US20060218952A1 - Refrigerating device and refrigerator - Google Patents

Refrigerating device and refrigerator Download PDF

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Publication number
US20060218952A1
US20060218952A1 US11/392,774 US39277406A US2006218952A1 US 20060218952 A1 US20060218952 A1 US 20060218952A1 US 39277406 A US39277406 A US 39277406A US 2006218952 A1 US2006218952 A1 US 2006218952A1
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United States
Prior art keywords
refrigerant
heat absorbing
absorbing means
compressor
refrigerating device
Prior art date
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Abandoned
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US11/392,774
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English (en)
Inventor
Etsushi Nagae
Kazuaki Mizukami
Hiroyuki Itsuki
Hiroshi Mukaiyama
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Sanyo Electric Co Ltd
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Sanyo Electric Co Ltd
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Filing date
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Assigned to SANYO ELECTRIC CO., LTD. reassignment SANYO ELECTRIC CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ITSUKI, HIROYUKI, MIZUKAMI, KAZUAKI, MUKAIYAMA, HIROSHI, NAGAE, ETSUSHI
Publication of US20060218952A1 publication Critical patent/US20060218952A1/en
Abandoned legal-status Critical Current

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    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started
    • 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
    • F25B2400/23—Separators
    • 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
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • 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
    • 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
    • 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 refrigerating device provided with a plurality of heat absorbing means which function in different temperature zones, and a refrigerator provided with this refrigerating device.
  • a refrigerator having: heat absorbing means for refrigerating; and heat absorbing means for freezing which functions at a temperature lower than that of the heat absorbing means for refrigerating.
  • the respective heat absorbing means are operated to perform a freezing operation and a refrigerating operation.
  • a refrigerant pools in a heat sink of the heat absorbing means for freezing, for example, during the freezing operation. Thereafter, in a case where the refrigerating operation is performed, there is a problem that an amount of the refrigerant in a refrigeration cycle becomes unstable.
  • a refrigerant recovering operation is performed as a method of precisely controlling an amount of a refrigerant to be circulated in the refrigeration cycle and reducing a refrigerant behavior delay in a refrigerator provided with the above-described heat absorbing means for refrigerating and heat absorbing means for freezing.
  • a compressor is operated while interrupting inflow of the refrigerant into the heat absorbing means for freezing after the freezing operation ends.
  • a fan for a radiator is operated, the refrigerant from the heat absorbing means for freezing is recovered, and the recovered refrigerant is sent to the radiator to condense.
  • the above-described conventional refrigerating device has a problem that during the refrigerant recovering operation, the fan for the radiator needs to be operated in order to allow the refrigerant sent to the radiator to condense, and power consumption and refrigerating device operation noise increase in some case. There is also a problem that the refrigerant cannot condense in the radiator in the refrigerating device having a supercritical pressure in a high-pressure-side circuit.
  • an object of the present invention is to provide a refrigerating device capable of efficiently performing a refrigerant recovering operation even in a case where the device includes a plurality of heat absorbing means functioning in different temperature zones, and a refrigerator including this refrigerating device.
  • a refrigerating device provided with a refrigeration cycle including: a compressor; a radiator connected to a discharge side of the compressor; first pressure reducing means connected to an outlet side of the radiator; a gas-liquid separator connected to an outlet side of the first pressure reducing means; first heat absorbing means through which a liquid refrigerant from the gas-liquid separator flows and which includes second pressure reducing means and a first heat sink; and second heat absorbing means disposed in parallel with the first heat absorbing means and including third pressure reducing means and a second heat sink, refrigerant pipes of the first and second heat absorbing means on the outlet side being combined and connected to a suction side of the compressor, the second heat absorbing means functioning in a temperature zone lower than that of the first heat absorbing means, a first cooling operation to operate the first heat absorbing means and a second cooling operation to operate the second heat absorbing means being switchable to each other, the refrigerating device comprising: control means for performing a refrigerant
  • the refrigerating device of the first aspect further comprises: blowing means for sending air to the second heat sink, and the blowing means is operated during the refrigerant recovering operation.
  • the compressor has an intermediate pressure section
  • the refrigerating device further comprises: a refrigerant pipe capable of introducing a gas refrigerant separated by the gas-liquid separator into the intermediate pressure section.
  • a high-pressure side of the refrigeration cycle is operated with a supercritical pressure.
