EP4051972A1 - Appareil frigorifique comprenant un compartiment pouvant être chauffé et refroidi - Google Patents

Appareil frigorifique comprenant un compartiment pouvant être chauffé et refroidi

Info

Publication number
EP4051972A1
EP4051972A1 EP20797692.9A EP20797692A EP4051972A1 EP 4051972 A1 EP4051972 A1 EP 4051972A1 EP 20797692 A EP20797692 A EP 20797692A EP 4051972 A1 EP4051972 A1 EP 4051972A1
Authority
EP
European Patent Office
Prior art keywords
storage chamber
temperature
expansion valve
heat exchanger
opening
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
EP20797692.9A
Other languages
German (de)
English (en)
Inventor
Andreas BABUCKE
Oliver Janda
Niels Liengaard
Clemens Mack
Matthias Mrzyglod
Vitali ULRICH
Carsten Weiss
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 EP4051972A1 publication Critical patent/EP4051972A1/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
    • 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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/325—Expansion valves having two or more valve members
    • 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
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits 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
    • F25D23/00—General constructional features
    • F25D23/12—Arrangements of compartments additional to cooling compartments; Combinations of refrigerators with other equipment, e.g. stove
    • 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
    • F25D29/00—Arrangement or mounting of control or safety devices
    • 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
    • F25D31/00—Other cooling or freezing apparatus
    • F25D31/005—Combined cooling and heating devices
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0253—Compressor control by controlling speed with variable speed
    • 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
    • F25B2600/2507—Flow-diverting 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves

