WO2002077544A1 - Systeme de refrigeration - Google Patents

Systeme de refrigeration Download PDF

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Publication number
WO2002077544A1
WO2002077544A1 PCT/JP2002/002734 JP0202734W WO02077544A1 WO 2002077544 A1 WO2002077544 A1 WO 2002077544A1 JP 0202734 W JP0202734 W JP 0202734W WO 02077544 A1 WO02077544 A1 WO 02077544A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
compressor
cooling
refrigerant
refrigeration
Prior art date
Application number
PCT/JP2002/002734
Other languages
English (en)
Japanese (ja)
Inventor
Kenji Tanimoto
Masaaki Takegami
Takeo Ueno
Kazuyoshi Nomura
Akihiro Kajimoto
Original Assignee
Daikin Industries, 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 Daikin Industries, Ltd. filed Critical Daikin Industries, Ltd.
Publication of WO2002077544A1 publication Critical patent/WO2002077544A1/fr

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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
    • F25B13/00—Compression machines, plants or systems, with 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/005—Outdoor unit expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02743—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using three four-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/021—Inverters therefor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present invention relates to a refrigeration apparatus, and more particularly to a refrigeration apparatus provided with an air conditioning heat exchanger and a cooling heat exchanger.
  • a refrigeration system that performs a refrigeration cycle has been known, and is widely used as an air conditioner that cools and heats a room or a refrigerator such as a refrigerator that stores foods and the like. Some of these refrigeration systems perform both air conditioning and refrigeration, as disclosed in WO 98/45651.
  • This type of refrigeration system includes, for example, a plurality of use-side heat exchangers such as an air-conditioning heat exchanger and a refrigeration heat exchanger, and is installed in a convenience store or the like.
  • This refrigeration system can perform both air conditioning in a store and cooling of a showcase, etc., by installing only one refrigeration system.
  • the discharge side of the compressor communicates with the outdoor heat exchanger during cooling of the air-conditioning heat exchanger, while the suction side of the compressor communicates with each of the plurality of use-side heat exchangers.
  • the plurality of use-side heat exchangers commonly communicate with the suction side of the compressor, so that the low-pressure refrigerant pressure is low in any of the use-side heat exchangers.
  • the pressure becomes the same. That is, the evaporation temperature is equal in any of the use side heat exchangers.
  • the COP (coefficient of performance) of the refrigerator was poor. That is, for example, the evaporating temperature required for cooling in an air conditioning heat exchanger is different from the evaporating temperature required for cooling in a refrigerated heat exchanger. Therefore, the evaporation temperature of the air-conditioning heat exchanger is low although it may be higher than the evaporation temperature of the refrigeration heat exchanger. This As a result, there is a problem that the air-conditioning heat exchanger and the refrigeration heat exchanger are not used in an optimal state.
  • the present invention has been made in view of the above points, and has as its object to improve the COP of the entire device. Disclosure of the invention
  • the first invention the first system of the compressor (232) ⁇ beauty second system of compressor (231), the heat source-side heat exchanger (23 3), A refrigerant circuit (220) in which an expansion mechanism (2 (36, 237), an air-conditioning heat exchanger (234) for air-conditioning the room, and a cooling heat exchanger (235) for cooling the inside of the refrigerator are connected and the refrigerant circulates
  • the refrigerant circuit (220) is configured such that the refrigerant evaporates at different temperatures in the air conditioning heat exchanger (234) and the cooling heat exchanger (235).
  • the second invention is directed to a refrigeration system that includes a first-system compressor (232) and a second-system compressor (231) and performs a vapor compression refrigeration cycle.
  • the discharge sides of the first-system compressor (232) and the second-system compressor (231) are connected to one end of a heat-source-side heat exchanger (233) via a high-pressure gas line (221). ing.
  • the other end of the heat source side heat exchanger (233) is connected to one end of an air conditioning heat exchanger (234) for air-conditioning the room and one end of a cooling heat exchanger (235) for cooling the inside of the refrigerator.
  • An expansion mechanism (236, 237) is provided at a branch (222b, 222c) of the liquid line (222).
  • the other end of the air-conditioning heat exchanger (234) is connected to a suction side of a second-system compressor (231) via a second low-pressure gas line (223).
  • the other end of the cooling heat exchanger (235) is connected to the suction side of a first-system compressor (2:32) via a first low-pressure gas line (224).
  • the auxiliary line having an opening / closing mechanism (226) is provided between the first low-pressure gas line (224) and the second low-pressure gas line (223). (225) is connected.
  • the compressor (232) of the first system and the compressor (231) of the second system gun are driven, the compressor (232) of the first system and the second system are driven.
  • the high-pressure refrigerant discharged from the integration of the compressor (231) is merged with high-pressure gas line (2 21) After that, it flows to the heat source side heat exchanger (233) and condenses.
  • the condensed liquid refrigerant flows through the liquid line (222), splits and expands, and then flows to the air conditioning heat exchanger (234) and the cooling heat exchanger (235).
  • the liquid refrigerant evaporates by exchanging heat with room air in the air-conditioning heat exchanger (234), and evaporates by exchanging heat with air in the refrigerator in the cooling heat exchanger (235).
  • the gas refrigerant evaporated in the air conditioning heat exchanger (234) flows through the second low-pressure gas line (223) and returns to the second system compressor (231).
  • the gas refrigerant evaporated in the cooling heat exchanger (235) flows through the first low-pressure gas line (224) and returns to the first system compressor (232). This refrigerant circulation operation is repeated to cool the room and cool the inside of the refrigerator.
  • the gas refrigerant evaporated in the cooling heat exchanger (235) and the gas refrigerant evaporated in the air-conditioning heat exchanger (234) are separately separated from the first system compressor (232) and the second system compressor. Therefore, the low-pressure refrigerant pressure is different between the air-conditioning heat exchanger (234) and the cooling heat exchanger (235).
  • the refrigerant evaporation temperature of the air-conditioning heat exchanger (234) is different from the refrigerant evaporation temperature of the cooling heat exchanger (235), and the refrigerant evaporation temperature of the air-conditioning heat exchanger (234) is high.
  • the evaporator (235) has a low refrigerant evaporation temperature, and so-called two-temperature evaporation is performed.
  • the opening / closing mechanism (226) when the cooling load of the air conditioning heat exchanger (234) is large or the cooling capacity is insufficient, the opening / closing mechanism (226) is opened.
  • the opening / closing mechanism (226) opens, the large capacity first system compressor (232) sucks a part of the refrigerant of the air conditioning heat exchanger (234).
  • the evaporation temperature of the air conditioning heat exchanger (234) decreases, and the cooling capacity of the air conditioning heat exchanger (234) improves.
  • the opening / closing mechanism (226) is opened.
  • the cooling operation of the cooling heat exchanger (235) and the cooling operation of the air conditioning heat exchanger (234) are performed by the first-stage compressor ( 232 ).
  • the opening and closing mechanism (226) is also opened when the first system compressor (232) stops abnormally.
  • the opening and closing mechanism (2 26) is open, the second system of the compressor; cooling operation and is performed in (2 31) Niyotsu Te air conditioning heat exchanger (234) cooling operation and cooling heat exchanger (235) It is.
  • An air conditioning heat exchanger (41) for air-conditioning the inside of the room and a cooling heat exchanger (45) for cooling the inside of the refrigerator are connected to form a refrigerant circuit (1E) in which the refrigerant circulates.
  • the refrigerant circuit (1E) is configured such that the refrigerant discharged from the second-stage compression mechanism (2E) passes through the heat-source-side heat exchanger (4), the expansion mechanism (42), and the air-conditioning heat exchanger (41).
  • a cooling operation that circulates back to the compression system (2E) of the second system in order, and the refrigerant discharged from the compression system (2D) of the first system uses the heat source side heat exchanger (4), the expansion mechanism (46), A refrigeration operation that circulates back to the first system compression mechanism (2D) through the cooling heat exchanger (45) in order, and discharges from the first system compression mechanism (2D) and the second system compression mechanism (2E) after the refrigerant flows the heat source-side heat exchanger (4) and merges, via an expansion mechanism diverted to the air conditioning heat exchanger (41) and the cooling heat exchanger (4 ⁇ ) (4 2, 46 ) flows
  • the first and second compression mechanisms (2D) and (2E) are individually circulated back to reduce the cooling and refrigeration operation at different temperature evaporation. It is configured to Kutomo selectively performed.
  • one end of the air-conditioning heat exchanger (41) is connected to the second system compression mechanism (2D) via a second low-pressure gas line (1M).
  • One end of the cooling heat exchanger (45) is connected to the suction side of the first compression mechanism (2E) via the first low-pressure gas line (1N).
  • An auxiliary line (21) having an opening / closing mechanism (7a, 7b) is connected between the first low-pressure gas line (1M) and the second low-pressure gas line (1N).
  • At least one of the plurality of cooling heat exchangers (45, 51) is configured as a refrigeration heat exchanger (51).
  • the gas side of the freezing heat exchanger (51) is connected to a refrigeration compressor (53) for two-stage compression of the refrigerant using the first-stage compression mechanism (2E) as a high-stage compressor. .
  • the cooling operation, the freezing operation, and the cooling / freezing operation are switched at least. Then, during the cooling / freezing operation, the gas refrigerant evaporated in the air conditioning heat exchanger (41) flows through the second low-pressure gas line (1N) and returns to the second system compression mechanism (1E). The gas refrigerant evaporated in the cooling heat exchanger (45) flows through the first low-pressure gas line (1M) and returns to the first system compression mechanism (1D). This cold The medium circulation operation is repeated to cool the room and cool the inside of the refrigerator.
  • the gas refrigerant evaporated in the air-conditioning heat exchanger (41) and the gas refrigerant evaporated in the cooling heat exchanger (45) are separately separated from the compression mechanism (1E) of the second system. Since the refrigerant is sucked into the compression mechanism (1D) of the first system, the low-pressure refrigerant pressure is different between the air conditioning heat exchanger (41) and the cooling heat exchanger (45). That is, the refrigerant evaporation temperature of the air-conditioning heat exchanger (41) is different from the refrigerant evaporation temperature of the cooling heat exchanger (45), and the refrigerant evaporation temperature of the air-conditioning heat exchanger (41) is high. The refrigerant evaporation temperature of the vessel (45) is low, and so-called two-temperature evaporation operation is performed.
  • the opening / closing mechanism (7b) when the cooling load of the air conditioning heat exchanger (41) is large or the cooling capacity is insufficient, the opening / closing mechanism (7b) is opened.
  • the opening / closing mechanism (7b) opens, the first-system compression mechanism (1D) having a large capacity sucks a part of the refrigerant in the air-conditioning heat exchanger (41).
  • the evaporation temperature of the air-conditioning heat exchanger (41) decreases, and the cooling capacity of the air-conditioning heat exchanger (41) improves.