  • the refrigerant recovered from the second heat sink is stored in the gas-liquid separator in a case where the high-pressure side of the refrigeration cycle is operated with the supercritical pressure, and the refrigerant recovered from the second heat sink is stored in the gas-liquid separator and/or the radiator in a case where the high-pressure side of the refrigeration cycle is not operated with the supercritical pressure.
  • the blowing means for sending air to the radiator is disposed close to the radiator, and the blowing means is operated at a time when the refrigerant recovered from the second heat sink is stored in the radiator.
  • a refrigerating device provided with a refrigeration cycle including: a compressor; a radiator connected to a discharge side of the compressor; first pressure reducing means connected to an outlet side of the radiator; a gas-liquid separator connected to an outlet side of the first pressure reducing means; first heat absorbing means through which a liquid refrigerant from the gas-liquid separator flows and which includes second pressure reducing means and a first heat sink; and second heat absorbing means disposed in parallel with the first heat absorbing means and including third pressure reducing means and a second heat sink, refrigerant pipes of the first and second heat absorbing means on the outlet side being combined and connected to a suction side of the compressor, wherein the second heat absorbing means functions in a temperature zone lower than that of the first heat absorbing means, a first cooling operation to operate the first heat absorbing means and a second cooling operation to operate the second heat absorbing means are switchable to each other, the refrigerating device permitting circulation of the refrigerant into the first heat absorbing means
  • a refrigerating device provided with a refrigeration cycle including: a compressor; a radiator connected to a discharge side of the compressor; first pressure reducing means connected to an outlet side of the radiator; a gas-liquid separator connected to an outlet side of the first pressure reducing means; first heat absorbing means through which a liquid refrigerant from the gas-liquid separator flows and which includes second pressure reducing means and a first heat sink; and second heat absorbing means disposed in parallel with the first heat absorbing means and including third pressure reducing means and a second heat sink, refrigerant pipes of the first and second heat absorbing means on the outlet side being combined and connected to a suction side of the compressor, wherein the second heat absorbing means functions in a temperature zone lower than that of the first heat absorbing means, a first cooling operation to operate the first heat absorbing means and a second cooling operation to operate the second heat absorbing means are switchable to each other, the refrigerating device operating a refrigerant recovering operation of permitting circulation of the refrig
  • the refrigerating device of the seventh or eighth aspect further comprises: blowing means for sending air to the second heat sink, and the blowing means is operated in a case where the compressor is operated at the high frequency.
  • a refrigerator comprises: a refrigerating device in any one of the first to tenth aspects.
  • the refrigerator of the eleventh aspect further comprises: a refrigerating chamber; and a freezing chamber operated at a temperature lower than that of the refrigerating chamber, the refrigerating chamber is cooled by the first heat absorbing means, and the freezing chamber is cooled by the second heat absorbing means.
  • FIG. 1 is a refrigerant circuit diagram showing a refrigerating device in one embodiment of the present invention
  • FIG. 2 is an enthalpy and pressure graph of a refrigeration cycle of the refrigerating device in the embodiment of the present invention
  • FIG. 3 is an enthalpy and pressure graph of a supercritical refrigeration cycle of the refrigerating device in the embodiment of the present invention
  • FIG. 4 is a timing chart showing a first control method in the refrigerating device of the embodiment of the present invention.
  • FIG. 5 is a timing chart showing a second control method in the refrigerating device of the embodiment of the present invention.
  • FIG. 6 is a schematic constitution diagram showing an example in which the refrigerating device of the embodiment of the present invention is applied to a refrigerator;
  • FIG. 7 is a refrigerant circuit diagram showing a refrigerating device in another embodiment of the present invention.
  • FIG. 8 is a refrigerant circuit diagram showing a refrigerating device in still another embodiment of the present invention.
  • FIG. 1 shows a refrigerant circuit diagram of a refrigerating device in one embodiment of the present invention.
  • a refrigerating device 30 includes: a compressor 1 ; a radiator 2 connected to a discharge side of the compressor 1 ; a fan 2 F which is disposed close to this radiator 2 and which cools a refrigerant in the radiator 2 ; an expansion valve 3 as pressure reducing means connected to an outlet side of the radiator 2 ; a gas-liquid separator 4 connected to a refrigerant pipe 4 A on an outlet side of this expansion valve 3 ; a refrigerant pipe 4 B in which a liquid refrigerant separated from this gas-liquid separator 4 circulates; first heat absorbing means 10 connected to one side from a branch point 9 A from which this refrigerant pipe 4 B is branched; and second heat absorbing means 11 connected to the other side from the branch point, disposed in parallel with the first heat absorbing means 10 , and functioning in a temperature
  • a refrigerant pipe 4 C in which a gas refrigerant separated from the gas-liquid separator 4 flows is connected to an intermediate pressure section of the compressor 1 , refrigerant pipes from the heat absorbing means 10 , 11 are combined with each other in a confluent point 9 B, and the subsequent refrigerant pipe is connected to a suction port of the compressor 1 , thereby forming a refrigeration cycle
  • the refrigerating device 30 includes: a stop valve 7 disposed between the gas-liquid separator 4 and the intermediate pressure section of the compressor 1 ; a stop valve 53 disposed between the confluent point 9 B and the suction port of the compressor 1 ; and a control device 26 .
