EP2420760A1 - Freezer-refrigerator and cooling storage unit - Google Patents

Freezer-refrigerator and cooling storage unit Download PDF

Info

Publication number
EP2420760A1
EP2420760A1 EP09843369A EP09843369A EP2420760A1 EP 2420760 A1 EP2420760 A1 EP 2420760A1 EP 09843369 A EP09843369 A EP 09843369A EP 09843369 A EP09843369 A EP 09843369A EP 2420760 A1 EP2420760 A1 EP 2420760A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
disposed
evaporator
freeze cycle
heat exchanger
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.)
Withdrawn
Application number
EP09843369A
Other languages
German (de)
English (en)
French (fr)
Inventor
Hengliang Zhang
Masahiro Nishiyama
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.)
Sharp Corp
Original Assignee
Sharp Corp
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
Priority claimed from JP2009100721A external-priority patent/JP2010249444A/ja
Priority claimed from JP2009276795A external-priority patent/JP5270523B2/ja
Application filed by Sharp Corp filed Critical Sharp Corp
Publication of EP2420760A1 publication Critical patent/EP2420760A1/en
Withdrawn legal-status Critical Current

Links

Images

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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
    • F25D19/04—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors with more than one refrigeration unit

Definitions

  • the present invention relates to a freezer-refrigerator that includes first and second evaporators that cool a refrigeration compartment and a freeze compartment, respectively. Besides, the present invention relates to a cooling storage unit that includes first and second compartments that have different temperatures from each other.
  • a refrigerant flows to operate a freeze cycle; in a low-temperature portion of the freeze cycle, first and second evaporators are disposed in parallel with each other.
  • the first evaporator is disposed behind the freeze compartment. Thanks to driving of an air blower, cold air generated by heat exchange with the first evaporator circulates in the freeze compartment and the refrigeration compartment, whereby the inside of the freeze compartment and the inside of the refrigeration compartment are cooled.
  • the second evaporator is disposed in the freeze compartment to directly freeze a stored thing in the freeze compartment.
  • FIG. 25 shows a freeze cycle of a freezer-refrigerator disclosed in the patent document 2.
  • a freeze cycle 40 has a compressor 41; thanks to the compressor 41, a refrigerant flows in an arrow direction, whereby the freeze cycle 40 is operated.
  • a heat radiator 42 is connected; branched at a three-way valve 46, first and second evaporators 44a, 44b are disposed in parallel with each other via first and second pressure reducers 43a, 43b. According to this, the heat radiator 42 is disposed in a high-temperature portion of the freeze cycle 40, while the first and second evaporators 44a, 44b are disposed in a low-temperature portion.
  • the first and second evaporators 44a, 44b are disposed behind the refrigeration compartment and the freeze compartment, respectively. Near the first and second evaporators 44a, 44b, air blowers (not shown) are disposed, respectively. Thanks to driving of each air blower, cold air generated by heat exchange with the first and second evaporators 44a, 44b circulates in the refrigerator compartment and the freeze compartment, whereby the refrigeration compartment and the freeze compartment are cooled.
  • patent documents 3, 4 disclose a dual freeze cycle that includes first and second freeze cycles which are operated by first and second compressors. In the first and second freeze cycles, a refrigerant including carbon dioxide flows, respectively. An intermediate heat exchanger, which performs heat exchange between a low-temperature portion of the first freeze cycle and a high-temperature portion of the second freeze cycle, is disposed; and in the high-temperature portion of the second freeze cycle, an evaporator is disposed.
  • the intermediate heat exchanger in the low-temperature portion of the first freeze cycle is kept at a low temperature.
  • the refrigerant in the second freeze cycle radiates heat in the intermediate heat exchanger to be condensed.
  • An evaporator in a low-temperature portion of the second freeze cycle is kept at a temperature lower than the intermediate heat exchanger. According to this, it is possible to supply extremely cold air into a storing compartment.
  • a receiver is disposed in a subsequent stage of the intermediate heat exchanger.
  • the receiver separates the refrigerant, which flows from the intermediate heat exchanger, into a gas and a liquid; and outputs the liquid refrigerant. According to this, it is possible to secure a circulation amount of the refrigerant by decreasing bubbles contained in the refrigerant that flows in the evaporator; and prevent deterioration of the cooling capability.
  • a patent document 5 discloses a conventional freezer-refrigerator.
  • a freeze compartment is disposed in an upper portion of a main body portion and a refrigeration compartment is disposed in a lower portion of the main body portion.
  • a mechanical compartment is disposed; in the mechanical compartment, first and second compressors are disposed.
  • the first compressor operates a first freeze cycle and the refrigeration compartment is cooled by an evaporator disposed in a low-temperature portion of the first freeze cycle.
  • the second compressor operates a second freeze cycle and the freeze compartment is cooled by an evaporator disposed in a low-temperature portion of the second freeze cycle.
  • the refrigeration compartment and the freeze compartment are independently cooled, whereby it is possible to achieve energy saving.
  • defrosting heaters are disposed below the first and second evaporators. By stopping the compressor and driving the defrosting heaters, the first and second evaporators are defrosted.
  • a patent document 6 discloses a freezer-refrigerator that defrosts an evaporator by means of a freeze cycle.
  • an evaporator is disposed in a low-temperature portion of the freeze cycle and a heat radiator is disposed in a high-temperature portion of the freeze cycle.
  • the heat radiator is disposed on a metal rear plate or the like of the freezer-refrigerator; and thanks to operation of the freeze cycle, radiates heat into the outside air via the rear plate.
  • the evaporator is cooled thanks to the operation of the freeze cycle; and a storing compartment is cooled by cold air that performs heat exchange with the evaporator.
  • a refrigerant in the freeze cycle is made to flow in an opposite direction by a switching means.
  • the evaporator is disposed in the high-temperature portion of the freeze cycle and raised in temperature, whereby the defrosting is performed.
  • a freezer-refrigerator disclosed in a patent document 7 has first and second evaporators that are connected in parallel with a compressor which operates a freeze cycle.
  • the first and second evaporators are disposed in a low-temperature portion of the freeze cycle and the flowing of a refrigerant is switched by a switching means.
  • a cooling plate is mounted on a refrigerant pipe in which the refrigerant flows.
  • the cooling plate covers a wide area of a rear surface of the refrigeration compartment and is exposed.
  • the second evaporator is disposed in a duct that is disposed behind the freeze compartment; and many fms are mounted on a refrigerant pipe in which the refrigerant flows.
  • An air blower is disposed in the duct.
  • the first evaporator is lowered in temperature and the inside of the refrigeration compartment is cooled by cold heat that is radiated from the cooling plate. If the flow path of the refrigerant is switched to the second evaporator, the second evaporator is lowered in temperature.
  • the air which flows in the duct thanks to driving of the air blower, and the second evaporator perform heat exchange with each other, whereby cold air is generated; and the cold air is output into the freeze compartment, whereby the freeze compartment is cooled.
  • the refrigeration compartment refrigerates and preserves the stored things at, for example, 0°C to 5°C and is kept at a compartment temperature higher than the freeze compartment that freezes and preserves the stored things at, for example, -20°C.
  • the first and second evaporators are disposed in parallel with each other, accordingly, kept at about the same temperature. Because of this, the first evaporator, which performs the cooling of the refrigeration compartment, is kept at a temperature lower than the temperature of the freeze compartment.
  • the evaporator disposed in the low-temperature portion of the freeze cycle is able to sufficiently cool the refrigeration compartment at a temperature a few degrees lower than the temperature of the refrigeration compartment.
  • thermodynamics it is known from a principle of thermodynamics that the lower the temperature of the low-temperature portion is, the lower the cooling effect of the freeze cycle becomes. Because of this, if the refrigeration compartment is cooled by means of the first evaporator that has a temperature extremely lower than the compartment temperature of the refrigeration compartment, the COP (Coefficient Of Performance) of the freeze cycle becomes low. Accordingly, there is a problem that power consumption of the freezer-refrigerator becomes large.
  • the evaporator for generating the cold air is disposed in the second freeze cycle. Because of this, even if the dual freeze cycle is disposed in a freezer-refrigerator, the refrigeration compartment and the freeze compartment are cooled by the same evaporator. According to this, like the above description, the temperature of the evaporator becomes an extremely low temperature compared with the compartment temperature of the refrigeration compartment, and there is a problem that the power consumption of the freezer-refrigerator becomes large.
  • the first and second compressors are disposed in the mechanical compartment that is disposed in the lower portion of the main body portion.
  • the first and second compressors are point sound sources as well, so that sounds released from them are superposed.
  • sounds, which have frequencies close to each other and the same phase are likely to be released from the respective compressors. If the sounds having the same phase are superposed, the sound-pressure level becomes double.
  • a hum sound becomes likely to occur. Accordingly, there is a problem that the noise of the freezer-refrigerator becomes large.
  • the first and second evaporators are raised in temperature by the defrosting heater to perform the defrosting, so that there is a problem that the power consumption of the freezer-refrigerator becomes large.
  • a defrosting heater is not disposed, so that the power consumption is reduced.
  • the heat radiator disposed in the high-temperature portion of the freeze cycle is disposed in the low-temperature portion during a time of defrosting, so that there is a problem that condensation occurs on the heat radiator and the rear plate.
  • the refrigerant selectively flows in the first and second evaporators, so that it is impossible to cool the refrigeration compartment and the freeze compartment at the same time. Because of this, there is a problem that during a high load time immediately after the stored things are housed, it is impossible to obtain a sufficient cooling capability in the refrigeration compartment and the freeze compartment at the same time. Especially, the refrigeration compartment undergoes the radiation cooling, so that it takes a long time to lower the temperature; and the freeze compartment is not cooled enough during the high load time of the refrigeration compartment.
  • a freezer-refrigerator includes:
  • the first and second freeze cycles are operated by the first and second compressors; the first and second refrigerants flow, so that the low-temperature portion and high-temperature portion of the first and second freeze cycles are formed.
  • the first refrigerant which has a high temperature and high pressure, flows in the first heat radiator of the high-temperature portion of the first freeze cycle to radiate heat, so that the first refrigerant is condensed.
  • the first refrigerant which has a low temperature and low pressure, flows in the first evaporator of the low-temperature portion of the first freeze cycle and the intermediate heat exchanger, so that the refrigeration compartment is cooled by cold air which is lowered in temperature by the first evaporator.
  • the second refrigerant which has a high temperature and high pressure, flows in the high-temperature portion of the second freeze cycle; and has heat sucked by the intermediate heat exchanger to radiate heat.
  • the second refrigerant which has a low temperature and low pressure, flows in the second evaporator of the low-temperature portion of the second freeze cycle, so that the freeze compartment is cooled by cold air which is lowered in temperature by the second evaporator.
  • the first evaporator and the intermediate heat exchanger may be disposed in series with each other or disposed in parallel with each other.
  • the intermediate heat exchanger is disposed in a subsequent stage of the first evaporator.
  • the first refrigerant after absorbing heat in the first evaporator, flows in the intermediate heat exchanger to perform heat exchange with the high-temperature portion of the second freeze cycle.
  • the freezer-refrigerator having the above structure according to the present invention includes a second heat radiator disposed in the high-temperature portion of the second freeze cycle.
  • the second refrigerant which has the high temperature and high pressure, flows in the second heat radiator of the high-temperature portion of the second freeze cycle and the intermediate heat exchanger, so that the second refrigerant radiates heat via the second heat radiator and the intermediate heat exchanger to be condensed.
  • the intermediate heat exchanger is disposed in a subsequent stage of the second heat radiator.
  • the second refrigerant after radiating heat via the second heat radiator, flows in the intermediate heat exchanger to perform heat exchange with the low-temperature portion of the first freeze cycle.
  • heat exchange is performed between the second refrigerant flowing from the second evaporator and the first refrigerant after flowing in the first evaporator.
  • the low-temperature second refrigerant flowing from the second evaporator absorbs heat from the first refrigerant before flowing in the first evaporator; the enthalpy of the first refrigerant decreases; and the first refrigerant as a refrigerant having a higher cooling capability flows in the first evaporator.
  • heat exchange is performed between the second refrigerant flowing from the second evaporator and the second refrigerant before flowing into the second evaporator.
  • the low-temperature second refrigerant flowing from the second evaporator absorbs heat from the second refrigerant before flowing in the second evaporator; the enthalpy of the second refrigerant decreases; and the second refrigerant as a refrigerant having a higher cooling capability flows in the second evaporator.
  • freezer-refrigerator having the above structure according to the present invention includes:
  • the intermediate heat exchange is disposed, so that it is possible to make compression ratios of a high-temperature cycle compressor and a low-temperature cycle compressor smaller than that of the conventional cycle; according to this, the compression efficiency increases, and it is possible to obtain the freezer-refrigerator that is excellent in energy saving characteristic.
  • the third internal heat exchanger performs heat exchange between the first refrigerant flowing from the first heat radiator and the first refrigerant flowing from the intermediate heat exchanger.
  • the second heat radiator disposed in the high-temperature portion of the second freeze cycle is disposed in a previous stage of the intermediate heat exchanger; and the second internal heat exchanger performs heat exchange between the second refrigerant flowing from the intermediate heat exchanger and the second refrigerant flowing from the second evaporator.
  • the first internal heat exchanger performs heat exchange between the first refrigerant flowing from the third internal heat exchanger and the second refrigerant flowing from the second internal heat exchanger.
  • freezer-refrigerator having the above structure according to the present invention includes:
  • freezer-refrigerator having the above structure according to the present invention includes:
  • the freezer-refrigerator having the above structure according to the present invention includes a receiver that is disposed in the flow path for the first refrigerant of intermediate heat exchanger; separates the first refrigerant into a gas and a liquid; and outputs a gas refrigerant.
  • the first and second freeze cycles are operated by the first and second compressors; the first and second refrigerants flow, so that the low-temperature portion and high-temperature portion of the first and second freeze cycles are formed.
  • the first refrigerant which has the low temperature and low pressure, flows in the first evaporator of the low-temperature portion of the first freeze cycle and the intermediate heat exchanger; and the refrigeration compartment is cooled by the cold air that is lowered in temperature by the first evaporator.
  • the second refrigerant which has the high temperature and high pressure, flows in the high-temperature portion of the second freeze cycle; and has heat absorbed by the intermediate heat exchanger to radiate heat.
  • the second refrigerant which has the low temperature and low pressure, flows in the second evaporator of the low-temperature portion of the second freeze cycle; and the freeze compartment is cooled by the cold air that is lowered in temperature by the second evaporator.
  • the first refrigerant which flows in the intermediate heat exchanger, performs, in a mixed state of a gas and a liquid, heat exchange with the second refrigerant; thereafter, the first refrigerant in the gas state, which is separated by the receiver, performs heat exchange with the second refrigerant to absorb heat.
  • the freezer-refrigerator having the above structure according to the present invention, in the intermediate heat exchanger, an upstream side of the first freeze cycle and a downstream side of the second freeze cycle perform heat exchange with each other; and a downstream side of the first freeze cycle and an upstream side of the second freeze cycle perform heat exchange with each other.
  • the first refrigerant which flows in the intermediate heat exchanger and is in the mixed state of a gas and a liquid, performs heat exchange with the second refrigerant that has heat radiated by the intermediate heat exchanger.
  • the first refrigerant which passes through the receiver and is in the gas state, performs heat exchange with the high-temperature second refrigerant.
  • the intermediate heat exchanger includes:
  • the freezer-refrigerator having the above structure according to the present invention includes the first and second heat radiators that are disposed in the high-temperature portions of the first and second freeze cycles, respectively; and the intermediate heat exchanger is disposed in a subsequent stage of the second heat radiator.
  • the first refrigerant radiates heat via the first heat radiator; thereafter, flows in the first evaporator of the low-temperature portion and the intermediate heart exchanger.
  • the second refrigerant radiates heat via the second heat radiator; thereafter, flows in the intermediate heat exchanger to perform heat exchange with the first refrigerant.
  • the second refrigerant flowing from the second evaporator performs heat exchange with the second refrigerant that flows from the intermediate heat exchanger; thereafter, performs heat exchange with the first refrigerant that flows from the first heat radiator.
  • the second refrigerant, which flows from the intermediate heat exchanger has heat absorbed by the second refrigerant, which flows from the second evaporator and has the low temperature; and the enthalpy decreases.
  • the first refrigerant, which flows from the first heat radiator has heat absorbed by the second refrigerant, which flows from the second evaporator and has the low temperature; and the enthalpy decreases.
  • the first and second refrigerants, which each have a high cooling capability flow in the first and second evaporators.
  • the first and second refrigerants include isobutane.
  • a boiling point of the first refrigerant is higher than a boiling point of the second refrigerant.
  • the first refrigerant includes isobutene; and the second refrigerant includes propane or carbon dioxide.
  • the freezer-refrigerator according to the present invention includes:
  • the first and second freeze cycles are operated by the first and second compressors; the first and second refrigerants flow, so that the low-temperature portion and high-temperature portion of the first and second freeze cycles are formed.
  • the refrigeration compartment is cooled by the first evaporator of the low-temperature portion of the first freeze cycle, while the freeze compartment is cooled by the second evaporator of the low-temperature portion of the second freeze cycle.
  • the first and second compressors are disposed in the first and second mechanical compartments, which are disposed in the main body portion, respectively.
  • the first mechanical compartment is disposed in the upper portion of the main body portion
  • the second mechanical compartment is disposed in the lower portion of the main body portion. According to this, the first and second compressors are disposed away from each other.
  • the freezer-refrigerator having the above structure according to the present invention includes an intermediate heat exchanger that performs heat exchange between a first heat exchange portion disposed in a subsequent stage of the first evaporator and a second heat exchange portion disposed in a high-temperature portion of the second freeze cycle.
  • the first refrigerant which has the low temperature and low pressure, flows in the first heat exchange portion of the low-temperature portion of the first freeze cycle
  • the second refrigerant which has the high temperature and high pressure
  • heat of the second refrigerant is absorbed by the first refrigerant in the intermediate heat exchanger.
  • the refrigeration compartment and the freeze compartment are vertically disposed in parallel with each other, and the first and second mechanical compartments are disposed near the refrigeration compartment and the freeze compartment, respectively; the first and second evaporators are disposed behind the refrigeration compartment and the freeze compartment, respectively; the intermediate heat exchanger is disposed between the first compressor and the second compressor, formed to vertically extend; the first heat exchange portion and the second heat exchange portion bend in a vertical direction; and refrigerant flow-in openings and refrigerant flow-out openings of the first and second heat exchange portions are disposed near the first mechanical compartment.
  • the refrigeration compartment is disposed at an upper position of the main body portion; the first mechanical compartment, which includes the first compressor, is disposed in the upper portion of the main body portion; the freeze compartment is disposed at a lower position of the main body portion; and the second mechanical compartment, which includes the second compressor, is disposed in the lower portion of the main body portion.
  • the first evaporator is disposed in the upper portion of the main body portion, while the second evaporator is disposed in the lower portion of the main body portion.
  • the intermediate heat exchanger is so disposed as to extend vertically in the main body portion; and is so formed as to bend in a vertical direction.
  • a refrigerant flow-in opening and a refrigerant flow-out opening are formed.
  • the refrigerant flow-in opening is connected to the first evaporator, while the refrigerant flow-out opening is connected to the first compressor.