  • the refrigerant evaporation temperature of the freezing heat exchanger (51) is further lowered.
  • a three-temperature evaporation operation is performed, and an optimum evaporation temperature suitable for the object to be cooled is maintained.
  • the refrigerant is evaporated at different temperatures in the air conditioning heat exchangers (234, 41) and the cooling heat exchangers (235, 45), so that the COP (coefficient of performance) can be improved.
  • Can be it is possible to optimize the evaporating temperature required for cooling in the air conditioning heat exchanger (234, 41) and the evaporating temperature required for cooling in the cooling heat exchanger (235, 45), respectively.
  • C ⁇ P can be improved.
  • the auxiliary line (225, 21) is provided, so that when the cooling capacity is insufficient, the second system compressor (231) or the second compression mechanism ( 1 E) can make up for the lack of cooling capacity. As a result, the comfort can be improved. Further, according to the third invention, if the first system compressor (232) or the second system compressor (231) fails, the other second system compressor (231) or the first system Can be compensated for by the compressor (232), so that a decrease in comfort due to a failure can be suppressed, and damage to products in the refrigerator can be suppressed.
  • FIG. 1 is a circuit diagram showing a refrigerant circuit according to Embodiment 1 of the present invention.
  • FIG. 2 to 25 show Embodiment 2 of the present invention
  • FIG. 2 is a circuit diagram showing a refrigerant circuit.
  • FIG. 3 is a refrigerant circuit diagram showing a refrigerant flow during the cooling operation.
  • FIG. 4 is a refrigerant circuit diagram showing a refrigerant flow during a refrigeration operation.
  • FIG. 5 is a refrigerant circuit diagram showing a refrigerant flow during the first cooling and freezing operation.
  • FIG. 6 is a refrigerant circuit diagram showing a refrigerant flow during the second cooling and freezing operation.
  • FIG. 7 is a refrigerant circuit diagram showing a refrigerant flow during the heating operation.
  • FIG. 8 is a refrigerant circuit diagram illustrating a refrigerant flow during the first heating and refrigeration operation.
  • FIG. 9 is a refrigerant circuit diagram illustrating a refrigerant flow during the second heating and refrigeration operation.
  • FIG. 10 is a refrigerant circuit diagram showing a refrigerant flow during the third heating / refrigeration operation (part 1).
  • FIG. 11 is a refrigerant circuit diagram showing a refrigerant flow during the third heating / refrigeration operation (part 2).
  • FIG. 12 is a control flowchart showing operation switching in the cooling mode.
  • FIG. 13 is a control flowchart showing capacity control during cooling operation.
  • Fig. 14 is a performance characteristic diagram showing the change characteristics of compressor capacity during cooling operation.
  • FIG. 15 is a control flowchart showing the capacity control during the refrigeration operation.
  • Figure 16 is a performance characteristic diagram showing the change characteristics of compressor capacity during refrigeration operation.
  • FIG. 17 is a Mollier chart showing refrigerant behavior during the first cooling and refrigeration operation.
  • Fig. 18 is a control diagram showing the operation switching between the first cooling and freezing operation and the first cooling and freezing operation.
  • FIG. 19 is a control flowchart showing operation switching in the heating mode.
  • FIG. 20 is a control flowchart showing control of the compressor capacity during the heating operation.
  • FIG. 21 is a control flowchart showing capacity control during the first heating and refrigeration operation.
  • FIG. 22 is a control flowchart showing capacity control during the second heating and refrigeration operation.
  • FIG. 23 is a control flowchart showing the capacity control in the third heating and refrigeration operation 1.
  • FIG. 24 is a control flow chart showing the capacity control in the third heating and refrigeration operation No. 2.
  • FIG. 25 is a control flowchart showing operation switching in the heating mode.
  • FIG. 26 shows a third embodiment of the present invention and is a circuit diagram illustrating a main part of a refrigerant circuit. BEST MODE FOR CARRYING OUT THE INVENTION
  • a refrigeration apparatus (210) As shown in FIG. 1, a refrigeration apparatus (210) according to the present embodiment is provided in a convenience store, and performs both cooling of a showcase and cooling of a store.
  • the refrigeration apparatus (210) includes a refrigerant circuit (220) for performing a vapor compression refrigeration cycle.
  • the refrigerant circuit (220) includes two systems of a first system, one first compressor (232) and a second system, one second compressor (231). It has an exchanger (233) and a plurality of utilization side heat exchangers of an air conditioning heat exchanger (234) and a cooling heat exchanger (23 ⁇ ).
  • Both the first compressor (232) and the second compressor (231) are hermetic, high-pressure dome-type scroll compressors.
  • the first compressor (232) and the second compressor (231) each include a compression means and an electric motor for driving the compression means housed in a cylindrical housing.
  • the first compressor (232) and the second compressor (231) are configured as variable capacity compressors in which the number of revolutions of the electric motor changes stepwise or continuously.
  • the discharge sides of the first compressor (232) and the second compressor (231) are connected to a high-pressure gas pipe (221), which is a single high-pressure gas line.
  • the high-pressure gas pipe (221) is connected to the gas side end of the outdoor heat exchanger (233).
  • the outdoor heat exchanger (233) is a heat source-side heat exchanger, and is constituted by a cross-fin type fin-and-tube heat exchanger.
  • the outdoor heat exchanger (233) is configured to exchange heat between the refrigerant circulating in the refrigerant circuit (220) and the outdoor air.
  • the outdoor heat exchanger (233) is provided with an outdoor fan (233F).
  • the liquid side end of the outdoor heat exchanger (233) is connected to a liquid pipe (222) which is a liquid line.
  • the liquid pipe (222) is composed of a main pipe (222a) and two branch pipes (222b, 222c). One end of the main pipe (222a) is connected to the liquid end of the outdoor heat exchanger (233), and two branch pipes (222b, 222c) are connected to the other end of the main pipe (222a). Have been.
  • the one branch pipe (222b) is connected to the liquid-side end of the air conditioning heat exchanger (234), and the other branch pipe (222c) is connected to the liquid-side end of the cooling heat exchanger (235). ing.
  • Each of the branch pipes (222b, 222c) is provided with an expansion valve (236, 237) as an expansion mechanism.
  • the air-conditioning heat exchanger (234) is a use-side heat exchanger that cools a room in a convenience store, and is composed of a cross-fin type fin 'and' tube type heat exchanger.
  • the air conditioning heat exchanger (234) is configured to exchange heat between the refrigerant circulating in the refrigerant circuit (220) and the indoor air in the store.
  • the air conditioning heat exchanger (234) is provided with an air conditioning fan (234F).
  • the cooling heat exchanger (235) is a use-side heat exchanger that cools the interior of the convenience store showcase, and is composed of a cross-fin type fin-and-tube heat exchanger. ing.
  • the cooling heat exchanger (235) is configured to exchange heat between the refrigerant circulating in the refrigerant circuit (220) and the inside air which is the air inside the showcase.
  • the cooling heat exchanger (235) is provided with a cooling fan (235F).
  • first low-pressure gas pipe (224) is connected, while the gas-side end of the air-conditioning heat exchanger (234) is connected to one end of a second low-pressure gas pipe (222) as a second low-pressure gas line. Is connected.
  • the other end of the first low-pressure gas pipe (224) is connected to the suction side of the first compressor (232), and the other end of the second low-pressure gas pipe (223) is connected to the second compressor (231). Connected to suction side. That is, the air conditioning heat exchanger (234) and the cooling heat exchanger (235) are separately connected to the low pressure side of the second compressor (231) and the low pressure side of the first compressor (232), respectively.
  • the low pressure refrigerant pressure is configured to be different.
  • the first compressor (2; 32) and the second compressor (2) are set so that the evaporation temperature of the air-conditioning heat exchanger (234) is high and the evaporation temperature of the cooling heat exchanger (235) is low. : 31) is driven, the refrigerant circuit (220), the refrigerant is adapted to different temperature evaporated in the air conditioning heat exchanger (2 3 4) cooling heat exchanger (23Deruta).
  • An auxiliary gas pipe (225) as an auxiliary line is connected between the first low-pressure gas pipe (224) and the second low-pressure gas pipe (223).
  • the auxiliary gas pipe (225) is provided with an opening / closing valve (226) as an opening / closing mechanism.
  • the on-off valve (226) is normally closed, but if the cooling capacity of the air conditioning heat exchanger (234) is insufficient, or if the second compressor (231) or the first compressor (232) is abnormal. It is configured to open when stopped by.
  • the first compressor (232) and the second compressor (231) are both driven.
  • the high-pressure refrigerant discharged from the first compressor (2; 32) and the second compressor (231) joins in the high-pressure gas pipe (221), flows into the outdoor heat exchanger (233), and is connected to the outdoor air. Exchanges heat and condenses.
  • the condensed liquid refrigerant flows through the liquid pipe (222), branches into the branch pipes (222b, 222c), expands with the expansion valves (236, 237), and then expands with the air-conditioning heat exchanger (234) and the cooling heat exchanger. (235).
  • the cooling heat exchanger (235) heat is exchanged with the air inside the showcase to evaporate.
  • the gas refrigerant evaporated in the air conditioning heat exchanger (234) flows through the second low-pressure gas pipe (223) and returns to the second compressor (231).
  • the gas refrigerant evaporated in the cooling heat exchanger (235) flows through the first low-pressure gas pipe (224) and returns to the first compressor (232).
  • the gas refrigerant evaporated in the air-conditioning heat exchanger (234) and the gas refrigerant evaporated in the cooling heat exchanger (235) are separately separated into a second compressor (231) and a first compressor ( 232), the low-pressure refrigerant pressure is different between the air-conditioning heat exchanger ( 234 ) and the cooling heat exchanger (235). That is, the capacity of the second compressor (231) is small, and the capacity of the first compressor (232) is large.
  • the refrigerant evaporation temperature of the air-conditioning heat exchanger (234) is different from the refrigerant evaporation temperature of the cooling heat exchanger (235), and the refrigerant evaporation temperature of the air-conditioning heat exchanger (234) is high.
  • the evaporator (235) has a low refrigerant evaporation temperature, and so-called two-temperature evaporation is performed.
  • the on-off valve (226) is opened.
  • the first compressor (232) having a large capacity sucks a part of the refrigerant in the air conditioning heat exchanger (234).
  • the evaporation temperature of the air-conditioning heat exchanger (234) decreases, and the cooling capacity of the air-conditioning heat exchanger (234) improves.
  • the on-off valve (226) is opened.
  • the cooling operation of the cooling heat exchanger (235) and the cooling operation of the air conditioning heat exchanger (234) are performed by one first compressor (232).
  • the on-off valve (226) is also opened when the first compressor (232) stops abnormally. This on-off valve
  • the first compressor (232) is stopped and only the second compressor (2 (31) is driven.
