EP3417212B1 - 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
EP3417212B1
EP3417212B1 EP17702371.0A EP17702371A EP3417212B1 EP 3417212 B1 EP3417212 B1 EP 3417212B1 EP 17702371 A EP17702371 A EP 17702371A EP 3417212 B1 EP3417212 B1 EP 3417212B1
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EP
European Patent Office
Prior art keywords
heat exchanger
throttle point
refrigeration appliance
appliance according
storage chamber
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
EP17702371.0A
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German (de)
English (en)
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EP3417212A1 (fr
Inventor
Andreas BABUCKE
Niels Liengaard
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
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BSH Hausgeraete GmbH
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Publication date
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Publication of EP3417212A1 publication Critical patent/EP3417212A1/fr
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Publication of EP3417212B1 publication Critical patent/EP3417212B1/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
    • 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
    • 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
    • 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
    • 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
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • F25B2600/2501—Bypass 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
    • F25B2700/2104—Temperatures of an indoor room or compartment

Definitions

  • the present invention relates to a refrigeration device, in particular a domestic refrigeration device, with a plurality of 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 tempering 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 throttling 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 be at room temperature or even slightly above.
  • the object of the present invention is to provide a refrigeration device with a plurality of storage chambers, which enables energy-efficient operation even if a high operating temperature is selected for a first storage chamber and a low operating temperature for a second storage chamber.
  • the control valve can be a directional control valve.
  • the directional control valve may form an upstream or a downstream end of the bypass line; preferably it forms the upstream end, since a small pipe cross-section is sufficient there and a more compact and cheaper valve can be used, while a valve at the downstream end must be spacious enough to also conduct expanded refrigerant in the first throttling point without excessive pressure drop.
  • control valve can be a shut-off valve arranged in the bypass line.
  • a shut-off valve forces all refrigerant flow through the internal heat exchanger; are in open condition both ways, via the internal heat exchanger and via the shunt line, can be passed, but the effect of the internal heat exchanger is small, especially if the first throttling point is in series with the internal heat exchanger parallel to the shunt line and directs the refrigerant into the shunt line.
  • a third heat exchanger is arranged in a branch of the refrigerant circuit, which extends to the second heat exchanger, bypassing the first and second throttle point and the first heat exchanger. In this way, a third storage chamber can be temperature-controlled.
  • the third heat exchanger in the branch is preferably preceded by a third throttling point and a fourth throttling point downstream.
  • a medium-pressure line section which extends between the first heat exchanger and the second orifice, and a second low-pressure line section can form a second internal heat exchanger.
  • the second internal heat exchanger contributes to energy-efficient operation in particular when the refrigerant is diverted past the first internal heat exchanger in order to keep the first storage chamber at a high operating temperature.
  • a third heat exchanger in the refrigerant circuit can be connected downstream of the first heat exchanger and upstream of the second heat exchanger.
  • a second inner heat exchanger can be formed by a medium-pressure line section, which extends between the first heat exchanger and a third throttle point upstream of the third heat exchanger, and a second low-pressure line section.
  • the control valve is coupled to a temperature sensor of the first storage chamber in order to control the distribution of the refrigerant to the high-pressure line section and the shunt line depending on the temperature detected by the temperature sensor.
  • the temperature of the refrigerant in the Heat exchanger of the first storage chamber arrives varies and - if the shunt line bypasses the first throttle point - can also be switched between condenser and evaporator operation of the first heat exchanger if necessary. In this way, operating temperatures close to the ambient temperature can also be maintained in the first storage chamber, which cannot be reliably achieved with a fixed predetermined position of the directional control valve.
  • the refrigerant circuit shown comprises a speed-controlled compressor 1 with a pressure connection 2 and a suction connection 3.
  • a high-pressure refrigerant line 4 which starts at the pressure connection 2, runs in the direction of circulation of the refrigerant first via a condenser 5 and a branch 6 to a directional control valve 7.
  • a section of the high-pressure Refrigerant line 4 leads from a first outlet of the directional control valve 7 via an internal heat exchanger 8 and a first throttle point 9 to a heat exchanger 10 which is associated with a first storage chamber 26 of the refrigerator.
  • a bypass line 11 connects a second outlet of the directional control valve 7 directly, bypassing the internal heat exchanger 8 and the throttle point 9, to the heat exchanger 10.
  • An outlet of the heat exchanger 10 is connected via a second internal heat exchanger 12 and a second throttle point 13 to a heat exchanger 14 which is associated with a second storage chamber 27 .
  • a low-pressure refrigerant line 15 extends from an outlet of the heat exchanger 14 via the second interior heat exchanger 12 and the first interior heat exchanger 8 back to the suction port 3.
  • the internal heat exchangers 8, 12 each comprise a section 16 or 17 of the low-pressure line 15 and a section 18 of the high-pressure refrigerant line 4 or a medium-pressure line section 19 which is in close thermally conductive contact with the low-pressure line section 16 or 17 fastened, e.g. soldered, or which is guided within the relatively spacious low-pressure line section 16 or 17.
