EP3918258A1 - Appareil frigorifique avec des évaporateurs parallèles et procédé de fonctionnement associé - Google Patents

Appareil frigorifique avec des évaporateurs parallèles et procédé de fonctionnement associé

Info

Publication number
EP3918258A1
EP3918258A1 EP20702978.6A EP20702978A EP3918258A1 EP 3918258 A1 EP3918258 A1 EP 3918258A1 EP 20702978 A EP20702978 A EP 20702978A EP 3918258 A1 EP3918258 A1 EP 3918258A1
Authority
EP
European Patent Office
Prior art keywords
compressor
refrigerant
mass flow
estimated
temperature
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
EP20702978.6A
Other languages
German (de)
English (en)
Inventor
Lars Mack
Hans Ihle
Achim Paulduro
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 EP3918258A1 publication Critical patent/EP3918258A1/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
    • 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
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
    • 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
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same 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
    • 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
    • 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
    • F25B2600/25—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
    • F25B2600/2519—On-off 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
    • F25B2700/15—Power, e.g. by voltage or current
    • F25B2700/151—Power, e.g. by voltage or current of the compressor motor
    • 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
    • F25B2700/17—Speeds
    • F25B2700/171—Speeds of the compressor
    • 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
    • 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
    • F25B2700/2106—Temperatures of fresh outdoor air
    • 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 refrigerator with parallel evaporators and a method for operating such a refrigerator.
  • the evaporators can be connected in series or in parallel in a refrigerant circuit.
  • Evaporators connected in series have the disadvantage that it is only possible to selectively cool the storage compartments to a very limited extent, since the evaporators can only be supplied with refrigerant either together or not at all.
  • Refrigerators with parallel evaporators have a more complicated structure because valves are required for a selective supply of the evaporators, which allow one or the other evaporator to be selectively cut off from the refrigerant supply.
  • the amount of the refrigerant to be recovered in this way should be determined as a function of the ambient temperature, in particular if the ambient temperature is low, the period in which the compressor operates when the valve is closed should be selected longer than when the valve is high. It can be achieved in this way that the amount of the refrigerant circulating when the warmer compartment is cooled is greater in the long-term time average at a low ambient temperature than at a high one; Individual case fluctuations, which result from the fact that when the need for cooling occurs in the warmer compartment, different amounts of liquid refrigerant can be contained in the evaporator of the colder compartment and, accordingly, the amounts of liquid refrigerant still contained therein after pumping can vary from case to case. cannot be prevented in this way.
  • the object is achieved, on the one hand, in a method for operating a refrigeration device with at least one warm and one cold storage compartment and a refrigeration machine, in which at least two evaporators, which are parallel to one another, for cooling each of the storage compartments with a compressor, a condenser and an intermediate one the condenser valve and the evaporators are connected in series to form a refrigerant circuit, with the steps
  • step b) the mass flow through the compressor is estimated and the point in time for carrying out step c) is determined on the basis of the estimated mass flow.
  • step b) is preferably only then carried out if the storage compartment last supplied before the time of step a) is the cold storage compartment.
  • the mass flow also decreases as the evaporator of the colder compartment empties during the pumping
  • the amount of the refrigerant remaining in the evaporator or the accumulated in the condenser can be inferred from the latter, and the duration of the pumping can be are controlled in such a way that in each individual case, after pumping over, a quantity of circulating refrigerant suitable for operating the evaporator in the warmer compartment is available.
  • the mass flow can be estimated with little effort on the basis of the power consumption and / or the speed of the compressor.
  • the mass flow can be estimated on the assumption that the temperature of the refrigerant at a suction port of the compressor
  • Evaporation temperature of the refrigerant in the evaporator of the cold storage compartment is. This results in the density of the refrigerant at the suction connection, and by multiplying this by the volume flow, the mass flow can be calculated.
  • the refrigerant absorbs ambient heat on the way from the evaporator to the suction connection.
  • a temperature sensor for detecting the mass flow rate In order to enable a more realistic estimate of the mass flow rate, a temperature sensor for detecting the mass flow rate.
  • Temperature of the suctioned refrigerant can be provided.
  • the mass flow can be estimated on the assumption that the temperature of the refrigerant at a suction connection of the compressor is below the ambient temperature by a fixed difference.
  • This first difference is typically 2-5 ° C, preferably about 4 ° C.
  • the volume throughput can be estimated from this and a known suction-side stroke volume of the compressor and the mass flow can be estimated by multiplying it by the density corresponding to the assumed temperature at the suction connection.
  • Compressor corresponds to the saturation vapor pressure of the refrigerant at the ambient temperature increased by the differential value.
  • the volume throughput at the pressure connection of the compressor can be calculated as the product of both and the mass flow as product of the volume throughput and the density of the refrigerant corresponding to the assumed temperature.
  • step can also be carried out before step b
  • Compartment temperature of the colder compartment are rated to be one of the normal
  • a compartment temperature that is too low will lengthen step b), and a compartment temperature that is too high will shorten it.
  • the mass flow can be repeatedly estimated during the pumping and step c) can be carried out if the estimate has given a value of the mass flow below a threshold.
  • the object is further achieved by using a refrigeration device, in particular a
  • Household refrigeration device with at least one warm and one cold storage compartment, a refrigeration machine in which at least two parallel evaporators for cooling each of the storage compartments with a compressor, a condenser and a shut-off valve arranged between the condenser and the evaporators are connected in series to form a refrigerant circuit are, and with a control unit for controlling the operation of the compressor, the control unit is set up, in particular programmed, to carry out the method described above.
  • the invention also relates to a computer program product with program code means which enable a computer to carry out the method described above or to function as a control unit in a refrigerator as described above.
  • FIG. 1 shows a block diagram of a refrigeration device according to the invention
  • Fig. 1 shows schematically a household refrigerator with at least one warm storage compartment 1 and a cold storage compartment 2, which are surrounded by a common heat-insulating housing 3.
  • the warm storage compartment 1 can, for example, be a normal cooling compartment and the cold storage compartment 2 can be a freezer compartment.
  • a refrigerant circuit includes one
  • Compressor 4 one connected to a pressure connection of the compressor 4