  • the refrigerant flow-in opening is connected to the second compressor, while the refrigerant flow-out opening is connected to the second evaporator.
  • freezer-refrigerator having the above structure according to the present invention includes:
  • the first refrigerant which has the high temperature and high pressure, flows in the first heat radiator to radiate heat, so that the first refrigerant is condensed.
  • the first refrigerant, which is condensed by the first heat radiator flows in the first pressure reducer, so that the first refrigerant is decompressed and expanded to become a damp vapor that has a low dry degree and a low temperature.
  • the second refrigerant, which is condensed by the intermediate heat exchanger flows in the second pressure reducer, so that the second refrigerant is decompressed and expanded to become a damp vapor that has a low dry degree and a low temperature.
  • the second refrigerant which flows from the second evaporator, performs heat exchange with the first pressure reducer in the first internal heat exchanger to absorb heat. According to this, the enthalpy of the first refrigerant decreases; and the first refrigerant having a higher cooling capability flows in the first evaporator.
  • the second refrigerant which flows from the second evaporator, performs heat exchange with the second pressure reducer in the second internal heat exchanger to absorb heat. According to this, the enthalpy of the second refrigerant decreases; and the second refrigerant having a higher cooling capability flows in the second evaporator.
  • the second internal heat exchanger is so disposed as to extend vertically; and the refrigerant flow-in side of the second pressure reducer is disposed in the upper portion of the main body portion.
  • the refrigerant flow-out side of the second pressure reducer is connected to the second evaporator that is disposed in the lower portion.
  • the first internal heat exchanger is so disposed as to continuously extend vertically from an upper end of the second internal heat exchanger.
  • the refrigerant flow-in side of the first pressure reducer is disposed in the lower portion of the main body portion, while the refrigerant flow-out side of the first pressure reducer is connected to the first evaporator that is disposed in the upper portion.
  • a first dryer which dehumidifies the first refrigerant before flowing into the first pressure reducer, is disposed in the second mechanical compartment; and a second dryer, which dehumidifies the second refrigerant before flowing into the second pressure reducer, is disposed in the first mechanical compartment.
  • the first refrigerant moisture of which is removed by the first dryer
  • the second refrigerator moisture of which is removed by the second dryer
  • the first pressure reducer flows in the first pressure reducer
  • the first dryer is disposed in the lower portion of the main body portion and connected to the refrigerant flow-in side of the first pressure reducer
  • the second dryer is disposed in the upper portion of the main body portion and connected to the refrigerant flow-in side of the second pressure reducer.
  • the second dryer is covered by a heat insulation member.
  • the intermediate heat exchanger includes a dual pipe in which an inside pipe is covered by an outside pipe; the first refrigerant flows in the inside pipe to form the first heat exchange portion; and the second refrigerant flows in the outside pipe in a direction opposite to the first refrigerant to form the second heat exchange portion.
  • the first refrigerant flowing in the inside pipe and the second refrigerant flowing in the outside pipe perform heat exchange via the inside pipe.
  • the second heat radiator is disposed between the second compressor and the intermediate heat exchanger.
  • the second refrigerant which has the high temperature and high pressure, flows in the second heat radiator to radiate heat, so that the second refrigerant is lowered in temperature.
  • the second refrigerant, which is lowered in temperature by the second heat radiator, is further cooled by the intermediate heat exchanger to condense.
  • the first and second internal heat exchangers are embedded in a rear wall of the heat insulation box body; and the second heat radiator is disposed on a rear surface of the main body portion.
  • the intermediate heat exchanger is embedded in the rear wall of the heat insulation box body.
  • an accumulator for separating a gas and a liquid from each other is disposed on a refrigerant flow-out side of the second evaporator and is not disposed on a refrigerant flow-out side of the first evaporator.
  • the second refrigerant flowing from the second evaporator is separated into a gas and a liquid; and the gas refrigerant is sent to the second compressor.
  • the first refrigerant which flows from the first evaporator and in which a gas and a liquid are mixed with each other, flows in the intermediate heat exchanger; and thanks to heat exchange with the high-temperature portion of the second freeze cycle, the first refrigerant becomes a gas refrigerant and is sent to the first compressor.
  • a heat insulation wall for partitioning the refrigeration compartment and the freeze compartment has a heat insulation performance in a level that is equal to that of a circumferential wall of the heat insulation box body.
  • part of heat radiation from the first heat radiator is used for a drained water process and prevention of condensation in the freezer-refrigerator.
  • the present invention includes:
  • the first and second freeze cycles are operated by the first and second compressors; the first and second refrigerants flow, so that the low-temperature portion and high-temperature portion of the first and second freeze cycles are formed.
  • the first refrigerant which has a low temperature and low pressure, flows in the first heat radiator of the high-temperature portion of the first freeze cycle, so that the first refrigerant is cooled by the cold air that is lowered in temperature by the first evaporator.
  • the second refrigerant which has a low temperature and low pressure, flows in the second evaporator of the low-temperature portion of the second freeze cycle, so that the freeze compartment is cooled by the cold air that is lowered in temperature by the second evaporator.
  • the operation of the second freeze cycle is stopped, while the first freeze cycle is operated.
  • the high-temperature portion of the first freeze compartment and the second evaporator perform heat exchange, so that the second evaporator is raised in temperature and the defrosting is performed.
  • freezer-refrigerator having the above structure according to the present invention includes:
  • a flow path of the first refrigerant is switched to the first heat radiator by the three-way valve.
  • the first and second evaporators are cooled and heat is radiated from the first heat radiator.
  • the flow of the first refrigerant which is from the refrigerant flow-out side of the first heat radiator to the defrosting heat exchanger, is stopped by the check valve.
  • the flow path of the first refrigerant is switched to the defrosting heat exchanger by the threes-way valve.
  • the first evaporator is cooled and heat is radiated from the defrosting heat exchanger.
  • the second evaporator performs heat exchange with the defrosting heat exchanger, so that the second evaporator is raised in temperature and the defrosting is performed.
  • the check valve is disposed near a joining point of a refrigerant flow-out side of the first heat radiator and a refrigerant flow-out side of the defrosting heat exchanger. According to this, the check valve and the defrosting heat exchanger are disposed away from each other. Because of this, when the flow path of the first refrigerant is switched to the first heat radiator by the three-way valve, the temperature rise of the second evaporator due to the first refrigerant, which flows from the first heat radiator and has the high temperature, is reduced.
  • the second evaporator and the defrosting heat exchanger include first and second refrigerant pipes in which the first and second refrigerants flow, respectively; and the first and second refrigerant pipes are connected to each other by a plurality of fins. According to this structure, heat of the first refrigerant having the high temperature is conducted to the second evaporator via the fins that connect the first and second refrigerant pipes to each other.
  • the second evaporator and the defrosting heat exchanger include first and second refrigerant pipes in which the first and second refrigerants flow, respectively; and the first and second refrigerant pipes are disposed side by side. According to this structure, heat of the first refrigerant having the high temperature is conducted to the second evaporator via a border wall between the first and second refrigerant pipes.
  • the sectional area of a refrigerant pipe of the defrosting heat exchanger is half of the sectional area of a refrigerant pipe of the first evaporator. According to this structure, the internal volume of the refrigerant pipe of the defrosting heat exchanger is made small and a large amount of the refrigerant is prevented from collecting in the defrosting heat exchanger after the defrosting.
  • the first compressor before defrosting the second evaporator, the first compressor is stopped for a predetermined period.
  • the first compressor is stopped and the three-way valve is switched to the defrosting heat exchanger, the compartment temperature of the refrigeration compartment rises; and if the predetermined period elapses, the first compressor is driven.
  • the first refrigerant flows in the defrosting heat exchanger, so that the second evaporator is defrosted and the refrigeration compartment is cooled.
  • the three-way valve may be switched to the defrosting heat exchanger.
  • the present invention includes:
  • the first and second freeze cycles are operated by the first and second compressors; the first and second refrigerants flow, so that the low-temperature portion and high-temperature portion of the first and second freeze cycles are formed.
  • the first refrigerant which has a low temperature and low pressure, flows in the refrigerant pipe of the first evaporator of the first freeze cycle, so that cold heat is radiated from the cooling plate and the refrigeration compartment is cooled.
  • the second refrigerant which has a low temperature and low pressure, flows in the second evaporator of the low-temperature portion of the second freeze cycle, so that the freeze compartment is cooled by the cold air which is lowered in temperature by the second evaporator
  • freezer-refrigerator having the above structure according to the present invention includes:
  • the temperature and the humidity of the refrigeration compartment are detected by the temperature sensor and the humidity sensor.
  • the dew point temperature of the refrigeration compartment is obtained from calculation and the like based on the detection results from the temperature sensor and the humidity sensor; and the first evaporator is kept at the dew point temperature or below. According to this, moisture of the outside air, which flows in thanks to the opening and closing of the door, condenses on a surface of the cooling plate.
  • an intermediate heat exchanger which performs heat exchange between the low-temperature portion of the first freeze cycle and a high-temperature portion of the second freeze cycle, is disposed.
  • the first refrigerant which has the low temperature and low pressure, flows in the first evaporator of the low-temperature portion of the first freeze cycle and the intermediate heat exchanger.
  • the second refrigerant which has the high temperature and high pressure, flows in the high-temperature portion of the second freeze cycle; and has heat absorbed by the intermediate heat exchanger to radiate heat.
  • the first evaporator and the intermediate heat exchanger may be disposed in series with each other or disposed in parallel with each other.
  • an insulation compartment having a temperature lower than a temperature of an upper portion is disposed; and in the refrigerant pipe of the first evaporator, a refrigerant flows from lower to upper.
  • the insulation compartments such as a chilled compartment, an ice compartment and the like which have a low temperature.
  • the cooling plate in the lower portion of the first evaporator touches the refrigerant pipe, which has the low temperature, to cool the insulation compartments.
  • a cooling storage unit includes:
  • the cooling storage unit having the above structure according to the present invention includes:
  • the cooling storage unit having the above structure according to the present invention includes a receiver that is disposed in a first freeze cycle of the intermediate heat exchanger, separates the first refrigerant into a gas and a liquid, and outputs the liquid refrigerant.
  • the cooling storage unit having the above structure according to the present invention includes:
  • the cooling storage unit having the above structure according to the present invention includes:
  • the refrigeration compartment is cooled by the first evaporator that is disposed in the first freeze cycle, while the freeze compartment is cooled by the second evaporator that is disposed in the second freeze cycle. Because of this, it is possible make a temperature difference between the first evaporator and the refrigeration compartment small; and it is possible to drive the first and second compressors with a high efficiency. Accordingly, the COP of the freeze cycle increases; and it is possible to reduce power consumption of the freezer-refrigerator.
  • the receiver is disposed in the first freeze cycle of the intermediate heat exchanger, so that even if a heat load on the freezer-refrigerator increases, the first refrigerant as the gas refrigerant performs the heat exchange with the second refrigerant. According to this, the first refrigerant surely rises in temperature and is sent to the first compressor, so that it is possible to keep the capability of the intermediate heat exchanger.
  • the first refrigerant as the gas refrigerant which flows from the receiver, absorbs heat to rise in temperature, thereafter, flows in the first compressor, so that it is possible to reduce a cold heat loss.
  • one of the first and second mechanical compartments, in which the first and second compressors are disposed is disposed in the upper portion of the main body portion, while the other is disposed in the lower portion, so that the first and second compressors, which are also point sound sources, are disposed away from each other.
  • the sound-pressure level of the point sound source decreases as the distance increases; and when a user comes close to one point sound source, the user is away from the other point sound source, so that the noise level the user hears becomes small.
  • the first and second compressors are disposed in the compartments different from each other, so that the same-phase sound and the same-frequency sound become unlikely to occur. According to this, the sound pressure due to the sounds, overlapping with each other, from the first and second compressors becomes low; and it is possible to reduce occurrence of a hum. Accordingly, it is possible to lower the noise of the freezer-refrigerator.
  • the second evaporator of the second freeze cycle is defrosted by the heat of the high-temperature portion of the first freeze cycle, so that first heat radiator of the first freeze cycle and the second heat radiator of the second freeze cycle do not reach a low temperature. Accordingly, it is possible to prevent condensation on the rear plate and the like of the freezer-refrigerator. Besides, it is unnecessary to additionally dispose a heater that defrosts the second evaporator, so that it is possible to curb temperature rise caused by a heater and the like during the defrosting time. Besides, most of the heat, which heats the second evaporator during the defrosting time, is heat from the refrigeration compartment, so that it is possible to cool the refrigeration compartment performing the defrosting. Accordingly, it is possible to curb the power consumption caused by the defrosting; and keep the power consumption of the freezer-refrigerator low.
  • the first and second freeze cycles are operated by the first and second compressors, respectively; the refrigeration compartment and the freeze compartment are cooled by the first and second evaporators; and the first evaporator has the cooling plate, so that it is possible to prevent the drying of the stored things; and during a high-load time and the like immediately after the stored things are housed, it is possible to obtain a sufficient cooling capability of the refrigeration compartment and the freeze compartment.
  • the high-load time of the refrigeration compartment it is possible to lower the second evaporator in temperature, so that it is possible to prevent insufficient cooling of the freeze compartment.
  • FIG. 1 is a side sectional view showing a freezer-refrigerator according to a first embodiment.
  • a freezer-refrigerator 1 is provided with a refrigeration compartment 2 in an upper portion for refrigerating and preserving stored things.
  • a vegetable compartment 3 which is kept at a temperature that is higher than a temperature of the refrigeration compartment 2 and suitable for preserving vegetables, is disposed.
  • a freeze compartment 4 for freezing and preserving stored things is disposed in a lower portion of the freezer-refrigerator 1.
  • a front surface of the refrigeration compartment 2 is opened and closed by a rotatable heat insulation door 2a.
  • Front surfaces of the vegetable compartment 3 and the freeze compartment 4 are opened and closed by drawer type of heat insulation doors 3a and 4a that are unitary with housing cases 3b and 4b, respectively.
  • a mechanical compartment 5 is disposed In the mechanical compartment 5, first and second compressors 11 and 21, which operate first and second freeze cycles 10 and 20 (see Fig. 2 ) described in detail later, respectively, are disposed.
  • first and second compressors 11 and 21 which operate first and second freeze cycles 10 and 20 (see Fig. 2 ) described in detail later, respectively, are disposed.
  • a first evaporator 14 connected to the first compressor 11 is disposed; and over the first evaporator 14, a refrigeration compartment air blower 15 is disposed.
  • a second evaporator 24 connected to the second compressor 21 is disposed; and over the second evaporator 24, a freeze compartment air blower 25 is disposed.
  • a defrosting heater 51 is disposed below the first evaporator 14, a defrosting heater 51 is disposed.
  • Cold air cooled by heat exchange with the first evaporator 14 is output into the refrigeration compartment 2 by the refrigeration compartment air blower 15.
  • the cold air flows in the refrigeration compartment 2 and flows in the vegetable compartment 3 that communicates with the refrigeration compartment 2.
  • the cold air flowing in the vegetable compartment 3 flows in the vegetable compartment 3 and returns to the first evaporator 14. According to this, the refrigeration compartment 2 and the vegetable compartment 3 are cooled.
  • Cold air cooled by heat exchange with the second evaporator 24 is output into the freeze compartment 4 by the freeze compartment air blower 25.
  • the cold air output into the freeze compartment 4 flows in the freeze compartment 4 and returns to the second evaporator 24. According to this, the freeze compartment 4 is cooled.
  • FIG. 2 shows a freeze cycle of the freezer-refrigerator 1.
  • a freeze cycle 30 of the freezer-refrigerator 1 is a cascade type of dual freeze cycle in which the first and second freeze cycles 10, 20 are connected to each other by an intermediate heat exchanger 31.
  • the first freeze cycle 10 forms a high temperature cycle while the second freeze cycle 20 forms a low temperature cycle.
  • heat exchange is performed between a low-temperature portion of the first freeze cycle 10 and a high-temperature portion of the second freeze cycle 20 by the intermediate heat exchanger 31. According to this, a low-temperature portion of the second freeze cycle 20 is kept at a temperature lower than the low-temperature portion of the first freeze cycle 10.
  • the first freeze cycle 10 operated by the first compressor 11 has: a first heat radiator 12, a first pressure reducer 13, and a first evaporator 14 that are connected by a refrigerant pipe 10a.
  • a first refrigerant such as isobutane and the like flows in an arrow S1 direction.
  • the first refrigerant flows and circulates via the first compressor 11, the first heat radiator 12, the first pressure reducer 13, the first evaporator 14 and the first compressor 11 in this order.
  • the second freeze cycle 20 operated by the second compressor 21 has: a second heat radiator 22, a second pressure reducer 23, and a second evaporator 24 that are connected by a refrigerant pipe 20a.
  • a second refrigerant such as isobutane and the like flows in an arrow S2 direction.
  • the second refrigerant flows and circulates via the second compressor 21, the second heat radiator 22, the second pressure reducer 23, the second evaporator 24 and the second compressor 21 in this order.
  • a heat exchange portion 31a disposed in the first freeze cycle 10 and a heat exchange portion 31c disposed in the second freeze cycle 20 are disposed side by side; and so formed as to be able to perform heat exchange with each other via a wall surface.
  • the heat exchange portion 31a is disposed in a subsequent stage of the first evaporator 14 while the heat exchange portion 31c is disposed in a subsequent stage of the second heat radiator 22.
  • first and second internal heat exchangers 32, 33 are disposed.
  • a heat exchange portion 32a disposed in the first freeze cycle 10 and a heat exchange portion 32b disposed in the second freeze cycle 20 are disposed side by side; and so formed as to be able to perform heat exchange with each other via a wall surface.
  • the heat exchange portion 32a is disposed in a subsequent stage of the first heat radiator 12; and the first refrigerant having a high temperature before flowing in the first evaporator 14 flows in the heat exchange portion 32a.
  • the heat exchange portion 32b is disposed in a subsequent stage of the second evaporator 24; and the second refrigerant having a low temperature after flowing from the second evaporator 24 flows in the heat exchange portion 32b.
  • the first pressure reducer 13 includes a capillary tube
  • the heat exchange portion 32a may double as the first pressure reducer 13.
  • a heat exchange portion 33a disposed in a subsequent portion of the heat exchanger 31c and a heat exchange portion 33b disposed in a subsequent stage of the second evaporator 24 are disposed side by side; and so formed as to be able to perform heat exchange with each other via a wall surface.
  • the heat exchange portion 33a the second refrigerant having a high temperature before flowing in the second evaporator 24 flows, while in the heat exchange portion 33b, the second refrigerant having a low temperature after flowing from the second evaporator 24 flows.
  • the heat exchange portion 33a may double as the second pressure reducer 23.
  • the first and second refrigerants flow in the refrigerant pipes 10a and 20a, respectively.
  • the first and second compressors 11, 21 compress the first and second refrigerants to a high temperature and a high pressure, while the first and second pressure reducers 13 and 23 decompress and expand the first and second refrigerants to a low temperature and a low pressure.
  • the first and second refrigerants flow from the first and second compressors; and thereafter flow in the first and second pressure reducers 13, 23, the first and second refrigerants serve as high-temperature portions of the first and second freeze cycles 10, 20.
  • the first and second refrigerants flow from the first and second pressure reducers 13, 23; and thereafter flow in the first and second compressors 11, 21, the first and second refrigerants serve as low-temperature portions of the first and second freeze cycles 10, 20.
  • the first refrigerant which is compressed by the first compressor 11 and has the high temperature and high pressure, is deprived of heat by the surrounding air via the first heat radiator 12 to condense.