  • the cooling heat exchanger ( 235) The expansion valve (237) is closed and the on-off valve (226) is closed.
  • the high-pressure refrigerant discharged from the second compressor (231) flows to the outdoor heat exchanger (233), exchanges heat with outdoor air, and condenses.
  • the condensed liquid refrigerant flows through the liquid pipe (222), expands at the expansion valve (236), and then flows to the air conditioning heat exchanger (234).
  • the air-conditioning heat exchanger (234) exchanges heat with room air in the store to evaporate, flows through the second low-pressure gas pipe (223), and returns to the second compressor (231). This refrigerant circulation operation is repeated.
  • the second compressor (231) When performing only the cooling operation of the cooling heat exchanger (235), the second compressor (231) is stopped and only the first compressor (232) is driven. At that time, the closing air conditioning heat exchanger (2 34) of the expansion valve (236), on-off valve (226) is closed.
  • the high-pressure medium discharged from the first compressor (232) flows to the outdoor heat exchanger (233) and exchanges heat with outdoor air to condense.
  • the condensed liquid refrigerant flows through the liquid pipe (222), expands at the expansion valve (237), and then flows to the cooling heat exchanger (235).
  • the cooling heat exchanger (235) the refrigerant exchanges heat with the air inside the showcase and evaporates, and returns to the first compressor (232) through the first low-pressure gas pipe (22). Repeat.
  • the COP coefficient of performance
  • the evaporating temperature required for cooling in the air-conditioning heat exchanger (234) and the evaporating temperature required for cooling in the refrigerated heat exchanger can be optimally set. it can.
  • the refrigeration apparatus (1) is provided in a convenience store, and is for cooling a showcase in a refrigerator and cooling and heating a store in a room.
  • the refrigerating apparatus (1) includes an outdoor unit (1A), an indoor unit (1B), a refrigeration unit (1C), and a refrigeration unit (1D), and performs a vapor compression refrigeration cycle. Circuit (1E).
  • the refrigerant circuit (1E) is configured to switch between a cooling cycle and a heating cycle.
  • the indoor unit (1B) is configured to switch between a cooling operation and a heating operation, and is installed, for example, at a sales floor.
  • the refrigeration unit (1C) is installed in a refrigeration showcase to cool the air inside the showcase.
  • the refrigeration unit (1D) is installed in a refrigeration showcase to cool the air inside the showcase.
  • the outdoor unit (1'A) has a non-inverter compressor (2 ⁇ ), a first invertor compressor (2 ⁇ ), and a second inverer compressor (2C). It has a switching valve (3 ⁇ ), a second four-way switching valve (3 ⁇ ), and an outdoor heat exchanger (4) as a heat source side heat exchanger.
  • Each of the above compressors (2 ⁇ , 2 ⁇ , 2C) is composed of, for example, a closed high-pressure dome-type scroll compressor.
  • the above-mentioned non-inverter compressor (2 ⁇ ) is of a fixed displacement type in which the motor is always driven at a constant speed.
  • the above-mentioned first inverter-in-compressor (2) and second inverter-in-compressor (2C) are configured such that the electric motor is controlled in-inverter and the capacity can be varied stepwise or continuously. .
  • the above-mentioned non-inverter compressor (2 ⁇ ), the first invar evening compressor (2 ⁇ ), and the second invar evening compressor (2C) are composed of the first system compression mechanism (2D) and the second It constitutes the system compression mechanism (2 ⁇ ). That is, the non-inverter compressor (2 ⁇ ) and the first invertor compressor (2 ⁇ ) constitute the first system compression mechanism (2D), and the second invertor compressor (2C) constitutes the second system.
  • the compression mechanism (2E) may be configured.
  • the present invention includes a first-stage compressor and a second-system compressor.
  • the Non'inba Isseki compressor (2A), the discharge pipe of the first inverter evening compressor (2B) and the second I Nba Isseki compressor (2C) (5 a, 5b , 5c) is one of high-pressure gas pipe connected to (8), the high-pressure gas pipe (8) is connected to one port of the first four-way switching valve (3 a).
  • a check valve (7) is provided in the discharge pipe (5a) of the non-inverter compressor (2A) and the discharge pipe (5c) of the second inverter compressor (2C).
  • the gas side end of the outdoor heat exchanger (4) is connected to one port of the first four-way switching valve (3A) by an outdoor gas pipe (9).
  • One end of a liquid pipe (10), which is a liquid line, is connected to the liquid side end of the outdoor heat exchanger (4).
  • a receiver (14) is provided in the middle of the liquid pipe (10), and the other end of the liquid pipe (10) is branched into a first communication liquid pipe (11) and a second communication liquid pipe (12). ing.
  • the outdoor heat exchanger (4) is, for example, a cross-fin type fin-and-tube heat exchanger, and an outdoor fan (4F), which is a heat source fan, is arranged in close proximity.
  • Each intake pipe of the non-inverting evening compressor (2A) and the first inverter evening compressor (2 B) (ea, 6b) are connected to the low-pressure gas pipe (1 5).
  • the suction pipe (6c) of the second invar compressor (2C) is connected to one port of the second four-way switching valve (3B).
  • a communication gas pipe (17) is connected to one port of the first four-way switching valve (3A).
  • One port of the first four-way switching valve (3A) is connected to one port of the second four-way switching valve (3B) by a connection pipe (18).
  • 1 Tsunopo Ichito the second four-way switching valve (3 B) is connected to the discharge pipe (5 second inverter evening compressor (2C) by an auxiliary gas pipe (19).
  • the first One port of the two-way four-way switching valve (3B) is configured as a closed closed port, that is, the second four-way switching valve (3B) may be a three-way switching valve.
  • the high pressure gas pipe (8) and the outdoor gas pipe (9) are connected to the first four-way switching valve (3A).
  • the first state (see the solid line in FIG. 1) in which the connecting pipe (18) communicates with the connecting gas pipe (17), and the high-pressure gas pipe (8) communicates with the connecting gas pipe (17) and is connected It is configured to switch to the second state (see the broken line in FIG. 1) in which the pipe (18) communicates with the outdoor gas pipe (9).
  • the second four-way switching valve (3B) is connected to the auxiliary gas pipe (19) and the closing port, and is connected to the connection pipe (18) and the suction pipe (6c) of the second inverter compressor (2C).
  • the first state (see the solid line in FIG. 1) where the connection pipe communicates with the auxiliary gas pipe (19) and the connection pipe (18), and the second state where the connection pipe (18) communicates with the blocking port (see FIG. 1). (See the broken line).
  • the low-pressure gas pipe (15) and each suction pipe (6a, 6b) of the first system compression mechanism (2D) constitute the first low-pressure gas line (1M).
  • the connecting gas pipe (17) and the suction pipe (6c) of the second system compression mechanism (2E) constitute the second low-pressure gas line (1N) during the cooling operation.
  • the first connecting liquid pipe (11), the second connecting liquid pipe (12), the connecting gas pipe (17) and the low-pressure gas pipe (15) are extended from the outdoor unit (1A) to the outside, and are connected to the outdoor unit (1A).
  • ) Are provided with shut-off valves (20) respectively.
  • a check valve at the branch end of the second communication liquid pipe (12) is provided in the outdoor unit (1A), and the refrigerant flows from the receiver (14) toward the shutoff valve (20). It is configured as follows.
  • the communication pipe (21) enables the suction sides of the non-inverting compressor (2A), the first inverting compressor (2B), and the second inverting compressor (2C) to communicate with each other.
  • It said communicating pipe (21) is provided with a main pipe (2 2) and the first auxiliary pipe (23) and a second auxiliary pipe which is branched from the main pipe (22) (24).
  • the main pipe (22) is connected to a suction pipe (ec) of the second invertor compressor (2C).
  • the first sub-tube (2 3 ) and the second sub-tube (2) are connected to a low-pressure gas pipe (15).
  • the first sub-tube (23) and the second sub-tube (24) are provided with solenoid valves (7a, 7b) as opening / closing mechanisms. And a check valve (7) are provided. That is, the first sub-tube (23) is connected to the non-inverter compressor (2A) of the first system compression mechanism (2D) or the second system compression mechanism (2E) from the first invertor compressor (2B). It is configured so that the refrigerant flows toward the second inverter compressor (2C).
  • the second sub-pipe (24) is connected from the second inversion compressor (2C), which is the second compression mechanism (2E), to the non-inverter compressor (2A), which is the first compression mechanism (2D). The refrigerant is configured to flow toward the first inverter compressor (2B).
  • An auxiliary liquid pipe (25) that bypasses the receiver (14) is connected to the liquid pipe (10).
  • the auxiliary liquid pipe (25) is provided with an outdoor expansion valve (26) as an expansion mechanism, through which a refrigerant mainly flows during heating.
  • a check valve (7) is provided between the outdoor heat exchanger (4) and the receiver (14) in the liquid pipe (10) to allow only the refrigerant flow toward the receiver (14).
  • the check valve (7) is located between the connection of the auxiliary liquid pipe (25) in the liquid pipe (10) and the receiver (14).
  • a liquid injection pipe (2a) is connected between the auxiliary liquid pipe (25) and the low-pressure gas pipe (15).
  • the liquid injection pipe (27) is provided with a solenoid valve (7C).
  • a degassing pipe (2 ⁇ ) is connected between the upper part of the receiver (14) and the discharge pipe (5a) of the non-inverter compressor (2A).
  • the gas vent pipe (28) is provided with a check valve (7) that allows only the coolant flow from the receiver (14) to the discharge pipe ().
  • the high-pressure gas pipe (8) is provided with an oil separator ( 3 mm). One end of an oil return pipe (31) is connected to the oil separator (30). The oil return pipe ( 31 ) is provided with a solenoid valve (7d), and the other end is connected to the suction pipe (6a) of the non-inverter compressor (2A).
  • a first oil leveling pipe (32) is connected between the dome of the non-inverter compressor (2A) and the suction pipe (6c) of the second inverter-night compressor (2C).
  • the first oil equalizing pipe (32) is provided with a check valve (7) for permitting oil flow from the non-inverter overnight compressor (2A) to the second invertor compressor (2C) and a solenoid valve (7e). Is provided.
  • a second oil leveling pipe (33) is connected to the dome of the first invar compressor (2B).
  • the other end of the second oil leveling pipe (33) is the check valve of the first oil leveling pipe (32). It is connected between (7) and the solenoid valve (7e).
  • a third oil equalizing pipe (34) is connected between the dome of the second Invar evening compressor (2C) and the low-pressure gas pipe (15).
  • the third oil leveling pipe (34) is provided with a solenoid valve (7f).
  • a floor heating circuit (35) is connected to the liquid pipe (10).
  • the floor heating circuit (35) includes a floor heating heat exchanger (36), a first pipe (37), and a second pipe (38).
