EP3931501A1 - Appareil de froid - Google Patents

Appareil de froid

Info

Publication number
EP3931501A1
EP3931501A1 EP20702094.2A EP20702094A EP3931501A1 EP 3931501 A1 EP3931501 A1 EP 3931501A1 EP 20702094 A EP20702094 A EP 20702094A EP 3931501 A1 EP3931501 A1 EP 3931501A1
Authority
EP
European Patent Office
Prior art keywords
evaporator
collector
refrigerant
expansion valve
storage compartment
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.)
Pending
Application number
EP20702094.2A
Other languages
German (de)
English (en)
Inventor
Stefan Holzer
Horst Drotleff
Matthias Mrzyglod
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
Publication of EP3931501A1 publication Critical patent/EP3931501A1/fr
Pending legal-status Critical Current

Links

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
    • F25D23/00—General constructional features
    • F25D23/06—Walls
    • F25D23/069—Cooling space dividing partitions
    • 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
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • 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
    • 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
    • F25B2400/16—Receivers
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/12—Sound
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the 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
    • 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
    • F25D2400/00—General features of, or devices for refrigerators, cold rooms, ice-boxes, or for cooling or freezing apparatus not covered by any other subclass
    • F25D2400/04—Refrigerators with a horizontal mullion

Definitions

  • the present invention relates to a refrigeration device, in particular a household refrigeration device such as a refrigerator or freezer or a combination device with a plurality of storage compartments kept at different operating temperatures.
  • capillary For reasons of cost, household refrigeration devices usually use a capillary as a throttle point to relax the refrigerant.
  • the capillary cannot be actively regulated; their mass flow is high as long as liquid refrigerant with high density is present at the inlet of the capillary. If this has flowed off via the capillary, refrigerant vapor penetrates into the capillary. Due to the low density of the steam, this leads to a reduction in the mass flow, so that the refrigerant condenses in front of the capillary; on the other hand, the steam flows through the capillary at a higher speed than the liquid refrigerant, and the resulting fluctuations in speed lead to clearly perceptible fluctuations in the operating noise .
  • thermostatic expansion valves which allow active control of the mass flow. These are usually arranged downstream of a collector in order to control the mass flow of the refrigerant on the basis of measured values from a pressure sensor so that there is always liquid refrigerant in the collector, which prevents the gaseous refrigerant from reaching the expansion valve.
  • the expansion valve is significantly more expensive than the capillary conventionally used in domestic refrigeration appliances, and the installation of a pressure sensor is complex, since the pressure sensor must communicate directly with the refrigerant to be measured and must be suitably sealed. Therefore, transferring this technology to household refrigeration appliances has not yet been considered, although it has the advantage - which is insignificant in commercial refrigeration systems and therefore not taken into account, but definitely relevant for household refrigeration appliances - that the expansion valve - because vapor does not flow through alternating with liquid refrigerant - works quietly.
  • One object of the present invention is to create a low-noise refrigeration device. This is achieved with little control effort and accordingly at low costs in that in a refrigerant circuit of the refrigeration device, in which a condenser, a collector, a throttle point and at least one first evaporator cooling a first storage compartment are connected in series in the specified order, the collector has a capacity which is dimensioned to accommodate at least half, preferably 90%, of the refrigerant in the liquid state.
  • the spacious collector gives the entire refrigerant circuit a large volume compared to conventional refrigerant circuits and requires a correspondingly larger charge of refrigerant. In this way, when the refrigeration device is in operation, sufficient liquid refrigerant can almost always be kept in reserve in order to keep refrigerant vapor away from the throttle point.
  • the collector can also be sized to provide space for non-condensable residual gas that was not evacuated when the refrigerant circuit was assembled.
  • Today's production methods allow the refrigerant circuit to be evacuated during assembly down to a residual amount of less than 30 mg N2.A volume of 3-4 cm 3 is required to accommodate this amount of gas at a compressor outlet pressure of approx. 6 bar.
  • the collector By making the collector sufficiently spacious, it is also possible to neutralize a larger amount of residual gas than is currently usually left behind when the refrigerant circuit is evacuated. Ie the spacious collector allows the To shorten the evacuation when assembling the refrigerant circuit and thus to increase productivity.
  • the total capacity of the collector in a household refrigerator of normal size is preferably at least 50 cm 3 .
  • a capacity of 200 cm 3 should not be exceeded in order not to unnecessarily increase the amount of refrigerant required for efficient operation.
  • an outlet of the collector should be deeper, preferably at least 2 cm, more preferably at least 4 cm deeper than an inlet.