  • the first refrigerant which is liquefied by the first heat radiator 12, is deprived of heat by the second refrigerant in the low-temperature portion of the second freeze cycle 20 in the first internal heat exchanger 32 to be further lowered in temperature.
  • the first refrigerant which is cooled to a large over-cooling degree by the first internal heat exchanger 32 and in the liquefied state, flows in the first pressure reducer 13.
  • the first refrigerant is decompressed and expanded by the first pressure reducer 13 and becomes a damp vapor that has a low dry degree and a low temperature.
  • the first refrigerant which becomes the low-temperature damp vapor, flows in the first evaporator 14, deprives the cold air in the refrigeration compartment 2 of heat to evaporate; and becomes a damp vapor that has a higher dry degree.
  • the first refrigerant which flows from the first evaporator 14 and is in the damp vapor state, flows in the intermediate heat exchanger 31, deprives the second refrigerant in the high-temperature portion of the second freeze cycle of heat to evaporate; and becomes an over-heated vapor.
  • the first refrigerant which becomes the over-heated vapor, returns to the first compressor 11. According to this, the first refrigerant circulates, whereby the first freeze cycle 10 is operated.
  • the second refrigerant which is compressed by the second compressor 21 and has the high temperature and high pressure, is deprived of heat by the surrounding air via the second heat radiator 22.
  • the second refrigerant which is lowered in temperature by the second heat radiator 22, flows in the intermediate heat exchanger 31 and is deprived of heat by the first refrigerant in the low-temperature portion of the first freeze cycle 10 to be further cooled to condense.
  • the liquefied second refrigerant is deprived of heat by the second refrigerant in the low-temperature portion of the second freeze cycle 20 in the second internal heat exchanger 33 to be further lowered in temperature.
  • the second refrigerant which is cooled to a large over-cooling degree by the second internal heat exchanger 33 and in the liquefied state, flows in the second pressure reducer 23.
  • the second refrigerant is decompressed and expanded by the second pressure reducer 23 and becomes a damp vapor that has a low temperature.
  • the second refrigerant which becomes the low-temperature damp vapor, flows in the second evaporator 24, deprives the cold air in the freeze compartment 4 of heat to evaporate; and becomes a damp vapor.
  • the second refrigerant which flows from the second evaporator 24 and is in the damp vapor state, is guided to the second internal heat exchanger 33 and the first internal heat exchanger 32; deprives the high-temperature second refrigerant and the high-temperature first refrigerant of heat to become an over-heated vapor.
  • the second refrigerant which becomes the over-heated vapor, returns to the second compressor 21. According to this, the second refrigerant circulates, whereby the second freeze cycle 20 is operated.
  • the second compressor 21 is driven after the first compressor 11 is driven and the temperature of the intermediate heat exchanger 31 decreases. And, the temperatures of the refrigeration compartment 2 and the freeze compartment 4 and a temperature difference between the heat exchange portions 31a and 31c of the intermediate heat exchanger 31 are monitored; and the rotation speeds of the first and second compressors 11, 21 are controlled by inverter control such that these speeds become predetermined values.
  • Fig. 3 shows a pressure-enthalpy diagram (P-H diagram) of the freeze cycle 30.
  • a vertical axis indicates pressure while a lateral axis indicates enthalpy.
  • the respective points A, B, C, D, E, E', a, b, b', c, d, e, and f correspond to the respective points of the freeze cycle shown in Fig. 2 .
  • the A-B indicates a process in the first compressor 11.
  • the B-C indicates a process in the first heat radiator 12.
  • the C-D indicates a process in the heat exchange portion 32a of the first internal heat exchanger 32.
  • the D-E indicates a process in the first pressure reducer 13.
  • the E-E' indicates a process in the first evaporator 14.
  • the E'-A indicates a process in the heat exchange portion 31a of the intermediate heat exchanger 31.
  • the a-b indicates a process in the second compressor 21.
  • the b-b' indicates a process in the second heat radiator 22.
  • the b'-c indicates a process in the heat exchange portion 31c of the intermediate heat exchanger 31.
  • the c-d indicates a process in the heat exchange portion 33a of the second internal heat exchanger 33.
  • the d-e indicates a process in the second pressure reducer 23.
  • the e-f indicates a process in the second evaporator 24.
  • the f-a indicates processes in the heat exchange portion 33b of the second internal heat exchanger 33 and the heat exchange portion 32b of the first internal heat exchanger 32.
  • the first and second freeze cycles 10, 20 are filled with the same refrigerant (e.g., isobutane), so that a temperature relationship and a pressure relationship between the first and second freeze cycles 10, 20 are easily understandable in the PH-diagram.
  • a pressure PA at the A point of the first freeze cycle 10 is slightly lower than a pressure Pb at the b point of the second freeze cycle 20. This is because the first freeze cycle 10 deprives the second freeze cycle 20 of heat.
  • the evaporation temperatures of the first and second evaporators 44a, 44b are about a temperature indicated by the e-f in Fig. 3 .
  • the evaporation temperature of the first evaporator 14 which cools the refrigeration compartment 2 according to the present embodiment, is indicated by the E-F in Fig. 3 .
  • the pressure P is, the higher the temperature is, so that the evaporation temperature of the first evaporator 14 becomes higher than the temperature in the case of the single freeze cycle.
  • Fig. 4 shows a relationship between an adiabatic compression efficiency and a compression ratio of a positive displacement compressor according to " Guide and Data Book" (1961, p. 498) from ASHRAE (American Society of Heating, Refrigerating and Air-Conditioning Engineers ).
  • a vertical axis indicates the adiabatic compression efficiency while a lateral axis indicates the compression ratio.
  • most of the compressors used in usual freezer-refrigerators today are positive displacement type. According to experimental data of refrigerants R12 and R22, it is possible to say that other refrigerants have the same tendency. According to this figure, the smaller the compression ratio of the compressor is, the higher the adiabatic compression efficiency of the compressor becomes.
  • the compression ratio of the conventional single freeze cycle 40 (see Fig. 25 ) is about 8.
  • the compression ratios of the first and second freeze cycles 10, 20 each become abut 2 to 3. Accordingly, both of the compression ratios of the first and second freeze cycles 10, 20 are smaller than the conventional, so that it is possible to drive the first and second compressors 11, 21 with a high efficiency.
  • the refrigeration compartment 2 is cooled by the first evaporator 14 disposed in the first freeze cycle 10, while the freeze compartment 4 is cooled by the second evaporator 24 disposed in the second freeze cycle 20. Because of this, it is possible to make the temperature difference between the first evaporator 14 and the refrigeration compartment 2 small; and drive the first and second compressors 11, 21 with a high efficiency. Accordingly, the COP of the freeze cycle 30 increases from the conventional, and it is possible to reduce the power consumption of the freezer-refrigerator 1.
  • the intermediate heat exchanger 31 may be disposed in parallel with the first evaporator 14. However, if the intermediate heat exchanger 31 is disposed in the subsequent stage of the first evaporator 14 in series, the first refrigerant flows in the first evaporator 14 before the second refrigerant is deprived of heat by the intermediate heat exchanger 31. Accordingly, the first evaporator 14 deprives the air in the refrigeration compartment 2 of heat without lowering the temperature of the air in the refrigeration compartment 2 by means of heat exchange that uses latent heat, so that it is possible to increase the cooling efficiency.
  • the second heat radiator 22 is provided which is disposed in the high-temperature portion of the second freeze cycle 20, so that it is possible to further lower the radiation heat of the entire first and second freeze cycles 10, 20. Accordingly, the COP of the freeze cycle 30 increases.
  • the intermediate heat exchanger 31 may be disposed in parallel with the second heat radiator 22. However, the intermediate heat exchanger 31 is disposed in the subsequent stage of the second heat radiator 22, so that the second refrigerant flows in the second heat radiator 22 before the second refrigerant is deprived of heat by the first refrigerant in the intermediate heat exchanger 31. Accordingly, after the second refrigerant performs heat exchange in the second heat radiator 22 to radiate heat, the second refrigerant is cooled by the intermediate heat exchanger 31, so that it is possible to more efficiently perform the heat exchange.
  • the first internal heat exchanger 32 is disposed which performs the heat exchange between: the second refrigerant flowing from the second evaporator 24; and the first refrigerant before flowing in the first evaporator 14, so that it is possible to lower the enthalpy of the first refrigerant; and further increase the cooling capability of the first refrigerant that flows in the first evaporator 14.
  • the second internal heat exchanger 33 is disposed which performs the heat exchange between: the second refrigerant flowing from the second evaporator 24; and the second refrigerant before flowing in the second evaporator 24, so that it is possible to lower the enthalpy of the second refrigerant; and further increase the cooling capability of the second refrigerant that flows in the second evaporator 24.
  • the second refrigerant which flows from the second evaporator 24, is heated to about the ambient temperature during a heat absorption process f-a in Fig. 3 . Because of this, a suction pipe of the second compressor 21 disposed in the mechanical compartment does not deprive the surrounding air of heat, so that it is possible to curb a heat loss. Besides, the temperature of the second refrigerant compressed by the second compressor 21 becomes higher than the ambient temperature, so that it becomes possible to radiate heat from the second heat radiator 22 into the surrounding area during a heat radiation process b-b' in Fig. 3 .
  • the heat radiation level of the entire freeze cycle 30 is high; and an output temperature Tb from the second compressor 21 is lower than an output temperature TB from the first compressor 11. Because of this, it is impossible to sufficiently raise the temperature of the refrigerant, which is sucked into the second compressor 21, by means of the second internal heat exchanger 33 only.
  • the first internal heat exchanger 32 in addition to the second internal heat exchanger 33, it is possible to raise the temperature of the second refrigerant sucked into the second compressor 21 such that the temperature of the second refrigerant after compression becomes over the ambient temperature. According to this, it becomes possible to radiate heat from the second heat radiator 22 into the surrounding area during the heat radiation process b-b' in Fig. 3 .
  • Fig. 5 is a view showing a freeze cycle of the freezer-refrigerator 1 according to a second embodiment.
  • the same portions as those shown in Fig. 1 to Fig. 4 described above are indicated by the same reference numbers.
  • the second heat radiator 22, the first and second internal heat exchangers 32 and 33 are removed from the first embodiment.
  • the other portions are the same as the first embodiment.
  • the second heat radiator 22 and the first and second internal heat exchangers 32, 33 are removed from the first embodiment, so that it is impossible to use the effects of the first and second internal heat exchangers 32, 33; and that the COP of the freeze cycle 30 slightly decreases.
  • the COP of the freeze cycle 30 slightly decreases.
  • the refrigeration compartment 2 is cooled by the first evaporator 14 disposed in the first freeze cycle 10, while the freeze compartment 4 is cooled by the second evaporator 24 disposed in the second freeze cycle 20. Because of this, it is possible to make the temperature difference between the first evaporator 14 and the refrigeration compartment 2 small; and drive the first and second compressors 11, 21 with a high efficiency. Accordingly, the COP of the freeze cycle 30 increases from the conventional, and it is possible to reduce the power consumption of the freezer-refrigerator 1.
  • Fig. 6 shows a freeze cycle of the freezer-refrigerator 1 according to a third embodiment.
  • a first receiver 17 is disposed in the flow path for the first refrigerant of the intermediate heat exchanger 31, while a second receiver 27 is disposed in a downstream with respect to the second evaporator 24.
  • the other portions are the same as the first embodiment.
  • the first and second receivers 17, 27 separate a gas and a liquid from each other, store the liquid refrigerant and output the gas refrigerant.
  • the first receiver 17 prevents the liquid refrigerant from flowing in the first compressor 11, while the second receiver 27 prevents the liquid refrigerant from flowing in the second compressor 21.
  • Fig. 7 is a view showing details of the intermediate heat exchanger 31.
  • the heat exchange portions 31a, 31b disposed in the first freeze cycle 10 and the heat exchange portions 31c, 31d disposed in the second freeze cycle 20 are disposed side by side; and so formed as to be able to perform heat exchange with each other via a wall surface.
  • the heat exchange portion 31a is disposed in the subsequent stage of the first evaporator 14, while the heat exchange portion 31d is disposed in the subsequent stage of the second heat radiator 22.
  • the heat exchangers 31a, 31b are disposed in an upstream and a downstream with respect to the first receiver 17, respectively. According to this, in the heat exchange portion 31a, the first refrigerant, in which a gas and a liquid are mixed with each other, is given vaporization heat (latent heat) to vaporize, while in the heat exchange portion 31b, the first refrigerant in a gas state is given sensible heat to rise in temperature.
  • the heat exchange portion 31a in an upstream of the first freeze cycle 1 is close to the heat exchange portion 31c in a downstream of the second freeze cycle 20 to perform heat exchange.
  • the heat exchange portion 31b in a downstream of the first freeze cycle 1 is close to the heat exchange portion 31d in an upstream of the second freeze cycle 20 to perform heat exchange.
  • the lengths of the heat exchange portions 31c, 31d are set such that the heat exchange portion 31d radiates sensible heat chiefly from the second refrigerant that has a high temperature; and the second refrigerant, which falls in temperature in the heat exchange portion 31d, radiates condensation heat (latent heat) chiefly at the heat exchange portion 31c.
  • the heat exchange portions 31a, 31c each constitute a latent-heat exchange portion that gives the latent heat of the second refrigerant as the latent heat of the first refrigerant
  • the heat exchange portions 31b, 31d each constitute a sensible-heat exchange portion that gives the sensible heat of the second refrigerant as the sensible heat of the first refrigerant.
  • the first refrigerant which flows from the first evaporator 14 and is in a damp vapor state, flows in the heat exchange portion 31a of the intermediate heat exchanger 31.
  • the first refrigerant in the heat exchange portion 31a deprives the second refrigerant in the heat exchange portion 31c of latent heat to vaporize; and flows in the first receiver 17.
  • the first refrigerant which flows in the first receiver 17, is separated into a gas and a liquid; the liquid refrigerant is stored and the gas refrigerant is output.
  • the first refrigerant which is output from the first receiver 17 and in the gas state, deprives the heat exchange portion 31d of sensible heat chiefly by means of the heat exchange portion 31b to rise in temperature; and becomes an over-heated vapor.
  • the second refrigerant which is lowered in temperature by the second heat radiator 22, flows in the heat exchange portion 31d of the intermediate heat exchanger 31.
  • the second refrigerator which flows in the heat exchange portion 31d, is deprived of latent heat chiefly by the first refrigerant in the heat exchange portion 31b to be further cooled.
  • the second refrigerant which is lowered in temperature and in the gas state, flows in the heat exchange portion 31c and is deprived of latent heat chiefly by the first refrigerant in the heat exchange portion 31a to condense.
  • the second refrigerant which condenses, is deprived of heat by the second refrigerants in the low-temperature portion of the second freeze cycle 20 to be further lowered in temperature.
  • Fig. 8 shows a pressure-enthalpy diagram (P-H diagram) of the freeze cycle 30 according to the present embodiment.
  • a vertical axis indicates pressure while a lateral axis indicates enthalpy.
  • the respective points A, B, C, D, E, E', F, a, b, b', b", c, d, e, and f correspond to the respective points of the freeze cycle shown in Fig. 6 ; a point F and a point b" are added to Fig. 3 described above.
  • the E'-F indicates a process in the heat exchange portion 31a of the intermediate heat exchanger 31.
  • the F-A indicates a process in the heat exchange portion 31b of the intermediate heat exchanger 31.
  • the b'-b" indicates a process in the heat exchange portion 31d of the intermediate heat exchanger 31.
  • the b"-c indicates a process in the heat exchange portion 31c of the intermediate heat exchanger 31.
  • Fig. 9 is a view showing a relationship between a position and a temperature of the intermediate heat exchanger 31.
  • Fig. 11 shows a relationship between a position and a temperature of the intermediate heat exchanger 31 of a freeze cycle 30' shown in Fig. 10 .
  • the first receive 17 is disposed in a subsequent stage of the intermediate heat exchanger 31.
  • the other portions are the same as the freeze cycle 30 shown in Fig. 25 described above.
  • vertical axes indicate the temperature and lateral axes indicate the position of the intermediate heat exchanger 31.
  • the respective points A, F, E', b', b", and c correspond to the respective points of the freeze cycles 30, 30' shown in Fig. 25 and Fig. 20 .
  • the second refrigerant undergoes heat radiation in the heat exchange portion 31d (b'-b"); and is condensed by the heat exchange portion 31 c (b" -c).
  • the first refrigerant evaporates in the heat exchange portion 31a (E' -F); and evaporates in the heat exchange portion 31b (F-A) as well.
  • the temperature difference between the first and second refrigerants in the heat exchange portion 31b becomes large, so that a loss due to the heat exchange is large.
  • the first refrigerant which is the gas refrigerant flowing from the first receiver 17, does not absorb heat from the second freeze cycle 20, so that the first refrigerant flows in the first compressor 11 keeping the evaporation temperature unchanged. Accordingly, a cold heat loss is likely to occur.
  • the first refrigerant evaporates in the heat exchange portion 31a (E'-F); and undergoes heat absorption in the heat exchange portion 31b (F-A). Because of this, in the intermediate heat exchanger 31, the latent-heat exchange and the sensible-heat exchange are performed matching with each other. Accordingly, it is possible to curb the temperature difference to the smallest limit; and reduce an effective energy loss caused by the heat exchange. Besides, the first refrigerant absorbs heat to rise in temperature, thereafter, flows in the first compressor 11, so that it is possible to reduce the cold heat loss.
  • the refrigeration compartment 2 is cooled by the first evaporator 14 disposed in the first freeze cycle 10, while the freeze compartment 4 is cooled by the second evaporator 24 disposed in the second freeze cycle 20. Because of this, it is possible to make the temperature difference between the first evaporator 14 and the refrigeration compartment 2 small; and drive the first and second compressors 11, 21 with a high efficiency. Accordingly, the COP of the freeze cycle 30 increases from the conventional, and it is possible to reduce the power consumption of the freezer-refrigerator 1.
  • the first receiver 17 is disposed in the flow path for the first refrigerant of the intermediate heat exchanger 31, so that even if the heat load on the freezer-refrigerator 1 changes, the first refrigerant, which is the gas refrigerant, performs the heat exchange with the second refrigerant. According to this, the first refrigerant surely rises in temperature and is sent to the first compressor 11, so that it is possible to keep the capability of the intermediate heat exchanger 31.
  • the first refrigerant, which is the gas refrigerant flowing from the first receiver 17 absorbs heat to rise in temperature, thereafter, flows in the first compressor 11, so that it is possible to reduce the cold heat loss.
  • the heat exchange portion 31a in the upstream of the first freeze cycle 10 and the heat exchange portion 31c in the downstream of the second freeze cycle 20 perform the heat exchange with each other
  • the heat exchange portion 31b in the downstream of the first freeze cycle 10 and the heat exchange portion 31d in the upstream of the second freeze cycle 20 perform the heat exchange with each other, so that the first refrigerant in the gas state flowing from the first receiver 17 and the second refrigerant having the high temperature perform the heat exchange with each other.
  • the sensible heat due to the heat radiation from the second refrigerant is used as the sensible heat for raising the first refrigerant in temperature; and it is possible to make the temperature difference in the heat exchange between the first and second refrigerants. Accordingly, it is possible to decrease the effective energy loss caused by the heat exchange and further reduce the power consumption of the freezer-refrigerator 1.
  • the first refrigerant deprives the second refrigerant of latent heat chiefly
  • the sensible-heat exchange portion 31b, 31d
  • the first refrigerant deprives the second refrigerant of sensible heat chiefly, so that the latent-heat exchange and the sensible-heat exchange between the first refrigerant and the second refrigerant are performed matching with each other, so that it is possible to make the temperature difference between both smaller.
  • Fig. 12 shows a freeze cycle of the freezer-refrigerator 1 according to a fourth embodiment.
  • the same portions as the third embodiment shown in Fig. 6 described above are indicated by the same reference numbers.
  • a third internal heat exchanger 34 is disposed in the subsequent stage of the first heat radiator 12. The other portions are the same as the third embodiment.
  • the heat exchange portion 34a disposed in the subsequent stage of the first heat radiator 12 and the heat exchange portion 34b disposed in the subsequent stage of the intermediate heat exchanger 31 are disposed side by side; and so formed as to be able to perform heat exchange with each other via a wall surface.
  • the first refrigerant having the hot temperature and flowing from the first heat radiator 12 flows, while in the heat exchange portion 34b, the first refrigerant having the low temperature and flowing from the intermediate heat exchanger 31 flows.
  • the first refrigerant which is liquefied by the first heat radiator 12, flows in the heat exchange portion 34a of the third internal heat exchanger 34. Besides, the first refrigerant, which flows from the heat exchange portion 31b of the intermediate heat exchanger 31, flows in the heat exchange portion 34b of the third internal heat exchanger 34.
