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EP3218659B1 - Appareil frigorifique sans givre - Google Patents

Appareil frigorifique sans givre Download PDF

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Publication number
EP3218659B1
EP3218659B1 EP15786986.8A EP15786986A EP3218659B1 EP 3218659 B1 EP3218659 B1 EP 3218659B1 EP 15786986 A EP15786986 A EP 15786986A EP 3218659 B1 EP3218659 B1 EP 3218659B1
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EP
European Patent Office
Prior art keywords
evaporator
refrigeration appliance
appliance according
frost
frost refrigeration
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.)
Active
Application number
EP15786986.8A
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German (de)
English (en)
Other versions
EP3218659A1 (fr
Inventor
Torsten Eschner
Panagiotis Fotiadis
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.)
BSH Hausgeraete GmbH
Original Assignee
BSH Hausgeraete 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 BSH Hausgeraete GmbH filed Critical BSH Hausgeraete GmbH
Priority to PL15786986T priority Critical patent/PL3218659T3/pl
Publication of EP3218659A1 publication Critical patent/EP3218659A1/fr
Application granted granted Critical
Publication of EP3218659B1 publication Critical patent/EP3218659B1/fr
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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
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
    • F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
    • F25D17/062—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation in household refrigerators
    • 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
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/06—Removing frost
    • F25D21/08—Removing frost by electric heating
    • 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
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/06—Removing frost
    • 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
    • F25D2700/00—Means for sensing or measuring; Sensors therefor
    • F25D2700/10—Sensors measuring the temperature of the evaporator