  • the shape of the collector can be chosen arbitrarily to a large extent or adapted to the available installation space, and its cross section can vary widely and in particular continuously in the flow direction. Pipelines leading to and from the collector, on the other hand, generally have a constant cross section for reasons of practicality.
  • a point in the refrigerant circuit at which the cross-section increases abruptly downstream of a supply line or the cross-section of the line is exceeded by more than a specified percentage can therefore be viewed as the inlet and outlet of the compressor, or at which the speed of the compressor upstream of the outgoing line, the cross-section decreases abruptly or drops below the cross-section of the line plus a specified percentage.
  • the inlet can be shaped to feed a horizontally oriented refrigerant flow into the collector.
  • the collector preferably has a maximum horizontal cross-sectional dimension of at least 8 mm or a maximum horizontal cross-sectional area of at least 0.5 cm 2 between inlet and outlet. Bigger ones Values, for example at least 15 mm or at least 2 cm 2 , are preferred in order to be able to make the collector compact.
  • the collector can contain built-in components that hinder the formation of eddies in the liquid refrigerant, such as partition walls or a bed of particles.
  • the throttle point can comprise a controllable expansion valve that is controlled using a temperature sensor.
  • the temperature sensor can be provided on a collecting container for liquid refrigerant overflowing from the first evaporator, which is connected to an outlet of the first evaporator and is arranged in a warmer environment than the environment of the first evaporator.
  • the collecting container creates a buffer, the degree of filling of which with liquid refrigerant can be estimated based on the measured temperature. By using this temperature to control the mass flow through the expansion valve, it can be ensured that when the compressor is running, there is always enough liquid refrigerant available upstream of the throttle point to be able to keep vapor away from the expansion valve. At the same time it is possible to completely flood the first evaporator with liquid refrigerant and thus a high, e.g. to provide the cooling capacity required for rapid cooling of freshly loaded refrigerated goods. Since the collecting container is installed in a warmer environment than the first evaporator, it can be ensured that liquid refrigerant which overflows from the first evaporator into the collecting container does not collect there, but instead evaporates immediately.
  • the collecting container can be separated from the first storage compartment by a thermal insulation layer.
  • the expansion valve it can be helpful to connect the expansion valve in series with a capillary, so that part of the pressure difference between the condenser and the first evaporator falls on the capillary and the rest on the expansion valve.
  • the capillary In order to avoid that already in the capillary shortly before its downstream end evaporation begins and that noises are produced by the fact that vapor and liquid refrigerant alternate at the exit of the capillary, the capillary should be arranged upstream of the expansion valve and the pressure difference falling across it should be small enough, to prevent refrigerant from evaporating before it reaches the expansion valve.
  • the capillary should be sized to have a smaller pressure drop than the controllable expansion valve.
  • the outlet of the condenser should be connected to the throttle point without the interposition of a further evaporator.
  • the collecting container is a second evaporator.
  • This can be of the same design as the first evaporator, e.g. a Rollbond, ToS or lamellar evaporator.
  • the second evaporator is expediently used to cool a second storage compartment.
  • the operating temperature of the second storage compartment should be higher than that of the first.
  • the evaporators can be arranged in direct thermal contact with the storage compartments cooled by them, ie the above-mentioned surroundings of the first evaporator and the collecting container or second evaporator can be these storage compartments themselves.
  • a compartment temperature sensor of the second storage compartment can then serve as the above-mentioned temperature sensor controlling the expansion valve. This avoids the costs associated with adding an additional sensor.
  • controllable expansion valve can be accommodated in a partition between the storage compartments.
  • a rear wall of the storage compartments remains completely available in order to attach one of the evaporators to it.
  • the above-mentioned thermal insulation layer can be part of the partition wall. Since the expansion valve cools down during operation, a recess in the thermal insulation layer that accommodates the expansion valve should be at least to the colder, i.e. generally be open to the first storage compartment.
  • its capacity should be dimensioned to provide space for at least half of the refrigerant in the liquid state.
  • the space does not need to be sufficient for the entire refrigerant, since liquid refrigerant generally only reaches the collecting container when the first evaporator is full.
  • a control circuit should be set up in order to set a high mass flow rate through the controllable expansion valve at a high sensed temperature and a low mass flow rate at a low sensed temperature.
  • FIG. 1 shows a block diagram of a refrigeration device according to a first embodiment
  • FIG. 2 shows a section through a collector according to a first embodiment
  • FIG. 3 shows a section through a collector according to a second embodiment