  • the first refrigerant (high-temperature refrigerant) in the heat exchange portion 34a is deprived of heat by the first refrigerant (low-temperature refrigerant) that flows in the heat exchange portion 34b.
  • the first refrigerant which flows from the heat exchange portion 34a of the third internal heat exchanger 34, flows in the heat exchange portion 32a of the first internal heat exchanger 32.
  • the first refrigerant which flows from the heat exchange portion 34b of the third internal heat exchanger 34, returns to the first compressor 11.
  • Fig. 13 shows a pressure-enthalpy diagram (P-H diagram) of the freeze cycle 30 according to the present embodiment.
  • a vertical axis indicates pressure while a lateral axis indicates enthalpy.
  • the respective points A, B, C, C', D, E, E', F, F', a, b, b', b", c, d, e, and f correspond to the respective points of the freeze cycle shown in Fig. 12 ; points C', F', and f are added to Fig. 8 described above.
  • the C-C' indicates a process in the heat exchange portion 34a of the third internal heat exchanger 34.
  • the C'-D indicates a process in the heat exchange portion 32a of the first internal heat exchanger 32.
  • the F-F' indicates a process in the heat exchange portion 31b of the intermediate heat exchanger 31.
  • the F'-A indicates a process in the heat exchange portion 34b of the third internal heat exchanger 34.
  • the f-f' indicates a process in the heat exchange portion 33b of the second internal heat exchanger 33.
  • the f'-a indicates a process in the heat exchange portion 32b of the first internal heat exchanger 32.
  • the first refrigerant in the first freeze cycle 10 deprives the second refrigerant in the second freeze cycle 20 of heat in the intermediate heat exchanger 31
  • the temperature of the first refrigerant becomes lower than the ambient temperature by 10°C or more in many cases. Because of this, in a case where the third internal heat exchanger 34 is not present, a suction pipe of the first compressor 11, which is disposed in the mechanical compartment, has a temperature lower than the ambient temperature, so that a heat loss occurs.
  • the third internal heat exchanger 34 is disposed, the first refrigerant flowing from the intermediate heat exchanger 31 is heated to about the ambient temperature by heat collection of the third internal heat exchanger 34 during the heat absorption process F'-A in Fig. 13 . Because of this, it is possible to curb the heat loss caused by the suction pipe of the first compressor 11.
  • Fig. 14 shows an example in which making use of the fact that the first pressure reducer 13 is a capillary tube, the first internal heat exchanger 32 and the third internal heat exchanger 34 are composed.
  • the first pressure reducer 13 functions as a heat exchange pipe of the first internal heat exchanger 32 or the third internal heat exchanger 34.
  • the first pressure reducer 13 constitutes the heat exchange portion 32a of the first internal heat exchanger 32 and the heat exchange portion 34a of the first internal heat exchanger 34; however, may constitute either one of them.
  • the first pressure reducer 13 forms the heat exchange portion 34a of the third internal heat exchanger 34; the pipes are connected to each other by soldering and the like and brought into tight contact with the heat exchange portion 34b.
  • the first pressure reducer 13 forms the heat exchange portion 32a of the third internal heat exchanger 32; the pipes are connected to each other by soldering and the like and brought into tight contact with the heat exchange portion 32b.
  • the first refrigerant which has the high temperature and high pressure and flows in the first pressure reducer 13, is, first in the third internal heat exchanger 34, deprived of heat by the first refrigerant which flows from the intermediate heat exchanger 31 and has the low temperature and low pressure. Thereafter, in the first internal heat exchanger 32, the first refrigerant is deprived of heat by the second refrigerant which flows from the second internal heat exchanger 33 and has the low temperature and low pressure. Accordingly, the first refrigerant is deprived of heat in the third internal heat exchanger 34 and the first internal heat exchanger 32 to expand; and becomes a refrigerant that has a low temperature and a low pressure.
  • the first pressure reducer 13 formed of the capillary tube function as the heat exchange pipe of the first internal heat exchanger 32 or the third internal heat exchanger 34, it is possible to reduce the number of components and lower the production cost of the freezer-refrigerator 1.
  • the second pressure reducer 23 is a capillary tube, it is possible to make the second pressure reducer 23 function as the heat exchange portion 33a of the second internal heat exchanger 33.
  • the second pressure reducer 23 is brought into tight contact with and connected by soldering and the like to the heat exchange portion 33b in the inside of the second internal heat exchanger 33.
  • the second refrigerant which flows in the second pressure reducer 23 and has the high temperature and high pressure, is, in the second internal heat exchanger 33, deprived of heat by the second refrigerant which flows from the second receiver 27 and has the low temperature and low pressure.
  • the second refrigerant is deprived of heat in the second internal heat exchanger 33 to expand; and becomes a refrigerant that has a low temperature and a low pressure. According to this, like the above description, it is possible to reduce the number of components and lower the production cost of the freezer-refrigerator 1.
  • first and second pressure reducers 13, 23 in the above first and third embodiments each may be formed of a capillary tube; and the first and second internal heat exchangers 32, 33 may be structured alike.
  • the refrigeration compartment 2 is cooled by the first evaporator 14 disposed in the first freeze cycle 10, while the freeze compartment 4 is cooled by the second evaporator 24 disposed in the second freeze cycle 20. Because of this, it is possible to make the temperature difference between the first evaporator 14 and the refrigeration compartment 2 small; and drive the first and second compressors 11, 21 with a high efficiency. Accordingly, the COP of the freeze cycle 30 increases from the conventional, and it is possible to reduce the power consumption of the freezer-refrigerator 1.
  • the third internal heat exchanger 34 is disposed which performs the heat exchange between the high-temperature first refrigerant of the first freeze cycle 10 and the low-temperature first refrigerant of the first freeze cycle 10, so that the low-temperature first refrigerant is heated to about the ambient temperature by the cold heat collection of the third internal heat exchanger 34. Because of this, it is possible to curb the heat loss caused by the suction pipe of the first compressor 11.
  • the third internal heat exchanger 34 performs the heat exchange between: the first refrigerant flowing from the first heat radiator 12; and the first refrigerant flowing from the intermediate heat exchanger 31, so that it is possible to easily collect the cold heat of the first refrigerant.
  • the second internal heat exchanger 33 performs the heat exchange between: the second refrigerant flowing from the intermediate heat exchanger 31; and the second refrigerant flowing from the second evaporator 24, so that it is possible to easily collect the cold heat of the second refrigerant.
  • the low-temperature second refrigerant is heated to about the ambient temperature by the cold heat collection of the second internal heat exchanger 33. Because of this, it is possible to curb the heat loss caused by the suction pipe of the second compressor 21.
  • the first internal heat exchanger 32 performs the heat exchange between: the first refrigerant flowing from the third internal heat exchanger 34; and the second refrigerant flowing from the second internal heat exchanger 33, so that it is possible to easily collect the cold heat of the second refrigerant.
  • the first pressure reducer 13 disposed in a previous stage of the first evaporator 14 includes the capillary tube; and the first pressure reducer 13 functions as the heat exchange pipe of the first internal heat exchanger 32 or the third internal heat exchanger 34, so that it is possible to reduce the number of components and lower the cost of the freezer-refrigerator 1.
  • the second pressure reducer 23 disposed in a previous stage of the second evaporator 24 includes the capillary tube; and the second pressure reducer 23 functions as the heat exchange pipe of the second internal heat exchanger 33, so that it is possible to reduce the number of components and lower the cost of the freezer-refrigerator 1.
  • the description is performed using the same refrigerant such as the isobutane and the like for the first and second refrigerants; however, different refrigerants may be used.
  • the boiling point of the first refrigerant is set higher than the boiling point of the second refrigerant.
  • the second refrigerant becomes higher than the first refrigerant in vapor density, so that it is possible to further increase the performance of the second freeze cycle 20, which is more preferred.
  • refrigerant the boiling point -12°C
  • propane the boiling point -40.09°C
  • carbon dioxide the boiling point -78.5°C
  • refrigerants are all natural refrigerants that use substances which are present in large quantities in the natural world. Accordingly, by increasing the cooling efficiency of the freeze cycle that uses the natural refrigerant, it is possible to achieve further reduction of the environmental load on the freezer-refrigerator 1.
  • Fig. 15 is a side sectional view showing a freezer-refrigerator according to a fifth embodiment of the present invention.
  • the main body portion of the freezer-refrigerator 1 has a heat insulation box body 3.
  • the refrigeration compartment 2 for refrigerating and preserving stored things is disposed in an upper portion of the heat insulation box body 3.
  • the front surface of the refrigeration compartment 2 is opened and closed by a rotary type of heat insulation door 2a.
  • the freeze compartment 4 for freezing and preserving stored things is disposed via a heat insulation wall 7.
  • the freeze compartment 4 is partitioned by a partition wall 8 disposed in a front portion; and housing cases 4c, 4d are vertically disposed.
  • the front surface of the freeze compartment 4 is opened and closed by drawer type of heat insulation doors 4a, 4b that are unitary with the housing cases 4c, and 4d, respectively.
  • the heat insulation wall 7 has a heat insulation performance in the same level of circumferential walls (upper wall, bottom wall, side wall and rear wall) of the heat insulation box body 3. According to this, heat exchange between the refrigeration compartment 2 and the freeze compartment 4 is curbed.
  • the first mechanical compartment 5 is disposed in which the first compressor 11 is disposed.
  • a second mechanical compartment 6 is disposed in which the second compressor 21 is disposed.
  • the first and second freeze cycles 10, 20 are operated by the first and second compressors 11, 21, respectively.
  • the first evaporator 14 connected to the first compressor 11 is disposed; over the first evaporator 14, the refrigeration compartment air blower 15 is disposed.
  • the second evaporator 24 connected to the second compressor 21 is disposed; over the second evaporator 24, the refrigeration compartment air blower 25 is disposed.
  • the cold air cooled by the heat exchange with the first evaporator 14 is output into the refrigeration compartment 2 by the refrigeration compartment air blower 15.
  • the cold air flows in the refrigeration compartment 2 and returns to the first evaporator 14. According to this, the refrigeration compartment 2 is cooled.
  • the cold air cooled by the heat exchange with the second evaporator 24 is output into the freeze compartment 4 by the freeze compartment air blower 25.
  • the cold air output into the freeze compartment 4 flows in the freeze compartment 4 and returns to the second evaporator 24. According to this, the freeze compartment 4 is cooled.
  • Fig. 16 is a rear perspective view showing pipe arrangement of the freezer-refrigerator 1.
  • Fig. 17 shows a freeze cycle of the freezer-refrigerator 1.
  • the freeze cycle 30 of the freezer-refrigerator 1 is a cascade type of dual freeze cycle in which the first and second freeze cycles 10, 20 are connected to each other by the intermediate heat exchanger 31.
  • the first freeze cycle 10 is indicated by a solid line
  • the second freeze cycle 20 is indicated by a broken line.
  • the first freeze cycle 10 operated by the first compressor 11 has: the first heat radiator 12, a first dryer 19, the first pressure reducer 13, and the first evaporator 14 that are connected by the refrigerant pipe 10a.
  • the first refrigerant such as isobutane and the like flows in the arrow S1 direction.
  • the first refrigerant flows and circulates via the first compressor 11, the first heat radiator 12, the first dryer 19, the first pressure reducer 13, the first evaporator 14 and the first compressor 11 in this order.
  • the first heat radiator 12 is formed by fixing the refrigerant pipe l0a to a metal plate that covers the rear surface and the side surfaces of the main body portion; and radiates heat into the outside air. Besides, the first heat radiator 12 has a front surface portion 12a and an evaporation portion 12b.
  • the front surface portion 12a is embedded in a front portion of the partition wall 8 and the like (see Fig. 15 ); and prevents, by means of the heat radiation, condensation on an opening circumferential portion of the freeze compartment 4 that touches the heat insulation doors 4a, 4b.
  • the evaporation portion 12b is disposed in the first mechanical compartment 6; and by means of the heat radiation, evaporates drained water collected on an evaporation tray (not shown). According to this, by means of the first heat radiator 12 of the first freeze cycle having a high temperature, it is possible to efficiently perform the prevention of condensation and the evaporation of drained water.
  • the first dryer 19 is disposed in the second mechanical compartment 6; and dehumidifies the first refrigerant that flows in the first pressure reducer 13.
  • the first pressure reducer 13 includes a capillary tube; forms the first internal heat exchanger 32; and performs the heat exchange with the second refrigerant that flows from the second evaporator 24.
  • the second freeze cycle 20 operated by the second compressor 21 has: the second heat radiator 22, a second dryer 29, the second pressure reducer 23, and the second evaporator 24 that are connected by the refrigerant pipe 20a.
  • the second refrigerant such as isobutane and the like flows in the arrow S2 direction.
  • the second refrigerant flows and circulates via the second compressor 21, the second heat radiator 22, the second dryer 29, the second pressure reducer 23, the second evaporator 24 and the second compressor 21 in this order.
  • the second heat radiator 22 is formed by fixing the refrigerant pipe 20a to a metal plate that covers the rear surface of the main body portion; and radiates heat into the outside air.
  • the second dryer 29 is disposed in the first mechanical compartment 5.
  • the second pressure reducer 23 includes a capillary tube; forms the second internal heat exchanger 33; and performs the heat exchange with the second refrigerant that flows from the second evaporator 24.
  • an accumulator 28 for separating a gas and a liquid from each other is disposed.
  • the intermediate heat exchanger 31 includes: the heat exchange portion 31a disposed in the first freeze cycle 10; and the heat exchange portion 31c disposed in the second freeze cycle 20.
  • the heat exchange portion 31a is disposed in the subsequent stage of the first evaporator 14, while the heat exchange portion 31c is disposed in the subsequent stage of the second heat radiator 22.
  • the first and second heat exchange portions 31a, 31c are formed side by side; and so formed as to be able to perform the heat exchange via a border wall.
  • the intermediate heat exchanger 31 includes a dual pipe that has an inside pipe and an outside pipe that are embedded in a rear wall of the heat insulation box body 3 (see Fig. 15 ); and is formed into a U-shape pipe that extends in a vertical direction and bends at a lower end.
  • the first refrigerant flows in the inside pipe to form the heat exchange portion 31a, while the second refrigerant flows in the outside pipe to form the heat exchange portion 31c.
  • a refrigerant flow-in opening 31g and a refrigerant flow-out opening 31h are formed at upper ends.
  • the first and second freeze cycles 10, 20 are provided with the first and second internal heat exchangers 32, 33.
  • the first and second internal heat exchangers 32, 33 are embedded in the rear wall of the heat insulation box body 3 (see Fig. 15 ).
  • the second pressure reducer 23 and the heat exchange portions 33b disposed in the second freeze cycle 20 are disposed side by side; and so formed as to be able to perform heat exchange with each other via a border wall.
  • a capillary tube forming the second pressure reducer 23 and a refrigerant pipe forming the heat exchange portion 33b are welded to each other, whereby the second internal heat exchanger 33 is formed.
  • the heat exchange portion 33b is disposed in the subsequent stage of the second evaporator 24; and the low-temperature second refrigerant flowing from the second evaporator 24 flows in the heat exchange portion 33b.
  • a refrigerant flow-in side of the second pressure reducer 23 is disposed in the main-body upper portion near the first compressor 11. According to this, the second internal heat exchanger 33 is so formed as to extend from the upper portion of the main body portion to the lower portion in which the second evaporator 24 is disposed, so that it is possible to secure a long heat exchange length.
  • the first pressure reducer 13 and the heat exchange portion 32b disposed in the second freeze cycle 20 are disposed side by side; and so formed as to be able to perform heat exchange with each other via a wall surface.
  • a capillary tube forming the second pressure reducer 13 and a refrigerant pipe forming the heat exchange portion 32b are welded to each other, whereby the first internal heat exchanger 32 is formed.
  • the heat exchange portion 32b is disposed in a subsequent stage of the heat exchange portion 33b of the second internal heat exchanger 33; and the low-temperature second refrigerant flowing from the second evaporator 24 flows in the heat exchange portion 32b.
  • a refrigerant flow-in side of the first pressure reducer 13 is disposed in the main-body lower portion near the second compressor 21. According to this, the first internal heat exchanger 32 is so formed as to extend from the lower portion of the main body portion to the upper portion in which the first evaporator 14 is disposed, so that it is possible to secure a long heat exchange length.
  • the first and second refrigerants flow in the refrigerant pipes l0a and 20a.
  • the first and second compressors 11, 21 compress the first and second refrigerants to a high temperature and a high pressure, while the first and second pressure reducers 13 and 23 decompress and expand the first and second refrigerants to a low temperature and a low pressure.
  • the first and second refrigerants flow from the first and second compressors 11, 21; and thereafter flow in the first and second pressure reducers 13, 23, the first and second refrigerants serve as high-temperature portions of the first and second freeze cycles 10, 20.
  • the first and second refrigerants flow from the first and second pressure reducers 13, 23; and thereafter flow in the first and second compressors 11, 21, the first and second refrigerants serve as low-temperature portions of the first and second freeze cycles 10, 20.
  • the first refrigerant which is compressed by the first compressor 11 and has the high temperature and high pressure, is deprived of heat by the surrounding air via the first heat radiator 12 to condense.
  • the first refrigerant which is liquefied by the first heat radiator 12, is dehumidified by the first dryer 19 to be dehydrated.
  • the first refrigerant which flows from the first dryer 19, is decompressed and expanded by the first pressure reducer 13 to become a damp vapor that has a low dry degree and a low temperature.
  • the first refrigerant is, in the first internal heat exchanger 32, deprived of heat by the second refrigerant in the low-temperature portion of the second freeze cycle 20 to be further lowered in temperature.
  • the first refrigerant which becomes the low-temperature damp vapor, flows in the first evaporator 14; deprives the cold air in the refrigeration compartment 2 of heat to evaporate; and becomes a damp vapor that has a higher dry degree.
  • the first refrigerant which flows from the first evaporator 14 and is in the damp vapor state, flows in the intermediate heat exchanger 31, deprives the second refrigerant in the high-temperature portion of the second freeze cycle of heat to evaporate; and becomes an over-heated vapor.
  • the first refrigerant which becomes the over-heated vapor, returns to the first compressor 11. According to this, the first refrigerant circulates, whereby the first freeze cycle 10 is operated.
  • the second refrigerant which is compressed by the second compressor 21 and has the high temperature and high pressure, is deprived of heat by the surrounding air via the second heat radiator 22.
  • the second refrigerant which is lowered in temperature by the second heat radiator 22, flows in the intermediate heat exchanger 31; and is deprived of heat by the first refrigerant in the low-temperature portion of the first freeze cycle 10 to be further cooled to condense.
  • the second refrigerant which is liquefied by the second heat radiator 22 and the intermediate heat exchanger 31, is dehumidified by the second dryer 29 to be dehydrated.
  • the second refrigerant which flows from the second dryer 29, is decompressed and expanded by the second pressure reducer 23 to become a damp vapor that has a low dry degree and a low temperature.
  • the second refrigerant is, in the second internal heat exchanger 32, deprived of heat by the second refrigerant in the low-temperature portion of the second freeze cycle 20 to be further lowered in temperature.
  • the second refrigerant, which becomes the low-temperature damp vapor flows in the second evaporator 24; deprives the cold air in the freeze compartment 4 of heat to evaporate; and becomes a damp vapor.
  • the second refrigerant which flows from the second evaporator 24 and is in the damp vapor state, is guided to the second internal heat exchanger 33 and the first internal heat exchanger 32; deprives the high-temperature second refrigerant and the high-temperature first refrigerant of heat to become an over-heated vapor.
  • the second refrigerant which becomes the over-heated vapor, returns to the second compressor 21. According to this, the second refrigerant circulates, whereby the second freeze cycle 20 is operated.
  • the rotation speeds of the first and second compressors 11, 21 are controlled by an inverter. According to this, the temperature levels of the first evaporator 14 and the second evaporator 24 are so controlled as to correspond to the temperatures of the refrigeration compartment 2 and the freeze compartment 4, respectively.
  • the freeze cycle 30 is so formed as to be the cascade type of dual freeze cycle in which the first and second freeze cycles 10, 20 are connected to each other by the intermediate heat exchanger 31; the refrigeration compartment 2 is cooled by the first evaporator 14, while the freeze compartment 4 is cooled by the second evaporator 24. Because of this, it is possible to make the temperature difference between the first evaporator 14 and the refrigeration compartment 2 small. Besides, the compression ratios of the first and second compressors 11, 21 become small, so that it is possible to drive the first and second compressors 11, 21 with a high efficiency. Accordingly, the COP of the freeze cycle 30 increases, and it is possible to reduce the power consumption of the freezer-refrigerator 1.