Definitions

  • Refrigeration device with a compartment that can be heated and cooled
  • the present invention relates to a refrigeration device, in particular a household refrigeration device, with at least one storage compartment that can be optionally heated or cooled.
  • Such a refrigeration device is known from DE 102016032 986 A, for example.
  • heat exchangers of the heatable and coolable compartment and a first cooled compartment are arranged in parallel line strands of the refrigerant circuit, and both strands open onto the evaporator of a second cooled compartment. Since the pressure in the latter evaporator is lower than in each of the heat exchangers, the second refrigerated compartment is inevitably the coldest, i.e. the first refrigerated compartment can be considered as a normal refrigerator compartment, the second as a freezer compartment.
  • four expansion valves are therefore required, which makes the known refrigeration device relatively expensive.
  • its refrigerant circuit is sensitive to overflowing the heat exchangers, which makes a sensitive and correspondingly complex control necessary.
  • One object of the present invention is therefore to create a refrigeration device with a storage compartment that can be heated and cooled, which is more simply constructed and can accordingly be implemented cost-effectively. Another object is to create an operating method for such a refrigeration device.
  • a refrigeration device in particular a household refrigeration device, with at least a first, a second and a third storage chamber, a refrigerant circuit, on which the following are connected in series between a pressure connection and a suction connection of a compressor: a condenser, a first expansion valve, a first heat exchanger of the first storage chamber, a second expansion valve, and a second heat exchanger of the second storage chamber; a third heat exchanger assigned to the third storage chamber and a Control circuit for controlling the operation of the compressor and the expansion valves, the control circuit is set up to maintain a higher storage temperature in the third storage chamber than in the second storage chamber.
  • connection between the second and third heat exchanger does not require any further expansion valve; on the contrary, this connection should be as free as possible of throttle points which impede the passage of refrigerant to the third heat exchanger or promote a pressure difference between the second and third heat exchanger.
  • the smallest free cross section of a refrigerant line connecting the heat exchangers is preferably essentially the same size, but in any case at least half as large as a mean free cross section of lines of the heat exchangers.
  • the speed of the compressor should be adjustable to a large number of values, preferably continuously, so that fluctuations in the temperature in the storage chambers over time and the additional consumption of electrical energy associated with these fluctuations can be minimized by uninterrupted operation of the compressor.
  • the control circuit is preferably set up to increase the speed of the compressor if the temperature of the second storage chamber is above a setpoint value and / or to reduce the speed of rotation if the temperature of the second storage chamber is below a setpoint value.
  • the cooling effect of the third heat exchanger is largely not based on the evaporation of liquid refrigerant in it, but rather on the vapor flowing through it originating from the second heat exchanger, the change in speed influences the cooling effect of the third heat exchanger at most slightly; On the other hand, the pressure decrease has a direct effect on the evaporation of the refrigerant taking place in the second heat exchanger.
  • the control circuit is preferably set up to increase the degree of opening of the first expansion valve when the temperature of the third storage chamber is above a target value, and / or to decrease the degree of opening of the first expansion valve when the temperature of the third storage chamber is below a target value.
  • the first expansion valve and the third heat exchanger in the refrigerant circuit are separated in one direction by two heat exchangers and the second expansion valve and in the other by the compressor, an adjustment of the first expansion valve surprisingly affects the third heat exchanger in particular. Opening the first expansion valve initially causes a reduction in the throttling effect of the entire refrigerant circuit.
  • the pressure in the second and third heat exchanger changes only slightly because of the fact that the throughput of the compressor increases as this pressure increases while the speed remains the same.
  • the main consequence of opening the first expansion valve is an increased flow of liquid refrigerant through the second expansion valve and consequently, at the latest after the second heat exchanger is completely filled with liquid refrigerant, an increased supply of liquid refrigerant to the third heat exchanger and thus increased cooling the third storage room.
  • the control circuit can also be configured to increase the degree of opening of the second expansion valve when the temperature of the third storage chamber is above a setpoint value and / or to reduce the degree of opening of the second expansion valve when the temperature of the third storage chamber is below a setpoint value.
  • a decision as to which of these two options is to be used is expediently made on the basis of a comparison of the setpoint temperature of the first storage chamber with the ambient temperature.
  • control circuit can be configured to increase the degree of opening of the second expansion valve when the temperature of the first storage chamber is above a target value, and / or to decrease the degree of opening of the second expansion valve when the temperature of the first Storage chamber is below a target value.
  • control circuit can be configured to increase the degree of opening of the first expansion valve when the temperature of the first storage chamber is below a setpoint value and / or to reduce the degree of opening of the first expansion valve when the temperature of the first storage chamber is above a setpoint value.