  • the first heat absorbing means 10 includes: an expansion valve 65 as pressure reducing means; and a heat sink 57 connected in series to this expansion valve 65 .
  • the second heat absorbing means 11 includes an expansion valve 66 as pressure reducing means; and a heat sink 58 connected in series to this expansion valve 66 .
  • a stop valve 52 is disposed between the heat sink 58 and the confluent point 9 B.
  • the expansion valves 3 , 65 , and 66 are constituted so that a squeezing degree is variable.
  • the squeezing degree of each valve is changed to lower a pressure of the refrigerant down to a predetermined pressure before the refrigerant reaches the heat sinks 57 , 58 , so that an evaporation temperature of the refrigerant can be controlled in the heat sinks 57 , 58 .
  • the expansion valves 65 , 66 have a function of refrigerant channel switching means.
  • the means of switched to the first heat absorbing means 10 or the second heat absorbing means 11 , and the refrigerant can be selectively circulated to one of the means.
  • the squeezing degree of the expansion valve 3 is changed, the pressure of the refrigerant is lowered to the predetermined pressure before the refrigerant reaches the gas-liquid separator 4 , and a gas refrigerant is generated.
  • the refrigerant is fed into the gas-liquid separator 4 in this state, a separation efficiency in the gas-liquid separator 4 can be changed.
  • the compressor 1 is a two-stage compressor, a sealed container contains a first-stage compressing section 1 A and a second-stage compressing section 1 B, and an intermediate cooler 1 C is disposed in the refrigerant pipe extending out of the sealed container in which the first-stage compressing section 1 A is connected to the second-stage compressing section 1 B.
  • the refrigerant pipe 4 C is connected to the compressor so that the gas refrigerant separated from the gas-liquid separator 4 can be introduced into the intermediate pressure section of the compressor 1 , that is, between the intermediate cooler 1 C and the second-stage compressing section 1 B as described above.
  • the gas refrigerant is introduced into the intermediate pressure section of the compressor 1 as shown by a broken-line arrow owing to a difference pressure in the refrigerant pipe 4 C.
  • the compressor 1 is not limited to the two-stage compressor.
  • the compressor is, for example, a one-stage compressor
  • the refrigerant pipe 4 C may be returned to an intermediate pressure section of the one-stage compressor.
  • a plurality of compressors may be connected.
  • fans 57 F, 58 F are disposed close to the heat sinks 57 , 58 , respectively.
  • cold air generated by the heat sink 57 is sent to a refrigerating chamber 21 via a duct 57 A by the fan 57 F
  • cold air generated by the heat sink 58 is sent to a freezing chamber 22 via a duct 58 A by the fan 58 F
  • the chambers 21 , 22 are cooled at a predetermined temperature, respectively.
  • the chambers 21 , 22 are provided with temperature sensors 21 T, 22 T.
  • the control device 26 is control means for controlling an operation frequency or an on/off state of the compressor 1 , open degrees of the expansion valves 3 , 65 , and 66 , on/off states of the fans 2 F, 57 F, and 58 F and the like based on information of the temperature sensors 21 T, 22 T and the like.
  • the device is constituted of, for example, a general-purpose microcomputer.
  • a carbon dioxide refrigerant (CO 2 ) which is a natural refrigerant is introduced as a refrigerant having a small load on environment in consideration of combustibility, toxicity and the like.
  • CO 2 carbon dioxide refrigerant
  • an oil as a lubricant of the compressor 1 there is used, for example, mineral oil, alkyl benzene oil, ether oil, polyalkylene glycol (PAG), polyol ester (POE) or the like.
  • FIG. 2 is an enthalpy and pressure (ph) graph of the refrigeration cycle in the embodiment
  • FIG. 3 is an enthalpy and pressure (ph) graph in a case where there is a supercritical pressure in a high-pressure-side circuit in the refrigeration cycle.