  • the refrigeration compartment 2 and the freeze compartment 4 are cooled, corresponding to the temperatures of the refrigeration compartment 2 and the freeze compartment 4, by the first and second evaporators 14, 24 disposed in the first and second freeze cycles 10, 20, so that it is possible to achieve dramatic reduction of the power consumption of the freezer-refrigerator 1 compared with the conventional.
  • the first mechanical compartment 5, in which the first compressor 11 is disposed is disposed in the upper portion of the main body portion; and the second mechanical compartment 6, in which the second compressor 21 is disposed, is disposed in the lower portion of the main body portion, so that the first and second compressors 11,21, which are also point sound sources, are disposed away from each other.
  • the sound pressure level of the point sound source decreases as the distance increases. For example, if the distance becomes double, the sound pressure level decreases about 6 dB. Because of this, when a user comes close to one sound source, the user is away from the other, so that the noise level the user hears becomes small.
  • the first and second compressors 11, 21 are disposed in the compartments different from each other, so that the same-phase sounds and the same-frequency sounds become unlikely to occur. According to this, the sound pressure due to the sounds, overlapping with each other, from the first and second compressors 11, 21 becomes low; and it is possible to reduce occurrence of a hum. Accordingly, it is possible to lower the noise of the freezer-refrigerator 1.
  • first mechanical compartment 5 is disposed in the lower portion of the main body portion and the second mechanical compartment 6 is disposed in the upper portion of the main body portion, likewise, it is possible to lower the noise.
  • the first mechanical compartment 5 and the refrigeration compartment 2 are disposed in the upper portion of the main body portion; the first evaporator 14 is disposed behind the refrigeration compartment 2; the second mechanical compartment 6 and the freeze compartment 4 are disposed in the lower portion of the main body portion; and the second evaporator 24 is disposed behind the freeze compartment 4.
  • the intermediate heat exchanger 31 extends vertically and is bent at a position away from the first compressor 11; and in the upper portion of the main body portion near the first mechanical compartment 5, the refrigerant flow-in openings 31g, 31e, and the refrigerant flow-out openings 31h, 31f are disposed.
  • connection length for the first evaporator 14, the intermediate heat exchanger 31 and the first compressor 11 is shortened. Accordingly, it is possible to shorten the pipe length of the first freeze cycle 10; and further increase the cooling efficiency of the first freeze cycle 10.
  • the first mechanical compartment 5 and the refrigeration compartment 2 may be disposed in the lower portion of the main body portion, while the second mechanical compartment 6 and the freeze compartment 4 may be disposed in the upper portion of the main body portion.
  • the intermediate heat exchanger 31 may be bent at an upper end; and at lower ends, the refrigerant flow-in openings 3 1 g, 31e, and the refrigerant flow-out openings 31h, 31f may be disposed.
  • the refrigeration compartment 2 and the freeze compartment 4 are vertically disposed; and the first and second mechanical compartments 5, 6 are disposed near the refrigeration compartment 2 and the freeze compartment 4, respectively.
  • the intermediate heat exchanger 31 is bent at a position away from the first compressor 11; and the refrigerant flow-in openings 31g, 31e, and the refrigerant flow-out openings 31h, 31f are disposed near the first mechanical compartment 5.
  • the first internal heat exchanger 32 which performs the heat exchange between: the first pressure reducer 13; and the low-temperature second refrigerant flowing from the second evaporator 24, is disposed, it is possible to lower the enthalpy of the first refrigerant that flows in the first evaporator 14. Accordingly, it is possible to further increase the cooling capability of the first refrigerant that flows in the first evaporator 14.
  • the second internal heat exchanger 33 which performs the heat exchange between: the second pressure reducer 23; and the low-temperature second refrigerant flowing from the second evaporator 24, is disposed, it is possible to lower the enthalpy of the second refrigerant that flows in the second evaporator 24. Accordingly, it is possible to further increase the cooling capability of the second refrigerant that flows in the second evaporator 24.
  • the refrigerant flow-in side of the first pressure reducer 13 is disposed in the lower portion of the main body portion; and the first internal heat exchanger 32 extends upward to be connected to the first evaporator 14.
  • the refrigerant flow-in side of the second pressure reducer 23 is disposed in the upper portion of the main body portion; and the first internal heat exchanger 32 extends downward to be connected to the second evaporator 24. According to this, it is possible to lengthen heat exchange lengths of the first and second internal heat exchanger 32, 33; and surely lower the enthalpy of the first and second refrigerants that flow in the first and second evaporators 14, 24.
  • the refrigerant flow-in side of the first pressure reducer 13 is disposed in the upper portion of the main body portion; and the refrigerant flow-in side of the second pressure reducer 23 is disposed in the lower portion of the main body portion.
  • the refrigerant flow-in side of the first pressure reducer 13 is disposed near the second compressor 21; and the refrigerant flow-in side of the second pressure reducer 23 is disposed near the first compressor 11.
  • the refrigerant flow-out opening 31 f of the heat exchange portion 31c of the intermediate heat exchanger 31 is disposed in the upper portion of the main body portion, so that it is possible to shorten the connection between the intermediate heat exchanger 31 and the second pressure reducer 23; and further increase the cooling efficiency of the second freeze cycle 20.
  • the refrigerant flow-out opening 31f of the heat exchange portion 31c is disposed in the lower portion of the main body portion. In other words, it is desirable that the refrigerant flow-out opening 31f of the heat exchange portion 31 c is disposed near the first compressor 11.
  • first mechanical compartment 5 and the freeze compartment 4 may be disposed in the lower portion of the main body portion, while the second mechanical compartment 6 and the refrigeration compartment 2 may be disposed in the upper portion of the main body portion.
  • the first dryer 19 is disposed in the second mechanical compartment 6, while the second dryer 29 is disposed in the first mechanical compartment 5, so that it is possible to shorten the pipe arrangement of the first dryer 19 and the first internal heat exchanger 32; and shorten the pipe arrangement of the second dryer 29 and the intermediate heat exchanger 31.
  • the second dryer 29 is covered by a heat insulation member 50, so that it is possible to prevent temperature rise of the low-temperature second refrigerant of the second freeze cycle 20 caused by heat invasion from the first mechanical compartment 5.
  • the intermediate heat exchanger 31 includes the dual pipe; and the first refrigerant flows in the inside pipe, while the second refrigerant flows in the outside pipe, so that the first refrigerant easily touches the inside pipe. According to this, it is possible to speed the evaporation of the first refrigerant and return the first refrigerant to the first compressor 11.
  • the second refrigerant touches the inside pipe and the outside pipe and condenses thanks to the heat radiation.
  • the flow directions of the first and second refrigerants that flow in the inside pipe and the outside pipe are opposite to each other, so that it is possible to efficiently conduct the sensible heat of the first refrigerant after the evaporation to the second refrigerant that is on the flow-in side. Accordingly, it is possible to increase the cooling efficiency of the freeze cycle 30.
  • the second heat radiator 22 is disposed between the second compressor 21 and the intermediate heat exchanger 31, so that it is possible to further lower the heat radiation temperature of the entire first and second freeze cycles 10, 20.
  • the second refrigerant flows in the second heat radiator 22 before the second refrigerant is deprived of heat by the first refrigerant in the intermediate heat exchanger 31. According to this, after the second refrigerant performs the heat exchange in the second heat radiator 22 to radiate heat, the second refrigerant is cooled by the intermediate heat exchanger 31, so that it is possible to more efficiently perform the heat exchange.
  • the first and second internal heat exchangers 32, 33 are embedded in the rear wall of the heat insulation box body 3; and the second heat radiator 22 is disposed on the rear surface of the main body portion, so that it is possible to concentrate the complicated pipe arrangement on the rear surface. According to this, it is possible to easily dispose a vacuum heat insulation member in the heat insulation box body 3; and increase the heat insulation performance of the heat insulation box body 3.
  • the intermediate heat exchanger 31 is embedded in the rear wall of the heat insulation box body 3, so that the intermediate heat exchanger 31, the second heat radiator 22, the first and second internal heat exchangers 32, 33, which all have a relatively low temperature, are concentratedly disposed on the rear surface. Accordingly, it is possible to reduce the heat loss of the freezer-refrigerator 1.
  • the accumulator 28 is disposed on the refrigerant flow-out side of the second evaporator 24 and an accumulator is not disposed on the refrigerant flow-out side of the first evaporator 14.
  • the intermediate heat exchanger 31 is disposed in the subsequent stage of the first evaporator 14, so that it is possible to surely make the first refrigerant evaporate. Because of this, even if an accumulator is not used, it is possible to prevent invasion of the liquid refrigerant into the first compressor 11. Accordingly, it is possible to reduce the cost.
  • the heat insulation wall 7, which partitions the refrigeration compartment 2 and the freeze compartment 4 has the heat insulation performance in the same level as the circumferential wall (upper wall, bottom wall side walls and rear wall) of the heat insulation box body 3, so that it is possible to surely prevent heat invasion from the refrigeration compartment 2 into the freeze compartment 4. According to this, it is possible to use the low-temperature cold air, which is cooled by the second freeze cycle 20, for only the cooling of the freeze compartment 4. Accordingly, it is possible to further reduce the power consumption of the freezer-refrigerator 1.
  • part of the heat radiation from the first heat radiator 12 is used for the condensation prevention by means of the front surface portion 12a; and used for the drained water process in the freezer-refrigerator 1 by means of the evaporation portion 12b, so that it is possible to efficiently perform the condensation prevention and the drained water process by means of the high-temperature first heat radiator 12 of the first freeze cycle 10.
  • the description is performed using the same refrigerant such as the isobutane and the like for the first and second refrigerants; however, different refrigerants may be used.
  • the boiling point of the first refrigerant is set higher than the boiling point of the second refrigerant.
  • the second refrigerant becomes higher than the first refrigerant in vapor density, so that it is possible to further increase the performance of the second freeze cycle 20, which is more preferred.
  • refrigerant the boiling point -12°C
  • propane the boiling point -40.09°C
  • carbon dioxide the boiling point -78.5°C
  • refrigerants are all natural refrigerants that use substances which are present in large quantities in the natural world. Accordingly, by increasing the cooling efficiency of the freeze cycle that uses the natural refrigerant, it is possible to achieve further reduction of the environmental load on the freezer-refrigerator 1.
  • the first and second freeze cycles 10, 20 are independently operated by the first and second compressors 11, 21, by dispersing and disposing the first and second mechanical compartments 5, 6 in the upper portion and the lower portion of the main body portion, it is possible to reduce the noise.
  • the freezer-refrigerator 1 according to the present embodiment has the same structure as the first embodiment, while the structure of the freeze cycle 30 is different.
  • Fig. 18 shows a freeze cycle of the freezer-refrigerator 1 according to the present embodiment.
  • the freezer-refrigerator 1 has the first freeze cycle 10 operated by the first compressor 11 and the second freeze cycle 20 operated by the second compressor 21.
  • the first freeze cycle 10 has: the first heat radiator 12, the first pressure reducer 13, and the first evaporator 14 that are connected by the refrigerant pipe 10a.
  • the first refrigerant such as the isobutane and the like flows in the arrow S1 direction.
  • the first refrigerant flows and circulates via the first compressor 11, the first heat radiator 12, the first pressure reducer 13, the first evaporator 14 and the first compressor 11 in this order.
  • the defrosting heat exchanger 35 is disposed in parallel with the first heat radiator 12.
  • a three-way valve 36 for switching the flow path is disposed; and the refrigerant pipe 10a, which branches off at the three-way valve 36, is connected to the defrosting heat exchanger 35.
  • a check valve 37 is disposed on the refrigerant flow-out side of the defrosting heat exchanger 35. The check valve 37 is disposed near a joining point 10b between: the refrigerant flow-out side of the first heat radiator 12; and the refrigerant flow-out side of the defrosting heat exchanger 35, and disposed away from the defrosting heat exchanger 35.
  • the first refrigerant flows as indicated by an arrow S1'. According to this, the first refrigerant flows and circulates via the first compressor 11, the defrosting heat exchange 35, the first pressure reducer 13, the first evaporator 14 and the first compressor 11 in this order.
  • the second freeze cycle 20 operated by the second compressor 21 has: the second heat radiator 22, the second pressure reducer 23, and the second evaporator 24 that are connected by the refrigerant pipe 20a.
  • the second refrigerant such as the isobutane and the like flows in the arrow S2 direction.
  • the second refrigerant flows and circulates via the second compressor 21, the second heat radiator 22, the second pressure reducer 23, the second evaporator 24 and the second compressor 21 in this order.
  • the defrosting heat exchanger 35 and the second evaporator 24 are so formed as to be able to perform heat exchange with each other.
  • Fig. 19 shows a detailed view of the defrosting heat exchanger 35 and the second evaporator 24.
  • the refrigerant pipes 10a, 20a of the defrosting heat exchanger 35 and the second evaporator 24 are so disposed as to be close to each other and to snake their way; and connected by many fins 37. According to this, the defrosting heat exchanger 35 and the second evaporator 24 easily perform the heat exchange via the fins 37.
  • the refrigerant pipes 10a, 20a may be disposed side by side; and may be so formed as to be able to perform the heat exchange via a border wall between the defrosting heat exchanger 35 and the second evaporator 24.
  • the sectional area of the first refrigerant pipe 10a of the defrosting heat exchanger 35 is so formed as to be half or below the sectional area of the first refrigerant pipe l0a of the first evaporator 14. According to this, when the three-way valve 36 is switched to the first heat radiator 12, it is possible to lessen the amount of the first refrigerant that remains in the defrosting heat exchanger 35.
  • the first and second heat radiators 12, 22 are joined to and disposed on the rear side of the metal plate (not shown) that covers the side surfaces, the rear surface and the like of the freezer-refrigerator 1. Besides, the first and second heat radiators 12, 22 extend in a heat insulation box body 6 and are disposed near the doors 2a, 3a, and 4a of the heat insulation walls 7, 8. According to this, it is possible to secure a sufficient heat radiation area and prevent condensation near the doors 2a, 3a and 4a.
  • the second and third internal heat exchangers 33, 34 are disposed which are the same as those in the fourth embodiment (see Fig. 12 ); and the first internal heat exchanger 32 (see Fig. 12 ) is removed.
  • the heat exchange portion 33a disposed in the subsequent stage of the second heat radiator 22 and the heat exchange portions 33b disposed in the subsequent stage of the second heat radiator 22 are disposed side by side; and so formed as to be able to perform the heat exchange with each other via the border wall.
  • the high-temperature second refrigerant flowing from the second heat radiator 22 flows in the heat exchange portion 33a, while the low-temperature second refrigerant flowing from the second heat radiator 22 flows in the heat exchange portion 33b.
  • the heat exchange portion 33a may double as the second pressure reducer 23.
  • the heat exchange portion 34a disposed in the subsequent stage of the first heat radiator 12 and the heat exchange portions 34b disposed in the subsequent stage of the first evaporator 14 are disposed side by side; and so formed as to be able to perform the heat exchange with each other via the border wall.
  • the high-temperature first refrigerant flowing from the first heat radiator 12 flows in the heat exchange portion 34a, while the low-temperature first refrigerant flowing from the first evaporator 14 flows in the heat exchange portion 34b.
  • the heat exchange portion 34a may double as the first pressure reducer 13.
  • the freezer-refrigerator 1 having the above structure, during a time the refrigeration compartment 2, the vegetable compartment 3, and the freeze compartment 4 are cooled, thanks to driving of the first and second compressors 11 and 21, the first and second refrigerants flow in the refrigerant pipes l0a and 20a.
  • the first and second compressors 11, 21 compress the first and second refrigerants to a high temperature and a high pressure, while the first and second pressure reducers 13 and 23 decompress and expand the first and second refrigerants to a low temperature and a low pressure.
  • the first refrigerant which is compressed by the first compressor 11 and has the high temperature and high pressure, is deprived of heat by the surrounding air via the first heat radiator 12 to condense.
  • the first refrigerant flowing from the first heat radiator 12 is prevented from flowing in the defrosting heat exchanger 35 by the check valve 37.
  • the check valve 37 is so disposed as to be away from the defrosting heat exchanger 35 and to be near the joining point 10b. Because of this, it is possible to reduce temperature rise of the second evaporator 24 caused by heat conduction via the first refrigerant l0a from the high-temperature first refrigerant that flows from the first heat radiator 12.
  • the first refrigerant which is liquefied by the first heat radiator 12, flows in the third internal heat exchanger 34 and performs the heat exchange with the first refrigerant flowing from the first evaporator 14 to be further lowered in temperature.
  • the first refrigerant which is cooled to a large over-cooling degree by the third internal heat exchanger 34 and in a liquid state, flows in the first pressure reducer 13.
  • the first refrigerant is decompressed and expanded by the first pressure reducer 13 and becomes a damp vapor that has a low dry degree and a low temperature.
  • the first refrigerant which becomes the low-temperature damp vapor, flows in the first evaporator 14, deprives the cold air in the refrigeration compartment 2 of heat to evaporate; and becomes a damp vapor that has a higher dry degree.
  • the first refrigerant which flows from the first evaporator 14 and is in the damp vapor state, flows in the third internal heat exchanger 34, deprives the high-temperature first refrigerant flowing from the first heat radiator 12 to evaporate; and becomes an over-heated vapor.
  • the first refrigerant which becomes the over-heated vapor, returns to the first compressor 11. According to this, the first refrigerant circulates, so that the first freeze cycle 10 is operated and the refrigeration compartment 2 and the vegetable compartment 3 are cooled.
  • the second refrigerant which is compressed by the second compressor 21 and has the high temperature and high pressure, is deprived of heat by the surrounding air via the second heat radiator 22 to condense.
  • the second refrigerant which is liquefied by the second heat radiator 22, flows in the second internal heat exchanger 33 and performs the heat exchange with the second refrigerant flowing from the second evaporator 24 to be further lowered in temperature.
  • the second refrigerant which is cooled to a large over-cooling degree by the second internal heat exchanger 33 and in a liquid state, flows in the second pressure reducer 23.
  • the second refrigerant is decompressed and expanded by the second pressure reducer 23 and becomes a damp vapor that has a low dry degree and a low temperature.
  • the second refrigerant which becomes the low-temperature damp vapor, flows in the second evaporator 24, deprives the cold air in the freeze compartment 4 of heat to evaporate; and becomes a damp vapor that has a higher dry degree.
  • the second refrigerant which flows from the second evaporator 24 and is in the damp vapor state, flows in the second internal heat exchanger 33, deprives the high-temperature second refrigerant flowing from the second heat radiator 22 of heat to evaporate; and becomes an over-heated vapor.
  • the second refrigerant which becomes the over-heated vapor, returns to the second compressor 21. According to this, the second refrigerant circulates, so that the second freeze cycle 10 is operated and the freeze compartment 4 is cooled.
  • Fig. 20 is a flow chart showing operation of the second evaporator 24 during a defrosting time.
  • a step #11 to perform defrosting of the second evaporator 24, the second compressor 21 is stopped.
  • the first compressor 11 is stopped.
  • the three-way valve 36 is switched to the defrosting heat exchanger 35.
  • a step #14 the process stands by from the time the first compressor 11 is stopped to a time a predetermined time elapses. According to this, the temperatures of the refrigeration compartment 2 and the vegetable compartment 3 rise. If the predetermined time elapses; and the refrigeration compartment 2 and the vegetable compartment 3 rise near an upper limit of a set temperature, the process goes to a step #15.
  • the three-way valve 36 may be switched to the defrosting heat exchanger 35 after the predetermined time elapses.
  • the standby time does not need to depend on time.
  • a sensor may be disposed in the refrigeration compartment 2 or the vegetable compartment 3; and the process may stand by until the upper limit of the set temperature is detected by the temperature sensor; thereafter may go to the step #15.
  • the first compressor 11 is driven. According to this, the first freeze cycle 10 is operated; and thanks to the heat exchange with the defrosting heat exchanger 35 in the high-temperature portion, the second evaporator 24 is raised in temperature and defrosted. Besides, the refrigeration compartment 2 and the vegetable compartment 3 are cooled. By raising the temperatures of the refrigeration compartment 2 and the vegetable compartment 3 in advance in the step #14, it is possible to prevent the refrigeration compartment 2 and the vegetable compartment 3 from being over-cooled during the defrosting time.
