or more shells 100a, 100b, and out an outlet 130.
  • the heating medium is configured to flow from the second shell 100b to the first shell 100a
  • the refrigerant is configured to flow from the first plurality of tubes 105a to the second plurality of tubes 105b.
  • the illustrated and described evaporator 40 has a counter flow configuration to maximize the heat transfer between the heating medium and the refrigerant.
  • the refrigerant provided at the outlet header 115 of the evaporator 40 may be a two-phase mixture including both liquid and vapor refrigerant. In one embodiment, 85 percent or less of the two-phase mixture is vaporized refrigerant.
  • the system 20 which is not part of the invention but helpful to understand the invention, includes an additional heat exchanger 45 configured to receive a first flow of refrigerant and a second flow of refrigerant.
  • the heat exchanger 45 may be positioned within the system 20 such that the first flow of refrigerant is provided from the outlet of the condenser 30.
  • the first flow of refrigerant is configured to pass through the heat exchanger 45 before being supplied to the expansion valve 35.
  • the second flow of refrigerant within the heat exchanger 45 is generally provided from the outlet of the evaporator 40.
  • the second flow of refrigerant is configured to pass through the heat exchanger 45 before being supplied to the compressor 25.
  • the warm liquid refrigerant from the condenser 30 in a heat transfer relationship with the refrigerant vapor or two-phase mixture exiting the evaporator 40, heat from the first flow of refrigerant transfers to the second flow of refrigerant.
  • the second flow of refrigerant supplied from the heat exchanger 45 to the compressor 25 is generally a superheated vapor.
  • a lubrication system may be integrated into the chiller system 20. Because lubricant may become entrained in the refrigerant as it passes through the compressor 25, an oil separator 55 is positioned directly downstream from the compressor 20. In one embodiment, the oil separator 55 is integrally formed with an outlet of the compressor 25. The refrigerant separated by the oil separator 55 is provided to the condenser 30, and the lubricant isolated by the oil separator 55 is recirculated to the moving portions (not shown) of the compressor 25, such as to the rotating bearings for example, where the lubricant becomes entrained in the refrigerant R and the lubricant cycle is repeated.
  • the chiller system 20 additionally includes a circuit 58 configured to recirculate liquid refrigerant of the two-phase mixture provide at the outlet 115 of the evaporator 40 to improve the efficiency of the chiller system 20.
  • the circuit 58 includes a flash gas refrigerant separator 60 configured to separate the liquid and vapor phases of the refrigerant.
  • the separator 60 is arranged generally downstream from the expansion device 35 and upstream from the evaporator 40 such that the two-phase refrigerant passes from the expansion device 35 into the separator 60.
  • a pump 65 is configured to draw the liquid refrigerant from a first outlet 66 of the separator 60 and supply it to the evaporator 40.
  • the outlet of the evaporator 40 is also connected to the separator 60 and configured to supply a two-phase refrigerant mixture thereto.
  • the liquid refrigerant is separated from the liquid and vapor mixture and recirculated through the evaporator 40 repeatedly until it is vaporized.
  • a second outlet 68 of the separator 60 is operably coupled to the compressor 25 such that the separated vaporized refrigerant is supplied directly thereto. In such instances, the vaporized refrigerant bypasses the evaporator 40.
  • the chiller system 20 includes a refrigerant to refrigerant heat exchanger 45
  • the vaporized refrigerant from the separator 60 may pass through the heat exchanger 45 before being supplied to the compressor 25.
  • the flash gas separator 60 is positioned generally downstream from the evaporator 40 and generally upstream from the compressor 25 relative to the flow of refrigerant.
  • the additional circuit 58 of the chiller system 20 also includes an ejector 70 arranged within the refrigerant flow path between the condenser 30 and the expansion valve 35. Refrigerant from the condenser 30 is provided to a first inlet 72 of the ejector 70. As the refrigerant flows through the ejector 70, the flow is accelerated and the pressure of the flow is decreased, such that the refrigerant supplied to the expansion device 35 is generally a liquid-vapor mixture.
  • the refrigerant passes to the flash gas separator 60 for separation into a liquid refrigerant and a vapor refrigerant.
  • a first outlet 66 of the separator 60 is fluidly connected to a second inlet 74 of the ejector 70.
  • the high velocity and pressure reduction of the refrigerant flow through the first inlet 72 of the ejector 70 draws the liquid refrigerant from the separator 60 into the ejector 70 through the second inlet 74. Therefore any liquid refrigerant provided at the outlet 115 of the evaporator 40 will repeatedly cycle through the circuit 58 and the evaporator 40 until being vaporized.
  • a second outlet 68 of the separator 60 is configured to supply the vaporized refrigerant within the separator 60 to the compressor 25.
  • the liquid refrigerant from the condenser 30 may pass through the heat exchanger 45 as the first flow of refrigerant before being supplied to the ejector 70 and the vaporized refrigerant provided at the second outlet 68 of the separator 60 may pass through the heat exchanger 45 as the second flow of refrigerant before being supplied to the compressor 25.
  • the flash gas separator 60 is positioned generally downstream from the condenser 30 and generally upstream from the expansion device 35 relative to the flow of refrigerant.
  • the ejector 70 is arranged generally downstream from the condenser 30 and generally upstream from the separator 60 relative to the flow of refrigerant. Refrigerant from the condenser 30 is provided to the first inlet 72 of the ejector 70 and refrigerant from the outlet 115 of the evaporator 40 is provided to the second inlet 74 of the ejector 70.
  • a liquid-vapor refrigerant mixture is supplied from the ejector 70 to the separator 60 where it is divided into liquid refrigerant and vapor refrigerant.
  • the liquid refrigerant within the separator 60 is provided to the expansion device 35 via a first outlet 66 in the separator 60.
  • the refrigerant is provided to the second inlet 74 of the ejector 70.
  • the high velocity and pressure reduction of the refrigerant flow through the ejector 70 draws the mixture of two phase refrigerant from the evaporator 40 through the second inlet 74 of the ejector 70.
  • the refrigerant then returns to the separator 60, where it is separated into liquid refrigerant and vapor refrigerant. Consequently, the liquid refrigerant provided at the outlet 115 of the evaporator 40 will continue to cycle through circuit 58 and the evaporator 40 until it is entirely vaporized.
  • the vapor compression cycle further benefits from this configuration in that the placement of the ejector 70 reduces the compression ratio of the compressor 25, thereby increasing the system coefficient of performance.
  • a second outlet 68 of the separator 60 is configured to supply the vaporized refrigerant to the compressor 25.
  • the vaporized refrigerant bypasses the expansion device 35 and the evaporator 40.
  • the liquid refrigerant from the condenser 30 may pass through the heat exchanger 45 as the first flow of refrigerant before being supplied to the ejector 70 and the vaporized refrigerant provided at the second outlet 68 of the separator 60 may pass through the heat exchanger 45 as the second flow of refrigerant before being supplied to the compressor 25.
  • the various embodiments of a chiller system 20 described herein have an efficiency or performance level at least equal to conventional systems that include a flooded evaporator.
  • the chiller system 20 is compatible with immiscible oil, which reduces the amount of oil needed by the system and therefore the cost.
  • the design of the lubrication system 50 may be simplified.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Lubricants (AREA)