Definitions

  • the present invention relates to a no-frost refrigerator with a forced-air evaporator, which is arranged in an evaporator chamber.
  • US 3,638,449 A A refrigeration device with a forced-air evaporator arranged in an evaporator chamber is known.
  • the moisture that is carried through the evaporator mainly condenses just beyond an upstream side of the evaporator, so that the frost formation in an upstream region of the evaporator is significantly stronger than in a downstream region, the more the frost formation concentrates on the upstream region defrosting is necessary more quickly.
  • US 3,638,449 A a free space adjacent to a side flank of the evaporator is provided, via which the air drawn in can bypassing the upstream region of the evaporator, if its free cross section is severely restricted by frost, can directly reach a downstream region of the evaporator.
  • an electrical heating wire is provided, which has a heat transfer relationship (not described further) with the refrigerant line and fins of the evaporator.
  • An object of the invention is to provide a no-frost refrigerator with extended intervals between defrost cycles.
  • the object is achieved by a refrigeration device with the features of claim 1.
  • the accumulation area offers the air circulating through the evaporator chamber a path with a relatively low flow resistance, so that a large part of the air flows through the first part and the accumulation area instead of through the entire evaporator , but exudes moisture as ripe in the accumulation area.
  • this frost increases the flow resistance of the accumulation area, so that the air flow through the second part of the evaporator increases and frost also increasingly precipitates there.
  • blockage only occurs when both the accumulation area and the second part of the evaporator are filled with frost.
  • the frost at least in the accumulation area forms a body extended in the flow direction of the air, it can prevent local overheating during defrosting, at least of the second part of the evaporator that is in direct thermal contact with the accumulation area, and thus enables defrosting with good energy efficiency. Because the accumulation area provides additional space for the frost, the time intervals between defrost cycles can also be increased. This has a positive effect on the energy consumption of the device, and it is also convenient for the user when times in which no cooling capacity can be called up to cool down freshly introduced goods into the device are rare. In order to achieve efficient cooling of the accumulation area and a correspondingly strong concentration of frost formation on the accumulation area, the second part of the evaporator must be able to reach lower temperatures than the first. For this reason, an injection point for refrigerant is provided on the second part.
  • the second part as a whole should preferably be upstream of the first part of the evaporator, so that the refrigerant only reaches the first part after it has already been warmed up somewhat in the second part.
  • the evaporator is preferably open on the first flank adjoining the accumulation area in order to allow air to pass between the accumulation area and the second part of the evaporator over the entire length of the accumulation area.
  • the first flank is preferably divided in the flow direction into a section adjacent to the accumulation area and a section adjacent to a wall of the evaporator chamber and delimiting the first part of the evaporator.
  • the section adjoining the accumulation area can also be delimited on both sides transversely to the direction of flow by the section abutting the wall of the evaporator chamber.
  • Such an arrangement can particularly promote a uniform distribution of the air across the width of the evaporator chamber, when air inlets of the upstream part of the evaporator chamber are each arranged at lateral corners of the evaporator chamber.
  • a defrost heater can be arranged on a second flank of the evaporator opposite the first flank.
  • the defrost heater is preferably designed as a surface heater which extends at least over the second part of the evaporator in order to defrost it and the accumulation area. It can extend over the entire second flank to also defrost the first part of the evaporator, however, since the amount of frost in the first part is generally smaller than that in the accumulation area and in the second part of the evaporator, the defrost heating at the level of the first part of the evaporator have a smaller heating power per unit area than in the amount of the second part.
  • the inflow side and the outflow side of the evaporator are preferably spaced apart in the depth direction of the refrigeration device.
  • the second flank of the evaporator can be a lower flank, so that the heat released by the surface heating arranged there can rise in the evaporator and thus reach the accumulation area.
  • a wall of the evaporator chamber opposite the first flank of the evaporator can have an infrared-reflecting surface layer in order to reflect radiation heat emitted by the evaporator back to this or to the accumulation area and thus to make it usable for defrosting.
  • the air flowing through the accumulation area can already release a large part of its moisture there, which considerably reduces the rate of frost formation in the first part of the evaporator.
  • Another consequence of the feature is that, when the forced ventilation is switched off, air that enters the evaporator chamber by convection from a storage compartment also releases its moisture in the accumulation area or in the second part of the evaporator.
  • the distribution of the frost in the evaporator chamber is therefore essentially independent of whether the moisture got into the evaporator chamber when the forced ventilation was switched on or off.
  • the frost distribution is therefore reproducible and the defrost heating can take the form Arrangement, distribution of the heating line or the like can be optimized in order to achieve a defrosting time that is as uniform as possible for the entire evaporator.
  • a temperature sensor for monitoring the defrosting process is preferably arranged on the second part of the evaporator, preferably adjacent to the accumulation area, i.e. typically on the first flank of the evaporator. This ensures that the main frost accumulation is always present in the area of the sensor.
  • a refrigerant outlet can also be arranged on the second part of the evaporator, adjacent to the refrigerant inlet.
  • a suction line starting from the refrigerant outlet can form a heat exchanger together with a capillary leading to the refrigerant inlet.
  • a section of the suction line which runs in the evaporator chamber from the second part of the evaporator to the rear wall, can form the above-mentioned heat exchanger.
  • Fig. 1 shows an evaporator chamber 1 of a household refrigeration device in a longitudinal section along a plane which extends vertically in the middle and in the depth direction through a body of the household refrigeration device.
  • a wall delimiting the evaporator chamber 1 upwards is formed by a rigid plate 2, for example made of solid polystyrene, over which a thermal insulation layer 3 extends.
  • the plate 2 can be part of an inner container of the refrigerator; then the thermal insulation layer 3 is generally a layer made of polyurethane foam, with which a space between the inner container and an outer skin of the refrigerator body is foamed in the usual manner.
  • the plate 2 and the thermal barrier layer 3 can also be parts of a horizontal partition between two storage compartments formed in the body of the refrigerator, here a freezer compartment 4 below the evaporator chamber 1 and a normal refrigerator compartment, not shown, above the thermal barrier layer 3.
  • thermal insulation board 5 made of expanded polystyrene is attached.
  • An infrared reflecting layer 6 is formed on an underside of this thermal insulation panel 5, here in the form of a sheet, preferably made of aluminum, which closely conforms to the contour of the underside of the thermal insulation panel 5.
