EP1577620A2 - Kühlapparat - Google Patents

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Publication number
EP1577620A2
EP1577620A2 EP05005499A EP05005499A EP1577620A2 EP 1577620 A2 EP1577620 A2 EP 1577620A2 EP 05005499 A EP05005499 A EP 05005499A EP 05005499 A EP05005499 A EP 05005499A EP 1577620 A2 EP1577620 A2 EP 1577620A2
Authority
EP
European Patent Office
Prior art keywords
refrigerant
gas
refrigerating machine
compressor
heat
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Withdrawn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
EP05005499A
Other languages
English (en)
French (fr)
Other versions
EP1577620A3 (de
Inventor
Hiroyuki Itsuki
Akira Sugawara
Hiroshi Mukaiyama
Etsushi Nagae
Satoshi Imai
Kazuaki Mizukami
Ichiro Kamimura
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.)
Sanyo Electric Co Ltd
Original Assignee
Sanyo Electric Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sanyo Electric Co Ltd filed Critical Sanyo Electric Co Ltd
Publication of EP1577620A2 publication Critical patent/EP1577620A2/de
Publication of EP1577620A3 publication Critical patent/EP1577620A3/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/04—Preventing the formation of frost or condensate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/052—Compression system with heat exchange between particular parts of the system between the capillary tube and another part of the refrigeration cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D2700/00—Means for sensing or measuring; Sensors therefor
    • F25D2700/12—Sensors measuring the inside temperature
    • F25D2700/123—Sensors measuring the inside temperature more than one sensor measuring the inside temperature in a compartment