  • this freezing operation refers to a case where the expansion valve 65 is closed by the control device 26 to circulate the refrigerant on a second heat absorbing means 11 side.
  • the refrigerant discharged from the compressor 1 radiates heat, and is cooled in the radiator 2 . That is, first the refrigerant is circulated in order of: ( 1 ) suction into the first-stage compressing section 1 A; and ( 2 ) discharge from the first-stage compressing section 1 A, and cooled in the intermediate cooler 1 C. Thereafter, the refrigerant is circulated in order of: ( 3 ) suction into the second-stage compressing section 1 B; and ( 4 ) discharge from the second-stage compressing section 1 B to an inlet of the radiator 2 .
  • the refrigerant reaches ( 5 ) an outlet of the radiator 2 and an inlet of the expansion valve 3 , and ( 6 ) outlet of the expansion valve 3 , and in this state, the refrigerant constitutes a two-phase mixture of a gas and a liquid.
  • a ratio between the gas and the liquid corresponds to a ratio between a length (gas) of a line segment of ( 6 ) to ( 7 ) and a length (liquid) of a line segment from ( 6 ) to ( 21 ).
  • This refrigerant enters the gas-liquid separator 4 in the form of the two-phase mixture.
  • the gas refrigerant separated here is introduced into the intermediate pressure section of the compressor 1 , that is, between the intermediate cooler 1 C and the second-stage compressing section 1 B by the refrigerant pipe 4 C.
  • ( 21 ) denotes an outlet of the gas-liquid separator 4 .
  • the gas refrigerant discharged from the separator reaches ( 3 ) the suction of the second-stage compressing section 1 B, and is compressed by the second-stage compressing section 1 B.
  • the liquid refrigerant separated by the gas-liquid separator 4 reaches the expansion valve 66 via the confluent point 9 A.
  • ( 7 ) denotes the outlet of the gas-liquid separator 4 and the inlet of the expansion valve 66
  • ( 8 ) denotes an outlet of the expansion valve 66 and an inlet of the heat sink 58
  • ( 22 ) denotes an outlet of the heat sink 58 .
  • the liquid refrigerant evaporates, absorbs heat from its periphery, and returns to ( 1 ) the suction into the first-stage compressing section 1 A.
  • a cycle is formed as shown by broken lines in FIGS. 2 and 3 .
  • the refrigerating operation is a case where the expansion valve 66 is closed by the control device 26 to circulate the refrigerant on a first heat absorbing means 10 side.
  • the refrigerant discharged from the compressor 1 radiates heat, and is cooled in the radiator 2 . That is, the refrigerant is circulated in order of: ( 9 ) suction into the first-stage compressing section 1 A; and ( 10 ) discharge from the first-stage compressing section 1 A, and cooled in the intermediate cooler 1 C. Thereafter, the refrigerant is circulated in order of: ( 11 ) suction into the second-stage compressing section 1 B; and ( 12 ) discharge from the second-stage compressing section 1 B to the inlet of the radiator 2 .
  • the refrigerant reaches ( 5 ) the outlet of the radiator 2 and the inlet of the expansion valve 3 , and ( 16 ) the outlet of the expansion valve 3 , and in this state, the refrigerant constitutes a two-phase mixture of a gas and a liquid.
  • a ratio between the gas and the liquid corresponds to a ratio between a length (gas) of a line segment of ( 16 ) to ( 14 ) and a length (liquid) of a line segment from ( 16 ) to ( 17 ).
  • This refrigerant enters the gas-liquid separator 4 in the form of the two-phase mixture.
  • the gas refrigerant separated here is introduced into the intermediate pressure section of the compressor 1 , that is, between the intermediate cooler 1 C and the second-stage compressing section 1 B by the refrigerant pipe 4 C.
  • ( 17 ) denotes an outlet of the gas-liquid separator 4 .
  • the gas refrigerant discharged from the separator reaches ( 11 ) the suction of the second-stage compressing section 1 B, and is compressed by the second-stage compressing section 1 B.
  • the liquid refrigerant separated by the gas-liquid separator 4 reaches the expansion valve 66 via the confluent point 9 A.
  • ( 14 ) denotes the outlet of the gas-liquid separator 4 and the inlet of the expansion valve 65
  • ( 15 ) denotes an outlet of the expansion valve 65 and an inlet of the heat sink 57
  • ( 24 ) denotes an outlet of the heat sink 57 .
  • the liquid refrigerant evaporates, absorbs heat from its periphery, and returns to ( 9 ) the suction into the first-stage compressing section 1 A.