  • One end of the first pipe (37) is connected between the check valve (7) and the closing valve (20) in the first communication liquid pipe (11), and the other end is a floor heating heat exchanger (36). It is connected to the.
  • One end of the second pipe (38) is connected between the check valve (7) and the receiver (14) in the liquid pipe (10), and the other end is connected to the floor heating heat exchanger (36).
  • the floor heating heat exchanger (36) is located at a cash register (a cash payment place), where clerks work for a long time in a convenience store.
  • the first pipe (37) and the second pipe (38) are provided with a shut-off valve (20), and the first pipe (37) is connected to the floor heating heat exchanger (36).
  • a check valve (7) is provided to allow only the refrigerant flow. If the floor heating heat exchanger (36) is not provided, the first pipe (37) and the second pipe (38) are directly connected.
  • the indoor unit (1B) includes an indoor heat exchanger (41) as a use-side heat exchanger and an indoor expansion valve (42) as an expansion mechanism.
  • the gas side of the indoor heat exchanger (41) is connected to a communication gas pipe (17).
  • the liquid side of the indoor heat exchanger (41) is connected to a second communication liquid pipe (12) via an indoor expansion valve (42).
  • the indoor heat exchanger (41) is, for example, a cross-fin type fin 'and' tube type heat exchanger, and an indoor fan (43), which is a use-side fan, is arranged in close proximity.
  • the refrigeration unit (1C) includes a refrigeration heat exchanger (4 ⁇ ) as a cooling heat exchanger and a refrigeration expansion valve (46) as an expansion mechanism.
  • the liquid side of the refrigeration heat exchanger (45) is connected to a first communication liquid pipe (11) via a solenoid valve (7) and a refrigeration expansion valve (46).
  • a low-pressure gas pipe (15) is connected to the gas side of the refrigeration heat exchanger (45).
  • the refrigeration heat exchanger (45) communicates with the suction side of the compression system (2D) of the first system, while the indoor heat exchanger (41) communicates with the second invertor compressor (2C) during cooling operation. To the suction side.
  • the refrigerant pressure (evaporation pressure) of the refrigeration heat exchanger (45) becomes lower than the refrigerant pressure (evaporation pressure) of the indoor heat exchanger (41).
  • the refrigerant evaporation temperature of the refrigeration heat exchanger (45) is, for example, 10 ° C
  • the refrigerant evaporation temperature of the indoor heat exchanger (41) is, for example, + 5 ° C.
  • Circuit (1E) constitutes the circuit for different temperature evaporation.
  • the refrigeration expansion valve (46) is a temperature-sensitive expansion valve, and a temperature-sensitive cylinder is attached to the gas side of the refrigeration heat exchanger (45).
  • the refrigerating heat exchanger (45) is, for example, a cross-fin type fin-and-tube heat exchanger, and a refrigerating fan (47), which is a cooling fan, is arranged in close proximity.
  • the refrigeration unit (1D) includes a refrigeration heat exchanger (51) as a cooling heat exchanger, a refrigeration expansion valve (52) as an expansion mechanism, and a booster compressor ( 53 ) as a refrigeration compressor. ing. On the liquid side of the refrigeration heat exchanger (51), a branch liquid pipe (13) branched from the first communication liquid pipe (11) is connected via a solenoid valve (7h) and a refrigeration expansion valve (52). .
  • the gas side of the refrigerating heat exchanger (51) and the suction side of the booth compressor (53) are connected by a connecting gas pipe (54).
  • a branch gas pipe (16) branched from the low pressure gas pipe (15) is connected to the discharge side of the booth compressor (53).
  • the branch gas pipe (16) is provided with a check valve (7) and an oil separator (55). Between the Oirusepare Isseki () and the connecting gas pipe (5 4), the oil return pipe having Kiyabirari tube (56) (57) it is connected.
  • the above-mentioned booth mixer (53) is connected to the first system compression mechanism (2D) so that the refrigerant evaporation temperature of the refrigeration heat exchanger (51) is lower than the refrigerant evaporation temperature of the refrigeration heat exchanger (45). Is compressing the refrigerant in two stages.
  • the refrigerant evaporation temperature of the refrigeration heat exchanger (51) is set to, for example, ⁇ 40 ° C.
  • the refrigeration expansion valve (52) is a temperature-sensitive expansion valve, and a temperature-sensitive cylinder is attached to the gas side of the refrigeration heat exchanger (45).
  • the above refrigeration heat exchanger (51) For example, it is a cross-fin type fin 'and' tube type heat exchanger, and a refrigeration fan (58), which is a cooling fan, is arranged in close proximity.
  • the check valve (7) of the connecting gas pipe (54) on the suction side of the booth compressor (53) and the branch gas pipe (16) on the discharge side of the bus compressor (53) are also connected.
  • a bypass pipe (59) having a check valve (7) is connected to the downstream side.
  • the bypass pipe (59) is configured to allow the refrigerant to flow by bypassing the booth compressor (53) when the booster compressor (53) is stopped due to a failure or the like.
  • the refrigerant circuit (1E) is provided with various sensors and various switches.
  • the high-pressure gas pipe (8) of the outdoor unit (1A) has a high-pressure pressure sensor (61) as pressure detection means for detecting high-pressure refrigerant pressure, and a discharge temperature as a temperature detection means for detecting high-pressure refrigerant temperature. And a sensor (62).
  • the discharge pipe (5c) of the second invertor compressor (2C) is provided with a discharge temperature sensor (63) as temperature detecting means for detecting the high-pressure refrigerant temperature.
  • the high-pressure refrigerant pressure is supplied to the discharge pipes (5a, 5b, 5c) of the non-inverter compressor (2A), the first inverter compressor (2B) and the second inverter compressor (2C).
  • a pressure switch (64) is provided that opens when a predetermined value is reached.
  • the suction pipes (6b, 6c) of the first invar compressor (2B) and the second invar compressor (2C) have low-pressure pressure sensors (pressure-detecting means) for detecting low-pressure refrigerant pressure.
  • pressure-detecting means pressure-detecting means
  • 65, 66 and a suction temperature sensor (67, 68) as a temperature detecting means for detecting the low-pressure refrigerant temperature.
  • the outdoor heat exchanger (4) is provided with an outdoor heat exchange sensor (69) as temperature detecting means for detecting an evaporation temperature or a condensation temperature as a refrigerant temperature in the outdoor heat exchanger (4). Further, the outdoor unit (1A) is provided with an outside air temperature sensor (70) as temperature detecting means for detecting the outdoor air temperature.
  • the indoor heat exchanger (41) is provided with an indoor heat exchange sensor (71) as temperature detecting means for detecting a condensation temperature or an evaporation temperature, which is a refrigerant temperature in the indoor heat exchanger (41).
  • a gas temperature sensor (72) as temperature detecting means for detecting a gas refrigerant temperature is provided on the side.
  • the indoor unit (1B) A room temperature sensor (73) is provided as temperature detecting means for detecting the air temperature.
  • the refrigeration unit (1C) is provided with a refrigeration temperature sensor (74) as temperature detecting means for detecting the temperature in the refrigerator inside the refrigeration showcase.
  • the refrigeration unit (1D) is provided with a refrigeration temperature sensor (75), which is a temperature detection means for detecting the temperature inside the refrigerator in the freezer showcase.
  • the second pipe (38) of the floor heating circuit (35) is provided with a liquid temperature sensor (76) as temperature detecting means for detecting a refrigerant temperature after flowing through the floor heating heat exchanger (36). ing.
  • the output signals of the various sensors and switches are input to the controller (80).
  • the controller (80) is configured to control the capacity of the first inverter compressor (2B) and the second inverter compressor (2C).
  • controller (80) controls the operation of the refrigerant circuit (1E), and controls the cooling operation, the freezing operation, the first cooling / freezing operation, the second cooling / freezing operation, the heating operation, the first heating / cooling operation, and the first cooling / freezing operation. It is configured to control by switching between the second heating and freezing operation and the third heating and freezing operation.
  • the cooling mode is switched to one of a cooling operation, a freezing operation, a first cooling / freezing operation, and a second cooling / freezing operation.
  • step ST1 it is determined whether or not the condition 1 that the low-pressure refrigerant pressure detected by the low-pressure pressure sensors (65, 66) is higher than 98 kPa while the air-conditioning thermostat is ON. .
  • step ST2 it is determined whether or not the condition 2 that the air conditioner is ON and the low-pressure refrigerant pressure is lower than 98 kPa is satisfied.
  • step ST3 it is determined whether or not the condition 3 that the low-pressure refrigerant pressure is higher than 98 kPa is satisfied in the state of the air conditioning system at 0FF.
  • the air conditioner N is a state in which the refrigerant evaporates in the indoor heat exchanger (41) to perform a cooling operation, and the air conditioner OFF is referred to as an indoor expansion valve (42). Is closed and the refrigerant is indoor heat exchanger (41) does not flow, and the indoor fan (43) is driven to stop the cooling operation.
  • step ST1 When the operation in the cooling mode is started, first, the determination in step ST1 is performed. When the condition 1 of step ST1 is satisfied, the process proceeds to step ST4, in which a first cooling / freezing operation for performing cooling, refrigeration, and freezing or a second cooling / refrigerating operation is performed and returns. If the condition 1 of step ST1 is not satisfied and the condition 2 of step ST2 is satisfied, the process proceeds to step ST5, performs the cooling operation, and returns. If condition 2 of step ST2 is not satisfied and condition 3 of step ST3 is satisfied, the process proceeds to step ST6, performs the freezing operation, and returns. If condition 3 of step ST 3 is not satisfied, the operation is continued and the operation returns.
  • This cooling operation is an operation that only cools the indoor unit (1B).
  • the non-inverter overnight compressor (2A) forms the first system compression mechanism (2D), and the first invertor overnight compressor (2B) and the second invertor compressor (2B).
  • the evening compressor (2C) constitutes the second system compression mechanism (2E). Then, only the first invar overnight compressor (2B) and the second invar overnight compressor (2C), which are the above-described second-system compression mechanisms (2E), are driven.
  • first four-way switching valve (3A) and the second four-way switching valve (3B) switch to the first state, respectively, as shown by the solid lines in FIG.
  • the solenoid valve (7b) of the second sub pipe (24) of the communication pipe (21) is opened, while the solenoid valve (7a) of the first sub pipe (23) of the communication pipe (21) and the outdoor expansion valve are opened.
  • the solenoid valve (7g) of the refrigeration unit (1C) and the solenoid valve (7h) of the refrigeration unit OD) are closed.
  • the refrigerant discharged from the first inverter compressor (2B) and the second inverter compressor (2C) passes through the outdoor gas pipe (9) from the first four-way switching valve (3A) and passes through the outdoor gas pipe (9). It flows to the heat exchanger (4) and condenses.
  • the condensed liquid refrigerant flows through the liquid pipe (10), flows through the receiver (14), flows through the second connecting liquid pipe (12), flows through the indoor expansion valve (42), and flows into the indoor heat exchanger (41). Evaporate.