  • the high-pressure and medium-pressure sections 18 and 19 can themselves be part of the adjacent throttle point 9 and 13, for example by being designed as capillaries.
  • a line branch 20, which separates from the high-pressure refrigerant line 4 at the junction 6, has a third throttle point 21, a heat exchanger 22 assigned to a third storage chamber 28, and a fourth throttle point 23.
  • a section 24 of the line branch 16 runs here in the first internal heat exchanger 8 in thermal contact with the same low-pressure line section 16 as the high-pressure line section 18; alternatively, together with another section of the low-pressure line 15, it could form a third internal heat exchanger.
  • the line branch 16 ends at a confluence 25, downstream of the second throttle point 13 and before the second heat exchanger 14.
  • the throttle points 9, 13, 21, 23 can all be designed as capillaries with a fixed, non-changeable flow conductivity.
  • fans 29 are provided in the storage chambers 26, 27, 28, which, if necessary, can be used by those assigned to the storage chamber Blow on heat exchanger 10, 14 or 22.
  • expansion valves with a controllable flow conductance can be used as throttle points 9, 13, 21, 23.
  • the fans 29 are then not absolutely necessary to regulate the temperatures of the storage chambers 26, 27, 28; can but nevertheless advantageously be provided in order to control not only the temperature but also the humidity in the storage chambers 26, 27, 28.
  • Another fan 30 can be provided on the condenser in order to intensify the heat exchange there as well, if required.
  • compressed refrigerant When the compressor 1 is in operation, compressed refrigerant reaches the branch 6 after a first cooling in the condenser 5.
  • the refrigerant is at least for the most part liquid, its temperature is a few degrees higher than the ambient temperature depending on the dimensioning of the condenser.
  • Part of the refrigerant flows via the throttling point 21, the heat exchanger 22 and the throttling point 23 to the heat exchanger 14 and from there back to the suction connection 3.
  • the pressure in the evaporator 14 is low enough to allow the storage chamber 27 to be operated as a freezer, the pressure in the heat exchangers 10, 22 is between that of the condenser 5 and that of the heat exchanger 14 and allows the storage chambers 26, 28 to be operated e.g Fresh cooling compartment or as a normal cooling compartment. In order to achieve higher temperatures, for example for operation as a cellar compartment, in one of the storage chambers 26, 28, the ambient temperature would have to be far enough above the desired compartment temperature.
  • the directional control valve 7 is open to the bypass line 11
  • the pressure difference between the condenser 5 and the heat exchanger 10 is negligible, and the temperature that occurs in the heat exchanger 10 is the evaporation temperature of the condenser 5 and heat exchanger 10 that corresponds to the combined pressure refrigerant.
  • the heat exchanger 10 then works as a second condenser, giving off heat to the storage chamber 15 . In this way, the storage chamber 26 reaches temperatures above the ambient temperature and can therefore be used for rapid thawing or heating of foodstuffs or for fermentation processes, for example for proving dough or preparing yoghurt.
  • the temperature of the refrigerant at the outlet of the heat exchanger 10 is generally still above the ambient temperature.
  • the second internal heat exchanger 12 ensures that the refrigerant cools down before it reaches the throttling point 13, thus enabling efficient cooling of the storage chamber 27.
  • the bearing chambers 26, 27, 28 can each be equipped with a temperature sensor in a manner known per se in order to determine the speed of the compressor 1 and the flow conductance values of the throttle points by comparing the actual temperatures in the bearing chambers 26, 27, 28 with setpoint values set by the user 9, 13, 21, 23 and/or to control the speeds of the fans 29.
  • a temperature sensor 31 of the bearing chamber 26 is also used to control the directional control valve 7: If this deviates significantly from the set setpoint, while the directional control valve 7 is in the 1 is in the position shown and none of the other storage chambers 27, 28 has a cooling requirement, then the directional control valve 7 is switched over in order to conduct warm refrigerant via the shunt line 11 into the heat exchanger 10.
  • the directional valve 7 in the position of 1 reset when the inflow of warm refrigerant allows the temperature of the storage chamber 26 to deviate significantly from the setpoint upwards.
  • setpoint temperatures can also be maintained in the storage chamber 26 which are close to the ambient temperature and which can sometimes be above and sometimes below as the ambient temperature fluctuates.
  • FIG. 2 shows a section of the refrigerant circuit of a refrigeration device according to a modified embodiment.
  • the directional valve 7 of 1 is replaced here by a shut-off valve 32 in the bypass line 11.
  • the path parallel to the shunt line 11 to the heat exchanger 10 via the high-pressure line section 18 and the throttle point 9 is constantly open. The functioning of this refrigerant circuit does not differ significantly from that in 1 shown. If the shut-off valve 32 is closed, the refrigerant can only reach the heat exchanger 10 via the throttle point 9 in this embodiment as well. When the shut-off valve 32 is open, the path via the throttling point 9 does not contribute significantly to the refrigerant flow.
  • FIG 3 shows a simplified refrigerant circuit according to a second embodiment of the invention.
  • the refrigerator has three storage chambers 26, 27, 28, but the heat exchanger 22 of the storage chamber 28 and the throttle point 21 upstream of the heat exchanger 22 are inserted between the line section 19 of the second internal heat exchanger 12 and the throttle point 13, so that a series connection of the Heat exchanger 10, 22, 14 of all three storage chambers 26, 27, 28 results.
  • the structure of the refrigerant circuit is compared to the 1 simplified because the branch 6, the throttle point 23 and the confluence 25 are omitted.
  • the only restriction that has to be accepted is that the target temperature of the storage chamber 26 cannot be lower than that of the storage chamber 28.
  • the possibility of operating the storage chamber 26 at temperatures close to the ambient temperature or above also exists here as with the refrigerant circuit 1 .
  • the directional valve 7 can also be replaced here by a shut-off valve in the bypass line 11, and a temperature sensor in the storage chamber 27 can be used to control the position of the directional valve 7 or the shut-off valve.