  • the refrigerant circulates to change its state as described above, and the refrigeration cycle is formed.
  • the control device 26 operates the fan 58 F during the freezing operation, and operates the fan 57 F during the refrigerating operation to thereby cool the chambers 22 , 21 , respectively.
  • the high-pressure-side circuit is operated under a supercritical pressure as shown in the enthalpy and pressure (ph) graph of FIG. 3 on the conditions that, for example, an outside air temperature is about 30° C. or more in summer, or a cooling load increases. Even in this case, it is possible to perform the freezing operation and the refrigerating operation in the same manner as in the refrigeration cycle shown in FIG. 2 as described above.
  • the refrigeration cycle efficiency can be improved.
  • carbon dioxide is used as the refrigerant
  • a gas content increases in the ratio of the gas and the liquid separated by the gas-liquid separator 4 as compared with a Freon-based refrigerant, a hydrocarbon-based refrigerant or the like.
  • the heat sinks 57 , 58 are selectively used based on a use temperature zone as described above.
  • the heat sink suitable for the temperature is usable, and there can be expected improvement of an operation efficiency of each operation.
  • the refrigerating device 30 of the present embodiment includes the heat sinks 57 , 58 which function in different temperature zones as described above.
  • the refrigerant sometimes pools in the heat sink 58 during, for example, the freezing operation performed at a temperature lower than that of the refrigerating operation.
  • a low-pressure-side circuit of the present embodiment that is, from the expansion valves 65 and 66 to the suction port of the first-stage compressing section 1 A via the confluent point 9 B, as shown also in FIGS. 2 and 3 , the pressure in the low-pressure-side circuit becomes higher during the refrigerating operation rather than during the freezing operation.
  • the stop valve 52 On the outlet side of the heat sink 58 , there is disposed the stop valve 52 for preventing a high-temperature refrigerant from being discharged into the heat sink 58 during the refrigerating operation.
  • the refrigerant stored in the heat sink 58 during the freezing operation as described above does not circulate in the refrigeration cycle during the subsequent refrigerating operation, and an amount of the refrigerant in the refrigeration cycle is unstable during the refrigerating operation.
  • FIG. 4 is a timing chart showing a first control method in the refrigerating device 30
  • FIG. 5 is a timing chart showing a second control method in the refrigerating device 30 .
  • a refrigerant recovering operation is executed at a time when the freezing operation is stopped. It is to be noted that in the present embodiment, there will be first described a case where the freezing operation is performed, but the freezing operation does not have to be performed first in the present invention.
  • the freezing operation is performed.
  • the control device 26 closes the expansion valve 65 , and opens the expansion valve 66 .
  • the device turns off the fan 57 F, and turns on the fan 58 F. Accordingly, the freezing operation is performed as described above.
  • This refrigerant recovering operation is an operation to recover the refrigerant stored in the heat sink 58 during the freezing operation. That is, in the freezing operation, when a temperature detected by the temperature sensor 22 T in the freezing chamber 22 reaches a predetermined temperature (e.g., ⁇ 26° C.), the control device 26 executes the refrigerant recovering operation.
  • a predetermined temperature e.g., ⁇ 26° C.
  • the control device 26 closes the expansion valve 66 in addition to the expansion valve 65 .
  • the compressor 1 and the fan 58 F are turned on. Accordingly, evaporation of the refrigerant stored in the heat sink 58 is promoted by the fan 58 F, and the stored refrigerant is sucked and recovered by the compressor 1 . Moreover, the recovered refrigerant is discharged by the compressor 1 .
  • the refrigerant discharged by the compressor 1 in this manner flows through the radiator 2 .
  • the refrigerant is sent to the gas-liquid separator 4 , and separated into the gas and the liquid. Moreover, since the expansion valves 65 and 66 are closed, the separated liquid refrigerant pools in this gas-liquid separator 4 .
  • the refrigerant recovering operation is performed as described above.
  • the refrigerant recovered from the heat sink 58 is stored in the gas-liquid separator 4 . Therefore, the fan 2 F does not have to be especially turned on during the refrigerant recovering operation, and it is possible to suppress power consumption and operation noise of the refrigerating device 30 .
  • the high-pressure-side circuit of the refrigeration cycle including the radiator 2 is sometimes operated with the supercritical pressure.
  • the radiator 2 since the radiator 2 has a supercritical state therein, the recovered refrigerant cannot condense in the radiator 2 as in the conventional example.