  • Evaporated gas refrigerant is connected to the gas pipe (17) From the first four-way switching valve (3A) and the second through the four-way switch valve (3B) second inverter Yu ⁇ compressor suction pipe (2 ⁇ ) to (6c) flows, first inverter evening compressor (2B ) And return to the second inverter compressor (2C). This circulation is repeated to cool the interior of the store.
  • a part of the low-pressure gas refrigerant is diverted from the suction pipe (6c) of the second inverter compressor (2C) to the communication pipe (21), and is diverted from the second sub pipe (24) to the first inverter compressor. People on the plane (2B) 0 0
  • step ST11 it is determined whether or not the condition 1 that the room temperature Tr detected by the room temperature sensor (73) is higher than the temperature obtained by adding 3 ° C to the set temperature Tset is satisfied.
  • step ST12 it is determined whether or not the condition 2 that the room temperature Tr is lower than the set temperature Tset is satisfied.
  • step ST11 the process proceeds to step ST13, in which the capacity of the first chamber overnight compressor (2B) or the second chamber overnight compressor (2C) is increased. To return. If the condition 1 in step ST11 above is not satisfied and the condition 2 in step ST12 is satisfied, the process proceeds to step ST14, where the first inverter—the evening compressor (2B) or the second inverter Increase the capacity of the compressor (2C) and return. If the condition 2 of step ST12 is not satisfied, the current compressor capacity is satisfied, so the routine returns and the above operation is repeated.
  • the control for increasing the compressor capacity is performed by first raising the first inverter compressor (2B) from the stopped state to the minimum capacity (see point A), and then starting with the first inverter. While maintaining the overnight compressor (2B) at the minimum capacity, drive the second invar overnight compressor (2C) from a stopped state to increase the capacity. Then, when the load further increases, the capacity of the 1st inverter-evening compressor (2B) is increased while the second inverter-compressor (2C) is maintained at the maximum capacity (see point B).
  • the control for decreasing the compressor capacity is the reverse of the above-described increase control.
  • the degree of opening of the indoor expansion valve (42) is controlled based on the detected temperatures of the indoor heat exchange sensor (71) and the gas temperature sensor (72), and is the same in the cooling mode hereinafter. ⁇ Refrigeration operation>
  • This refrigeration operation is an operation that only cools the refrigeration unit (1C) and the refrigeration unit (1D).
  • the non-inverter compressor (2A) and the first invertor compressor (2B) constitute a first system compression mechanism (2D), and the second invertor compressor (2D).
  • the compressor (2C) forms the second system compression mechanism (2E).
  • the booth evening compressor (53) is also driven. You.
  • the first four-way switching valve (3A) switches to the first state as shown by the solid line in FIG. Furthermore, the solenoid valve (7g) of the refrigeration unit (1C) and the solenoid valve (7h) of the refrigeration unit (1D) are opened, while the two solenoid valves (7a, 7b) of the communication pipe (21) and the chamber are opened. The outer expansion valve (26) and the indoor expansion valve (42) are closed.
  • the refrigerant discharged from the non-inverter overnight compressor (2A) and the first invertor compressor (2B) is subjected to outdoor heat exchange from the first four-way switching valve (3A) via the outdoor gas pipe (9). It flows into the vessel (4) and condenses.
  • the condensed liquid refrigerant flows through the liquid pipe (10), flows through the receiver (14), flows through the first connecting liquid pipe (11), and partially passes through the refrigeration expansion valve (46) to the refrigeration heat exchanger (45). Flow and evaporate.
  • the refrigerant pressure in the refrigerating heat exchanger (51) is suctioned by the booth compressor (53), and is lower than the refrigerant pressure in the refrigerating heat exchanger (45).
  • the refrigerant temperature (evaporation temperature) in the refrigeration heat exchanger (51) becomes ⁇ 40 ° C.
  • the refrigerant temperature (evaporation temperature) in the refrigeration heat exchanger (45) Is 1 o ° c.
  • step ST21 it is determined whether or not the condition 1 that the low pressure refrigerant pressure LP detected by the low pressure pressure sensors (65, 66) is higher than 392 kPa is satisfied.
  • step ST22 it is determined whether or not the condition 2 that the low-pressure coolant pressure LP is lower than 245 kPa is satisfied.
  • step ST21 If the condition 1 of step ST21 is satisfied, the process proceeds to step ST23, in which the capacity of the first inverter / night compressor (2B) or the non-inverter / night compressor (2A) is increased and the routine returns. . If the condition 1 of step ST21 above is not satisfied and the condition 2 of step ST22 is satisfied, the process proceeds to step ST24, where the first invar overnight compressor (2B) or non-inverter compression is performed. (2A) and return. If the condition 2 of step ST22 is not satisfied, the current compressor capacity is satisfied, so the routine returns and the above operation is repeated.
  • the control for increasing the compressor capacity is as follows. First, the first inverter compressor (2B) is driven with the non-inverter compressor (2A) stopped (see point A). , Increase capacity. After the first Invar evening compressor (2B) rises to its maximum capacity (see point B), if the load further increases, the non-invertor evening compressor (2A) is driven and the first Invar evening compressor is simultaneously operated. (2B) to the minimum capacity (see point C). Thereafter, when the load further increases, the capacity of the first inverter compressor (2B) is increased.
  • the control for decreasing the compressor capacity is the reverse of the above-described increase control.
  • the degree of opening of the refrigeration expansion valve (46) and the refrigerating expansion valve (52) is controlled by a temperature-sensitive cylinder, and is the same for each operation.
  • This first cooling / freezing operation is an operation in which cooling of the indoor unit (1B) and cooling of the refrigeration unit (1C) and the refrigeration unit (1D) are performed simultaneously.
  • the non-inverter overnight compressor (2A) and the first invar overnight compressor (2B) constitute the first system compression mechanism (2D)
  • the second inverter compressor (2C) forms the second system compression mechanism (2E).
  • the above non-inver evening It drives the compressor (2A), the first Inver / Earth compressor (2B) and the second Inver / Earth compressor (2C), and also drives the booth and evening compressor (53).
  • first four-way switching valve (3A) and the second four-way switching valve (3B) switch to the first state, respectively, as shown by the solid lines in FIG. Furthermore, the solenoid valve (7g) of the refrigeration unit (1C) and the solenoid valve (7h) of the refrigeration unit (1D) are opened, while the two solenoid valves (7a, 7b) of the communication pipe (21) and The outdoor expansion valve (26) is closed.
  • the refrigerant discharged from the non-inverting compressor (2A), the first inverting compressor (2B), and the second inverting compressor (2C) merge in the high-pressure gas pipe (8), It flows from the four-way switching valve (3A) to the outdoor heat exchanger (4) via the outdoor gas pipe (9), and condenses.
  • the condensed liquid refrigerant flows through the liquid pipe (10), passes through the receiver (14), and flows into the first connecting liquid pipe (11) and the second connecting liquid pipe (12).
  • the liquid refrigerant flowing through the second communication liquid pipe (12) flows through the indoor expansion valve (42) to the indoor heat exchanger (41) and evaporates.
  • Evaporated gas refrigerant is contacted gas pipe (17) or al first four-way switch valve (3A) and the second four-way selector valve (3 B) suction pipe via () a flow second inverter evening compressor ( Return to 2C).
  • a part of the liquid refrigerant flowing through the first communication liquid pipe (11) flows through the refrigeration expansion valve (46) to the refrigeration heat exchanger (45) and evaporates.
  • the other liquid refrigerant flowing through the first communication liquid pipe (11) flows through the branch liquid pipe (13), flows through the refrigeration expansion valve (52), flows into the refrigeration heat exchanger (51), and evaporates.
  • Gas refrigerant evaporated in the freezing heat exchanger (5 1) is compressed is sucked into the booth evening compressor (53), it is discharged to the branch gas pipe (16).
  • This circulation is repeated to cool the inside of the store, which is indoors, and at the same time, cool the inside of the refrigerator, which is a showcase for refrigeration and a case for freezing.
  • the refrigerant is compressed to the point A by the second invar overnight compressor (2C). Ma Further, the refrigerant is compressed to the point B by the non-inverter overnight compressor (2A) and the first invertime compressor (2B). The refrigerant at point A and the refrigerant at point B merge and condense to become the refrigerant at point C. Part of the refrigerant at point C is decompressed to point D by the indoor expansion valve (42), evaporates at, for example, + 5 ° C, and is sucked into the second inverter compressor (2C) at point E.
  • the indoor expansion valve 42
  • a part of the refrigerant at the point C is decompressed to the point F by the refrigeration expansion valve (46).
  • the refrigerant evaporates at ⁇ 10 ° C.
  • a part of the refrigerant at point C is sucked by the booth compressor (53), so the pressure is reduced to point H by the refrigerating expansion valve (52). At this point, it is sucked into the booth compressor (53).
  • the refrigerant compressed to point J by the booth compressor (53) is sucked into the non-inverter overnight compressor (2A) and the first invertor compressor (2B) at point G.
  • the refrigerant in the refrigerant circuit (1E) is evaporated at different temperatures by the first-stage compression mechanism (2D) and the second-system compression mechanism (2E), and further evaporated by the booster compressor (53).
  • Three types of evaporation temperatures are achieved by stage compression.
  • the second cooling / refrigerating operation is an operation when the cooling capacity of the indoor unit (1B) during the first cooling / refrigerating operation is insufficient.
  • the second cooling / freezing operation is basically the same as that of the first cooling / freezing operation, but the solenoid valve of the second auxiliary pipe (24) in the communication pipe (21) is used. (7b) is different from the first cooling / refrigeration operation in that it is opened.
  • the non-invertor evening compressor (2A), the first invar evening compressor (2B), and the second invar-evening compressor (2C) refrigerant discharged from, condensed in the outdoor heat exchanger (4), evaporated in the indoor heat exchange exchanger (41) and the cold storage heat exchanger (45) and the freezing heat exchanger (5 1).
  • the refrigerant evaporated in the indoor heat exchanger (41) returns to the second inverter evening compressor (2C), evaporated in the refrigerating heat exchanger (4Deruta) and the freezing heat exchanger (5 1) refrigerant, It returns to the non-inverter overnight compressor (2A) and the first invertor compressor (2B).
  • the second auxiliary pipe (24) in the communication pipe (21) is in communication, the above indoor heat exchange
  • the refrigerant pressure of the compressor (41) is increased by the non-inverter compressor (2A) and the first invertor.
  • the pressure drops to the suction pressure of the evening compressor (2B).
  • the evaporation temperature of the indoor heat exchanger (41) decreases, and the lack of cooling capacity is compensated.
