EP3417213B1 - Appareil de froid pourvu d'une pluralité de compartiments de stockage - Google Patents

Appareil de froid pourvu d'une pluralité de compartiments de stockage Download PDF

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Publication number
EP3417213B1
EP3417213B1 EP17702099.7A EP17702099A EP3417213B1 EP 3417213 B1 EP3417213 B1 EP 3417213B1 EP 17702099 A EP17702099 A EP 17702099A EP 3417213 B1 EP3417213 B1 EP 3417213B1
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EP
European Patent Office
Prior art keywords
heat exchanger
refrigeration appliance
appliance according
line section
storage chamber
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EP17702099.7A
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German (de)
English (en)
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EP3417213A1 (fr
Inventor
Andreas BABUCKE
Niels Liengaard
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BSH Hausgeraete GmbH
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BSH Hausgeraete 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
    • F25D11/022—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures with two or more evaporators
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/062—Capillary expansion 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
    • 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/052—Compression system with heat exchange between particular parts of the system between the capillary tube and another part of the refrigeration 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
    • 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle

Definitions

  • the present invention relates to a refrigeration appliance, in particular a household refrigeration appliance, with several storage chambers that can be operated at different temperatures.
  • a refrigeration device with several storage chambers in which a first throttle point, a first heat exchanger for temperature control of the first storage chamber, a second throttle point and a second heat exchanger for cooling the second storage chamber are connected in series in a refrigerant circuit.
  • the pressure drop at the second throttle point causes a pressure difference between the two heat exchangers, so that the evaporation temperature of the refrigerant in the second heat exchanger is lower than in the first and thus a lower operating temperature can be set in the second storage chamber than in the first.
  • the first heat exchanger can work as an evaporator or as a condenser. When operating as a condenser, the operating temperature of the first storage chamber can reach values at room temperature or even slightly above.
  • the US 2014/0020410 A1 reveals air conditioning.
  • the object of the present invention is to create a refrigeration device with several storage chambers that enables energy-efficient operation even if for a first Storage chamber has a high operating temperature and a low operating temperature is selected for a second storage chamber.
  • a first controllable throttle point, a first heat exchanger for temperature control of the first storage chamber, a second controllable throttle point and a second heat exchanger for cooling the second storage chamber are in series between a pressure connection and a suction connection connected, at least one warm line section located upstream of the second heat exchanger and a cold line section located downstream of the second heat exchanger are guided in thermal contact with one another to form an internal heat exchanger, and the first heat exchanger is connected to the pressure connection, bypassing the warm line section.
  • the warm line section of the inner heat exchanger is located between the first heat exchanger and the second heat exchanger.
  • a shunt line branch can be provided upstream of the second heat exchanger, which contains a third controllable throttle point and a third heat exchanger.
  • the warm line section can also be located in the shunt line branch.
  • It is preferably located upstream of the third heat exchanger in order to enable energy-efficient cooling operation there.
  • the refrigerant can reach the second heat exchanger, regardless of the route , can only be achieved after pre-cooling in one of the internal heat exchangers.
  • the warm line section of the second internal heat exchanger is located between an outlet of the third heat exchanger and an inlet of the second heat exchanger.
  • Refrigerant vapor extracted from the second heat exchanger can first be warmed up in the second internal heat exchanger before it reaches the first internal heat exchanger.
  • the cooling that the compressed refrigerant achieves in the first internal heat exchanger is therefore less than if the second internal heat exchanger were not present or connected behind the first heat exchanger; This can prevent a storage chamber cooled by the third heat exchanger from cooling down more than desired when the second storage chamber requires long-term cooling.
  • An expansion valve can be provided as a controllable throttle point.
  • a controllable throttle point can be formed by at least two parallel line branches and a valve for controlling the distribution of the refrigerant to the line branches.
  • one of the parallel line branches can comprise a capillary.
  • One of the parallel passages can also form a warm line section of a further internal heat exchanger. If, in particular, the first controllable throttle point is constructed in this way, there is the possibility of either applying non-precooled refrigerant to the first heat exchanger, bypassing each internal heat exchanger, in order to heat the first storage chamber, or to cool the first storage chamber via this further internal one to supply heat exchangers.
  • the in Fig. 1 The refrigerant circuit shown includes a 1 with a pressure connection 2 and a suction connection 3.
  • a refrigerant line 4 starting from the pressure connection 2 runs in the direction of circulation of the refrigerant via a condenser 5 to a branch 6 and divides there into two branches 7, 8.
  • the branch 7 extends over a first controllable throttle point 9, for example an expansion valve, a heat exchanger 10 and a second controllable throttle point 11 to a confluence 12.
  • a first controllable throttle point 9 for example an expansion valve
  • a heat exchanger 10 for example an expansion valve
  • a second controllable throttle point 11 to a confluence 12.