  • 4 shows a schematic section through the refrigeration device from FIG. 1;
  • FIG. 5 shows a block diagram of a refrigeration device according to a second embodiment of the invention.
  • FIG. 6 shows a schematic section through the refrigeration device from FIG. 5.
  • the refrigerant circuit comprises, in a manner known per se, a compressor 1, from whose pressure connection 2 a pressure line 3 extends via a condenser 4 and a collector 5 or dryer to a throttle point 6.
  • a compressor 1 from whose pressure connection 2 a pressure line 3 extends via a condenser 4 and a collector 5 or dryer to a throttle point 6.
  • a suction pipe 9 extending from the evaporator 8 guides the refrigerant back to a suction connection 10 of the compressor 1.
  • the pressure line 3 is widened locally to form a chamber 11 functioning as a vapor separator with an inlet 12 at the upper end and an outlet 13 at the lower end.
  • a mixture of liquid refrigerant and vapor from the condenser 4 enters the collector 5 via the inlet 12. Since the free cross section of the collector 5 is larger than that of the pressure line 3 in front of and behind it, the flow velocity of the refrigerant in the collector is reduced, and both Phases of the refrigerant have the opportunity to separate from one another. So that this can take place without being hindered by capillary effects, the free cross section of the collector 5 should at least locally reach an area of at least 0.5 cm 2 or the diameter should reach a value of at least 8 mm.
  • a sufficient retention time of the refrigerant for the phase separation is achieved by a large volume of the chamber; this is preferably dimensioned in order to offer at least half of the total refrigerant present in the device in the liquid state, ie with a refrigerant charge of 50 or 100 g and a density of 0.5 g / cm 3 , the capacity of the chamber should be at least 50 or 100 cm 3 .
  • a bed of granulate, in particular of a dryer material that binds residual water in the refrigerant can also be accommodated in an area of the collector 5 near the outlet.
  • FIG. 2 shows a schematic axial section through a collector 5 according to a first embodiment.
  • the collector 5 is here a rotationally symmetrical hollow body which is made of the same metal as sections 37, 38 of the pipeline 3 which are soldered to the hollow body at the inlet 12 or outlet 13.
  • the hollow body itself is assembled from an upper housing part 39 and a lower housing part 40 after a dryer granulate 41 has been fixed in the lower housing part to bind the residual water and through a sieve 42, fleece or the like pushed over it.
  • the volume occupied by the dryer granulate 41 takes up only a small part, in any case less than half, of the volume of the collector.
  • inflowing liquid and gaseous refrigerants can segregate without being impaired by flow obstacles.
  • the sections 37, 38 can have different cross-sections; In particular, a smaller cross section is sufficient for section 38 which only carries liquid refrigerant than for section 37 which also carries steam.
  • FIG. 3 shows a second embodiment of the collector 5.
  • dryer granulate 41 can be accommodated in the lower part of the interior of the collector 5; alternatively, a separate dryer can be inserted into the refrigerant circuit for this.
  • An upstream section 37 of the line 3 opens horizontally and offset against an axis of rotational symmetry 43 of the collector 5 into the interior, so that the flow of liquid and vaporous refrigerant fed in via it is set in rotation about the axis 43 and the liquid portion on the walls of the collector is deposited.
  • the rotation comes to a standstill, dampened by the sieve or fleece 42 and possibly the dryer granulate 41.
  • the free volume of the collector 5 is 50 to 200 cm 3 . With a density of the liquid refrigerant of approx. 2 g / cm 3 and a filling quantity of typically 100 g, this volume is sufficient to take up at least half of the refrigerant in liquid form.
  • the throttle point 6 comprises at least one controllable expansion valve 14.
  • a capillary 15 is also provided between the collector 5 and the expansion valve 14. The capillary 15 is dimensioned in order to generate only the smaller part of the pressure drop between the condenser 4 and the evaporator 7, the larger part arises at the controllable expansion valve 14.
  • the above-mentioned section 38 can be an integral part of this capillary 15;
  • the capillary 15 extends continuously from the outlet 13 of the collector 5 to the expansion valve 14.
  • the nitrogen flow through the capillary can be 500-800 l / h with a pressure drop of 6 bar.
  • the series connection with the capillary 15 enables the expansion valve 14 to precisely control smaller mass flows for a given pressure difference than if the expansion valve were exposed to the pressure of the refrigerant alone.
  • the capillary 15 is arranged upstream of the expansion valve 14, the pressure in the capillary 15 is high enough over its entire length to prevent the evaporation of refrigerant in the capillary 15.
  • the evaporator 8 is connected to the evaporator 7 in such a way that liquid refrigerant only reaches the evaporator 8 when the evaporator 7 is full.
  • the evaporator 7 can be equipped with a refrigerant pipe 17 which rises continuously from an inlet 18 to an outlet 19 of the evaporator 7, so that vapor generated in the evaporator 7 flows off in the direction of the outlet 19, but liquid refrigerant past the rising vapor in the direction of the inlet 18 can flow.
  • a temperature sensor 20 can be attached to the evaporator 8; Preferably, it is attached without direct contact to the evaporator 8 in a storage compartment 21 cooled by this (see FIG. 4), typically a normal refrigeration compartment of the refrigeration device, in order to detect the temperature of the storage compartment 21. This shows, with a delay and averaged over time, the amount of liquid refrigerant that reaches the evaporator 8. ok