  • the refrigerant recovered from the heat sink 58 is stored in the gas-liquid separator 4 as described above. Therefore, even in a case where the supercritical pressure is brought in the high-pressure-side circuit, the refrigerant recovering operation can be performed.
  • the control device 26 turns on the fan 2 F disposed close to the radiator 2 . Accordingly, the refrigerant recovered and thereafter discharged by the compressor 1 is allowed to condense in the radiator 2 . This is applicable depending on use mode or installation place.
  • the fan 2 F is turned on to thereby further cool the refrigerant, and a refrigerant recovering speed can be increased.
  • power consumption or the like increases. However, this is applicable depending on the use mode or the installation place.
  • the control device 26 executes a control so as to store the refrigerant recovered by the refrigerant recovering operation in the gas-liquid separator 4 .
  • the control device 26 may store the refrigerant recovered by the refrigerant recovering operation in the gas-liquid separator 4 and/or the radiator 2 .
  • the control device 26 closes the expansion valves 65 and 66 , and turns off the compressor 1 and the fans 57 F, 58 F. Accordingly, the operation in the refrigerating device 30 is stopped. Thereafter, in the refrigerating device 30 of the present embodiment, the control device 26 opens the expansion valve 65 , closes the expansion valve 66 , turns on the fan 57 F, and turns off the fan 58 F. Accordingly, the freezing operation is performed as described above. Thereafter, the freezing operation is executed again. In the first control method of the present embodiment, the operations are successively executed as described above.
  • the refrigerant recovering operation is performed to recover the refrigerant stored in the heat sink 58 by the freezing operation before performing the refrigerating operation.
  • control device 26 opens the expansion valve 65 , closes the expansion valve 66 , and turns on the fans 57 F, 58 F. Moreover, the control device 26 operates the compressor 1 at a frequency higher than that during usual operation. It is to be noted that a part shown by a one-dot chain line in the timing chart of the compressor 1 in FIG. 5 is a timing at which the compressor 1 is operated at the high frequency.
  • the pressure in the heat sink 57 becomes lower than that in the heat sink 58 .
  • the fan 58 F is turned on to promote the evaporation of the refrigerant stored in the heat sink 58 , so that the compressor 1 sucks and recovers the stored refrigerant.
  • the recovered refrigerant pools in the gas-liquid separator 4 or the like as described above in the first control method.
  • the refrigerant recovering operation is performed as described above, and thereafter the refrigerating operation and the freezing operation are successively executed.
  • FIG. 6 shows a schematic constitution diagram of the refrigerator including the refrigerating device 30 of the present embodiment.
  • This refrigerator 40 includes an upper-stage refrigerating chamber 41 , and a lower-stage freezing chamber 42 .
  • in-chamber partition walls 61 , 62 are disposed in inner parts of the chambers 41 , 42 , respectively.
  • the above-described heat sinks 57 , 58 , and fans 63 , 64 are disposed in an air path 44 defined by the in-chamber partition walls 61 , 62 .
  • a temperature sensor 42 T is disposed in the freezing chamber 42
  • a temperature sensor 41 T is disposed in the refrigerating chamber 41 .
  • the first heat absorbing means 10 and the second heat absorbing means 11 are switched as described above.
  • the refrigerant is passed through one of the heat sinks 57 , 58 , and the corresponding fans 63 , 64 are driven.
  • cold air is supplied to the refrigerating chamber 41 .
  • cold air is supplied to the freezing chamber 42 .
  • the refrigerator 40 of the present embodiment includes the refrigerating device 30 constituted as described above, it is possible to obtain a high cooling performance and a high efficiency operation even in a case where carbon dioxide is used in the refrigerant. Furthermore, in the refrigerator 40 , if the above-described first or second control method is performed by the fans 63 , 64 instead of the fans 57 F, 58 F, the refrigerant recovering operation can be executed.
  • the expansion valve 65 is closed, and the expansion valve 66 is opened to circulate the refrigerant in the second heat absorbing means 11 .
  • the expansion valve 66 is closed, and the expansion valve 65 is opened to circulate the refrigerant in the first heat absorbing means 10 .
  • the present invention is not limited to this embodiment.
  • the refrigerator 40 in a case where the refrigerating chamber 41 and the freezing chamber 42 at room temperature need to be rapidly cooled during so-called pull-down, in a case where the compressor 1 is started to operate from the operation stop state, or highly loaded, or in a case where the temperature of the refrigerating chamber 41 or the freezing chamber 42 is not less than a predetermined temperature, both the expansion valves 65 and 66 are opened at a required open degree. Accordingly, the refrigerant is circulated on opposite sides of the first heat absorbing means 10 and the second heat absorbing means 11 , and the chambers 41 , 42 can be rapidly cooled, respectively.