  • branch 8 there are a third controllable throttle point 13, a heat exchanger 14 and a fourth controllable throttle point 15 row connected; At confluence 12, branches 7, 8 meet again. From there, the refrigerant line 4 runs via a heat exchanger 16 to the suction connection 3 of the compressor 1.
  • the heat exchangers 10, 16, 14 are each surrounded by a common insulating shell 20 together with a first storage chamber 17, a second storage chamber 18 and a third storage chamber 19 of the refrigerator.
  • a section 21 of the refrigerant line 4 located downstream of the heat exchanger 16 and a section 22 which connects the heat exchanger 10 to the second controllable throttle point 11 form an inner heat exchanger 23.
  • the sections 21, 22 may be superficially soldered together, or the warm section 22 may be wrapped around the section 21 or extend inside the cold section 21 to give off heat to the refrigerant vapor flowing in the cold section 21.
  • a further internal heat exchanger 24 comprises a warm section 25 located upstream of the third controllable throttle point 13 and belonging to the branch 8 and a cold section 26 located downstream of the evaporator 16 in the refrigerant line 4.
  • section 26 is downstream from section 21 of internal heat exchanger 23; but it could also lie upstream of this or overlap with it.
  • An electronic control unit 27 is connected to temperature sensors 28 in the three storage chambers 17, 18, 19 and controls the speed of the compressor 1 as well as the pressure drops at the controllable throttle points 9, 11, 13, 15 based on a comparison of those in the storage chambers 17, 18, 19 prevailing temperatures with setpoints set by the user.
  • the adjustable setpoint can be above the ambient temperature; then the pressure drop at the throttle point 9 is minimal, the heat exchanger 10 works as a condenser. After passing through the heat exchanger 10 and before reaching the controllable throttle point 11, the refrigerant is pre-cooled in the inner heat exchanger 23 before it reaches the heat exchanger 16 of the storage chamber 18. Since the pressure in the heat exchanger 16 is inevitably lower than in the heat exchangers 10 and 14, the heat exchanger 16 always works as an evaporator, and the temperature of the storage chamber 18 is lower than that of the storage chambers 17, 19.
  • a temperature below the ambient temperature can also be set as the setpoint for the storage chamber 17; then the control unit 27 sets the pressure drop in the throttle points 9 to a non-disappearing value. The higher this is, and consequently the lower the temperature of the storage chamber 17, the lower the temperature of the refrigerant at the outlet of the heat exchanger 10, and the lower the heat exchange in the inner heat exchanger 23.
  • the section 25 of the inner heat exchanger 24 is located upstream of the controllable throttle point 13 and the heat exchanger 14, so that the refrigerant circulating through this section 25 releases heat before reaching the heat exchanger 14. Temperatures above the ambient temperature are therefore difficult to achieve in the storage chamber 19, but this is not necessary since the storage chamber 17 is available for storage at elevated temperatures. Temperatures below the ambient temperature, on the other hand, can be achieved with better efficiency in the storage chamber 19 than in the storage chamber 17.
  • Fig.2 shows a second embodiment of the refrigeration device according to the invention.
  • a control unit and temperature sensors in the storage chambers 17, 18, 19 are present here in the same way as in the first embodiment, but are not shown in the figure for the sake of clarity.
  • the other components also largely correspond to those of the Fig. 1 ; one difference lies in the arrangement of the internal heat exchangers.
  • the inner heat exchanger 24 Fig. 1 is also in Fig. 2 identically present, but the inner heat exchanger 21 is replaced by an inner heat exchanger 30, in which a section 31 of the branch 8, which lies between the outlet of the heat exchanger 14 and the controllable throttle point 15, is in thermal contact with the section 21.
  • the branch 7 has no internal heat exchanger at all, the branch 8 has two instead.
  • this structure proves to be particularly efficient in practice.
  • the reason is that the refrigerant flow rate on branch 8 is normally significantly larger than on branch 7; Even if long running times of the compressor 1, including uninterrupted operation, are required to keep the storage chamber 18 at its target temperature or the compressor 1 is even operated in a speed-controlled manner, the fact that the refrigerant vapor with which the compressed refrigerant in the inner heat exchanger 24 is brought into thermal contact, has already been preheated in the inner heat exchanger 29, subcooling of the storage chamber 19.
  • Fig. 3 shows a section of the refrigerant circuit according to a modification, both in the arrangement of the internal heat exchanger according to Fig. 1 as well as according to Fig. 2 is applicable.
  • the controllable throttle point 9 is not designed here as an expansion valve, but rather it comprises a parallel connection of two line branches 31, 32, one of which, 31, comprises a capillary 33 and the other, 32, comprises a shut-off valve 34.
  • the shut-off valve 34 When the shut-off valve 34 is open, virtually all of the refrigerant circulating on the branch 7 flows through the shut-off valve 34, and the influence of the capillary 33 on the pressures and flows in the refrigerant circuit is negligible.
  • the pressure in the heat exchanger 10 is then practically identical to that in the condenser 5, and the storage chamber 17 can be operated above the ambient temperature as described above.
  • the shut-off valve 34 is closed, then the refrigerant in branch 7 can only flow through the capillary 33, and a low pressure and a correspondingly low temperature are established in the heat exchanger 10.
  • a part of the capillary 33 or a section 35 of the line branch 31 upstream of it can be included here in the inner heat exchanger 24 in order to enable more efficient cooling operation of the storage chamber 17. Since the refrigerant flow via the capillary 33 is negligible when the shut-off valve 34 is open, this inclusion has no influence on the possibility of reaching high temperatures in the storage chamber 17.
  • the capillary 33 can be replaced by an expansion valve.
  • controllable throttle points 11, 13, 15 can also be the same as in Fig. 3 have the structure shown for the throttle point 9.

