US20190390882A1 - Refrigeration Appliance And Method For The Operation Thereof - Google Patents

Refrigeration Appliance And Method For The Operation Thereof Download PDF

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Publication number
US20190390882A1
US20190390882A1 US16/483,905 US201816483905A US2019390882A1 US 20190390882 A1 US20190390882 A1 US 20190390882A1 US 201816483905 A US201816483905 A US 201816483905A US 2019390882 A1 US2019390882 A1 US 2019390882A1
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Prior art keywords
temperature
evaporator
temperature zone
compressor
throttling point
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Abandoned
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US16/483,905
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English (en)
Inventor
Matthias Mrzyglod
Vitali Ulrich
Niels Liengaard
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BSH Hausgeraete GmbH
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BSH Hausgeraete GmbH
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Filing date
Publication date
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Assigned to BSH HAUSGERAETE GMBH reassignment BSH HAUSGERAETE GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LIENGAARD, NIELS, MRZYGLOD, MATTHIAS, ULRICH, Vitali
Publication of US20190390882A1 publication Critical patent/US20190390882A1/en
Abandoned legal-status Critical Current

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Classifications

    • F25B41/062—
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • 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
    • 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
    • F25B2600/11—Fan speed control
    • F25B2600/112—Fan speed control of evaporator fans
    • 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
    • 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
    • F25D2700/12—Sensors measuring the inside temperature
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B40/00—Technologies aiming at improving the efficiency of home appliances, e.g. induction cooking or efficient technologies for refrigerators, freezers or dish washers