  • the choice between the alternatives can be made on the basis of a comparison of the setpoint temperature of the first storage chamber with the ambient temperature.
  • a third expansion valve, a fourth heat exchanger of a fourth storage chamber and a fourth expansion valve can be connected to one another in series and connected in parallel to the first expansion valve, the first heat exchanger and the second expansion valve. In this way, several compartments that can be optionally heated or cooled can be created in the refrigerator.
  • the temperatures in these compartments can be set independently of one another by adjusting the evaporation pressures using the upstream and downstream expansion valves.
  • the degree of opening of the third expansion valve can also be increased if the temperature of the third storage chamber is above a target value, and / or the degree of opening of the third expansion valve can be reduced if the temperature of the third storage chamber is below a target value lies.
  • further storage chambers can be provided, each with an assigned heat exchanger and the expansion valves connected upstream and downstream of this in a branch of the refrigerant circuit.
  • a fan for driving the exchange of air between the heat exchanger and the storage chamber can be assigned to at least one of the heat exchangers.
  • Such a fan is advantageous in order to intensify the heat exchange with the storage chamber and thus to achieve a high exchange rate with a compact heat exchanger. They are not absolutely necessary to control the cooling of the various storage chambers. In the simplest case, such a fan can therefore be operated at an unregulated or fixed speed.
  • a storage chamber is operated in a cooled manner, it can be useful to regulate the speed of the fan based on a predetermined temperature difference between the evaporator and the storage chamber in order to reduce the extent to which the air in the storage chamber is dried by condensation on the evaporator or the Adjust the moisture content of the air.
  • the object is also achieved by a method for operating a refrigeration device as described above with the steps:
  • FIG. 1 shows a block diagram of a refrigeration device according to the invention.
  • FIG. 2 shows a flow diagram of an operating method of the refrigeration device.
  • Fig. 1 shows a block diagram of a refrigeration device according to the invention. At least three bearing chambers 2, 3, 4 are recessed in a heat-insulating housing 1. A heat exchanger 5, 6, 7 is assigned to each of these storage chambers 2, 3, 4. The assignment can consist in the fact that the heat exchanger is embedded in the manner of a cold wall evaporator between an inner container of the storage chamber and an insulating material layer surrounding the inner container, or that the heat exchanger 5, 6, 7 is embedded in the inner container 8 of the relevant storage chamber 2, 3 , 4 is mounted. In the latter case, a partition 9 can be provided in the inner container, which divides the volume of the inner container into the storage chamber 2, 3, 4 and a heat exchanger chamber 10 accommodating the heat exchanger 5, 6, 7.
  • a fan 11 can be assigned to each heat exchanger 5, 6, 7 to prevent the heat transfer between the storage chamber 2, 3, 4 and its heat exchanger 5 , 6, 7 intensify.
  • the speed or power of such a fan 11 can be predetermined or, as will be explained in more detail below, controllable.
  • Each storage chamber 2, 3, 4 is equipped with a temperature sensor 12. Measured values from the temperature sensors 12 are recorded by a control circuit 13.
  • a refrigerant circuit comprises, one after the other, a condenser 15, a pressure line 16, a first expansion valve 17, the heat exchanger 5, a second expansion valve 18, the second heat exchanger 6, the third heat exchanger 7 and a suction line 19 which leads to a suction connection of the compressor 14.
  • the expansion valves 17, 18 are from Design known per se, not described here, and designed to maintain a pressure difference between inlet and outlet that is predetermined by a control signal.
  • the source of the control signals is the control circuit 13.
  • the pressure line 16 and the suction line 19 run in opposite directions over part of their length in close contact with one another in order to form an internal heat exchanger 22 in which the compressed refrigerant passes to the residual heat shortly before reaching the expansion valve 17 Vents in the suction line 19.
  • the pressure difference that can be set at the expansion valve 17 is variable within wide limits.
  • the expansion valve 17 allows a pressure to be set in the heat exchanger 5 that differs only slightly, if at all, from the pressure at the pressure connection of the compressor 14, so that refrigerant condensation takes place in the heat exchanger 5 as in the condenser 15 and the storage chamber 2 at a set temperature can be operated above ambient temperature, and refrigerant condensed in the condenser 15 and heat exchanger 5 is fed to the heat exchangers 6 and 7 via the expansion valve 18.
  • An upper limit of the temperature at which the storage chamber 2 can be operated should not be below + 18 ° C.
  • the requirements for the expansion valve 18 are less stringent: in order to enable the storage chamber 3 to be operated as a freezer compartment, a non-negligible pressure drop at the expansion valve 18 is necessary even if the storage chamber 2 is operated as a normal refrigeration compartment.
  • the maximum pressure difference at the expansion valve 18 should be sufficient to enable freezer operation of the storage chamber 3 even when essentially the full output pressure of the compressor 14 is present at the inlet of the expansion valve 18.
  • both heat exchangers 6, 7 and a line connecting them can be manufactured from the same type of tube with constant cross-sectional dimensions.
  • Setpoint temperatures for all three storage chambers 2, 3, 4 can be set on a user interface 20 of the control circuit 13. If one of the storage chambers 2, 3, 4 has a fan 11, the user interface 20 can also provide the option of selecting a humidity value for the relevant storage chamber.