  • a lower wall which separates the evaporator chamber 1 from the freezer compartment 4, comprises a shell 7 injection molded from plastic, which is anchored to the plate 2 and possibly to a rear wall of the inner container, and a further thermal insulation plate 8 made of expanded polystyrene, which is in the shell 7 is glued.
  • a cuboidal evaporator 9 in the form of a lamella is arranged between the thermal insulation panels 5, 8. Its slats 10 extend parallel to the section plane of the Fig. 1 and are frequently crossed by a refrigerant line 11 running in meanders. On a lower flank 17 of the evaporator 9, lower edges of the fins 10 touch a surface heating 12, which rests flat on the thermal insulation panel 8.
  • the surface heater 12 can be formed, for example, by a heat-conducting plate, for example an aluminum sheet, to which a heating resistor is glued, electrically insulated by being embedded in foils.
  • the heat insulation plate 5 and the IR-reflecting layer 6 attached to it are divided in the depth direction of the body into a front section 13 which, together with upper edges of the fins 10 on an upper flank 14 of the evaporator 9, delimits an accumulation region 15 which is elongated in the depth direction of the body, and a rear section 16 which directly contacts the upper edges of the fins 10 of the evaporator 9.
  • a front part of the flank 14 adjoining the accumulation region 15 is designated by 18, a rear part touching the rear section 16 by 19; Accordingly, a distinction is made below between a front part 20 of the evaporator 9 below the accumulation area 15 and a rear part 21 of the evaporator 9.
  • the IR-reflecting layer 6 By touching the rear part 21 of the evaporator 9 on the one hand the IR-reflecting layer 6 and on the other hand the surface heating 12, it divides the evaporator chamber 1 into an upstream part 22 and a downstream part 23. Air coming from a fan arranged in the downstream part 23 24 is sucked from the freezer compartment 4 into the upstream part 22 via inlet openings 25 at the front edge of the shell 7, can only reach the downstream part 23 by moving the rear part 21 of the evaporator 9, below the rear section 16 of the layer 6, passes through to an outflow side 26.
  • the Air enters the evaporator 9 directly on an inflow side 27 facing the inlet openings 25 and also passes through its front part 20; alternatively, there is a way in which the air first enters the accumulation area 15 and by passing over the front part 18 of the flank 14 into the evaporator 9, the front part 20 of which bypasses at least part of its length.
  • Fig. 2 shows a horizontal section through the evaporator chamber 1 along the plane II-II Fig. 1 .
  • the cutting plane of the Fig. 1 is in Fig. 2 marked with II.
  • each air channels 28 run through side walls of the body and finally through the heat insulation layer 3 to open to the right and left of the inlet openings 25 in the upstream part 18 of the evaporator chamber 1.
  • the width of the accumulation area 15 is somewhat smaller than that of the evaporator chamber 1, so that openings 29 of the air channels 28 into the evaporator chamber 1 each face the accumulation area 15 over a part of their width, while on another part the thermal insulation panel 5 extends directly over the inflow side 27 of the evaporator 9 protrudes.
  • Fig. 3 shows the evaporator 9 in a second horizontal section along the plane III-III of the Fig. 1 , which is lower than level II-II.
  • the outlines of the thermal insulation board 5 and the accumulation area 15, which lie outside the section plane III-III, are drawn in as a dashed line.
  • the density of the slats 10 is different in the rear part 21 and in the front part 20, below the accumulation area 15. In the case shown here, the density of the slats 10 in the rear part 21 is twice as high as in the front, every second slat 10 ends at the border to the front part 20.
  • the course of the refrigerant line 11 in the evaporator 9 is in Fig. 3 clearly visible.
  • the refrigerant line 11 here forms an upper layer 30 (see FIG. Fig. 1 ), which, starting from an injection point 29 at a front right corner of the evaporator 9, in the top right corner Fig. 3 , extends in meanders up to a rear right corner 32, and a lower layer 31, which, congruently covered by the upper layer, goes back to the front right corner extends.
  • the refrigerant line 11 merges into a suction line 33 which, in addition to the outermost right-hand lamella 10, extends in the direction of a rear wall of the refrigeration device body and runs downwards to a compressor (not shown).
  • a capillary 34 via which fresh refrigerant arrives at the injection point 29, is guided here over part of its length within the suction line 33 in order to form a heat exchanger and only emerges from the injection point 29 shortly before it.
  • the position of the injection point 29 adjacent to the inflow side 27 of the evaporator 9 has the result that, when refrigerant circulates in the refrigerant line 11, the front part 20 of the evaporator 9 reaches a significantly lower temperature than the rear part 21. Therefore, there is air in is sucked by the fan 20 through the evaporator chamber 1 at this time, a considerable proportion of its moisture already reaches the upper edges of the fins 10 of the front part 20, so that, starting from these upper edges, frost grows into the accumulation area 15.
  • the flow resistance of the accumulation area 15 increases over time, and as the accumulation area 15 closes, the air is increasingly forced to enter the evaporator 9 via the inflow side 27 and also to pass through its front part 20.
  • the reduced density of the fins 10 in the front part 21 compared to the rear part 21 means that the air, when it enters the evaporator 9 via the inflow side 27, can travel a relatively long way in the latter until it completely releases its moisture has, and the frost layer, which is thereby deposited on the fins 10, extends far from the inflow side 23 into the interior of the evaporator 9. A large amount of frost can therefore be stored in the evaporator 9 and the accumulation area 15 before the flow resistance is increased so much that defrosting must take place.
  • Fig. 4 shows a schematic plan view of an embodiment of the surface heating 12.
  • a heating wire 35 extends in meanders on a heat-conducting base plate 36.
  • the density of the meanders or the length of the heating wire 35 per unit area of the base plate 36 is clear below the front part 20 of the evaporator 9 higher than below the rear part 21 in order to provide the amount of heat required to defrost the tire in the front part 20 and the accumulation area 15 in a short time can and at the same time to avoid excessive heating of the slightly frosted rear part 21.
  • the area performance in the front and rear part of the surface heating 12 can be fine-tuned in that the heating wire 35 has different cross sections in the front and rear part.
  • the defrosting process continues until a temperature sensor 37, which is placed centrally in the front part 18 of the upper flank 14 of the evaporator 9, detects a predetermined switch-off temperature just above 0 ° C.
  • the switch-off temperature is selected just above 0 ° C. in such a way that it is reached after briefly completely defrosting the front part 20 and the accumulation area 15.
  • the amount of heat that the panel heater 12 emits into the rear part 21 during defrosting can be greater than the amount of heat required to defrost the rear part 21. If the rear part 21 is completely ice-free before the end of the defrosting process and it is heated even further, the heat reaches the rear section 16 of the infrared-reflecting layer 6 via the fins 10 and spreads forward in this, so that the frost in the Accumulation area 15 is also defrosted from above. A close contact between the upper edges of the fins 10 and the layer 6 in the rear part 21 thus helps to prevent the rear part 21 from overheating, which would have to be removed again after the defrosting process has ended.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Defrosting Systems (AREA)