  • step ST31 it is determined whether the solenoid valve (7) of the second sub pipe (24) is closed, and the solenoid valve (7) of the second sub pipe (24) is closed. If there is, the process proceeds to step ST32, and the first cooling and refrigeration operation described above is executed. Thereafter, four determinations of steps ST33 to ST36 are performed.
  • step ST33 it is determined whether or not the condition 1 that the room temperature Tr is higher than the temperature obtained by adding 3 ° C to the set temperature Tset is satisfied.
  • step ST34 it is determined whether or not the condition 2 that the first invar compressor (2B) is operated at the maximum capacity (maximum frequency) is satisfied.
  • step ST35 it is determined whether or not the condition 3 that the capacity of the non-inverted overnight compressor (2A) and the first inverted overnight compressor (2B) is not the maximum is satisfied.
  • step ST37 where the solenoid valve (7b) of the second sub pipe (24) is opened, Switch to the second cooling / freezing operation. That is, in this case, since the cooling capacity is insufficient, the evaporation temperature of the indoor heat exchanger (41) is reduced.
  • Step ST41 it is determined whether or not the condition 5 that the room temperature Tr is higher than the temperature obtained by adding 3 ° C to the set temperature Tset is satisfied.
  • step ST 4 Move to 3 to increase the capacity of the first-stage compression mechanism (2D) of the non-inverter overnight compressor (2A) and the first invertor compressor (2B). If the condition of step ST41 is satisfied 6, the process proceeds to step ST44, where the first-stage compression mechanism of the non-inverter compressor (2A) and the first inverter compressor (2B) is used. Decrease 2D) ability.
  • step ST45 determines whether or not the low-pressure refrigerant pressure is lower than 245 kPa.
  • the heating mode is switched to any one of the heating operation, the freezing operation, the first heating / freezing operation, the second heating / freezing operation, and the third heating / freezing operation.
  • step ST51 it is determined whether or not the condition 1 that the low-pressure refrigerant pressure detected by the low-pressure pressure sensors (65, 66) is higher than 98 kPa in the state of the air conditioning thermostat ON.
  • step ST52 it is determined whether or not the condition 2 that the condition of the air conditioner is ON and the low-pressure refrigerant pressure is lower than 98 kPa is satisfied.
  • step ST53 it is determined whether or not the condition 3 that the low-pressure refrigerant pressure is higher than 98 kPa is satisfied in the state of the air conditioning system 0FF.
  • thermo ON means the state where the refrigerant is condensed in the indoor heat exchanger (41) and the heating operation is being performed
  • air conditioning thermo OFF means that the indoor expansion valve (42) is closed. A state in which the refrigerant does not flow through the indoor heat exchanger (41) and the indoor fan (43) is driven to suspend the heating operation.
  • step ST51 When the operation in the heating mode is started, first, the determination in step ST51 is performed. And, if the condition 1 of the step ST 51 is satisfied, the step The process proceeds to ST54 where the first heating / freezing operation or the second heating / freezing operation, which is the heating mode 1, is performed, and the process returns. If the condition 1 in step S ⁇ 51 is not satisfied and the condition 2 in step S ⁇ 52 is satisfied, the process proceeds to step ST55 to perform the heating operation or the third heating / freezing operation and return. If the condition 2 of step S ⁇ 53 is not satisfied and the condition 3 of step S ⁇ 53 is satisfied, the process proceeds to step ST56, performs refrigeration operation, and returns. If condition 3 of step S S53 is not satisfied, the operation continues as it is and returns.
  • the refrigeration operation is the same as the refrigeration operation in the cooling mode.
  • This heating operation is an operation that only heats the indoor unit (1 mm) and the floor heating circuit (35). During this heating operation, as shown in Fig. 7, the non-inverter compressor
  • the first four-way switching valve (3 ⁇ ) switches to the second state as shown by the solid line in FIG. 7, and the second four-way switching valve (3 ⁇ ) as shown by the solid line in FIG. Switch to the first state.
  • the solenoid valve (7b) of the second sub pipe (24) of the communication pipe (21) is opened, while the solenoid valve (7a) of the first sub pipe (23) of the communication pipe (21) is opened.
  • the refrigerant discharged from the first inverter compressor (2B) and the second inverter compressor (2C) flows from the first four-way switching valve (3A) through the communication gas pipe (17) to the indoor heat source. It flows to the exchanger (41) and condenses. The condensed liquid refrigerant flows into the second connecting liquid pipe.
  • step ST61 it is determined whether or not the condition 1 that the room temperature Tr detected by the room temperature sensor (73) is higher than the temperature obtained by adding 3 ° C to the set temperature Tset is satisfied.
  • step ST62 it is determined whether or not the condition 2 that the room temperature Tr is lower than the set temperature Tset is satisfied.
  • Step ST 6 When they meet the condition 1 of step ST 6 1, the routine goes to Step ST 6 3, increasing the capacity of the first Inba Isseki compressor (2 B) or second Inba Isseki compressor (2C) And return. If the condition 1 in step ST61 above is not satisfied and the condition 2 in step ST62 is satisfied, the process proceeds to step ST64, where the first inverter—the second compressor (2B) or the second inverter is used. Increase the capacity of the compressor (2C) and return. If the condition 2 of step ST62 is not satisfied, the current compressor capacity is satisfied, so the routine returns and the above operation is repeated. The compressor capacity increase / decrease control is performed as shown in FIG.
  • the degree of opening of the outdoor expansion valve (26) is controlled by the superheat degree based on the saturation temperature corresponding to the pressure based on the low-pressure pressure sensors ( 65 , 66) and the temperature detected by the suction temperature sensors (67, 68).
  • the degree of opening of the indoor expansion valve (42) is supercooled based on the temperatures detected by the indoor heat exchange sensor (71) and the liquid temperature sensor (76). In particular, since the refrigerant temperature after flowing out of the floor heating heat exchanger (36) is used, a predetermined floor heating capacity is maintained.
  • the opening control of the outdoor expansion valve (26) and the indoor expansion valve (42) is the same in the heating mode hereinafter. .
  • This first heating and refrigeration operation is a heat recovery operation that heats the indoor unit (1B) and cools the refrigeration unit (1C) and the refrigeration unit (1D) without using the outdoor heat exchanger (4). It is.
  • the non-inverter overnight compressor (2A) and the first inverter compressor (2B) constitute a first system compression mechanism (2D).
  • the invertor compressor (2C) constitutes the second system compression mechanism (2E). Then, the above-described non-inverter evening compressor (2A) and the first invar evening evening compressor (2B) are driven, and the booth evening compressor (53) is also driven. The above-mentioned No. 2 Invar evening compressor (2C) is stopped.
  • the first four-way switching valve (3A) switches to the second state as shown by the solid line in FIG. 8 and the second four-way switching valve (3B) as shown by the solid line in FIG. Switch to the first state. Furthermore, the solenoid valve (() of the refrigeration unit (1C) and the solenoid valve (7h) of the refrigeration unit (1D) are open, while the two solenoid valves (7a, 7b) of the communication pipe (21) and the outdoor unit are open. Expansion valve (26) is closed.
  • the refrigerant discharged from the non-inverting and evening compressors (2A) and the first inverting and evening compressor (2B) exchanges indoor heat via the connecting gas pipe (17) from the first four-way switching valve (3A). It flows into the vessel (41) and condenses.
  • the condensed liquid refrigerant flows from the second connecting liquid pipe (12) to the floor heating circuit (35), and from the floor heating heat exchanger (36) to the first connecting liquid pipe (11) via the receiver (14). .
  • the gas refrigerant evaporated in the refrigerating heat exchanger (51) is sucked by the booth compressor (53), compressed, and discharged to the branch gas pipe (16).
  • This cycle is repeated to heat the interior of the store and heat the floor, and at the same time, cool the inside of the refrigerator, which is a showcase for refrigeration and a showcase for freezing.
  • the cooling capacity (evaporative heat) of the refrigeration unit (1C) and the refrigeration unit (1D) and the heating capacity (condensed heat) of the indoor unit (1B) and the floor heating circuit (35) balance. 100% heat recovery is performed.
  • the compressor capacity during the first heating and refrigeration operation is controlled as shown in Fig. 21. In this control, the following four decisions are made.
  • step ST71 the room temperature Tr detected by the room temperature sensor (73) is lower than the temperature obtained by subtracting 3 ° C from the set temperature Tset, and the low-pressure refrigerant pressure LP detected by the low-pressure pressure sensors (65, 66). It is determined whether or not the condition 1 that the pressure is higher than 392 kPa is satisfied.
  • step ST72 it is determined whether or not the condition 2 that the room temperature Tr is lower than the temperature obtained by subtracting 3 ° C from the set temperature Tset and the low-pressure refrigerant pressure LP is lower than 245 kPa is satisfied.
  • step ST73 it is determined whether or not the condition 3 that the indoor temperature Tr is higher than the set temperature Tset and the low-pressure refrigerant pressure LP is higher than 392 kPa is satisfied.
  • step ST74 it is determined whether or not the condition 4 that the indoor temperature Tr is higher than the set temperature Tset and the low-pressure refrigerant pressure LP is lower than 245 kPa is satisfied.
  • step ST71 If the condition 1 of step ST71 is satisfied, the process proceeds to step ST75, in which the capacity of the first invar overnight compressor (2B) or the non-invar evening compressor (2A) is increased, and then the process returns. . If the condition 1 of step ST71 is not satisfied and the condition 2 of step ST72 is satisfied, the process proceeds to step ST76, and the third heating / refrigerating operation described later, that is, the operation of insufficient heating capacity is performed. And return. If the condition 2 of step ST72 is not satisfied and the condition 3 of step ST73 is satisfied, the process proceeds to step ST77, and the second heating / refrigeration operation described later, that is, an operation having excess heating capacity is performed. And return.
  • step ST78 the first invar overnight compressor (2B) or the non-inverter compressor is used. (2A) Improve the ability and return. If the condition 4 of step ST74 is not satisfied, the current compression function is satisfied, so the routine returns and the above operation is repeated.
  • the compressor capacity increase / decrease control is performed as shown in FIG.
  • the second heating / refrigeration operation is an excessive heating operation in which the heating capacity of the indoor unit (1B) is excessive during the first heating / refrigeration operation.
  • the second time heating freezing operation as shown in FIG. 9, to constitute a non-inverting evening compressor (2A) and the first inverter evening compressor (2 B) and the first system compression mechanism (2D), 2nd Inver Evening Compressor (2C) is the 2nd system Constructs the gun compression mechanism (2E). Then, the non-inverter overnight compressor (2A) and the first invar evening compressor (2B) are driven, and the booth evening compressor (53) is also driven. The above-mentioned No. 2 invar overnight compressor (2C) is stopped.