  • 2 shows a flow chart of a working method of the control circuit 13. In step S1, the temperatures T2, T3. T4 in storage chambers 2,
  • step S2 the setpoint temperature T2s set by the user for the storage chamber 2 is compared with the ambient temperature T env . If the former is lower, that is, if the storage chamber 2 is being cooled, the method goes to step S3.
  • step S3 the temperature T2 is compared with the target temperature T2s. If both values T2, T2s agree within a predetermined tolerance interval, the method goes directly to step S4. If the measured temperature T2 is significantly lower than T2s, then the control circuit reduces the degree of opening of the expansion valve 18 (S5) in order to increase the pressure or the boiling temperature of the refrigerant in the heat exchanger 5 in this way.
  • the reduction in the degree of opening can consist in an increase in the pressure difference to be maintained between the heat exchangers 5 and 6 by the expansion valve 18.
  • step S6 the degree of opening is increased (or the pressure difference is reduced) if the temperature T2 is significantly higher than T2s.
  • step S5 or S6 can be a constant, or it can take into account circumstances such as the amount of the difference between T2 and T2s or the period of time that the deviation between T2 and T2s already lasts, in order to minimize the time until correspondence between T2 and T2s is restored or control overshoots.
  • step S4 the temperature T3 is compared with the setpoint temperature T3s set by the user for the storage chamber 3.
  • the heat exchanger 6 of the storage chamber 3 always works as an evaporator; To this end, it is continuously supplied with liquid refrigerant during operation, which either condenses in the condenser 15 and only a small part evaporates in the heat exchanger 5, or because condensation has taken place in the heat exchanger 5 in addition to that of the condenser.
  • the heat exchanger 6 is therefore the coldest of the heat exchangers 5, 6, 7, and T3, T3s are normally located in one for one, since it, like the heat exchanger 7, is essentially the suction pressure of the compressor 14 and it is well supplied with liquid refrigerant Freezer compartment typical range below -10 ° C, e.g. around -18 ° C. If both values T3, T3s match within a predetermined tolerance interval, the method goes directly to step S7. If the measured temperature T3 is significantly lower than T3s, then the control circuit 13 reduces the speed of the compressor 14 (S8) in order to increase the pressure or the boiling temperature of the refrigerant in the heat exchanger 6 in this way. Conversely, the speed is increased in step S9 if the temperature T3 is significantly higher than T3s.
  • step S8 or S9 can be a constant, or it can take into account circumstances such as the amount of the difference between T3 and T3s or the time span that the deviation between T3 and T3s has already lasted, in order to minimize the time until correspondence between T3 and T3s is restored or control overshoots.
  • step S7 the temperature T4 is compared with the setpoint temperature T4s set by the user for the storage chamber 4. If the two values T4, T4s match within a predetermined tolerance interval, the method goes back to step S1 after a predetermined waiting time (S12). If the measured temperature T4 is significantly lower than T4s, the control circuit reduces the degree of opening of the expansion valve 17 (S10) in order to reduce the mass flow of the refrigerant and thus to reduce the amount of liquid refrigerant that reaches the heat exchanger 7 . Conversely, the degree of opening is increased in step S11 if the temperature T4 is significantly higher than T4s, so that more liquid refrigerant reaches the heat exchanger 7.
  • step S2 If, on the other hand, it is determined in step S2 that heating mode has been selected for the storage chamber 2, ie if T2s> T env , then T2 is then also compared with T2s (S3 '), but if T2 is significantly below T2s, the Expansion valve 17 further open (S5 '), or if T2 is significantly above T2s, further closed (S6').
  • the temperature T4 in the storage chamber 4 is then regulated via the expansion valve 18: if it is determined in step S7 'that this is lower than the target temperature T4s, then the degree of opening of the expansion valve 18 is reduced to reduce the amount of liquid refrigerant in the heat exchanger 7 to decrease (S10 '), in the opposite case (S1T) the degree of opening is increased.
  • a fan 21 can be arranged on the condenser 15 in order to blow ambient air over the condenser 15 and thus accelerate the heat dissipation via the condenser 15.
  • the fan 21 can run at a fixed speed. It is also conceivable that the control circuit 13 varies its speed in the same direction as that of the compressor 14 or with the ambient temperature in order to take into account the increased heat accumulation at the condenser 15 with increased compressor output.
  • the speeds of the fans 11 are independent of the temperatures in the storage chambers 2, 3, 4 and the environment. They can be fixed; in particular in the case of the storage chamber 4 that can be used as a normal refrigeration compartment, it can be useful to give the user at the interface 20 the choice between different power levels or speeds of the fan 11 there.
  • the higher the power of the fan 11, the smaller the temperature difference between the storage chamber 4 and the evaporator 7, which is sufficient to maintain the setpoint temperature T4s of the storage chamber 4.
  • the higher the temperature of the heat exchanger 7, the smaller the proportion of air humidity from the storage chamber 4 that condenses on the heat exchanger 7 and has to be conducted outside.
  • a high fan output is therefore suitable for storing items that are sensitive to drying out.
  • a lower fan output can be set for items to be cooled that tend to form mold or the like in high humidity.
  • the refrigerant circuit can have a plurality of line strands, which each extend between connection points 23 of the pressure line 16 and 24 of a line connecting the expansion valve 18 to the heat exchanger 6, each of which, analogously to the components 17, 5, 18 has in series an upstream expansion valve, a heat exchanger for the further storage chamber and a downstream expansion valve.