  • Condenser 5 a valve assembly 6 with an input connected to the condenser 5 and two outputs, a first throttle point 7, typically a capillary, which is connected to a first output of the valve assembly 6, a first evaporator 8 connected to an output of the throttle point 7 Cooling the warm storage compartment 1, a second throttle point 9, which at the second output of the
  • Valve assembly 6 is connected, a second evaporator 10 connected to an outlet of the throttle point 9 for cooling the cold storage compartment 2
  • the valve assembly 6 supports a first state in which it connects its input to the first output, a second state in which it connects the input to the second output, and a third state in which the input and both outputs are separated.
  • it can have a directional control valve 14 in series with a shut-off valve 15.
  • a fan 16, 17 can be provided in each of the two storage compartments 1, 2 in order to drive an air flow via the evaporator 8, 10 of the relevant compartment and thus influence the cooling capacity of the relevant evaporator 8, 10.
  • Control circuit 18 preferably a microprocessor or microcontroller
  • the control circuit 18 can also have an ambient temperature sensor 21, a temperature sensor 19 for detecting the temperature of the evaporator 8 of the warmer compartment 1, and a current intensity sensor 23 for detecting a supply current of the compressor 4 and / or one
  • Speed sensor 24 to be connected to detect the speed of the compressor 4.
  • step S1 of comparing those measured by the temperature sensors 19, 20 is carried out
  • Compartment temperatures T1, T2 are repeated until one of them has a
  • Switch-on threshold T1ein or T2ein has risen. If the exceeded
  • Switch-on threshold T2 is on, i.e. if there is a need for cold in the colder compartment 2, the compressor 4 is switched on (S2).
  • the refrigerant then sucked in by the compressor 4 originates primarily from the warmer evaporator 8 as long as it contains liquid refrigerant.
  • the valve assembly 6 is immediately switched to the second state (S3) in order to compress and liquefy the condenser 5
  • step S5 the compressor 4 is also switched on (S5), but the speed selected for the compressor 4 in this case can differ from the speed set in step S2. If the evaporator supplied in an immediately preceding operating phase of the compressor 4 was the evaporator 8, then it can be assumed that refrigerant has already been pumped out of the evaporator 10 and the quantity in circulation is sufficient for efficient operation of the evaporator 8. In this case, the method immediately jumps to step S7 described below. Otherwise, the valve assembly 6 remains in the third state, so that the pump 4 promotes Refrigerant jams in the condenser 5. Since thus no fresh refrigerant reaches the evaporator 8, the pressure in the suction line 13 decreases until the pressure in the evaporator 10 falls below, the check valve 11 opens and refrigerant from the
  • Evaporator 10 is suctioned off.
  • step S6 the control circuit 18 sets the valve assembly 6 into the first state (S7), the refrigerant that has accumulated in the condenser flows out to the first evaporator 8, and the latter starts to cool the compartment 1 . Since the temperature of compartment 1 is higher than that of compartment 2, this is also the pressure of the one flowing out of evaporator 8
  • compartment 1 The efficiency with which compartment 1 is cooled depends on the amount of this circulating refrigerant. If this is too low, then a large part of the refrigerant must be in the
  • the condenser must be concentrated so that a pressure suitable for liquefaction can be built up, and there is little refrigerant available for evaporation
  • step S6 This is achieved in step S6 by estimating the mass flow of the refrigerant drawn off from the evaporator 10. This mass flow is greater, the greater the amount of refrigerant currently contained in the evaporator 10; simplifying it can be assumed that the amount of vapor drawn off per unit of time is directly proportional to the amount of liquid refrigerant in the evaporator 10.
  • the mass flow also corresponds to the volume flow rate of the compressor 4 on the suction side, multiplied by the density of the drawn-in refrigerant.
  • the former is the product of the constant and known stroke volume of the compressor 4 and that of that
  • Speed sensor measured speed the latter can be derived from the temperature of the evaporator 10 detected by the temperature sensor 22 using the vapor pressure curve of the refrigerant. I.e. the control circuit 18 measures that as shown in FIG.
  • Evaporator temperature determines the pressure p in the evaporator 10 (S32) and multiplies this by the volume flow rate Q of the compressor 4 (S33) in order to obtain the mass flow m. As soon as this mass flow falls below a predetermined limit value in the course of repeated measurements of the rotational speed and the evaporator temperature (S34), the condition of step S6 is fulfilled and the control unit switches the valve assembly 6 into the first state.
  • Evaporation temperature of the refrigerant in the evaporator 10 decreases, but the measured evaporator temperature follows this actual evaporation temperature only with a delay. On the other hand, it can be assumed that both temperatures still correspond to one another when the compressor 4 is started up. This fact can be exploited in that, according to a variant shown in FIG. 4, the mass flow m only immediately after the start of the compressor 4 on the basis of its stationary speed n reached shortly after the start and the temperature T20 of the compartment 2 or T22 measured at this time of the evaporator 10 is estimated (S41).
  • Operating time At is estimated higher in step S42 than if a compartment temperature between the switch-on and switch-off value is measured. Conversely, a compartment temperature above the switch-on value can indicate that a large amount of fresh, warm refrigerated goods have been loaded into the compartment 2 shortly before and the liquid refrigerant of the evaporator 10 is therefore largely used up; in this case, the operating time At is estimated in step S42 to be lower than at a normal compartment temperature between the switch-on and switch-off values.
  • the temperature at which the refrigerant reaches the compressor 4 is no longer the evaporator temperature, but rather approaches the ambient temperature on the way through the suction line 12.
  • a temperature sensor is provided directly at the suction connection of the compressor 4 in order to measure the temperature of the refrigerant arriving there, it can be assumed in a simplified manner that this temperature is around a constant value of e.g. 4-5 ° C lower than the ambient temperature measured by sensor 21.
  • the mass flow is thus estimated in that the volume throughput of the compressor 4 is not multiplied by the density at the evaporator temperature as described above, but by the density at the measured or estimated temperature at the suction port of the compressor 4.
  • This enables the control circuit 18 to derive the pressure both at the suction and at the pressure connection of the compressor 4 from the measured value of the ambient temperature.
  • the mechanical power (isentropic power) provided by the compressor 4 for compressing the refrigerant is proportional to the product of the pressure difference and
  • the control circuit (typically about 70%) of the electrical power consumed by the compressor. This means that the mass flow is a product of volume flow and density is proportional to the electrical power of the compressor 4, and that a limit value of the mass flow is undershot when the electrical power of the compressor 4 falls below a limit value. Since the supply voltage can be assumed to be constant, it is sufficient in this case that the control circuit
  • step S6 is carried out as soon as it falls below a limit value which depends on the ambient temperature.
  • the relationship between the limit value of the electrical power and the ambient temperature can be determined empirically and stored in a memory
  • Control circuit 18 can be stored.