Definitions

  • the present invention relates to a refrigerating machine having a unit for selectively introducing gas refrigerant separated in a gas-liquid separator into an intermediate pressure portion of a compressor.
  • Patent Document 1 JP-A-2003-106693
  • gas refrigerant separated in the gas-liquid separator is introduced into the intermediate pressure portion of the compressor while kept to a gas state, so that there is achieved an effect that the efficiency of the compressor can be enhanced.
  • this type of refrigerating machine is equipped with a heat absorbing unit containing heat absorbers which selectively function in different temperature zone in a refrigerating cycle.
  • a heat absorbing unit containing heat absorbers which selectively function in different temperature zone in a refrigerating cycle.
  • heat absorbers functioning as a refrigerator and a freezer are disposed in the refrigerating cycle, and a refrigerating or freezing operation is carried out by using any one of the heat absorbers. In this case, it is important to carry out the refrigerating or freezing operation without reducing the efficiency under any operation.
  • an object of the present invention is to provide a refrigerating machine in which when heat absorbing units selectively functioning in different temperature zones are provided in the refrigerating cycle, the high efficiency operation can be performed in any temperature zone without reducing the efficiency.
  • a refrigerating machine having a compressor, a radiator, a pressure-reducing device, a gas-liquid separator, a unit for selectively introducing gas refrigerant separated in the gas-liquid separator into an intermediate pressure portion of the compressor, and a low pressure side circuit in which liquid refrigerant separated in the gas-liquid separator is circulated, wherein the low pressure side circuit is provided with a heat absorbing unit functioning selectively in one of different temperature zones, and refrigerant passing through the selected heat absorbing unit is returned to a suction portion of the compressor.
  • the heat absorbing unit has plural heat absorbers which function in different temperature zones, the heat absorbers function selectively, and there is provided a unit for guiding cold air passing through the heat absorbers to chambers controlled to the corresponding temperature zones.
  • the respective heat absorbers may be disposed in chambers which are respectively controlled to the corresponding temperature zones.
  • the heat absorbing unit may be provided with one heat absorber which functions selectively in different temperature zones, and there is provided a unit for selectively guiding cold air passing through the heat absorber through a change-over dumper to plural chambers controlled to different temperature zones.
  • the heat absorber may be disposed in a chamber controlled to a low temperature zone.
  • refrigerant such as carbon dioxide refrigerant or the like with which the high pressure side is set to supercritical pressure under operation may be filled.
  • the low pressure side circuit for circulating liquid refrigerant separated in the gas-liquid separator is provided, and the low pressure side circuit is provided with the absorbing unit which selectively functions in different temperature zones. Therefore, high-efficiency operation can be performed in the respective temperature zones.
  • Fig. 1 is a refrigerant circuit diagram showing an embodiment of the present invention.
  • a refrigerating machine 30 has a compressor 1, a radiator 2, a pressure-reducing device 3 and a gas-liquid separator 4.
  • a refrigerant circuit extending from the compressor 1 through the radiator 2 to the inlet port of the pressure-reducing device 3 constitutes a high pressure side circuit.
  • the pressure-reducing device 3 is designed so that the opening degree of the diaphragm thereof is variable. By varying the opening degree, the pressure of refrigerant is reduced until the refrigerant reaches the gas-liquid separator 4, and a lot of gas refrigerant occurs. Under this state, the refrigerant is input to the gas-liquid separator 4, whereby the separation efficiency in the gas-liquid separator 4 can be varied.
  • the compressor 1 is a two-stage compressor, and it contains a first-stage compressing portion 1A, a second-stage compressing portion 1B and an intermediate cooler 1C between the first-stage compressing portion 1A and the second-stage compressing portion 1B.
  • Reference numeral 8 represents a check valve.
  • the refrigerating machine 30 has an introducing unit 5 which can introduce gas refrigerant separated in the gas-liquid separator 4 to the intermediate portion of the compressor 1, that is, between the intermediate cooler 1C and the second-stage compressing portion 1B.
  • the compressor is not limited to the two-stage compressor.
  • the introducing unit 5 may return the refrigerant to the intermediate pressure portion of the one-stage compressor.
  • the introducing unit 5 comprises a gas pipe 6 and an opening/closing valve 7 provided to the gas pipe 6.
  • the opening/closing valve 7 When the opening/closing valve 7 is opened, the gas refrigerant separated in the gas-liquid separator 4 is passed through the gas pipe 6, and introduced to the intermediate pressure portion of the compressor 1 as indicated by an arrow of a broken line due to the pressure difference in the gas pipe 6.
  • the refrigerating machine 30 is provided with a low pressure side circuit 9 for circulating liquid refrigerant separated in the gas-liquid separator 4, and the low pressure side circuit 9 is provided with a heat absorbing unit 10 which functions selectively in different temperature zones.
  • the heat absorbing unit 10 comprises a three-way valve 11, a first capillary tube 12, a second capillary tube 13 provided in parallel to the first capillary tube 12, and one heat absorber 14.
  • the resistance value of the first capillary tube 12 is set to be larger than the resistance value of the second capillary tube 13. Therefore, when the refrigerant is made to flow to the first capillary tube 12 by switching the three-way valve 11 and also the driving frequency of the compressor 1 is reduced, the flow amount of the refrigerant flowing into the heat absorber 14 is reduced, the evaporation temperature is increased and thus refrigerating operation is carried out. When the driving frequency is fixed and only the resistance value of the capillary tube is increased, the evaporation temperature is lowered.