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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 comprenant au moins une première et une deuxième chambre de stockage (26, 27) et un cycle de l'agent réfrigérant, dans lequel un premier point d'étranglement (9), un premier échangeur de chaleur (10) pour mise à une bonne température de la première chambre de stockage (26), un deuxième point d'étranglement (13) et un deuxième échangeur de chaleur (14) pour la réfrigération de la deuxième chambre de stockage (27) sont raccordés en série,
    une section de conduit haute pression (18) placée en amont du premier point d'étranglement (9) et une section de conduit basse pression (16) placée en aval du deuxième échangeur de chaleur (14) formant un premier échangeur de chaleur (8) interne, caractérisé en ce qu'un conduit en dérivation (11) s'étend parallèlement à la section de conduit haute pression (18) vers le premier échangeur de chaleur (10) en contournant le premier échangeur de chaleur (8) interne et le premier point d'étranglement (9), et une vanne de réglage (7, 32) sert à régler la distribution de l'agent réfrigérant sur la section de conduit haute pression (18) et le conduit en dérivation (11).
  2. Appareil frigorifique selon la revendication 1, caractérisé en ce que la vanne de réglage est une vanne à voies (7).
  3. Appareil frigorifique selon la revendication 2, caractérisé en ce que la vanne à voies (7) forme l'extrémité amont du conduit en dérivation (11).
  4. Appareil frigorifique selon la revendication 1, caractérisé en ce que la vanne de réglage est une vanne antiretour (32) se trouvant dans le conduit en dérivation (11).
  5. Appareil frigorifique selon l'une des revendications 1 à 4, caractérisé en ce qu'un troisième échangeur de chaleur (22) se trouve dans une ramification (20) du cycle de l'agent réfrigérant, lequel s'étend, en contournant le premier et le deuxième point d'étranglement (9, 13) et le premier échangeur de chaleur (10), vers le deuxième échangeur de chaleur (14).
  6. Appareil frigorifique selon la revendication 5, caractérisé en ce qu'un troisième point d'étranglement (21) se trouve en amont du troisième échangeur de chaleur (22) dans la ramification (20), et un quatrième point d'étranglement (23) se trouve en aval.
  7. Appareil frigorifique selon la revendication 5 ou 6, caractérisé en ce qu'une section de conduit moyenne pression (19), qui s'étend entre le premier échangeur de chaleur (10) et le deuxième point d'étranglement (13), et une deuxième section de conduit basse pression (17) forment un deuxième échangeur de chaleur (12) interne.
  8. Appareil frigorifique selon l'une des revendications 1 à 4, caractérisé en ce qu'un troisième échangeur de chaleur (22) dans le cycle d'agent réfrigérant se trouve en aval du premier échangeur de chaleur (10) et en amont du deuxième échangeur de chaleur (14).
  9. Appareil frigorifique selon la revendication 8, caractérisé en ce qu'une section de conduit moyenne pression (19), qui s'étend entre le premier échangeur de chaleur (10) et un troisième point d'étranglement (21) en amont du troisième échangeur de chaleur (22), et une deuxième section de conduit basse pression (17) forment un deuxième échangeur de chaleur (12) interne.
  10. Appareil frigorifique selon l'une des revendications précédentes, caractérisé en ce que la perméabilité d'au moins un des points d'étranglement (9, 13, 21, 23) est réglable.
  11. Appareil frigorifique selon l'une des revendications précédentes, caractérisé en ce qu'au moins un ventilateur (29) est associé à l'un des échangeurs de chaleur (10, 14, 22).
  12. Appareil frigorifique selon l'une des revendications précédentes, caractérisé en ce que la vanne de réglage (7, 32) est couplée à un détecteur de température (31) de la première chambre de stockage (26), pour régler la distribution de l'agent réfrigérant sur la section de conduit haute pression (18) et le conduit en dérivation (11) en fonction de la température détectée par le détecteur de température (31).
EP17702371.0A 2016-02-19 2017-01-31 Appareil de froid pourvu d'une pluralité de compartiments de stockage Active EP3417212B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016202564.3A DE102016202564A1 (de) 2016-02-19 2016-02-19 Kältegerät mit mehreren Lagerkammern
PCT/EP2017/052044 WO2017140494A1 (fr) 2016-02-19 2017-01-31 Appareil de froid pourvu d'une pluralité de compartiments de stockage