Claims (13)

  1. Appareil frigorifique No Frost avec un compartiment congélation (4) et un évaporateur (9) à aération forcée, disposé dans une chambre d'évaporateur (1) et qui est essentiellement en cube avec un côté afflux (27) et un côté écoulement (26), lesquels sont orientés à la perpendiculaire du sens de flux de l'air dans la première partie (20) de l'évaporateur (9), et avec des flancs (14, 17) raccordant le côté afflux (27) et le côté écoulement (26), au moins une partie arrière (21) de l'évaporateur (9) séparant l'une de l'autre une partie (22) en amont par rapport au sens de flux de l'air à travers la chambre d'évaporateur (1) et une partie (23) en aval de la chambre d'évaporateur (1), la partie en amont (22) de la chambre d'évaporateur (1) comprenant une zone d'accumulation (15), laquelle est contiguë à un premier (14) des flancs, est disposée parallèlement en technique de flux et en contiguïté, par rapport à une partie avant (20) de l'évaporateur (9) et étant refroidie par la partie avant (20) de l'évaporateur (9), et un ventilateur (24) dans la partie en aval (23) aspirant, du compartiment congélation (4) dans la partie en amont (22), de l'air par des orifices d'entrée (25) sur le bord avant d'un bac (7), caractérisé en ce que la partie arrière (21) est en contact d'une part avec une couche réfléchissant des IR (6) et d'autre part avec un chauffage de surface (12) et en ce que la partie avant (20) de l'évaporateur (1) comprend un point d'injection (29) pour le fluide frigorigène.
  2. Appareil frigorifique No Frost selon la revendication 1, caractérisé en ce que, sur base du sens de flux du fluide frigorigène dans une conduite du fluide frigorigène (11) de l'évaporateur, la deuxième partie (20) est située en amont de la première partie (21) de l'évaporateur (9).
  3. Appareil frigorifique No Frost selon la revendication 1 ou 2, caractérisé en ce que le premier flanc (14) est segmenté dans le sens de flux dans une partie (18) contiguë à la zone d'accumulation (15) et une partie (19) adjacente à une paroi de la chambre d'évaporateur (1).
  4. Appareil frigorifique No Frost selon l'une des revendications précédentes, caractérisé en ce que la partie (18) du flanc (14) contiguë à la zone d'accumulation (15) est délimitée en oblique par rapport au sens de flux, des deux côtés, par la partie (19) contiguë à la paroi de la chambre d'évaporateur (1).
  5. Appareil frigorifique No Frost selon l'une des revendications précédentes, caractérisé en ce que le chauffage de surface est un chauffage pour dégivrage (12).
  6. Appareil frigorifique No Frost selon la revendication 5, caractérisé en ce que le chauffage de surface (12) s'étend au moins sur les deux parties (20) de l'évaporateur (9).
  7. Appareil frigorifique No Frost selon l'une des revendications 1 à 6, caractérisé en ce que le côté afflux (27) et le côté écoulement (26) sont écartés dans le sens de la profondeur de l'appareil frigorifique.
  8. Appareil frigorifique No Frost selon l'une des revendications 1 à 7, caractérisé en ce qu'une paroi de la chambre d'évaporateur située en face du premier flanc (14), comprend la couche réfléchissant des IR (6).
  9. Appareil frigorifique No Frost selon l'une des revendications précédentes, caractérisé en ce qu'un capteur de température (37) est disposé sur la partie avant (20) de l'évaporateur (9).
  10. Appareil frigorifique No Frost selon la revendication 9, caractérisé en ce que le capteur de température (37) est positionné contigu à la zone d'accumulation (15).
  11. Appareil frigorifique No Frost selon la revendication 10, caractérisé en ce que la zone d'accumulation (15) s'étend au-dessus du capteur de température (37).
  12. Appareil frigorifique No Frost selon l'une des revendications précédentes, caractérisé en ce qu'une sortie du fluide frigorigène est disposée sur la partie avant (20) de l'évaporateur (1).
  13. Appareil frigorifique No Frost selon l'une des revendications précédentes, caractérisé en ce que la partie avant (20) de l'évaporateur (9) est face à un côté avant de l'appareil frigorifique No Frost et la partie arrière de l'évaporateur est face à une paroi arrière de l'appareil frigorifique No Frost, et en ce qu'une conduite d'aspiration (33) de la partie arrière (20) de l'évaporateur (1) coure jusqu'à la paroi arrière et forme, avec un capillaire (34) menant à une entrée du fluide frigorigène (29), un échangeur de chaleur.
EP15786986.8A 2014-11-10 2015-10-29 Appareil frigorifique sans givre Active EP3218659B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL15786986T PL3218659T3 (pl) 2014-11-10 2015-10-29 Urządzenie chłodzące No Frost