Definitions

  • the present invention relates to a refrigeration appliance, in particular a household refrigeration appliance, having a plurality of temperature zones, and a method for operating a refrigeration appliance of this kind.
  • DE 10 2013 226 341 A1 discloses a refrigeration appliance having a first and a second temperature zone, in which a refrigerant circuit includes a compressor, a first evaporator for cooling the first temperature zone and, connected in series with the first evaporator, a second evaporator for cooling the second temperature zone, and in which a controllable expansion valve is connected upstream of each evaporator in the refrigerant circuit.
  • the object is achieved, in a first aspect, in that in a refrigeration appliance having at least a first and a second temperature zone and a refrigerant circuit that includes a compressor, a first evaporator for cooling the first temperature zone and a second evaporator for cooling the second temperature zone, wherein the first evaporator is connected in series with the second evaporator, downstream thereof in the refrigerant circuit, and a first controllable throttling point is connected in the refrigerant circuit upstream of the first evaporator and downstream of the second evaporator, a first regulator controls the degree of opening of the first controllable throttling point, independently of the temperature of the first temperature zone, by way of the temperature of the second temperature zone.
  • the basic concept here is that the mass flow in the refrigerant circuit is determined by the intake conditions (pressure and temperature) that prevail at a suction connector of the compressor and an outlet of the first evaporator leading to this suction connector. If the degree of opening of the first controllable throttling point is changed, it takes considerable time before this results in a change in the intake conditions (superheated gas at evaporation pressure) in the first evaporator, which lies between the first throttling point and the suction connector. As long as the intake conditions remain the same, adjustment of the degree of opening has no effect on the mass flow but does have an effect on the cooling power of the second evaporator, which lies upstream of the first controllable throttling point.
  • the first regulator should be set up to increase the degree of opening of the first controllable throttling point when a setpoint temperature in the second temperature zone is exceeded, and to reduce the degree of opening of the first controllable throttling point when the temperature falls below a setpoint temperature in the second temperature zone. If for example the first regulator increases the degree of opening of the first controllable throttling point, then the pressure in the second evaporator falls, and the temperature thereof then also falls, with the result that the second temperature zone is cooled to a greater extent, as desired; conversely, the pressure and temperature of the second evaporator rise when the degree of opening of the first controllable throttling point is increased.
  • the first regulator should be a proportional regulator, preferably a PI controller—that is to say the change in the degree of opening caused by the first regulator should include a term that is proportional to the deviation between the actual and the setpoint temperature, and preferably also a term that is proportional to the duration of the deviation.
  • the second temperature zone should have a temperature sensor that is connected to an input to the first regulator. Further measurement variables are not required to control the first controllable throttling point—that is to say that this input may be the only input to the first regulator to receive a measurement variable.
  • the compressor regulator should be set up to increase the speed of the compressor when a setpoint temperature in the last temperature zone, as seen in the direction of flow, is exceeded, and to reduce the speed of the compressor when the temperature falls below a setpoint temperature in the last temperature zone, as seen in the direction of flow.
  • increasing the speed brings about not only a reduction in the pressure and temperature in the first evaporator but at the same time also an increase in the mass flow of refrigerant, with the result that an additional cooling power that is required is provided in one of the temperature zones.
  • this favors rapid reinstatement of an energy-efficient steady operating state of the refrigeration appliance if the need for cooling has changed in all the temperature zones after a change in the ambient temperature.
  • the compressor regulator may be coupled to the first regulator and be set up to increase the speed when the degree of opening of the first controllable throttling point is increased and to reduce it when the degree of opening of the first controllable throttling point is reduced. In this way, a proactive adaptation of the compressor speed is already possible at a point in time before a change in the degree of opening of the first controllable throttling point has had any effect on the cooling power of the first evaporator.
  • the compressor regulator may also be a proportional or PI controller.
  • the principle of the invention may be extended to an indefinite number of evaporators connected in series, for example by connecting a third evaporator, which is for controlling the temperature of a third temperature zone, upstream of the second evaporator in the refrigerant circuit by way of a second controllable throttling point, and by providing a second regulator in order to control the degree of opening of the second controllable throttling point by way of the temperature of the third temperature zone independently of the temperature of the second temperature zone.
  • the compressor regulator may in that case also be coupled to the second regulator in order to take account of a change to the degree of opening of the second controllable throttling point when the compressor speed is established.
  • the second regulator for controlling the second throttling point may operate entirely independently of the first regulator.
  • both regulators may be implemented in the form of software on the same processor; the fact that they are mutually independent is seen in the fact that the two do not have access to the same temperature sensors, nor does one of the regulators use output data from the other as input data.