Publications (2)

Publication Number Publication Date
EP3417212A1 EP3417212A1 (fr) 2018-12-26
EP3417212B1 true EP3417212B1 (fr) 2023-05-17

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EP17702371.0A Active EP3417212B1 (fr) 2016-02-19 2017-01-31 Appareil de froid pourvu d'une pluralité de compartiments de stockage

Country Status (6)

Country Link
US (1) US20190032985A1 (fr)
EP (1) EP3417212B1 (fr)
CN (1) CN108700346A (fr)
DE (1) DE102016202564A1 (fr)
PL (1) PL3417212T3 (fr)
WO (1) WO2017140494A1 (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
DE102019213220A1 (de) * 2019-09-02 2021-03-04 BSH Hausgeräte GmbH Kältegerät mit heiz- und kühlbaren Fächern
DE102019216582A1 (de) * 2019-10-28 2021-04-29 BSH Hausgeräte GmbH Kältegerät mit heiz- und kühlbarem Fach
US12092390B2 (en) 2022-05-20 2024-09-17 Whirlpool Corporation Refrigerator appliance with convertible compartment

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Publication number Publication date
US20190032985A1 (en) 2019-01-31
CN108700346A (zh) 2018-10-23
EP3417212A1 (fr) 2018-12-26
WO2017140494A1 (fr) 2017-08-24
PL3417212T3 (pl) 2023-09-18
DE102016202564A1 (de) 2017-08-24

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