  • a step #16 the process stands by until a predetermined time elapses. According to this, the defrosting of the second evaporator 24 advances; if the predetermined time elapses and the defrosting is completed, the process goes to a step #17. In the step #17, the three-way valve 36 is switched to the first heat radiator 12. In a step #18, the process stands by until a predetermined time elapses. At the time of switching the three-way valve 36, the first compressor 11 may be temporarily stopped Besides, after the predetermined time elapses, the three-way valve 36 may be switched to the first heat radiator 12.
  • step #19 the second compressor 21 is driven. According to this, the second freeze cycle 20 is operated and the freeze compartment 4 is cooled.
  • the first evaporator 14 for cooling the refrigeration compartment 2 is higher than the second evaporator 24 in temperature; accordingly, is less than the second evaporator 24 in frost amount thereon.
  • the temperature of the air in the refrigeration compartment 2 is 0°C or higher. Accordingly, by only stopping the first compressor 11 and driving the refrigeration compartment air blower 31, it is possible to defrost the first evaporator 14 by means of the heat of the air in the refrigeration compartment 2. Because of this, a defrosting heater 51 (see Fig. 1 ) is not driven usually, and driven at an unusual frost occurrence time.
  • the first and second freeze cycles 10, 20 are operated by the first and second compressors 11, 21, respectively; and the refrigeration compartment 2 and the freeze compartment 4 are cooled by the first and second evaporators 14, 24, so that the temperature of the first evaporator 14 for cooling the refrigeration compartment 2 is kept higher than the temperature of the second evaporator 24 to increase the cooling efficiency; and it is possible to reduce the power consumption of the freezer-refrigerator 1.
  • the second evaporator 24 of the second freeze cycle 20 is defrosted by the heat of the high-temperature portion of the first freeze cycle 10, so that first heat radiator 12 of the first freeze cycle 10 and the second heat radiator 22 of the second freeze cycle 20 do not reach a low temperature. Accordingly, it is possible to prevent condensation on the side surfaces, the rear surface and the like of the freezer-refrigerator 1. Besides, it is unnecessary to additionally dispose a heater that defrosts the second evaporator 22, so that it is possible to curb temperature rise caused by a heater and the like during the defrosting time. Accordingly, it is possible to curb the power consumption caused by the defrosting; and keep the power consumption of the freezer-refrigerator 1 low.
  • the first heat radiator 12 and the defrosting heat exchanger 35 are disposed in parallel with each other; and the three-way valves 36 and the check valve 37 are disposed on the refrigerant flow-in side and the refrigerant flow-out side, respectively, so that it is possible to easily achieve the freezer-refrigerator 1 that defrosts the second evaporator 24 of the second freeze cycle 20 by means of the heat of the high-temperature portion of the first freeze cycle 10.
  • the check valve 37 is so disposed as to be away from the defrosting heat exchanger 35 and to be near the joining point 10b, so that it is possible to reduce temperature rise of the second evaporator 24 caused by heat conduction via the first refrigerant pipe l0a from the high-temperature first refrigerant that flows from the first heat radiator 12. Accordingly, it is possible to increase the cooling efficiency of the freezer-refrigerator 1.
  • the first compressor 11 is stopped for the predetermined period before the defrosting of the second evaporator 24, so that it is possible to raise in advance the temperatures of the refrigeration compartment 2 and the vegetable compartment 3 to prevent the refrigeration compartment 2 and the vegetable compartment 3 from being over-cooled during the defrosting time.
  • the sectional area of the first refrigerant pipe l0a of the defrosting heat exchanger 35 is so formed as to be half or below the sectional area of the first refrigerant pipe l0a of the first evaporator 14, so that after the defrosting of the second evaporator 24 is ended and the three-way valve 36 is switched to the first heat radiator 12, a large quantity of the first refrigerant does not remain in the defrosting heat exchanger 35. Accordingly, it is possible to curb the amount the refrigerant that is injected in the first freeze cycle 10.
  • the present invention is applicable to any cooling storage units alike that include the dual type of freeze cycle in which the first and second evaporators 14, 24 are disposed in the first and second cooling compartments that have the compartment temperatures different from each other.
  • the present invention is applicable to a freeze cycle application apparatus, typically, the freezer-refrigerator 1 for home use.
  • Fig. 21 is a front view showing a freezer-refrigerator according to a seventh embodiment.
  • the freezer-refrigerator 1 is provided with the refrigeration compartment 2 for refrigerating and preserving stored things in an upper portion of the heat insulation box body 6 that forms the main body portion.
  • the freeze compartment 4 for freezing and preserving stored things is disposed via the heat insulation wall 8.
  • the front surface of the refrigeration compartment 2 is opened and closed by a rotatable door (not shown).
  • the front surface of the freeze compartment 4 is opened and closed by a drawer type of door (not shown) that is unitary with a housing case (not shown).
  • the mechanical compartment 5 is disposed behind the freeze compartment 4.
  • the first and second compressors 11, 21 which operate the first and second freeze cycles 10, 20 respectively described in detail later, are disposed.
  • insulation compartments 7a, 7b which are insulated from an upper portion by a partition wall 2a, are disposed.
  • the insulation compartments 7a, 7b include an ice compartment and a chilled compartment that are kept at temperatures lower than the upper portion f the refrigeration compartment 2.
  • the rear surface of the refrigeration compartment 2 is covered by a metal cooling plate 14b. As described in detail later, the cooling plate 14b forms the first evaporator 14 (see Fig. 22 ) to radiate cold heat.
  • a duct (not shown) is formed behind the freeze compartment 4; and in the duct, the second evaporator 24 is disposed. Over the second evaporator 24, the freeze compartment air blower 25 is disposed. Thanks to driving of the freeze compartment air blower 25, the cold air performing the heat exchange with the second evaporator 24 is output into the freeze compartment 4 from an output opening 4a in the upper portion. The cold air in the freeze compartment 4 is returned to the second evaporator 24 via a return opening 4b in the lower portion.
  • Fig. 22 is a front sectional view showing pipe arrangement of the freeze cycle of the freezer-refrigerator 1.
  • the freezer-refrigerator 1 has the first freeze cycle 10 operated by the first compressor 11 and the second freeze cycle 20 operated by the second compressor 21.
  • the first freeze cycle 10 has: the first heat radiator 12, the first pressure reducer 13, and the first evaporator 14 that are connected by the refrigerant pipe 10a.
  • the first refrigerant such as the isobutane and the like flows in the arrow S1 direction.
  • the first refrigerant flows and circulates via the first compressor 11, the first heat radiator 12, the first pressure reducer 13, the first evaporator 14 and the first compressor 11 in this order.
  • the second freeze cycle 20 operated by the second compressor 21 has: the second heat radiator 22, the second pressure reducer 23, and the second evaporator 24 that are connected by the refrigerant pipe 20a.
  • the second refrigerant such as the isobutane and the like flows in the arrow S2 direction.
  • the second refrigerant flows and circulates via the second compressor 21, the second heat radiator 22, the second pressure reducer 23, the second evaporator 24 and the second compressor 21 in this order.
  • the first evaporator 14 is formed by fixing the cooling plate 14 to the refrigerant pipe 14a in which the refrigerant flows.
  • the cooling plate 14 includes a metal plate that has a high thermal conductivity; and the front shape is formed into substantially a rectangular shape.
  • As a material of the cooling plate 14b it is possible to select aluminum, stainless steel, copper, brass, a plated steel plate and the like. It is more desirable that considering thermal conductivity, resistance to corrosion, strength, light weight, price and the like, the cooling plate 14b is formed of aluminum.
  • the thickness of the cooling plate 14b is formed to be 0.5 mm to 1 mm. According to this, it is possible to have a sufficient thermal conduction performance and obtain a high strength at low price.
  • the refrigerant flow-in side is disposed at a lower position and the refrigerant flow-out side is disposed at an upper position; and the first refrigerant flows from lower to upper.
  • the cooling plate 14b has a high thermal conductivity, accordingly, the temperature is substantially evened; however, the refrigerant flow-in side becomes lower than the refrigerant flow-out side in temperature. Because of this, the temperature of the refrigerant pipe 14a that faces the insulation compartments 7a, 7b is low, so that it is possible to surely keep the insulation compartments 7a, 7b at low temperatures.
  • the second evaporator 24 is formed by joining many fins to the refrigerant pipe.
  • the cold air flowing in the duct (not shown) on the rear surface of the freeze compartment 4 performs heat exchange with the fins, whereby cold air is generated and output into the freeze compartment 4.
  • the first and second heat radiators 12, 22 are joined to and disposed on a metal rear plate (not shown) that covers a rear surface of the heat insulation box body 6. Besides, the first and second heat radiators 12, 22 extend in the heat insulation box body 6 and are disposed in front of the heat insulation wall 8. According to this, it is possible to secure a sufficient heat radiation area and prevent condensation near the doors of the refrigeration compartment 2 and the freeze compartment 4.
  • Fig. 23 is a block diagram showing a structure of the freezer-refrigerator 1.
  • the freezer-refrigerator 1 includes a control portion 65 that controls each portion.
  • the first and second compressors 11, 21, the freeze compartment air blower 25, an operation panel 66, a door open-close detection portion 63, temperature sensors 61, 62, and a humidity sensor 64 are connected to the control portion 65.
  • the operation panel 66 is disposed on the door of the refrigeration compartment 2 and sets the compartment temperatures of the refrigeration compartment 2 and the freeze compartment 4.
  • the door open-close detection portion 63 detects opening and closing of the door of the refrigeration compartment 2.
  • the temperature sensors 61, 62 detect the compartment temperatures of the refrigeration compartment 2 and the freeze compartment 4, respectively. Based on detected temperatures by the temperature sensors 61, 62, the control portion 65 drives the first and second compressors 11,21, and the refrigeration compartment 2 and the freeze compartment 4 are kept at the set temperatures.
  • the humidity sensor 64 detects the humidity in the refrigeration compartment 2.
  • the freezer-refrigerator 1 having the above structure, during a time the refrigeration compartment 2 and the freeze compartment 4 are cooled, thanks to driving of the first and second compressors 11 and 21, the first and second refrigerants flow in the refrigerant pipes l0a and 20a.
  • the first and second compressors 11, 21 compress the first and second refrigerants to a high temperature and a high pressure, while the first and second pressure reducers 13 and 23 decompress and expand the first and second refrigerants to a low temperature and a low pressure.
  • the first refrigerant which is compressed by the first compressor 11 and has the high temperature and high pressure, is deprived of heat by the surrounding air via the first heat radiator 12 to condense.
  • the first refrigerant which is liquefied by the first heat radiator 12, flows in the first pressure reducer 13.
  • the first refrigerant is decompressed and expanded by the first pressure reducer 13 and becomes a damp vapor that has a low dry degree and a low temperature.
  • the first refrigerant which becomes the low-temperature damp vapor, flows in the first evaporator 14, deprives the cold air in the refrigeration compartment 2 of heat to evaporate; and becomes a damp vapor that has a higher dry degree.
  • the first refrigerant which flows from the first evaporator 14 and is in the damp vapor state, returns to the first compressor 11. According to this, the first refrigerant circulates, so that the first freeze cycle 10 is operated.
  • the refrigeration compartment 2 cold heat is radiated from the entire cooling plate 14b that covers the rear surface of the refrigeration compartment 2, so that the refrigeration compartment 2 undergoes radiation cooling. According to this, the cold air does not directly impinge on the stored things in the refrigeration compartment 2, so that it is possible to prevent the stored things from being dried.
  • the second refrigerant which is compressed by the second compressor 21 and has the high temperature and high pressure, is deprived of heat by the surrounding air via the second heat radiator 22 to condense.
  • the second refrigerant which is liquefied by the second heat radiator 22, flows in the second pressure reducer 23.
  • the second refrigerant is decompressed and expanded by the second pressure reducer 23 and becomes a damp vapor that has a low dry degree and a low temperature.
  • the second refrigerant which becomes the low-temperature damp vapor, flows in the second evaporator 24, deprives the cold air that flows in the duct of the freeze compartment 4 of heat to evaporate; and becomes a damp vapor that has a higher dry degree.
  • the second refrigerant which flows from the second evaporator 24 and is in the damp vapor state, returns to the second compressor 21. According to this, the second refrigerant circulates, so that the second freeze cycle 20 is operated.
  • the freeze compartment 4 the cold air, which performs the heat exchange in the second evaporator 24, is output, and the freeze compartment 4 is cooled.
  • the door open-close detection portion 63 the temperature and humidity in the refrigeration compartment 2 are detected by the temperature sensor 61 and the humidity sensor 64.
  • the control portion 65 based on the temperature and humidity in the refrigeration compartment 2, obtains a dew point temperature by calculation. And, the control portion 65 drives the first compressor 11 for a predetermined period such that the temperature in the refrigeration compartment 2 becomes the dew point temperature or below.
  • the cooling plate 14b goes into a foggy state. If the humidity in the refrigeration compartment 2 is found lower than a predetermined value based on the detection by the humidity sensor 64, the first compressor 11 is controlled such that the refrigeration compartment 2 has the set temperature. Here, the condensation on the surface of the cooling plate 14b gradually evaporates, so that the stored things in the refrigeration compartment 2 are further prevented from being dried.
  • the first and second freeze cycles 10, 20 are operated by the first and second compressors 11,21, respectively; the refrigeration compartment 2 and the freeze compartment 4 are cooled by the first and second evaporators 14, 24; and the first evaporator 14 has the cooling plate 14b. According to this, it is possible to prevent the stored things from being dried without directly directing the cold air to the stored things; and even the temperature distribution in the refrigeration compartment 2 by equally radiating cold heat from the cooling plate 14b that covers the wall surface of the refrigeration compartment 2.
  • the refrigeration compartment 2 and the freeze compartment 4 are able to obtain a sufficient cooling capability. Especially, during the high-load time of the refrigeration compartment 2, it is possible to lower the second evaporator 24 in temperature, so that it is possible to prevent insufficient cooling of the freeze compartment 4. Besides, during the high-load time of the freeze compartment 4, it is possible to lower the first evaporator 14 in temperature; and keep the humidity in the refrigeration compartment 2 by holding the condensation on the cooling plate 14b. According to this, even in a case where the freeze compartment 4 has a high load, it is possible to further reduce the drying of the stored things in the refrigeration compartment 2.
  • the adiabatic compression efficiency of the compressor increases as the compression ratio decreases. Because of this, by operating the first and second freeze cycles 10, 20 by means of the first and second compressors 11, 21 respectively, it is possible to lower the compression ratio; and drive the first and second compressors 11, 21 with a high efficiency.
  • the first freeze cycle 10 is operated such that the first evaporator reaches the dew point temperature or below when the door of the refrigeration compartment 2 is opened and then closed, so that it is possible to condense moisture of the outside air and hold the condensation by the cooling plate 14b; and further reduce the drying of the stored things.
  • the insulation compartments 7a, 7b having temperatures lower than the upper portion are disposed; and the refrigerant flows from lower to upper in the refrigerant pipe 14a of the first evaporator 14.
  • the cooling plate including the metal plate has a high thermal conductivity, accordingly, the temperature is evened; however, the refrigerant flow-in side becomes lower than the refrigerant flow-out side in temperature. Because of this, the temperature of the refrigerant pipe 14a that faces the insulation compartments 7a, 7b is low, so that it is possible to surely keep the insulation compartments 7a, 7b at low temperatures.
  • Fig. 24 is a front sectional view showing pipe arrangement of a freeze cycle of a freezer-refrigerator according to an eighth embodiment.
  • the freeze cycle 30 of the freezer-refrigerator 1 according to the present embodiment is structured in the same way as the second embodiment shown in Fig. 5 described above.
  • the freeze cycle 30 is so formed as to be the cascade type of dual freeze cycle in which the first and second freeze cycles 10, 20 are connected to each other by the intermediate heat exchanger 31.
  • the other portions are the same as the first embodiment.
  • the heat exchange portion 31a disposed in the first freeze cycle 10 and the heat exchange portions 31b disposed in the second freeze cycle 20 are disposed side by side; and so formed as to be able to perform the heat exchange with each other via the wall surface.
  • the heat exchange portion 31a is disposed in the subsequent stage of the first evaporator 14, while the heat exchange portion 31b is disposed in the subsequent stage of the second heat radiator 22. Accordingly, thanks to the intermediate heat exchanger 31, the heat exchange is performed between the low-temperature portion of the first freeze cycle 10 and the high-temperature portion of the second freeze cycle 20.
  • the first and second refrigerants flow in the refrigerant pipes l0a and 20a.
  • the first and second compressors 11, 21 compress the first and second refrigerants to a high temperature and a high pressure, while the first and second pressure reducers 13 and 23 decompress and expand the first and second refrigerants to a low temperature and a low pressure.
  • the first refrigerant which is compressed by the first compressor 11 and has the high temperature and high pressure, is deprived of heat by the surrounding air via the first heat radiator 12 to condense.
  • the first refrigerant which is liquefied by the first heat radiator 12, flows in the first pressure reducer 13.
  • the first refrigerant is decompressed and expanded by the first pressure reducer 13 and becomes a damp vapor that has a low dry degree and a low temperature.
  • the first refrigerant which becomes the low-temperature damp vapor, flows in the first evaporator 14, deprives the cold air in the refrigeration compartment 2 of heat to evaporate; and becomes a damp vapor that has a higher dry degree.
  • the first refrigerant which flows from the first evaporator 14 and is in the damp vapor state, flows in the intermediate heat exchanger 31, deprives the second refrigerant in the high-temperature portion of the second freeze cycle 20 of heat to evaporate; and becomes an over-heated vapor.
  • the first refrigerant which becomes the over-heated vapor, returns to the first compressor 11. According to this, the first refrigerant circulates, so that the first freeze cycle 10 is operated.
  • the second refrigerant which is compressed by the second compressor 21 and has the high temperature and high pressure, is deprived of heat by the surrounding air via the second heat radiator 22.
  • the second refrigerant which is lowered in temperature by the second heat radiator 22, flows in the intermediate heat exchanger 31 and is deprived of heat by the first refrigerant in the low-temperature portion of the first freeze cycle 10 to be further cooled to condense.
  • the liquefied second refrigerant flows in the second pressure reducer 23.
  • the second refrigerant is decompressed and expanded by the second pressure reducer 23 and becomes a damp vapor that has a low temperature.
  • the second refrigerant which becomes the low-temperature damp vapor, flows in the second evaporator 24, deprives the cold air in the freeze compartment 4 of heat to evaporate; and becomes a damp vapor.
  • the second refrigerant which flows from the second evaporator 24 and is in the damp vapor state, returns to the second compressor 21 According to this, the second refrigerant circulates, so that the second freeze cycle 20 is operated.
  • the second compressor 21 is driven after the first compressor 11 is driven and the temperature of the intermediate heat exchanger 31 decreases. And, the temperatures of the refrigeration compartment 2 and the freeze compartment 4 and a temperature difference between the heat exchange portions 31a and 31b of the intermediate heat exchanger 31 are monitored; and the rotation speeds of the first and second compressors 11, 21 are controlled by inverter control such that these speeds become predetermined values.
  • the intermediate heat exchanger 31 is disposed, so that heat of the high-temperature portion of the second freeze cycle 20 is absorbed by the intermediate heat exchanger 31. According to this, the second evaporator 24 is lowered in temperature further than the intermediate heat exchanger 31, whereby it is possible to easily generate the cold air that has a low temperature.
  • the first and second refrigerants which flow in the first and second freeze cycles 10, 21, include isobutane; however, different refrigerants may be used.
  • the boiling point of the second refrigerant is set lower than the boiling point of the first refrigerant.
  • the second refrigerant becomes higher than the first refrigerant in vapor density, so that it is possible to further increase the performance of the second freeze cycle 20.
  • isobutane the boiling point -12°C
  • propane the boiling point -40.09°C
  • carbon dioxide the boiling point -78.5°C
  • an internal heat exchanger may be disposed which performs heat exchange between the first refrigerant flowing from the first heat radiator 12 and the first refrigerant flowing from the first evaporator 14. According to this, it is possible to lower the enthalpy of the first refrigerant before flowing in the first evaporator 14; and it is possible to further increase the cooling capability of the first refrigerant that flows in the first evaporator 14.
  • an internal heat exchanger may be disposed which performs heat exchange between the second refrigerant flowing from the second heat radiator 22 and the second refrigerant flowing from the second evaporator 24.
  • the present invention is applicable to a freezer-refrigerator that includes first and second evaporators which cool a refrigeration compartment and a freeze compartment, respectively.
  • the present invention is applicable to a cooling storage unit that includes first and second evaporators which cool first and second cooling compartments that have temperatures different from each other.