  • an upstream controllable throttling point Between a pressure-side connector of the compressor and the evaporators there may be provided an upstream controllable throttling point.
  • the degree of opening of this throttling point may be controlled by way of a drop in temperature at the first evaporator.
  • a distribution regulator that is used for this purpose may in turn be independent, in the sense specified above, of the first, second and any further regulators.
  • the object is further achieved by a method for operating a refrigeration appliance having at least a first and a second temperature zone and a refrigerant circuit that includes a compressor, a first evaporator for cooling the first temperature zone and a second evaporator for cooling the second temperature zone, wherein the first evaporator is connected in series with the second evaporator, downstream thereof in the refrigerant circuit, and a first controllable throttling point is connected in the refrigerant circuit upstream of the first evaporator and downstream of the second evaporator, in which the temperature of the second temperature zone is measured and the degree of opening of the first controllable throttling point, independently of the temperature of the first temperature zone, is controlled by way of the temperature of the second temperature zone.
  • the speed of the compressor may be increased, and if the degree of opening of the same controllable throttling point is reduced the speed of the compressor may be reduced.
  • FIG. 1 shows a schematic illustration of the refrigeration appliance according to the invention, according to a first embodiment
  • FIG. 2 shows a flow chart of an operating method of a regulator of the refrigeration appliance
  • FIG. 3 shows a modified detail of the refrigeration appliance
  • FIG. 4 shows an illustration analogous to FIG. 1 , according to a second embodiment
  • FIG. 5 shows a flow chart of an operating method of a compressor regulator.
  • FIG. 1 shows schematically a refrigeration appliance according to a first embodiment of the invention.
  • the refrigeration appliance is a combination appliance, and includes a plurality of temperature zones 1 , 2 , 3 , 4 , typically in the form of storage compartments in a housing 5 , which are each closable by a door and are separated from one another by heat-insulating walls.
  • Each temperature zone 1 , 2 , 3 , 4 has an evaporator 6 , 7 , 8 and 9 respectively, which are connected within a refrigerant circuit having a compressor 10 and a condenser 11 .
  • At least two evaporators, in this case the evaporators 6 , 7 , 8 are connected in series along a branch 13 of a refrigerant line 12 ; as shown, the refrigerant line 12 may have further branches 14 that are parallel to the branch 13 and supply further evaporators, in this case the evaporator 9 .
  • Each evaporator 6 , 7 , 8 , 9 and the condenser 11 are combined with a respective ventilator 25 for increasing the heat transfer output.
  • the temperature zones 1 , 2 , 3 , 4 may each be divided, in a manner known per se, into a storage compartment and an evaporator chamber, which receives the evaporator 6 , 7 , 8 or 9 , in which case the ventilator 25 drives the air exchange between the storage compartment and the evaporator chamber.
  • the temperature difference that must prevail between an evaporator and the storage compartment cooled thereby in order to be able to keep the storage compartment at its setpoint temperature depends on the extent of the air exchange between the storage compartment and the evaporator chamber. If this is small, then the evaporator temperature must be low, and since maintaining a low evaporator temperature requires a high output from the compressor 11 the energy efficiency of the appliance is limited. Because of the low evaporator temperature, almost all the water vapor reaching the evaporator chamber from the storage compartment is precipitated at the evaporator, so the air humidity in the storage compartment is low. Conversely, the temperature difference between the evaporator and the storage compartment can be kept small if the ventilator 25 provides a high exchange of air.
  • a high-pressure portion 15 of the refrigerant line 12 extends from a pressure-side connector 16 of the compressor 10 , through the condenser 11 and, in this case, a branching point 17 , to an upstream throttling point 18 , 19 .
  • the upstream throttling point 18 , 19 has a constant flow resistance. In this case, it is formed in each case in a manner known per se by a capillary that opens into the evaporator 8 and 9 respectively.
  • zone 3 is the warmest of the temperature zones 1 , 2 , 3 and zone 1 is the coldest.
  • the zone 3 may for example form a normal refrigerator compartment
  • the zone 2 may form a crisper compartment
  • the zone 1 may form a freezer compartment.
  • the branches 13 , 14 meet again at a merge point 22 , and a low-pressure portion 23 of the refrigerant line 12 leads to a suction connector 24 of the compressor 10 .
  • a plurality of regulators 27 , 28 , 29 are implemented on a microprocessor 26 .
  • the regulators 27 , 28 , 29 comprise utilities that share the processing power of the microprocessor 26 but do not access common data.
  • Each regulator 27 , 28 , 29 receives and processes measurement values from one particular temperature sensor 30 , 31 and 32 respectively.
  • FIG. 2 shows an operating method for the regulator 27 .
  • step S 1 a measurement value of the temperature is read off from the associated sensor 30 .
  • step S 2 the measurement value is compared with a setpoint temperature for the temperature zone 6 that is predetermined by the user. If the measurement value is within a tolerance range around the setpoint temperature, the method moves on to step S 3 , in which a time span ⁇ t is allowed to elapse before the program returns to step S 1 in order to repeat the method at regular intervals.
  • step S 2 If it is determined in step S 2 that the measured temperature is above the tolerance range, then there is clearly a need for greater cooling power in the temperature zone 8 .
  • the regulator 27 actuates the throttling point 20 in step S 4 in order to reduce the flow resistance thereof by a fixed value OR.
  • the extent of the reduction may be fixedly predetermined or be proportional to the discrepancy between the measured temperature and the setpoint temperature.