  • FIG. 7 shows a refrigerant circuit diagram of a refrigerating device 50 in this case.
  • components denoted with the same reference numerals of Embodiment 1 have identical or similar functions or effects.
  • the present embodiment is different from Embodiment 1 in that third heat absorbing means 10 B is disposed instead of the first heat absorbing means 10 , and fourth heat absorbing means 11 B is disposed instead of the second heat absorbing means 11 .
  • the third heat absorbing means 10 B includes a refrigerant circulation control valve 93 , a capillary tube 12 , and a heat sink 57 .
  • the fourth heat absorbing means 11 B includes a refrigerant circulation control valve 94 , a capillary tube 13 having a resistance value larger than that of the capillary tube 12 , and a heat sink 58 . That is, the third and fourth heat absorbing means 10 B, 11 B include the refrigerant circulation control valves 94 , 95 and the capillary tubes 12 , 13 instead of the expansion valves 65 and 66 in the first and second heat absorbing means 10 , 11 .
  • the refrigerant circulation control valves 94 , 95 have a function of refrigerant channel switching means.
  • a control device 26 closes one of the valves to thereby perform the freezing operation in a case where the refrigerant is passed on a capillary tube 13 side, and perform the refrigerating operation in a case where the refrigerant is passed on a capillary tube 12 side.
  • the refrigerating device 50 of the present embodiment does not include the expansion valves 65 and 66 , the present invention can be realized at low cost. Needless to say, the refrigerating device 50 of the present embodiment is applicable to a refrigerator in the same manner as in the refrigerating device 30 of Embodiment 1.
  • FIG. 8 shows a refrigerant circuit diagram of a refrigerating device 70 in this case.
  • the refrigerating device includes a three-way valve 91 as refrigerant channel switching means, fifth heat absorbing means 10 C instead of the first heat absorbing means 10 , and sixth heat absorbing means 11 C instead of the second heat absorbing means 11 .
  • the fifth heat absorbing means 10 C includes a capillary tube 12 and a heat sink 57 .
  • the sixth heat absorbing means 11 C includes a capillary tube 13 having a resistance value larger than that of the capillary tube 12 , and a heat sink 58 . That is, the fifth and sixth heat absorbing means 10 C, 11 C include the capillary tubes 12 , 13 instead of the expansion valves 65 and 66 in the first and second heat absorbing means 10 , 11 , and the means include the three-way valve 91 as the refrigerant channel switching means. It is to be noted that the three-way valve 91 is also switchable into a state in which any refrigerant is not passed on a capillary tube 12 or 13 side.
  • the control device 26 controls the switching of the three-way valve 91 to circulate the refrigerant in one of the fifth and sixth heat absorbing means 10 C, 11 C. Accordingly, a freezing operation and a refrigerating operation are switched.
  • the operations can be executed by first and second control methods in the same manner as in Example 1.
  • the circulation of the refrigerant into the heat absorbing means 10 C, 11 C may be selected by the three-way valve 91 .
  • the refrigerating device 70 of the present embodiment does not include the expansion valves 65 and 66 , the present invention can be realized at low cost. Needless to say, the refrigerating device 70 of the present embodiment is applicable to a refrigerator in the same manner as in the refrigerating devices 30 , 50 of the above embodiments.
  • the present invention has been described above in detail in accordance with the embodiments, but the present invention is not limited to them, and can be variously modified.
  • the carbon dioxide refrigerant is introduced in the refrigerant circuit, but the present invention is not limited to the embodiments, and the present invention is also applicable to a case where another refrigerant such as a Freon-based or hydrocarbon-based refrigerant is introduced.
  • the expansion valve 3 may be replaced with a capillary tube if necessary.