  • a control circuit 22 is connected to the temperature sensor 20 and the expansion valve 14 in order to control the latter on the basis of measured values from the temperature sensor 20. It can also be connected to the compressor 1 in order to control its speed on the basis of these measured values and possibly a temperature measured in a storage compartment 23 (see FIG. 4) cooled by the evaporator 7.
  • the expansion valve 14 is opened further. This happens gradually, i.e. As long as the target value is exceeded, the control circuit 22 increases the degree of opening of the expansion valve 14 continuously or in regular small steps to ensure that the increase in the degree of opening does not lead to the collector 5 temporarily drying out and to the entry of steam into the throttle point 6. The likelihood of this happening is further reduced by the large volume of the collector 5 and the fact that if the setpoint is exceeded, it is to be expected that the evaporator 8 will contain little or no liquid refrigerant and accordingly a large amount must be stored in the collector 5 .
  • the increasing supply of liquid refrigerant to the evaporator 7 due to the increase in the degree of opening causes it to overflow, and refrigerant penetrating into the evaporator 8 leads to a decrease in the temperature detected by the temperature sensor 20, so that the target value is reached or undershot and the control circuit 22 denies The opening degree of the expansion valve 14 is no longer increased.
  • the degree of opening of the expansion valve 14 is gradually reduced. This reduces the amount of liquid refrigerant that reaches the evaporator 8, and the temperature of the storage compartment 21 detected by the temperature sensor 20 gradually increases.
  • the cooling power available at the evaporator 7 does not change as long as liquid refrigerant still reaches the evaporator 8. Only when this no longer happens and the evaporator 7 is only incompletely filled with liquid refrigerant does its cooling capacity also decrease.
  • control circuit 22 also determines the speed of the compressor 1 based on the cooling requirement of the Storage compartment 23 controls. If the measured temperature exceeds a setpoint in the latter, the speed of the compressor 1 is gradually increased. If the degree of opening of the expansion valve 14 is not changed at the same time, this leads to increased evaporation in the evaporator 8 and a corresponding increase in the amount of liquid refrigerant in the collector 5.
  • FIG. 4 shows a schematic cross section through a body 24 of the refrigeration device of FIG. 1.
  • the colder storage compartment 23 is arranged below the warmer one 21 and separated from the latter by an intermediate wall 25.
  • the partition 25 is designed as a hollow body with outer walls 26, the interior of which is filled with an insulating material 27.
  • the suction tube 9 runs in a rear wall of the body 24 along both storage compartments 23, 21 downwards; over part of its length, the capillary 15 runs inside or in contact with its outer wall to form the internal heat exchanger 16.
  • a recess 28 in the layer of insulation material 27 is provided to accommodate the expansion valve 14. Since the latter cools down during operation, the recess 28 is open to the storage compartment 23 in order to allow a flow of heat to the expansion valve 14 from there.
  • the recess can be closed by a little heat-insulating cover 29, which can be removed in order to enable repairs to the expansion valve 14 if necessary.
  • FIG. 5 shows a second embodiment of the refrigeration device in a representation analogous to FIG. Components of the refrigerant circuit that are the same as those already described above are given the same reference numerals and are not described again.
  • the second evaporator 8 is replaced here by a collecting container 30 which does not necessarily cool a storage compartment. Instead, the collecting container 30 can be in an evaporator chamber 31 of a no-frost refrigeration device in relation to the direction of rotation of a be arranged between the evaporator chamber 31 and storage compartment 21 or 23 upstream of the evaporator 7 circulating air flow, as shown by way of example in FIG.
  • FIG. 6 shows a section through an intermediate wall 32 of a no-frost refrigeration device.
  • the evaporator chamber 31 is separated from the cold storage compartment 23 below by a thin partition 33 and from the warmer storage compartment 21 above it by a wall filled with insulating material 27.
  • a fan 34 is arranged in a manner known per se downstream of the evaporator 7, which is designed as a lamellar evaporator, in order to suck in air from one of the compartments 21, 23 in each case via an inlet 35. From which compartment the air is sucked in is determined by the position of a flap 36. Regardless of the position in which the flap 36 is located, the air that is sucked in is always warmer upstream of the evaporator 7 than downstream of the same.
  • the collecting container 30 Since the collecting container 30 is mounted in the evaporator chamber 31 upstream of the evaporator 7, it is located in a warmer environment than the latter, and refrigerant that overflows from the evaporator 7 into the collecting container 30 can still evaporate in this. Since the common capacity of evaporator 7 and collecting container 30 is sufficiently dimensioned to absorb all of the refrigerant present in the refrigerant circuit in the liquid state, overflow of collecting container 30 into suction pipe 9 can be excluded.