  • step S 2 is repeated and the measured temperature continues to be above the tolerance range, then the flow resistance of the throttling point 20 is reduced again. In this way, the flow resistance is varied in a manner proportional to the time integral of the standard deviation until the cooling requirement in the temperature zone 3 is sufficient and the temperature measured by the sensor 30 is within the tolerance range.
  • step S 5 the regulator increases the flow resistance of the throttling point 20 by the value OR such that the temperature of the evaporator 8 rises. Increasing the flow resistance may, again, be repeated in successive iterations of the method.
  • the operating method of the regulator 28 comprises the same steps as those illustrated in FIG. 2 .
  • step S 1 the temperature of the temperature zone 2 or its evaporator 7 is read off from the sensor 31 ; in step S 2 , it is compared with the setpoint value established for this temperature zone and, depending on the result, the flow resistance of the throttling point 21 is maintained unchanged, reduced (step S 4 ) or increased (S 5 ).
  • the extent OR of the change may but need not be identical to that used in the regulator 27 .
  • the reduction results in a fall in the pressure and temperature in the evaporator 7 and, to a lesser extent, in the evaporator 8 , such that a greater cooling power is available in both evaporators 7 , 8 .
  • the regulator 29 performs a slightly modified method, in which, if the setpoint temperature is exceeded, the speed of the compressor 10 is increased in step S 4 and, if the temperature falls below the setpoint temperature, it is reduced in step S 5 .
  • S 4 results in a fall in the evaporating temperature in the associated evaporator 6 but at the same time an increase in the mass flow, so that overall more cooling power to be distributed to the different evaporators is available.
  • S 5 raises the evaporating temperature while at the same time throttling the mass flow.
  • the compressor regulator 29 may be coupled to the regulators 27 , 28 in order to receive therefrom information on a change in the flow resistance of the throttling points 20 , 21 controlled thereby and to track the speed of the compressor 10 that corresponds to the change before the change in the flow resistance has taken effect as a change to the temperature in the temperature zone 1 .
  • a coupling of this kind may for example comprise, whenever one of the regulators 27 , 28 has increased or reduced the flow resistance by OR step S 4 , having the compressor regulator 29 reduce or raise the speed of the compressor 10 by a corresponding increment AU.
  • FIG. 5 shows an operating method of the compressor regulator 29 that implements a coupling of this kind. Steps S 1 to S 5 correspond to those in FIG.
  • step S 2 apart from the fact that if, in step S 2 , the measured temperature is above the setpoint value for the temperature zone 1 , then the speed is increased by a fixed value ⁇ U′ in step S 4 , or if it is below the setpoint value it is reduced by the value ⁇ U′ in step S 5 .
  • a check is carried out in step S 6 of whether, since the preceding iteration, at least one of the regulators 27 , 28 has made a change OR to the flow resistance at its controllable throttling point 20 or 21 .
  • the speed is reduced by ⁇ U (S 7 ), and in the event of a reduction it is increased by ⁇ U (S 8 ).
  • the value of ⁇ U may differ, depending on the throttling point 20 or 21 at which the change to the flow resistance took place.
  • controllable throttling points 18 ′, 19 ′ may be expansion valves of the same type as the ones at the throttling points 20 , 21 , but they may also—as shown in FIG. 3 —be a parallel circuit comprising a capillary 33 and a shutoff valve 34 .
  • the pressure in the evaporator 8 may be brought into line with that of the condenser 11 , with the result that refrigerant in the evaporator 8 condenses instead of evaporating, and the temperature zone 3 is heated by the heat this releases.
  • the regulators 28 , 29 continue to operate by the method described in conjunction with FIG. 2 in order to distribute the available cooling power to the temperature zones 1 , 2 as required.
  • FIG. 4 shows a diagram analogous to FIG. 1 , of a refrigeration appliance according to a further embodiment of the invention.
  • Identical reference numerals in both figures designate components that have already been described in conjunction with FIG. 1 ; statements made in relation to these components in the description of FIG. 1 also apply here and need not be repeated.
  • An additional temperature sensor 35 is mounted adjacent to the infeed point for the evaporator 6 in order to detect the evaporating temperature thereof reliably even if the extent to which it is filled with liquid refrigerant is not sufficient to keep it at the evaporating temperature over its entire extent.
  • the temperature sensor 35 may also serve to control a defrosting heater for the purpose of defrosting the evaporator 6 .
  • a further temperature sensor 36 is also mounted at an outlet of the evaporator 6 or at the low-pressure portion 23 , in order to detect the temperature of the refrigerant vapor flowing back to the compressor 10 .
  • a further regulator 37 is connected to both temperature sensors 35 , 36 in order to monitor the difference between the temperatures and to use this difference to control the flow resistance of an expansion valve that is inserted as a controllable throttling point 18 ′ between the condenser 11 and the evaporator 8 . Too small a difference is an indication of a high filling level of the evaporator 6 and the possibility that liquid refrigerant is reaching the low-pressure portion 23 as a result of overfilling.
  • the regulator 37 increases the flow resistance of the throttling point 18 ′, such that more liquid refrigerant builds up upstream of the throttling point 18 ′ and in response the quantity of refrigerant in the evaporator 6 falls. If by contrast there is too great a difference—that is to say if the temperature measured by the sensor 35 , of the refrigerant vapor that is removed by suction, is only a little lower than the compartment temperature of the temperature zone 1 , then this is an indication of insufficient filling of the evaporator 6 , and the flow resistance of the throttling point 18 ′ is reduced to allow more liquid refrigerant to penetrate through the evaporators 8 , 7 and into the evaporator 6 .