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)
EP09843369A 2009-04-17 2009-12-11 Freezer-refrigerator and cooling storage unit Withdrawn EP2420760A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2009100721A JP2010249444A (ja) 2009-04-17 2009-04-17 冷凍冷蔵庫
JP2009276795A JP5270523B2 (ja) 2009-12-04 2009-12-04 冷凍冷蔵庫
PCT/JP2009/070739 WO2010119591A1 (ja) 2009-04-17 2009-12-11 冷凍冷蔵庫及び冷却庫

Publications (1)

Publication Number Publication Date
EP2420760A1 true EP2420760A1 (en) 2012-02-22

Family

ID=42982268

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09843369A Withdrawn EP2420760A1 (en) 2009-04-17 2009-12-11 Freezer-refrigerator and cooling storage unit

Country Status (4)

Country Link
EP (1) EP2420760A1 (zh)
CN (1) CN102395840B (zh)
RU (1) RU2496063C2 (zh)
WO (1) WO2010119591A1 (zh)

Cited By (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3001794A1 (fr) * 2013-02-04 2014-08-08 Jean-Luc Maire Sous-refroidisseur actif pour systeme de climatisation
WO2016117934A1 (en) * 2015-01-23 2016-07-28 Lg Electronics Inc. Refrigerator
CN106352573A (zh) * 2016-08-26 2017-01-25 青岛海信电子设备股份有限公司 一种冷媒直接制冷系统及控制方法
US20170030619A1 (en) * 2015-07-28 2017-02-02 Lg Electronics Inc. Refrigerator
EP2941603A4 (en) * 2012-12-17 2017-06-21 Astronautics Corporation Of America Use of unidirectional flow modes of magnetic cooling systems
US10060654B2 (en) 2014-10-16 2018-08-28 Sanden Holdings Corporation Heat pump type heating apparatus
US20180283764A1 (en) * 2017-03-28 2018-10-04 Haier Us Appliance Solutions, Inc. Refrigerator appliance with a caloric heat pump
US10527325B2 (en) 2017-03-28 2020-01-07 Haier Us Appliance Solutions, Inc. Refrigerator appliance
US10541070B2 (en) 2016-04-25 2020-01-21 Haier Us Appliance Solutions, Inc. Method for forming a bed of stabilized magneto-caloric material
US10551095B2 (en) 2018-04-18 2020-02-04 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly
US10557649B2 (en) 2018-04-18 2020-02-11 Haier Us Appliance Solutions, Inc. Variable temperature magneto-caloric thermal diode assembly
US10648705B2 (en) 2018-04-18 2020-05-12 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly
US10648703B2 (en) 2016-07-19 2020-05-12 Haier US Applicance Solutions, Inc. Caloric heat pump system
US10648706B2 (en) 2018-04-18 2020-05-12 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly with an axially pinned magneto-caloric cylinder
US10648704B2 (en) 2018-04-18 2020-05-12 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly
US10684044B2 (en) 2018-07-17 2020-06-16 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly with a rotating heat exchanger
US10782051B2 (en) 2018-04-18 2020-09-22 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly
US10830506B2 (en) 2018-04-18 2020-11-10 Haier Us Appliance Solutions, Inc. Variable speed magneto-caloric thermal diode assembly
EP3582999A4 (en) * 2017-02-17 2020-12-16 LG Electronics Inc. -1- REFRIGERATOR, COOLING OR HEATING DEVICE AND ADIABATIC VACUUM BODY
US10876770B2 (en) 2018-04-18 2020-12-29 Haier Us Appliance Solutions, Inc. Method for operating an elasto-caloric heat pump with variable pre-strain
US10989449B2 (en) 2018-05-10 2021-04-27 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly with radial supports
US11015842B2 (en) 2018-05-10 2021-05-25 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly with radial polarity alignment
US11015843B2 (en) 2019-05-29 2021-05-25 Haier Us Appliance Solutions, Inc. Caloric heat pump hydraulic system
US11022348B2 (en) 2017-12-12 2021-06-01 Haier Us Appliance Solutions, Inc. Caloric heat pump for an appliance
US11054176B2 (en) 2018-05-10 2021-07-06 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly with a modular magnet system
US11092364B2 (en) 2018-07-17 2021-08-17 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly with a heat transfer fluid circuit
US11112146B2 (en) 2019-02-12 2021-09-07 Haier Us Appliance Solutions, Inc. Heat pump and cascaded caloric regenerator assembly
US11125477B2 (en) 2017-08-25 2021-09-21 Astronautics Corporation Of America Drum-type magnetic refrigeration apparatus with improved magnetic-field source
US11149994B2 (en) 2019-01-08 2021-10-19 Haier Us Appliance Solutions, Inc. Uneven flow valve for a caloric regenerator
EP3734187B1 (en) * 2014-07-21 2021-10-27 LG Electronics Inc. Refrigerator
US11168926B2 (en) 2019-01-08 2021-11-09 Haier Us Appliance Solutions, Inc. Leveraged mechano-caloric heat pump
US11193697B2 (en) 2019-01-08 2021-12-07 Haier Us Appliance Solutions, Inc. Fan speed control method for caloric heat pump systems
US11274860B2 (en) 2019-01-08 2022-03-15 Haier Us Appliance Solutions, Inc. Mechano-caloric stage with inner and outer sleeves
EP3985328A4 (en) * 2019-06-12 2022-07-27 Daikin Industries, Ltd. REFRIGERATION CIRCUIT SYSTEM
US11402136B2 (en) 2017-08-25 2022-08-02 Astronautics Corporation Of America Drum-type magnetic refrigeration apparatus with multiple bed rings
US11680742B2 (en) 2017-09-22 2023-06-20 Lg Electronics Inc. Refrigerator including a drawer supporter having a cold air discharge port
DE102022127314A1 (de) 2022-10-18 2024-04-18 Hefei Hualing Co., Ltd. Kühleinheit für einen Kühlschrank