  • the flow amount of the refrigerant flowing into the heat absorber 14 is increased, the evaporation temperature is lowered and the freezing operation is carried out.
  • the refrigerant passed through the heat absorber 14 is passed through a heat exchanger 15 disposed near to the pressure-reducing device 3, heat-exchanged by the heat exchanger 15 to be heated.
  • the refrigerant thus heated is passed through a check valve 8, and then returned to the suction portion of the compressor 1.
  • the above construction is equipped with a unit 23 for selectively guiding cold air passed through the heat absorber 14 to plural chambers (refrigerating chamber 21, freezing chamber 22) controlled to different temperature zones.
  • the unit 23 contains an air blowing duct 24 and a change-over dumper 25.
  • a controller 26 is connected to the change-over dumper 25.
  • the controller 26 is connected to the three-way valve 11. For example when the load of the freezing chamber 22 is increased, by switching the three valve 11, the refrigerant is made to successively flow through the second capillary tube 13 having the small resistance value and the heat absorbing unit in this order. The evaporation temperature in the heat absorber 14 is reduced, and the change-over dumper 25 is tilted to the position shown in Fig. 1 to guide cold air to the freezing chamber 22.
  • the refrigerant is made to successively flow through the first capillary tube 12 having a large resistance value and the heat absorber 14 in this order, and the evaporator temperature in the heat absorber 14 is increased. Then, the change-over dumper 25 is titled to the opposite side to the position shown in Fig 1 to guide cold air to the refrigerating chamber 21 .
  • the refrigerant with which the high pressure side is set to supercritical pressure during operation for example, carbon dioxide refrigerant is filled in the refrigerant circuit described above.
  • Fig. 2 is an enthalpy-pressure (ph) diagram of the refrigerating cycle containing the two-stage compressor of this embodiment.
  • the high pressure side circuit is driven at supercritical pressure during operation as indicated by the enthalpy-pressure (ph) diagram of Fig. 3.
  • the refrigerant with which the high pressure circuit is driven at supercritical pressure may contain ethylene, diborane, ethane, nitride oxide or the like.
  • a represents a ph value at the suction port of the first-stage compressing portion 1A
  • b represents a ph value at the discharge port of the first-stage compressing portion 1A
  • c represents a ph value at the outlet port of the intermediate cooler 1C
  • d represents a ph value at the suction port of the second-stage compressing portion 1B
  • e represents the discharge port of the second-stage compressing portion 1A.
  • the refrigerant becomes a two-phase mixture of gas/liquid.
  • the ratio of gas and liquid corresponds to the ratio of the length of a line segment (gas) h-i and the length of a line segment (liquid) h-n.
  • the refrigerant enters the gas-liquid separator 4 under the two-phase mixture.
  • the gas refrigerant separated in the gas-liquid separator 4 is introduced to the intermediate pressure portion of the compressor 1, that is, introduced between the intermediate cooler 1C and the second-stage compressing portion 1B.
  • "n" represents a ph value at the outlet port of the gas-liquid separator 4.
  • the refrigerant passed through the outlet port of the gas-liquid separator 4 reaches the suction port of the second-stage compressing portion 1B of "d", and is compressed in the second-stage compressing portion 1A.
  • the liquid refrigerant separated in the gas-liquid separator 4 is circulated in the low pressure side circuit 9.
  • the gas refrigerant separated in the gas-liquid separator 4 is not usable for cooling even when it is circulated to the low pressure side circuit 9, and returning of this gas refrigerant to the suction port of the first-stage compressing portion 1A reduces the compression efficiency of the compressor 1.
  • the gas refrigerant separated in the gas-liquid separator 4 is introduced to the intermediate pressure portion of the compressor 1, that is, between the intermediate cooler 1C and the second-stage compressing portion 1B, and thus the compression efficiency of the compressor 1 can be enhanced.
  • particularly carbon dioxide refrigerant is filled in the refrigerant circuit, and thus with respect to the ratio of gas and liquid which are separated from each other in the gas-liquid separator 4, the gas amount (the line segment h-i) is larger as compared with chlorofluorocarbon refrigerant, and the large amount of gas refrigerant is introduced to the intermediate pressure portion of the compressor 1 to thereby enhance the efficiency.
  • all the constituent elements of the heat absorbing unit 10 functioning selectively in different temperature zones that is, the three-way valve 11, the first and second capillary tubes 12 and 13 and the heat absorber 14 are provided in the low pressure side circuit 9 in which the liquid refrigerant separated in the gas-liquid separator 4 is circulated. Therefore, for example in both the cases where refrigerating operation is carried out and where freezing operation is carried out, the high-efficiency operation can be performed without reducing the efficiency.
  • Fig. 4 shows an example in which the above embodiment is applied to a refrigerator.
  • a refrigerator 40 has a refrigerating chamber 41 at the upper stage, and a freezing chamber 42 at a lower stage.
  • a refrigerator partition wall 43 is provided at an inner back side of the freezing chamber 42, and the heat absorber 14 is disposed in an air flow path 44 partitioned by the refrigerator partition wall 43.
  • a first change-over dumper 45 is disposed at the inlet port of the air flow path 44, and the first change-over duper 45 is switched between a closing position (broken-line position) at which the inlet port A of the air flow path 44 is closed and an opening position (solid-line position) at which the inlet port A of the air flow path 44 is opened.
  • a back-side air flow path 46 is formed in the back wall 47 of the refrigerator 40, and when the first change-over dumper 45 is switched to the broken-line position, the inlet port A of the air flow path 44 and the refrigerating chamber 41 intercommunicate with each other through the back-side air flow path 46.