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

L'invention concerne un appareil frigorifique, en particulier un appareil frigorifique ménager, comprenant au moins une première, une deuxième et une troisième chambre de stockage (2, 3, 4), et un circuit de fluide frigorigène sur lequel les éléments suivants sont reliés en série entre un raccord de pression et un raccord d'aspiration d'un compresseur (14) : un condenseur (15), un premier détendeur (17), un premier échangeur de chaleur (5) de la première chambre de stockage (2), un second détendeur (18), et un deuxième échangeur de chaleur (6) de la deuxième chambre de stockage (3), un troisième échangeur de chaleur (7) associé à la troisième chambre de stockage (4), et un circuit de commande (13) pour commander le fonctionnement du compresseur (14) et des détendeurs (17, 18). Le troisième échangeur de chaleur (7) est relié en série en aval du deuxième échangeur de chaleur (6). Le circuit de commande (13) est conçu pour maintenir une température de stockage (T4s) plus élevée dans la troisième chambre de stockage (4) que dans la deuxième chambre de stockage (3).
EP20797692.9A 2019-10-28 2020-10-19 Appareil frigorifique comprenant un compartiment pouvant être chauffé et refroidi Pending EP4051972A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019216582.6A DE102019216582A1 (de) 2019-10-28 2019-10-28 Kältegerät mit heiz- und kühlbarem Fach
PCT/EP2020/079314 WO2021083697A1 (fr) 2019-10-28 2020-10-19 Appareil frigorifique comprenant un compartiment pouvant être chauffé et refroidi

Publications (1)

Publication Number Publication Date
EP4051972A1 true EP4051972A1 (fr) 2022-09-07

Family

ID=73030082

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20797692.9A Pending EP4051972A1 (fr) 2019-10-28 2020-10-19 Appareil frigorifique comprenant un compartiment pouvant être chauffé et refroidi

Country Status (5)

Country Link
US (1) US20220364781A1 (fr)
EP (1) EP4051972A1 (fr)
CN (1) CN114616432B (fr)
DE (1) DE102019216582A1 (fr)
WO (1) WO2021083697A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102019218352A1 (de) * 2019-11-27 2021-05-27 BSH Hausgeräte GmbH Kältegerät mit variabel nutzbarem Fach

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DE10162500A1 (de) * 2001-12-19 2003-07-03 Bsh Bosch Siemens Hausgeraete Kältemaschine mit einem druckseitigen Kältemittelsammler
JP4497915B2 (ja) * 2003-12-19 2010-07-07 三洋電機株式会社 冷却装置
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JP2016136082A (ja) * 2015-01-05 2016-07-28 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． 冷却装置
DE102015216933A1 (de) * 2015-09-03 2017-03-09 BSH Hausgeräte GmbH Kältegerät mit mehreren Lagerkammern
DE102016202565A1 (de) * 2016-02-19 2017-08-24 BSH Hausgeräte GmbH Kältegerät mit mehreren Lagerkammern
DE102016202564A1 (de) * 2016-02-19 2017-08-24 BSH Hausgeräte GmbH Kältegerät mit mehreren Lagerkammern
CN106322912B (zh) * 2016-08-31 2019-01-11 长虹美菱股份有限公司 冰箱用电子膨胀阀的控制方法
CN206531342U (zh) * 2017-02-24 2017-09-29 中山市尊品电器有限公司 一种混合式温度控制存储柜
DE102017205429A1 (de) * 2017-03-30 2018-10-04 BSH Hausgeräte GmbH Kältegerät und Betriebsverfahren dafür
DE102017218977A1 (de) * 2017-10-24 2019-04-25 BSH Hausgeräte GmbH Haushaltskältegerät mit einem Auftaufach und Verfahren zum Betreiben eines solchen Haushaltskältegerätes
CN107990579B (zh) * 2017-11-08 2020-02-18 西安交通大学 制冷系统、具有该制冷系统的冰箱及其控制方法
CN208936577U (zh) * 2018-10-11 2019-06-04 武汉巨力鼎兴冷链股份有限公司 具有高、低温冷藏切换功能的冷库循环系统

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DE102019216582A1 (de) 2021-04-29

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