Families Citing this family (39)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012086089A1 (ja) * 2010-12-24 2012-06-28 株式会社前川製作所 ヒートポンプ装置の運転制御方法及び装置
JP2012255601A (ja) * 2011-06-09 2012-12-27 Sharp Corp 冷凍冷蔵庫
CN102364266A (zh) * 2011-10-31 2012-02-29 浙江大学 一种双温位的蒸汽压缩冷变换器
CN103982959B (zh) * 2013-09-29 2017-08-11 郭舜成 热量传递装置、温度冷却装置和温度聚集装置
RU2563049C2 (ru) * 2013-11-25 2015-09-20 Открытое акционерное общество "Центральный научно-исследовательский институт "Курс" (ОАО "ЦНИИ "Курс") Каскадная холодильная машина
CN105202852A (zh) * 2015-09-15 2015-12-30 杭州华日家电有限公司 一种基于高效节能的电冰箱制冷循环系统及其控制方法
US10281177B2 (en) 2016-07-19 2019-05-07 Haier Us Appliance Solutions, Inc. Caloric heat pump system
US10443585B2 (en) 2016-08-26 2019-10-15 Haier Us Appliance Solutions, Inc. Pump for a heat pump system
CN106568274A (zh) * 2016-10-27 2017-04-19 青岛海尔特种电冰柜有限公司 双回路多温区制冷设备
CN106524651A (zh) * 2016-10-27 2017-03-22 青岛海尔特种电冰柜有限公司 分体式双流路制冷设备
CN106482369A (zh) * 2016-10-27 2017-03-08 青岛海尔特种电冰柜有限公司 多温区制冷循环双系统及多温区制冷设备
CN106568275A (zh) * 2016-10-27 2017-04-19 青岛海尔特种电冰柜有限公司 多温区双流路制冷装置
CN106556202A (zh) * 2016-10-27 2017-04-05 青岛海尔特种电冰柜有限公司 多温区双制冷装置
CN106556203A (zh) * 2016-10-27 2017-04-05 青岛海尔特种电冰柜有限公司 分体式双制冷装置
CN106440626A (zh) * 2016-10-27 2017-02-22 青岛海尔特种电冰柜有限公司 多温区双制冷循环系统及多温区制冷设备
CN106482371A (zh) * 2016-10-27 2017-03-08 青岛海尔特种电冰柜有限公司 多温区双制冷系统及多温区制冷设备
CN106556201A (zh) * 2016-10-27 2017-04-05 青岛海尔特种电冰柜有限公司 双回路分体式制冷设备
CN106595106A (zh) * 2016-10-27 2017-04-26 青岛海尔特种电冰柜有限公司 双回路多温区制冷装置
CN106568219A (zh) * 2016-10-27 2017-04-19 青岛海尔特种电冰柜有限公司 多温区双流路制冷设备
US10386096B2 (en) 2016-12-06 2019-08-20 Haier Us Appliance Solutions, Inc. Magnet assembly for a magneto-caloric heat pump
US10451320B2 (en) 2017-05-25 2019-10-22 Haier Us Appliance Solutions, Inc. Refrigerator appliance with water condensing features
US10422555B2 (en) * 2017-07-19 2019-09-24 Haier Us Appliance Solutions, Inc. Refrigerator appliance with a caloric heat pump
US10451322B2 (en) 2017-07-19 2019-10-22 Haier Us Appliance Solutions, Inc. Refrigerator appliance with a caloric heat pump
KR102449175B1 (ko) 2017-08-01 2022-09-29 엘지전자 주식회사 진공단열체 및 냉장고
KR102459784B1 (ko) 2017-08-01 2022-10-28 엘지전자 주식회사 진공단열체 및 냉장고
KR102449177B1 (ko) 2017-08-01 2022-09-29 엘지전자 주식회사 진공단열체 및 냉장고
KR102529116B1 (ko) * 2017-08-01 2023-05-08 엘지전자 주식회사 진공단열체, 진공단열체의 제작방법, 및 그 진공단열체로 단열하는 냉온장고
KR102427466B1 (ko) 2017-08-01 2022-08-01 엘지전자 주식회사 차량, 차량용 냉장고, 및 차량용 냉장고의 제어방법
KR102459786B1 (ko) 2017-08-16 2022-10-28 엘지전자 주식회사 진공단열체 및 냉장고
CN107643781B (zh) * 2017-09-12 2021-04-23 合肥美的电冰箱有限公司 酒柜及其控制方法和控制装置
KR102454399B1 (ko) 2017-09-22 2022-10-14 엘지전자 주식회사 냉장고
US10520229B2 (en) 2017-11-14 2019-12-31 Haier Us Appliance Solutions, Inc. Caloric heat pump for an appliance
US10641539B2 (en) 2018-04-18 2020-05-05 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly
US11346583B2 (en) * 2018-06-27 2022-05-31 Emerson Climate Technologies, Inc. Climate-control system having vapor-injection compressors
CN109737625B (zh) * 2019-03-04 2023-07-25 珠海格力电器股份有限公司 一种热泵系统、控制方法和热泵干燥装置
JP2020180721A (ja) * 2019-04-24 2020-11-05 シャープ株式会社 冷蔵庫
CN110579064A (zh) * 2019-09-23 2019-12-17 珠海格力电器股份有限公司 一种制冷系统及包含其的冷库
CN113432326A (zh) * 2020-03-23 2021-09-24 青岛海尔智能技术研发有限公司 复叠式压缩制冷系统以及具有其的制冷设备
CN117404870A (zh) * 2023-12-13 2024-01-16 珠海格力电器股份有限公司 冰箱控制方法、装置、电子设备及存储介质

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59127887U (ja) 1983-02-18 1984-08-28 日本電子機器株式会社 内燃機関のグロ−プラグ制御装置
SU1490400A1 (ru) * 1987-11-09 1989-06-30 Одесский Технологический Институт Холодильной Промышленности Каскадно-регенеративна система предварительного охлаждени
JPH0536258U (ja) 1991-10-18 1993-05-18 三菱重工業株式会社 二元冷凍機
JPH09138046A (ja) * 1995-11-16 1997-05-27 Sanyo Electric Co Ltd 冷却装置
JPH10103800A (ja) * 1996-09-27 1998-04-21 Sanyo Electric Co Ltd 複合型冷凍装置
JPH10153375A (ja) 1996-11-22 1998-06-09 Matsushita Refrig Co Ltd 冷凍冷蔵庫
JP2000205665A (ja) * 1999-01-08 2000-07-28 Daikin Ind Ltd 冷凍装置
JP2000356445A (ja) 1999-06-11 2000-12-26 Toshiba Corp 冷蔵庫
JP4380905B2 (ja) 2000-10-13 2009-12-09 シャープ株式会社 冷蔵庫
JP2002340449A (ja) 2001-05-15 2002-11-27 Mitsubishi Heavy Ind Ltd 冷凍ユニット
DE10163187A1 (de) * 2001-12-21 2003-07-03 Bsh Bosch Siemens Hausgeraete Kältegerät
JP4294351B2 (ja) * 2003-03-19 2009-07-08 株式会社前川製作所 Ｃｏ２冷凍サイクル
JP2005049064A (ja) * 2003-07-31 2005-02-24 Sanyo Electric Co Ltd 空調冷凍装置
JP4409316B2 (ja) * 2004-03-11 2010-02-03 サンデン株式会社 冷却装置
JP2005326121A (ja) * 2004-05-17 2005-11-24 Sanden Corp 空気調和装置
CN1862151A (zh) * 2005-05-12 2006-11-15 乐金电子(天津)电器有限公司 回热式制冷循环系统空调器

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2010119591A1 *

Cited By (51)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10288327B2 (en) 2012-12-17 2019-05-14 Astronautics Corporation Of America Use of unidirectional flow modes of magnetic cooling systems
EP2941603A4 (en) * 2012-12-17 2017-06-21 Astronautics Corporation Of America Use of unidirectional flow modes of magnetic cooling systems
US9746214B2 (en) 2012-12-17 2017-08-29 Astronautics Corporation Of America Use of unidirectional flow modes of magnetic cooling systems
FR3001794A1 (fr) * 2013-02-04 2014-08-08 Jean-Luc Maire Sous-refroidisseur actif pour systeme de climatisation
EP3734187B1 (en) * 2014-07-21 2021-10-27 LG Electronics Inc. Refrigerator
US10060654B2 (en) 2014-10-16 2018-08-28 Sanden Holdings Corporation Heat pump type heating apparatus
WO2016117934A1 (en) * 2015-01-23 2016-07-28 Lg Electronics Inc. Refrigerator
KR20160091106A (ko) * 2015-01-23 2016-08-02 엘지전자 주식회사 냉장고
DE112016000456B4 (de) 2015-01-23 2023-01-19 Lg Electronics Inc. Kühlschrank
US10502460B2 (en) 2015-01-23 2019-12-10 Lg Electronics Inc. Refrigerator
US20180045433A1 (en) * 2015-01-23 2018-02-15 Lg Electronics Inc. Refrigerator
KR20170013764A (ko) * 2015-07-28 2017-02-07 엘지전자 주식회사 냉장고
US11073317B2 (en) * 2015-07-28 2021-07-27 Lg Electronics Inc. Refrigerator
EP3128262A1 (en) * 2015-07-28 2017-02-08 Lg Electronics Inc. Refrigerator
US20210341194A1 (en) * 2015-07-28 2021-11-04 Lg Electronics Inc. Refrigerator
US10627143B2 (en) 2015-07-28 2020-04-21 Lg Electronics Inc. Refrigerator
US20170030619A1 (en) * 2015-07-28 2017-02-02 Lg Electronics Inc. Refrigerator
US10541070B2 (en) 2016-04-25 2020-01-21 Haier Us Appliance Solutions, Inc. Method for forming a bed of stabilized magneto-caloric material
US10648703B2 (en) 2016-07-19 2020-05-12 Haier US Applicance Solutions, Inc. Caloric heat pump system
CN106352573A (zh) * 2016-08-26 2017-01-25 青岛海信电子设备股份有限公司 一种冷媒直接制冷系统及控制方法
EP3582999A4 (en) * 2017-02-17 2020-12-16 LG Electronics Inc. -1- REFRIGERATOR, COOLING OR HEATING DEVICE AND ADIABATIC VACUUM BODY
US11872921B2 (en) 2017-02-17 2024-01-16 Lg Electronics Inc. Refrigerator, refrigerating or warming apparatus, and vacuum adiabatic body
US11400847B2 (en) 2017-02-17 2022-08-02 Lg Electronics Inc. Refrigerator, refrigerating or warming apparatus, and vacuum adiabatic body
US10527325B2 (en) 2017-03-28 2020-01-07 Haier Us Appliance Solutions, Inc. Refrigerator appliance
US20180283764A1 (en) * 2017-03-28 2018-10-04 Haier Us Appliance Solutions, Inc. Refrigerator appliance with a caloric heat pump
US11009282B2 (en) 2017-03-28 2021-05-18 Haier Us Appliance Solutions, Inc. Refrigerator appliance with a caloric heat pump
US11402136B2 (en) 2017-08-25 2022-08-02 Astronautics Corporation Of America Drum-type magnetic refrigeration apparatus with multiple bed rings
US11125477B2 (en) 2017-08-25 2021-09-21 Astronautics Corporation Of America Drum-type magnetic refrigeration apparatus with improved magnetic-field source
US11680742B2 (en) 2017-09-22 2023-06-20 Lg Electronics Inc. Refrigerator including a drawer supporter having a cold air discharge port
US11022348B2 (en) 2017-12-12 2021-06-01 Haier Us Appliance Solutions, Inc. Caloric heat pump for an appliance
US10830506B2 (en) 2018-04-18 2020-11-10 Haier Us Appliance Solutions, Inc. Variable speed magneto-caloric thermal diode assembly
US10648704B2 (en) 2018-04-18 2020-05-12 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly
US10551095B2 (en) 2018-04-18 2020-02-04 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly
US10876770B2 (en) 2018-04-18 2020-12-29 Haier Us Appliance Solutions, Inc. Method for operating an elasto-caloric heat pump with variable pre-strain
US10557649B2 (en) 2018-04-18 2020-02-11 Haier Us Appliance Solutions, Inc. Variable temperature magneto-caloric thermal diode assembly
US10782051B2 (en) 2018-04-18 2020-09-22 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly
US10648705B2 (en) 2018-04-18 2020-05-12 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly
US10648706B2 (en) 2018-04-18 2020-05-12 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly with an axially pinned magneto-caloric cylinder
US11015842B2 (en) 2018-05-10 2021-05-25 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly with radial polarity alignment
US11054176B2 (en) 2018-05-10 2021-07-06 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly with a modular magnet system
US10989449B2 (en) 2018-05-10 2021-04-27 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly with radial supports
US11092364B2 (en) 2018-07-17 2021-08-17 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly with a heat transfer fluid circuit
US10684044B2 (en) 2018-07-17 2020-06-16 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly with a rotating heat exchanger
US11168926B2 (en) 2019-01-08 2021-11-09 Haier Us Appliance Solutions, Inc. Leveraged mechano-caloric heat pump
US11274860B2 (en) 2019-01-08 2022-03-15 Haier Us Appliance Solutions, Inc. Mechano-caloric stage with inner and outer sleeves
US11193697B2 (en) 2019-01-08 2021-12-07 Haier Us Appliance Solutions, Inc. Fan speed control method for caloric heat pump systems
US11149994B2 (en) 2019-01-08 2021-10-19 Haier Us Appliance Solutions, Inc. Uneven flow valve for a caloric regenerator
US11112146B2 (en) 2019-02-12 2021-09-07 Haier Us Appliance Solutions, Inc. Heat pump and cascaded caloric regenerator assembly
US11015843B2 (en) 2019-05-29 2021-05-25 Haier Us Appliance Solutions, Inc. Caloric heat pump hydraulic system
EP3985328A4 (en) * 2019-06-12 2022-07-27 Daikin Industries, Ltd. REFRIGERATION CIRCUIT SYSTEM
DE102022127314A1 (de) 2022-10-18 2024-04-18 Hefei Hualing Co., Ltd. Kühleinheit für einen Kühlschrank

Also Published As

Publication number Publication date
RU2496063C2 (ru) 2013-10-20
WO2010119591A1 (ja) 2010-10-21
CN102395840B (zh) 2014-01-29
CN102395840A (zh) 2012-03-28
RU2011146643A (ru) 2013-05-27

Similar Documents

Publication Publication Date Title
EP2420760A1 (en) Freezer-refrigerator and cooling storage unit
US20100287961A1 (en) Refrigerator and control method for the same
JP6687384B2 (ja) 冷蔵庫
US10088216B2 (en) Refrigerator and method of controlling the same
JP5178771B2 (ja) 冷凍冷蔵庫
JP5261066B2 (ja) 冷凍冷蔵庫及び冷却庫
JPWO2017179500A1 (ja) 冷蔵庫および冷却システム
CA2710478A1 (en) Defrost system and method for a subcritical cascade r-744 refrigeration system
WO2013088462A1 (ja) 冷蔵庫
CN102997558A (zh) 冰箱
JP2010043750A (ja) 冷凍冷蔵庫
JP6559335B2 (ja) 冷蔵庫
JP2004324902A (ja) 冷凍冷蔵庫
JP2010121842A (ja) 冷蔵庫
JP2010060146A (ja) 冷凍冷蔵庫及び冷却庫
US20210239384A1 (en) Refrigerator
JP2004333092A (ja) 冷凍冷蔵庫
JP5056026B2 (ja) 自動販売機
JP5916174B2 (ja) 冷蔵庫
JP2010249444A (ja) 冷凍冷蔵庫
JP5694897B2 (ja) 冷蔵庫
JP2017026210A (ja) 冷蔵庫
KR101858227B1 (ko) 냉장고
JP2012087952A (ja) 冷凍冷蔵庫
CN208859932U (zh) 一种提高空调能效比的制冷设备

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20111011

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20160804