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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)
  • Combustion & Propulsion (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Claims (12)

  1. Appareil frigorifique avec au moins une première chambre de stockage (17), une deuxième chambre de stockage (18) et un circuit d'agent frigorifique, dans lequel sont reliés en série, entre un raccord de pression (2) et un raccord d'aspiration (3) d'un condensateur (1), un condenseur (5), un premier point d'étranglement commandable (9), un premier échangeur de chaleur (10) pour tempérer la première chambre de stockage (17), un deuxième point d'étranglement commandable (11) et un deuxième échangeur de chaleur (16) pour réfrigérer la deuxième chambre de stockage (18), dans lequel au moins une section de conduite chaude (22, 26, 30) située en amont du deuxième échangeur de chaleur (16) et une section de conduite froide (21, 25) située en aval du deuxième échangeur de chaleur (16) sont menées en contact thermique l'une par rapport à l'autre, afin de constituer un échangeur de chaleur intérieur (23, 24, 29), et le premier échangeur de chaleur (10) est relié au raccord de pression (2) en contournant la section de conduite chaude (22, 26, 30), dans lequel l'appareil frigorifique présente une unité de commande électronique (27) et des capteurs de température (28) dans les deux chambres de stockage (17,18), dans lequel l'unité de commande électronique (27) est reliée aux capteurs de température (28) dans les deux chambres de stockage (17, 18) et est aménagée pour la commande de la vitesse de rotation du condensateur (1) ainsi que des baisses de pression au niveau des points d'étranglement commandables (9, 11) au moyen d'une comparaison des températures régnant dans les chambres de stockage (17, 18) aux valeurs de consigne réglées par l'utilisateur, de sorte que lorsque la valeur de consigne réglable pour la première chambre de stockage tempérée (17) excède la température ambiante, la baisse de pression au niveau du premier point d'étranglement (9) est minimale et le premier échangeur de chaleur (10) travaille comme un condenseur.
  2. Appareil frigorifique selon la revendication 1, caractérisé en ce qu'en amont du deuxième échangeur de chaleur (14), une branche de conduite de dérivation (8), qui comprend un troisième point d'étranglement commandable (11) et un troisième échangeur de chaleur (14), est reliée en parallèle à une branche de conduite (7) contenant le premier point d'étranglement commandable (9) et le premier échangeur de chaleur (10).
  3. Appareil frigorifique selon la revendication 1 ou 2, caractérisé en ce que la section de conduite chaude (22) est située dans le circuit d'agent frigorifique entre le premier échangeur de chaleur (10) et le deuxième échangeur de chaleur (16).
  4. Appareil frigorifique selon la revendication 2, caractérisé en ce que la section de conduite chaude (26, 30) est située dans la branche de conduite de dérivation (8).
  5. Appareil frigorifique selon la revendication 4, caractérisé en ce que la section de conduite chaude (26) est située en amont du troisième échangeur de chaleur (14).
  6. Appareil frigorifique selon la revendication 4, caractérisé en ce que la branche de conduite de dérivation (8) présente un quatrième point d'étranglement commandable (15) en aval du troisième échangeur de chaleur (14) et la section de conduite chaude (30) est située entre le troisième échangeur de chaleur (14) et le quatrième point d'étranglement commandable (15).