Claims (6)

  1. Kühlsystem (20), umfassend:
    einen Dampfverdichtungskreis, der in der Strömungsrichtung eines zirkulierenden Kältemittels (R) umfasst:
    einen Verdichter (25);
    einen Kondensator (30);
    einen Ejektor (70), der einen ersten Einlass (72), der fluidisch mit einem Auslass des Kondensators (30) verbunden ist, einen zweiten Einlass (74) und einen Auslass umfasst;
    ein Expansionsventil (35), das fluidisch an den Auslass des Ejektors (70) gekoppelt ist;
    einen Verdampfer (40);
    einen Abscheider (60), der dazu konfiguriert ist, das Zweiphasengemisch in flüssiges Kältemittel und dampfförmiges Kältemittel zu trennen,
    wobei der Verdampfer (40) ein Wärmetauscher mit direktem Austausch ist, sodass das während eines Betriebs des Kühlsystems (20) an einem Auslass des Verdampfers (40) bereitgestellte Kältemittel ein Zweiphasengemisch aus flüssigem Kältemittel und dampfförmigem Kältemittel ist und das dampfförmige Kältemittel weniger als oder gleich etwa 85 % des Zweiphasengemisches umfasst; und
    wobei der Abscheider (60) Teil einer sogenannten Effizienzschaltung (58) ist, die zum Verbessern der Effizienz des Kühlsystems (20) konfiguriert ist und einen Einlass, der fluidisch an einen Auslass (115) des Verdampfers (40) gekoppelt ist, einen ersten Auslass (66), der fluidisch an den zweiten Einlass (74) des Ejektors (70) gekoppelt und dazu konfiguriert ist, dem zweiten Einlass (74) des Ejektors (70) flüssiges Kältemittel zuzuführen, und einen zweiten Auslass (68) umfasst, der fluidisch an eine Einlassseite des Verdichters (25) gekoppelt ist.
  2. Kühlsystem (20) nach Anspruch 1, wobei das Kältemittel (R) ein niedriges Treibhauspotential aufweist.
  3. Kühlsystem (20) nach Anspruch 2, wobei das Kältemittel (R) ein HFO beinhaltet.
  4. Kühlsystem (20) nach Anspruch 1, ferner umfassend ein Schmiersystem, das einen Ölabscheider (55) beinhaltet, der im Wesentlichen stromabwärts des Verdichters (25) angeordnet ist, wobei der Ölabscheider (55) dazu konfiguriert ist, einer oder mehreren sich bewegenden Komponenten des Verdichters (25) Öl zuzuführen, das von dem Kältemittel (R) abgeschieden wurde.
  5. Kühlsystem (20) nach Anspruch 4, wobei das Öl unmischbares Öl ist.
  6. Kühlsystem (20) nach Anspruch 1, ferner umfassend: einen Kältemittel-Kältemittel-Wärmetauscher (45), der fluidisch mit dem Dampfverdichtungskreis und der Effizienzschaltung (58) gekoppelt ist, wobei der Kältemittel-Kältemittel-Wärmetauscher (45) dazu konfiguriert ist, das von einem Auslass des Ejektors (60) bereitgestellte dampfförmige Kältemittel in einen überhitzten Dampf umzuwandeln.
EP14809083.0A 2014-08-21 2014-08-21 Kühlsystem Active EP3183514B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/IB2014/001842 WO2016027116A1 (en) 2014-08-21 2014-08-21 Improved direct expansion evaporator based chiller system

Publications (2)

Publication Number Publication Date
EP3183514A1 EP3183514A1 (de) 2017-06-28
EP3183514B1 true EP3183514B1 (de) 2021-06-30

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US (1) US20170268808A1 (de)
EP (1) EP3183514B1 (de)
CN (1) CN106662365B (de)
ES (1) ES2886603T3 (de)
WO (1) WO2016027116A1 (de)

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WO2016027116A1 (en) 2016-02-25
CN106662365B (zh) 2021-04-27
US20170268808A1 (en) 2017-09-21
ES2886603T3 (es) 2021-12-20
CN106662365A (zh) 2017-05-10
EP3183514A1 (de) 2017-06-28

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