  • a fan 48 and a second change-over dumper 49 are disposed at the outlet port B of the air flow path 44, and the second change-over dumper 49 is switched between a closing position (broken-line position) at which the outlet port B of the air blow path 44 is closed and an opening position (solid-line position) at which the outlet port B of the air blow path 44 is opened.
  • the second change-over dumper 49 closes an opening 51 of an intermediate partition wall 50.
  • Fig. 5 shows an cooling example 1.
  • the area from the initial point to the point a corresponds to the freezing operation.
  • the dumpers 45 and 49 are located at the solid-line positions
  • cold air cooled by the heat absorber 14 is circulated in the air flow path 44, and fed to the freezing chamber 42, whereby the temperature of the freezing chamber 42 is gradually reduced.
  • the temperature of the refrigerating chamber 41 to which no cold air is fed is gradually increased.
  • the compressor 1 is turned on, the fan 48 is turned on, and each of the dumpers 45 and 49 is switched to the solid-line position.
  • refrigerant is made to flow into the second capillary tube 13, and the opening/closing valve 7 is opened.
  • the opening/closing valve 7 is opened with a predetermined time delay in order to prevent short-cut of the refrigerant passing through the opening/closing valve 7 at the start time of the operation of the compressor 1. Subsequently, this control is repeated from d point to i point.
  • Fig. 6 shows a cooling example 2.
  • the time period from 1 point to m point corresponds to the freezing operation.
  • the dumpers 45 and 49 are set to the solid-line position
  • cold air cooled by the heat absorber 14 is circulated in the air flow path 44 and fed to the freezing chamber 42. Accordingly, the temperature of the freezing chamber 42 is gradually reduced.
  • the temperature of the refrigerating chamber 41 to which no cold air is fed is gradually increased.
  • the compressor 1 is turned on
  • the fan 48 is turned on
  • each of the dumpers 45 and 49 is switched to the solid-line position and the three-way valve 11 is switched, so that the refrigerant is made to flow in the second capillary tube 13 and the opening/closing valve 7 is opened.
  • the refrigerating operation is carried out.
  • air in the refrigerating chamber 41 is circulated through the back-side air blow path 46, and cold air cooled by the heat absorber 14 is passed through the opening 51 of the intermediate partition wall 50 to the refrigerating chamber 41. Accordingly, the temperature of the refrigerating chamber 41 turns into reduction, however, the temperature of the freezing chamber 42 to which no cold air is fed turns into increase.
  • Fig. 7 shows another embodiment. This embodiment is different from the embodiment shown in Fig. 4 in the dumper construction at the outlet and inlet ports of the air flow path 44.
  • the dumper at the inlet port A is constructed by two dumpers 145A and 145B, and the dumper at the outlet port B is constructed by two dumpers 149A and 149B.
  • Fig. 8 shows another embodiment. This embodiment is different from the embodiment of Fig. 4 in the construction of the heat absorbing unit 10. That is, the heat absorbing unit 10 comprises a fourth capillary tube 55 and an electric motor operated valve 56 connected t the fourth capillary tube 55 in series.
  • Reference numeral 54 represents an electric motor operated valve.
  • the fourth capillary tube 55 has a fixed resistance value, and the overall resistance value can be varied by adjusting the resistance value of the fourth capillary tube 55 and the valve opening degree of the electric motor operated valve 56, so that the refrigeration or freezing operation can be performed. Substantially the same effect as the above embodiment can be achieved.
  • Fig. 9 shows the construction of another refrigerant circuit.
  • the heating unit of this embodiment comprises a three-way valve 11, a first capillary tube 12, a heat absorber for refrigeration which is connected to the first capillary tube 12 in series, a second capillary tube 13 which is provided in parallel to the above elements, and a heat absorber 58 for freezing which is connected to the second capillary tube 13.
  • Reference numeral 59 represents a check valve.
  • Fig. 10 shows an applied example to a refrigerator.
  • the refrigerator 40 has a refrigerating chamber 41 at the upper stage and a freezing chamber 42 at the lower stage.
  • Inner partition walls 61 and 62 are provided at the inner back sides of the respective chambers 41 and 42, and the heat absorbers 57 and 58 and fans 63 and 64 are provided in the air flow paths 44 partitioned by the inner partition walls 61 and 62, respectively.
  • the three-way valve 11 is switched in accordance with the thermo-on, thermo-off of the refrigerating operation and the freezing operation so that refrigerant is made to flow into any one of the heat absorbers 57 and 58, and the corresponding fan 62 or 63 is operated.
  • Fig. 11 shows another construction.
  • This construction is different from the construction of Fig. 10 in the construction of the heat absorbing unit 10.
  • the three-way valve is eliminated from the heat absorbing unit 10, however, electric motor operated valves 65 and 66 are connected to the capillary tubes 12 and 13, respectively.
  • Reference numeral 67 represents an electric motor operated valve.
  • the electric motor operated valves 65 and 66 are turned on or off in accordance with the thermo-on or thermo-off of the refrigerating operation and the freezing operation so that refrigerant is made to selectively flow into any one of the heat absorbers 57 and d58, and also the corresponding fan 62 or 63 is driven.
  • the same effect as the embodiment described above can be achieved.
  • carbon dioxide refrigerant is filled in the refrigerant circuit, however, the refrigerant used in the present invention is not limited to carbon dioxide.
  • chlorofluorocarbon (Freon) type refrigerant or the like may be used.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Combustion & Propulsion (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)
  • Separation By Low-Temperature Treatments (AREA)
EP05005499A 2004-03-15 2005-03-14 Kühlapparat Withdrawn EP1577620A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004072853 2004-03-15
JP2004072853A JP2005257236A (ja) 2004-03-15 2004-03-15 冷凍装置