  7. Appareil frigorifique selon la revendication 5, caractérisé en ce qu'il comprend un deuxième échangeur de chaleur intérieur (21, 29), dans lequel une section de conduite chaude (22, 30) du deuxième échangeur de chaleur intérieur (21, 29) est située entre une sortie du premier ou du troisième échangeur de chaleur (10, 16) et une entrée du deuxième échangeur de chaleur (14).
  8. Appareil frigorifique selon la revendication 7, caractérisé en ce qu'une section de conduite froide (21) du deuxième échangeur de chaleur intérieur (22, 29) est située entre une sortie du deuxième échangeur de chaleur (16) et la section de conduite froide (25) du premier échangeur de chaleur intérieur (24).
  9. Appareil frigorifique selon l'une des revendications précédentes, caractérisé en ce qu'au moins un des points d'étranglement commandables (9, 11, 13, 15) comprend une soupape de détente.
  10. Appareil frigorifique selon l'une des revendications précédentes, caractérisé en ce qu'au moins un des points d'étranglement commandables (9) comprend au moins deux branches de conduite parallèles et une soupape (32) pour la commande de la répartition de l'agent frigorifique entre les branches de conduite.
  11. Appareil frigorifique selon la revendication 10, caractérisé en ce que l'une des branches de conduite parallèles comprend un tube capillaire (31).
  12. Appareil frigorifique selon la revendication 10, caractérisé en ce que l'une des branches de conduite parallèles constitue une section de conduite chaude d'un échangeur de chaleur intérieur.
EP17702099.7A 2016-02-19 2017-01-31 Appareil de froid pourvu d'une pluralité de compartiments de stockage Active EP3417213B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016202565.1A DE102016202565A1 (de) 2016-02-19 2016-02-19 Kältegerät mit mehreren Lagerkammern
PCT/EP2017/051971 WO2017140488A1 (fr) 2016-02-19 2017-01-31 Appareil de froid pourvu d'une pluralité de compartiments de stockage

Publications (2)

Publication Number Publication Date
EP3417213A1 EP3417213A1 (fr) 2018-12-26
EP3417213B1 true EP3417213B1 (fr) 2023-10-04

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US (1) US11092376B2 (fr)
EP (1) EP3417213B1 (fr)
CN (1) CN108700349B (fr)
DE (1) DE102016202565A1 (fr)
WO (1) WO2017140488A1 (fr)

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CN107351624B (zh) * 2016-05-10 2020-08-25 比亚迪股份有限公司 热泵空调系统及电动汽车
CN107356003B (zh) 2016-05-10 2021-04-20 比亚迪股份有限公司 热泵空调系统及电动汽车
CN112303944A (zh) 2019-07-31 2021-02-02 特灵国际有限公司 用于控制来自过冷却器的过热的系统和方法
DE102019216582A1 (de) * 2019-10-28 2021-04-29 BSH Hausgeräte GmbH Kältegerät mit heiz- und kühlbarem Fach
DE102019218352A1 (de) * 2019-11-27 2021-05-27 BSH Hausgeräte GmbH Kältegerät mit variabel nutzbarem Fach
DE102020207648A1 (de) 2020-06-22 2021-12-23 BSH Hausgeräte GmbH Kältegerät mit einem Saugrohr-Wärmetauscher und Verfahren zum Betrieb eines Kältegeräts mit einem Saugrohr-Wärmetauscher

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CN108700349B (zh) 2021-01-12
EP3417213A1 (fr) 2018-12-26
US20190032986A1 (en) 2019-01-31
WO2017140488A1 (fr) 2017-08-24
CN108700349A (zh) 2018-10-23
DE102016202565A1 (de) 2017-08-24
US11092376B2 (en) 2021-08-17

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