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014222851.4A DE102014222851A1 (de) 2014-11-10 2014-11-10 No-Frost-Kältegerät
PCT/EP2015/075143 WO2016074941A1 (fr) 2014-11-10 2015-10-29 Appareil frigorifique antigivre

Publications (2)

Publication Number Publication Date
EP3218659A1 EP3218659A1 (fr) 2017-09-20
EP3218659B1 true EP3218659B1 (fr) 2020-04-15

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Application Number Title Priority Date Filing Date
EP15786986.8A Active EP3218659B1 (fr) 2014-11-10 2015-10-29 Appareil frigorifique sans givre

Country Status (6)

Country Link
US (1) US10371434B2 (fr)
EP (1) EP3218659B1 (fr)
CN (1) CN107076495B (fr)
DE (1) DE102014222851A1 (fr)
PL (1) PL3218659T3 (fr)
WO (1) WO2016074941A1 (fr)

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US12135161B2 (en) * 2019-05-20 2024-11-05 Pepsico, Inc. Defrosting system for a cold plate and method of defrosting a cold plate
DE102020202172A1 (de) * 2020-02-20 2021-08-26 BSH Hausgeräte GmbH Kältegerät mit Lamellenverdampfer
PL3885680T3 (pl) * 2020-03-24 2024-07-15 Electrolux Appliances Aktiebolag Urządzenie chłodnicze wyposażone w zespół wentylatora i sposób wytwarzania wspomnianego urządzenia
CN116255786A (zh) * 2021-12-10 2023-06-13 合肥美的电冰箱有限公司 制冷装置及制冷设备

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Also Published As

Publication number Publication date
CN107076495A (zh) 2017-08-18
EP3218659A1 (fr) 2017-09-20
WO2016074941A1 (fr) 2016-05-19
PL3218659T3 (pl) 2020-09-21
CN107076495B (zh) 2021-06-29
DE102014222851A1 (de) 2016-05-12
US20170314840A1 (en) 2017-11-02
US10371434B2 (en) 2019-08-06

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