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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)
  • Air Conditioning Control Device (AREA)
US16/483,905 2017-03-30 2018-03-20 Refrigeration Appliance And Method For The Operation Thereof Abandoned US20190390882A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102017205426.3 2017-03-30
DE102017205426.3A DE102017205426A1 (de) 2017-03-30 2017-03-30 Kältegerät und Betriebsverfahren dafür
PCT/EP2018/057009 WO2018177809A1 (fr) 2017-03-30 2018-03-20 Appareil frigorifique et procédé de fonctionnement associé

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US20190390882A1 true US20190390882A1 (en) 2019-12-26

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US (1) US20190390882A1 (fr)
EP (1) EP3601902B1 (fr)
CN (1) CN110462307A (fr)
DE (1) DE102017205426A1 (fr)
WO (1) WO2018177809A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20210239382A1 (en) * 2020-02-04 2021-08-05 Samsung Electronics Co., Ltd. Refrigerator

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* Cited by examiner, † Cited by third party
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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Publication number Priority date Publication date Assignee Title
JPS50150956A (fr) * 1974-05-25 1975-12-04
JPS51137154U (fr) * 1975-04-28 1976-11-05
JP2000356447A (ja) * 1999-06-14 2000-12-26 Matsushita Refrig Co Ltd 冷凍システムのインバータ装置
JP2001116423A (ja) * 1999-10-15 2001-04-27 Fuji Electric Co Ltd 冷凍空調装置
JP2001133112A (ja) * 1999-11-10 2001-05-18 Matsushita Refrig Co Ltd 冷蔵庫
DE102012211270A1 (de) * 2012-06-29 2014-01-02 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät mit einer verstellbaren Drosselung
CN102997610B (zh) * 2012-12-31 2015-01-21 合肥美的电冰箱有限公司 制冷设备的控制方法
DE102013223737A1 (de) * 2013-11-20 2015-05-21 BSH Hausgeräte GmbH Einkreis-Kältegerät
DE102013226341A1 (de) 2013-12-18 2015-06-18 BSH Hausgeräte GmbH Kältegerät mit mehreren Kältefächern
CN105276913B (zh) * 2015-04-13 2018-01-30 Tcl智能科技（合肥）有限公司 风冷冰箱风机转速调整方法及风冷冰箱
DE102015211960A1 (de) * 2015-06-26 2016-12-29 BSH Hausgeräte GmbH Kältegerät mit Luftfeuchteüberwachung

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20210239382A1 (en) * 2020-02-04 2021-08-05 Samsung Electronics Co., Ltd. Refrigerator

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EP3601902B1 (fr) 2022-05-18
DE102017205426A1 (de) 2018-10-04
CN110462307A (zh) 2019-11-15
EP3601902A1 (fr) 2020-02-05
WO2018177809A1 (fr) 2018-10-04

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