Landscapes

  • 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)

Abstract

Dans un appareil de froid, en particulier un appareil de froid domestique, comportant un condenseur (4), au moins un premier évaporateur (7) refroidissant un premier compartiment de stockage (23), un point d'étranglement (6) qui relie une sortie du condenseur (4) à une entrée du premier évaporateur (7), un récipient collecteur (8, 30) pour le réfrigérant liquide débordant du premier évaporateur (7), qui est relié à une sortie du premier évaporateur (7) et qui est disposé dans un environnement plus chaud que l'environnement du premier évaporateur (7), un capteur de température (20) est associé au récipient collecteur (8, 30), et le point d'étranglement (6) comprend une soupape de détente (14) commandable qui est commandée en fonction de la température détectée par le capteur de température (20).
EP20702094.2A 2019-02-27 2020-01-23 Appareil de froid Pending EP3931501A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019202649.4A DE102019202649A1 (de) 2019-02-27 2019-02-27 Kältegerät
PCT/EP2020/051642 WO2020173626A1 (fr) 2019-02-27 2020-01-23 Appareil de froid

Publications (1)

Publication Number Publication Date
EP3931501A1 true EP3931501A1 (fr) 2022-01-05

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP20702094.2A Pending EP3931501A1 (fr) 2019-02-27 2020-01-23 Appareil de froid

Country Status (4)

Country Link
EP (1) EP3931501A1 (fr)
CN (1) CN113498469B (fr)
DE (1) DE102019202649A1 (fr)
WO (1) WO2020173626A1 (fr)

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CN114812026B (zh) * 2021-01-28 2023-03-14 合肥美的电冰箱有限公司 制冷设备及其控制方法、装置、电子设备及存储介质

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Publication number Publication date
CN113498469B (zh) 2023-04-18
WO2020173626A1 (fr) 2020-09-03
CN113498469A (zh) 2021-10-12
DE102019202649A1 (de) 2020-08-27

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