  • This second heating and refrigeration operation is an operation when the heating capacity is excessive during the first heating and refrigeration operation, and the second four-way switching valve (3B) is connected to the second heating and refrigeration operation as shown by the solid line in FIG. This is the same as the first heating and refrigeration operation except that the state is switched to
  • a part of the refrigerant discharged from the non-inverter and evening compressor (2A) and the first invertor and evening compressor (2B) flows into the indoor heat exchanger (41) and condenses as in the first heating and refrigeration operation. .
  • the condensed liquid refrigerant flows through the floor heating circuit (35), and flows from the floor heating heat exchanger (36) to the liquid pipe (10).
  • the other refrigerant discharged from the non-inverting compressor (2A) and the first inverting compressor (2B) is supplied from the auxiliary gas pipe (19) to the second four-way switching valve (3B) and the first four-way switching valve (3B).
  • the cooling capacity (the amount of heat of evaporation) between the refrigerating unit (1C) and the freezing unit (1D) and the heating capacity (the amount of heat of condensation) of the indoor unit (1B) and the floor heating circuit (35)
  • the surplus heat of condensation is released outside the room by the outdoor heat exchanger (4) without a bump.
  • the compressor capacity and outdoor fan (4F) air volume during the second heating and refrigeration operation are controlled as shown in FIG. 22, and the following four determinations are made.
  • step ST81 the room temperature Tr detected by the room temperature sensor (73) is lower than the temperature obtained by subtracting 3 ° C from the set temperature Tset, and the low-pressure pressure sensor (65, 66) It is determined whether or not the condition 1 that the low-pressure refrigerant pressure LP detected by is higher than 392 kPa is satisfied.
  • step ST82 it is determined whether or not the condition 2 that the indoor temperature Tr is lower than the temperature obtained by subtracting 3 ° C from the set temperature Tset and the low-pressure refrigerant pressure LP is lower than 245 kPa is satisfied.
  • step ST83 it is determined whether or not the condition 3 that the indoor temperature Tr is higher than the set temperature Tset and the low-pressure refrigerant pressure LP is higher than 392 kPa is satisfied.
  • step ST84 it is determined whether or not the condition 4 that the indoor temperature Tr is higher than the set temperature Tset and the low-pressure refrigerant pressure LP is lower than 245 kPa is satisfied.
  • step ST81 If the condition 1 of step ST81 is satisfied, the process proceeds to step ST85, in which the capacity of the No. 1 overnight compressor (2B) or the non-inverter overnight compressor (2A) is increased, and the flow returns. . If the condition 1 of step ST81 is not satisfied and the condition 2 of step ST82 is satisfied, the process proceeds to step ST86, in which the flow rate of the outdoor fan (4F) is reduced and the process returns. In other words, since the heating capacity is not enough, the amount of heat condensed in the outdoor heat exchanger (4) is given to the indoor heat exchanger (41). If the condition 2 in step ST83 is not satisfied and the condition 3 in step ST83 is satisfied, the process proceeds to step ST87, in which the air flow of the outdoor fan (4F) is increased and the process returns. .
  • step ST83 the process proceeds to step ST88, where the first invertor compressor (2B) or the non-inverter compressor ( Reduce the ability of 2A) and return. If condition 4 of step ST84 is not satisfied, the current compression function is satisfied, so the routine returns and the above operation is repeated.
  • the compressor capacity increase / decrease control is performed as shown in FIG.
  • the third heating and refrigeration operation is a heating capacity shortage operation in which the heating capacity of the indoor unit (1B) is insufficient during the first heating and refrigeration operation.
  • one mode of this third heating and refrigeration operation is that the non-inverter evening compressor (2A) and the first invar evening compressor (2B) have the first system compression mechanism (2D). And the second chamber overnight compressor (2C) forms the second system compression mechanism (2E). And the above non-invar overnight compressor (2A) and the 1st room overnight compressor (2B) are driven, and the booth evening compressor (53) is also driven. The above-mentioned No. 2 Invar evening compressor (2C) is stopped.
  • the third heating and refrigeration operation is an operation when the heating capacity is insufficient during the first heating and refrigeration operation, that is, when the amount of evaporative heat is insufficient, and the second subcooling operation of the communication pipe (21) is performed. Except that the solenoid valve (7b) in the pipe (24) is open, it is the same as the above-mentioned first heating and refrigeration operation.
  • the refrigerant discharged from Non'inba Isseki compressor (2 A) and the first inverter Isseki compressor (2B) is condensed is flow in the first heating freezing operation as well as the indoor heat exchanger (41) .
  • the condensed liquid refrigerant flows through the floor heating circuit (35), and flows from the floor heating heat exchanger (36) to the receiver (14).
  • the other liquid refrigerant from the receiver (14) flows through the liquid pipe (10) to the outdoor heat exchanger (4) and evaporates.
  • the evaporated gas refrigerant flows through the outdoor gas pipe (9), passes through the first four-way switching valve (3A) and the second four-way switching valve (3B), and enters the suction pipe (6c) of the second inverter compressor (2C). ).
  • the gas refrigerant flows into the low-pressure gas pipe (15) via the second sub pipe (24) of the communication pipe (21), and flows from the refrigeration unit (1C) and the refrigeration unit (1D). And return to the non-inver evening compressor (2A) and the first inver evening compressor (2B).
  • the interior of the store is heated and the floor is heated, and at the same time, the interior of the refrigerator, which is a showcase for cooling and a showcase for freezing, is cooled.
  • the cooling capacity (the amount of heat of evaporation) between the refrigerating unit (1C) and the freezing unit (1D) and the heating capacity (the amount of condensing heat) of the indoor unit (1B) and the floor heating circuit (35). Insufficient heat of evaporation is obtained from the outdoor heat exchanger (4) without ban- lance.
  • step ST91 the room temperature Tr detected by the room temperature sensor (73) is lower than the temperature obtained by subtracting 3 ° C from the set temperature Tset, and the low-pressure refrigerant pressure LP detected by the low-pressure pressure sensors (65, 66). It is determined whether or not the condition 1 that the pressure is higher than 392 kPa is satisfied.
  • step ST92 it is determined whether or not the condition 2 that the room temperature Tr is lower than the temperature obtained by subtracting 3 ° C from the set temperature Tset and the low-pressure refrigerant pressure LP is lower than 245 kPa is satisfied.
  • step ST93 it is determined whether or not the condition 3 that the indoor temperature Tr is higher than the set temperature Tset and the low-pressure refrigerant pressure LP is higher than 3922 kPa is satisfied.
  • step ST94 it is determined whether or not the condition 4 that the indoor temperature Tr is higher than the set temperature Tset and the low-pressure refrigerant pressure LP is lower than 245 kPa is satisfied.
  • step ST95 in which the capacity of the first inverter / night compressor (2B) or the non-inverter / night compressor (2A) is increased and the routine returns.
  • step ST96 since the heating capacity is likely to be insufficient, the third heating and refrigeration described later is performed. Switch to operation 2 and return.
  • step ST97 where the air flow of the outdoor fan (4F) is reduced and the process returns.
  • step ST98 the first invertor compressor (2B) or the non-inverter compressor ( 2A) and return. If the condition 4 of step ST94 is not satisfied, the current compression function is satisfied, so the routine returns and the above operation is repeated.
  • the compressor capacity increase / decrease control is performed as shown in FIG.
  • the second heating and refrigeration operation 2 is another mode of the third heating and refrigeration operation, and is an operation for driving the second member overnight compressor (2C).
  • the non-inverter compressor (2A) and the first invar compressor (2B) constitute a first-system compression mechanism (2D).
  • the second Invar overnight compressor (2C) is the second Configure the system compression mechanism (2E).
  • the non-inverter compressor (2A), the first invar evening compressor (2B) and the second invar evening compressor (2C) are driven, and the booth evening compressor (53) is also driven.
  • the second heating / refrigeration operation 2 is an operation in the case where the heating capacity is insufficient in the third heating / refrigeration operation 1 described above, that is, the operation when the amount of evaporative heat is insufficient. solenoid valve is closed in the second auxiliary pipe (2 4), other points second inverter evening compressor (2C) is driven, to be the same as one of the third heating freezing operation.
  • the refrigerant discharged from the non-invar overnight compressor (2A), the first invar overnight compressor (2B), and the second invar evening compressor (2C) passes through the communication gas pipe (17) and passes through the indoor heat exchanger ( 41) and condenses.
  • the condensed liquid refrigerant flows through the floor heating circuit (35), and flows from the floor heating heat exchanger (36) to the receiver (14).
  • the other liquid refrigerant from the receiver (14) flows through the liquid pipe (10) to the outdoor heat exchanger ( 4 ) and evaporates.
  • the evaporated gas refrigerant flows through the outdoor gas pipe (9), passes through the first four-way switching valve (3A) and the second four-way switching valve (3B), flows through the suction pipe (6c), and then passes through the second inverter compressor. Return to (2C).
  • the interior of the store is heated and the floor is heated, and at the same time, the interior of the refrigerator, which is a showcase for cooling and a showcase for freezing, is cooled.
  • the cooling capacity (evaporative heat) of the refrigeration unit (1C) and the refrigeration unit (1D) and the heating capacity (condensed heat) of the indoor unit (1B) and the floor heating circuit (35) are balanced.
  • Insufficient heat of evaporation is obtained from the outdoor heat exchanger ( 4 ).
  • the non-inverter overnight compressor (2A), the first inverter compressor (2B) and the second inverter compressor (2C) are driven to secure the heating capacity.
  • the compressor capacity and the outdoor fan (4F) air volume in the second heating / refrigeration operation 2 are controlled as shown in FIG. 24, and the following four determinations are made.
  • step ST101 the room temperature Tr detected by the room temperature sensor (73) is lower than the temperature obtained by subtracting 3 ° C from the set temperature Tset, and the low-pressure pressure sensor
  • step ST102 it is determined whether or not the condition 1 that the low-pressure refrigerant pressure LP detected by (65, 66) is higher than 392 kPa is satisfied.
  • step ST102 it is determined whether or not the condition 2 that the indoor temperature Tr is lower than the temperature obtained by subtracting 3 ° C from the set temperature Tset and the low-pressure refrigerant pressure LP is lower than 245 kPa is satisfied.
  • step ST103 it is determined whether or not the condition 3 that the indoor temperature Tr is higher than the set temperature Tset and the low-pressure refrigerant pressure LP is higher than 392 kPa is satisfied.
  • step ST104 it is determined whether or not the condition 4 that the indoor temperature Tr is higher than the set temperature Tset and the low-pressure refrigerant pressure LP is lower than 245 kPa is satisfied.
  • step ST105 in which the capacity of the second member overnight compressor (2C) is increased and the first member overnight compressor (2C) is increased. (2B) or raise the capacity of the non-inverter compressor (2A) and return. If the condition 1 of step ST101 is not satisfied and the condition 2 of step ST102 is satisfied, the process proceeds to step ST106 and the refrigeration unit (1C) and the refrigeration unit ( 1) Since the capacity of D) is too low, the capacity of the second inverter compressor (2C) is increased while the capacity of the second inverter compressor (2C) is increased.