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 comprenant au moins un compartiment de stockage à chaud et un compartiment de stockage à froid (1, 2) et une machine frigorifique dans laquelle au moins deux évaporateurs (8, 10) parallèles l'un à l'autre et destinés à refroidir respectivement l'un des compartiments de stockage (1, 2) sont reliés en série à un compresseur (4), un condenseur (5) et une vanne d'arrêt (15) disposée entre le condenseur et les évaporateurs pour former un circuit de réfrigérant. L'invention concerne également un procédé de fonctionnement de cet appareil frigorifique, comprenant les étapes suivantes : a) décider si une nouvelle demande de réfrigération dans le compartiment de stockage à chaud (1) est apparue et, dans l'affirmative, b) faire fonctionner le compresseur (4) avec la vanne d'arrêt (15) fermée pour accumuler le réfrigérant dans le condenseur (5), c) ouvrir la vanne d'arrêt (15) et charger l'évaporateur (8) du compartiment de stockage à chaud (1) avec le réfrigérant accumulé. Le procédé est caractérisé en ce qu'à l'étape b), le débit massique à travers le compresseur (4) est estimé et le moment pour exécuter l'étape c) est déterminé sur la base du débit massique estimé.
EP20702978.6A 2019-02-01 2020-01-27 Appareil frigorifique avec des évaporateurs parallèles et procédé de fonctionnement associé Pending EP3918258A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019201291.4A DE102019201291A1 (de) 2019-02-01 2019-02-01 Kältegerät mit parallelen Verdampfern und Betriebsverfahren dafür
PCT/EP2020/051933 WO2020157010A1 (fr) 2019-02-01 2020-01-27 Appareil frigorifique avec des évaporateurs parallèles et procédé de fonctionnement associé