Publications (2)

Publication Number Publication Date
EP1577620A2 true EP1577620A2 (de) 2005-09-21
EP1577620A3 EP1577620A3 (de) 2006-05-17

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP05005499A Withdrawn EP1577620A3 (de) 2004-03-15 2005-03-14 Kühlapparat

Country Status (5)

Country Link
US (1) US20050198978A1 (de)
EP (1) EP1577620A3 (de)
JP (1) JP2005257236A (de)
KR (1) KR100610294B1 (de)
CN (1) CN1321299C (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1577622A2 (de) * 2004-03-19 2005-09-21 SANYO ELECTRIC Co., Ltd. Kältemaschine
WO2016034443A1 (de) * 2014-09-04 2016-03-10 BSH Hausgeräte GmbH Kältegerät und kältemaschine dafür

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US20060147003A1 (en) * 2004-12-30 2006-07-06 Carrier Corporation Remote telephone access control of multiple home comfort systems
JP5446064B2 (ja) * 2006-11-13 2014-03-19 ダイキン工業株式会社 熱交換システム
CN102353204B (zh) * 2011-08-24 2013-09-04 合肥美的电冰箱有限公司 冰箱
KR101940246B1 (ko) * 2012-02-23 2019-04-11 엘지전자 주식회사 냉장고 및 냉장고 제어방법
KR101954198B1 (ko) * 2012-01-25 2019-03-05 엘지전자 주식회사 냉장고
US20130186129A1 (en) * 2012-01-25 2013-07-25 Lg Electronics Inc. Refrigerator
US20150075212A1 (en) * 2013-09-16 2015-03-19 The Coca-Cola Company Carbon Dioxide Refrigeration System with a Multi-Way Valve
TWI526661B (zh) * 2013-12-13 2016-03-21 財團法人工業技術研究院 溫控方法及應用其之溫控系統

Citations (9)

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US5056329A (en) * 1990-06-25 1991-10-15 Battelle Memorial Institute Heat pump systems
EP0541343A1 (de) * 1991-11-04 1993-05-12 General Electric Company Kälteanlagen
JP2000266453A (ja) * 1999-03-12 2000-09-29 Matsushita Refrig Co Ltd 冷蔵庫
JP2000346526A (ja) * 1999-06-10 2000-12-15 Matsushita Refrig Co Ltd 冷却システム
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EP1577620A3 (de) 2006-05-17
KR20060043162A (ko) 2006-05-15
CN1670449A (zh) 2005-09-21
KR100610294B1 (ko) 2006-08-09
JP2005257236A (ja) 2005-09-22
US20050198978A1 (en) 2005-09-15

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