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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)
  • Chemical Kinetics & Catalysis (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)
US11/392,774 2005-03-30 2006-03-30 Refrigerating device and refrigerator Abandoned US20060218952A1 (en)

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JP2005100186A JP2006275496A (ja) 2005-03-30 2005-03-30 冷凍装置及び冷蔵庫

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EP2142868A1 (en) * 2007-03-30 2010-01-13 Lg Electronics Inc. Controlling process for refrigerator
EP2167885A1 (en) * 2007-06-29 2010-03-31 Sinvent AS A closed circuit vapour compression refrigeratiion system and a method for operating the system
US20100152902A1 (en) * 2007-03-30 2010-06-17 Ji Won Sung Method for controlling of refrigerator
US20120085114A1 (en) * 2010-10-07 2012-04-12 Audi Ag Refrigerant circuit of an hvac system of a motor vehicle
US20120322354A1 (en) * 2011-06-16 2012-12-20 Andres Michael J Heat pump for supplemental heat
US20150121926A1 (en) * 2013-11-04 2015-05-07 Lg Electronics Inc. Refrigerator
US20150121927A1 (en) * 2013-11-04 2015-05-07 Lg Electronics Inc. Refrigerator
US9217594B2 (en) 2011-10-05 2015-12-22 Toyota Jidosha Kabushiki Kaisha Method of controlling cooling device
US20180156498A1 (en) * 2015-06-17 2018-06-07 Mitsibishi Electric Corporation Refrigerant circuit and air conditioning device
EP3288796A4 (en) * 2015-05-01 2018-10-24 Thermo King Corporation Integrated thermal energy module within an air-cooled evaporator design
US20220275976A1 (en) * 2019-09-23 2022-09-01 Gree Electric Appliances, Inc. Of Zhuhai Refrigeration System and Refrigerated Storage

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US8904812B2 (en) 2010-02-10 2014-12-09 Mitsubishi Electric Corporation Refrigeration cycle apparatus
JP5492845B2 (ja) * 2011-09-07 2014-05-14 日立アプライアンス株式会社 冷蔵庫
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US9964339B2 (en) 2016-01-19 2018-05-08 Heatcraft Refrigeration Products Llc Cooling system with low temperature load
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EP2142868A1 (en) * 2007-03-30 2010-01-13 Lg Electronics Inc. Controlling process for refrigerator
US20100152902A1 (en) * 2007-03-30 2010-06-17 Ji Won Sung Method for controlling of refrigerator
US8418488B2 (en) * 2007-03-30 2013-04-16 Lg Electronics Inc. Method for controlling of refrigerator
EP2142868A4 (en) * 2007-03-30 2014-01-08 Lg Electronics Inc CONTROL METHOD FOR REFRIGERATOR
EP2167885A1 (en) * 2007-06-29 2010-03-31 Sinvent AS A closed circuit vapour compression refrigeratiion system and a method for operating the system
EP2167885A4 (en) * 2007-06-29 2014-09-24 Sinvent As STEAM COMPRESSION COOLING SYSTEM WITH CLOSED CIRCUIT AND METHOD FOR OPERATING THE SYSTEM
US20120085114A1 (en) * 2010-10-07 2012-04-12 Audi Ag Refrigerant circuit of an hvac system of a motor vehicle
US9242527B2 (en) * 2010-10-07 2016-01-26 Hanon Systems Refrigerant circuit of an HVAC system of a motor vehicle
US20120322354A1 (en) * 2011-06-16 2012-12-20 Andres Michael J Heat pump for supplemental heat
US10266034B2 (en) * 2011-06-16 2019-04-23 Hamilton Sundstrand Corporation Heat pump for supplemental heat
US9217594B2 (en) 2011-10-05 2015-12-22 Toyota Jidosha Kabushiki Kaisha Method of controlling cooling device
US20150121927A1 (en) * 2013-11-04 2015-05-07 Lg Electronics Inc. Refrigerator
US9733009B2 (en) * 2013-11-04 2017-08-15 Lg Electronics Inc. Refrigerator
US9777956B2 (en) * 2013-11-04 2017-10-03 Lg Electronics Inc. Refrigerator
US20150121926A1 (en) * 2013-11-04 2015-05-07 Lg Electronics Inc. Refrigerator
EP3288796A4 (en) * 2015-05-01 2018-10-24 Thermo King Corporation Integrated thermal energy module within an air-cooled evaporator design
US10436495B2 (en) 2015-05-01 2019-10-08 Thermo King Corporation Integrated thermal energy module within an air-cooled evaporator design
US20180156498A1 (en) * 2015-06-17 2018-06-07 Mitsibishi Electric Corporation Refrigerant circuit and air conditioning device
US11320175B2 (en) * 2015-06-17 2022-05-03 Mitsubishi Electric Corporation Refrigerant circuit
US20220275976A1 (en) * 2019-09-23 2022-09-01 Gree Electric Appliances, Inc. Of Zhuhai Refrigeration System and Refrigerated Storage

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JP2006275496A (ja) 2006-10-12
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