Publications (1)

Publication Number Publication Date
EP3918258A1 true EP3918258A1 (fr) 2021-12-08

Family

ID=69411414

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20702978.6A Pending EP3918258A1 (fr) 2019-02-01 2020-01-27 Appareil frigorifique avec des évaporateurs parallèles et procédé de fonctionnement associé

Country Status (5)

Country Link
US (1) US11959682B2 (fr)
EP (1) EP3918258A1 (fr)
CN (1) CN113366269B (fr)
DE (1) DE102019201291A1 (fr)
WO (1) WO2020157010A1 (fr)

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3462156B2 (ja) 1999-11-30 2003-11-05 株式会社東芝 冷蔵庫
CN100400989C (zh) 2001-03-21 2008-07-09 广东科龙电器股份有限公司 冰箱及其控制方法
DE102006015989A1 (de) 2006-04-05 2007-10-11 BSH Bosch und Siemens Hausgeräte GmbH Verfahren zum Betreiben eines Kältegeräts mit parallel geschalteten Verdampfern und Kältegerät dafür
DE102011075004A1 (de) * 2011-04-29 2012-10-31 BSH Bosch und Siemens Hausgeräte GmbH Einkreis-Kältegerät
DE102012214117A1 (de) * 2012-08-09 2014-02-13 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät und Betriebsverfahren dafür
DE102012218345A1 (de) * 2012-10-09 2014-04-10 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät mit zwei Verdampfern
CN103940158B (zh) * 2014-04-22 2017-01-11 珠海格力电器股份有限公司 空调室外机、空调系统和空调系统的操作方法
DE102014217673A1 (de) * 2014-09-04 2016-03-10 BSH Hausgeräte GmbH Kältegerät und Kältemaschine dafür
DE102014217671A1 (de) * 2014-09-04 2016-03-10 BSH Hausgeräte GmbH Kältegerät mit mehreren Lagerfächern
CN105042985B (zh) * 2015-07-10 2017-09-22 合肥美菱股份有限公司 一种并联双系统冰箱流量的分配方法
CN105180538B (zh) * 2015-08-14 2017-12-22 河南师范大学 变频压缩机功率分配装置及其运行方法
DE102016203895A1 (de) * 2016-03-09 2017-09-14 BSH Hausgeräte GmbH Kältegerät mit einem Gefrierfach und einem Kältemittelkreis und Verfahren zum Betrieb eines Kältegeräts
CN106595126B (zh) * 2016-12-16 2019-12-20 广东美的暖通设备有限公司 外机控制系统、热泵机组及其控制方法
WO2018194324A1 (fr) 2017-04-17 2018-10-25 Samsung Electronics Co., Ltd. Dispositif à cycle de réfrigération et soupape de régulation de débit à trois voies
JP2019074300A (ja) * 2017-04-17 2019-05-16 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． 冷凍サイクル装置、その制御方法、及び三方流量制御弁
US11353246B2 (en) * 2018-06-11 2022-06-07 Hill Phoenix, Inc. CO2 refrigeration system with automated control optimization
CN109140811A (zh) * 2018-10-11 2019-01-04 武汉巨力鼎兴冷链股份有限公司 一种具有高、低温冷藏切换功能的冷库循环系统

Also Published As

Publication number Publication date
US20220099339A1 (en) 2022-03-31
US11959682B2 (en) 2024-04-16
CN113366269B (zh) 2023-02-17
WO2020157010A1 (fr) 2020-08-06
CN113366269A (zh) 2021-09-07
DE102019201291A1 (de) 2020-08-06

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