  • step ST102 Lower ability and return. If the condition 2 of step ST102 is not satisfied and the condition 3 of step ST103 is satisfied, the process moves to step ST107 and the refrigeration unit (1C) and the refrigeration unit (1D) ), The capacity of the 2nd Invar evening compressor (2C) is reduced while the 1st Invar evening compressor is reduced.
  • step ST103 or increase the capacity of the non-inverter overnight compressor (2A) and return. If the condition 3 of step ST103 is not satisfied and the condition 4 of step ST104 is satisfied, the process proceeds to step ST108, and the capacity of the 2nd chamber overnight compressor (2C) And the capacity of the No. 1 invertor overnight compressor (2B) or non-inverter overnight compressor (2A) is returned. If the condition 4 of step ST104 is not satisfied, the current compression function is satisfied, and the routine returns. repeat.
  • step ST111 it is determined whether or not the condition 1 that the high-pressure refrigerant pressure HP is higher than 2664 kPa is satisfied.
  • this condition 1 is satisfied, the high pressure refrigerant pressure is high and the current heating capacity is large, and the process proceeds to step ST112 to determine whether or not the outdoor heat exchanger (4) is an evaporator.
  • step ST1 12 If the outdoor heat exchanger (4) is an evaporator, for example, if the state is 1 in the third heating / freezing operation, the process proceeds from step ST1 12 to step ST1 13 and the outdoor fan (4F Judgment is made as to whether the air volume of) is minimum. If the airflow of the outdoor fan (4F) is the lowest, the process proceeds from step ST113 to step ST114, and switches to the second heating / refrigeration operation and returns.
  • step ST115 the airflow of the outdoor fan (4F) is reduced and the process returns.
  • step ST116 the process proceeds to step ST116 to determine whether or not the air flow of the outdoor fan (4F) is maximum. When the air flow of the outdoor fan (4F) is the maximum, the process moves from step ST116 to step ST117 to reduce the compression function and return. On the other hand, if the airflow of the outdoor fan (4F) is not the maximum in step ST116, the process proceeds to step ST118, and the airflow of the outdoor fan (4F) is increased and the operation is resumed.
  • step ST111 If the condition 1 of step ST111 is not satisfied, the process moves to step ST121, and it is determined whether or not the condition 2 that the high-pressure refrigerant pressure HP is lower than 196 kPa is satisfied. When this condition 2 is satisfied, the high pressure refrigerant pressure is low and the current heating capacity is low, and the process proceeds to step ST122 to determine whether or not the outdoor heat exchanger (4) is a condenser.
  • step ST122 determines whether the air flow rate of the outdoor fan (4F) is minimum. If the air flow of the outdoor fan (4F) is the minimum, the process moves from step ST123 to step ST124, and switches to the first heating / freezing operation and returns. If the air flow rate of the outdoor fan (4F) is not the lowest in step ST123, the process proceeds to step ST125, where the airflow rate of the outdoor fan (4F) is reduced and the process returns.
  • the switching to the first heating / freezing operation or the second heating / refrigerating operation is performed by the above switching.
  • a refrigerant recovery operation is performed in the refrigeration operation and the first heating refrigeration operation described above. That is, in FIG. 8, since the liquid refrigerant may accumulate in the outdoor heat exchanger (4) and the outdoor gas pipe (9), the solenoid valve (7b) in the second sub pipe (24) of the communication pipe (21) Open for a few minutes, or drive the second invar overnight compressor (2C) for a predetermined time to collect the excess refrigerant.
  • the refrigerant is evaporated at a different temperature during the first cooling and refrigeration operation, so that the COP (coefficient of performance) can be improved.
  • the evaporation temperature required for cooling in the indoor heat exchanger (41) and the evaporation temperature required for cooling in the refrigeration heat exchanger (45) can be optimized respectively, so that C 0 P is improved. be able to.
  • the second system compression mechanism (2E) can make up for the insufficient cooling capacity. As a result, comfort can be improved.
  • the first system compression mechanism (2D) or the second system compression mechanism (2E) is In the event of a failure, they can compensate for each other, so that a reduction in comfort due to the failure can be suppressed, and damage to the products in the showcase can be suppressed.
  • a four-way switching valve (91) is provided in place of the solenoid valves (7a, 7b) of the communication pipe (21) of the second embodiment. 'That is, two check valves (7, 7) are respectively provided in the first sub-tube (23) and the second sub-tube (24) of the communication pipe (21). Then, one port of the four-way switching valve (91) is connected between the two check valves (7, 7) in the first auxiliary pipe through the first passageway (9 2) (3) I have.
  • the other one port of the four-way switching valve (91) is connected between the two check valves (7, 7) in the second auxiliary pipe (24) via the second passage (93). .
  • Another one port of the four-way switching valve (91) is connected to a gas vent pipe (28) via a third passage (94).
  • the remaining one port of the four-way switching valve (91) is configured as a closed closed port. That is, the four-way switching valve (91) may be a three-way switching valve.
  • the four-way switching valve (91) is switched to the solid line state in FIG. 26, and the first passage (92) And the second passage (93).
  • the gas refrigerant in the suction pipe (6c) of the second inverter compressor (2C) flows from the first sub pipe (23) through the first passage (92), passes through the four-way switching valve (91), It flows to the two passages (93), and to the low-pressure gas pipe (15) via the second auxiliary pipe (24).
  • the four-way switching valve (91) When the refrigerant flows from the first system compression mechanism (2D) to the second system compression mechanism (2E), the four-way switching valve (91) is switched to the solid state shown in FIG. when the second passage (93) and P in this case for communicating the gas ⁇ of the low-pressure gas pipe (15) flows through the first passage from the first auxiliary pipe (23) (92), four-way selector valve (91 ), Flows into the second passage (93), and flows through the second sub pipe (24) to the suction pipe (6 c) of the second invar compressor (2 C).
  • the four-way switching valve (91) When shutting off the suction side of the first system compression mechanism (2D) and the suction side of the second system compression mechanism (2E), the four-way switching valve (91) is switched to the broken line state in FIG.
  • the first passage (92) is connected to the third passage (94), and the second passage (93) is connected to the closing port.
  • Other configurations, operations, and effects are the same as those of the first embodiment. Another embodiment of the invention
  • the present invention includes a plurality of air conditioning heat exchanger (234 ) May be provided, or a plurality of cooling heat exchangers (23 ⁇ ) may be provided. That is, a plurality of air conditioning heat exchangers (234) may be connected in parallel with each other, or a plurality of cooling heat exchangers (23 ⁇ ) may be connected in parallel with each other.
  • a plurality of the first compressors (231) and the second compressors (232) may be provided. That is, two or more first-stage compressors (231) for operating one or more air-conditioning heat exchangers (234) may be provided. Further, two or more second-system compressors (232) for operating one or more cooling heat exchangers (235) may be provided.
  • one air-conditioning heat exchanger (41), one cooling heat exchanger (45), and one refrigeration heat exchanger (51) are provided.
  • the present invention may include a plurality of air conditioning heat exchangers (45), a plurality of cooling heat exchangers (45), and a plurality of refrigeration heat exchangers.
  • An exchange (51) may be provided. That is, a plurality of air conditioning heat exchangers (41) may be connected in parallel with each other, or a plurality of refrigeration heat exchangers (45) may be connected in parallel with each other. Alternatively, a plurality of refrigerating heat exchangers (51) may be connected in parallel with each other.
  • cooling and heating are performed.
  • the present invention may be such that only the operation in the cooling mode is performed.
  • Industrial applicability As described above, the refrigeration apparatus according to the present invention is useful for cooling a showcase or the like, and is particularly suitable for simultaneous cooling of a showcase and indoor air conditioning.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

Cette invention concerne un système de réfrigération comprenant un premier compresseur (232) et un second compresseur (231) reliés, sur leur côté décharge, à une extrémité d'un échangeur de chaleur (233) avec l'extérieur par l'intermédiaire d'un tuyau pour gaz haute pression (221). L'autre extrémité de l'échangeur de chaleur (233) avec l'extérieur est raccordé à une extrémité d'un échangeur de chaleur (234) pour la climatisation d'un local et à une extrémité d'un échangeur de chaleur (235) pour le refroidissement d'un compartiment via un tuyau pour liquide (222). On trouve des soupapes de détente dans les tronçons de raccordement (222b, 222c) du tuyau pour liquide (222). L'autre extrémité de l'échangeur de chaleur (234) pour la climatisation est relié au côté aspiration du second compresseur (231) par l'intermédiaire d'un second tuyau pour gaz basse pression (223). A l'opposé, l'autre extrémité de l'échangeur de chaleur (235) pour le refroidissement est relié au côté aspiration du premier compresseur (232) via un premier tuyau pour gaz basse pression (224). L'évaporation du réfrigérant se fait à des températures différentes dans l'échangeur de chaleur (234) pour la climatisation et dans l'échangeur de chaleur (235)thermique pour le refroidissement.
PCT/JP2002/002734 2001-03-23 2002-03-22 Systeme de refrigeration WO2002077544A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2001-084272 2001-03-23
JP2001084272 2001-03-23
JP2001-164780 2001-05-31
JP2001164780A JP3855683B2 (ja) 2001-03-23 2001-05-31 冷凍装置

Publications (1)

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WO2002077544A1 true WO2002077544A1 (fr) 2002-10-03

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PCT/JP2002/002734 WO2002077544A1 (fr) 2001-03-23 2002-03-22 Systeme de refrigeration

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JP (1) JP3855683B2 (fr)
WO (1) WO2002077544A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100432436C (zh) 2003-07-28 2008-11-12 大金工业株式会社 冷冻装置
JP4073376B2 (ja) * 2003-07-31 2008-04-09 三洋電機株式会社 冷凍システム及び冷凍システムの制御方法
JP2007051788A (ja) * 2005-08-15 2007-03-01 Daikin Ind Ltd 冷凍装置
JP5194884B2 (ja) * 2008-02-29 2013-05-08 ダイキン工業株式会社 冷凍装置
JP2009228996A (ja) * 2008-03-24 2009-10-08 Fuji Electric Retail Systems Co Ltd 冷却システム

Citations (5)

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Publication number Priority date Publication date Assignee Title
JPS6160346B2 (fr) * 1980-05-13 1986-12-20 Nakano Reiki Kk
JPS6227817Y2 (fr) * 1981-12-22 1987-07-16
JPH062447B2 (ja) * 1985-04-29 1994-01-12 日本電装株式会社 冷凍車用冷凍冷房装置
JPH06221698A (ja) * 1993-01-26 1994-08-12 Sanyo Electric Co Ltd 冷凍装置
JPH0783520A (ja) * 1993-09-16 1995-03-28 Hitachi Ltd 空気調和機

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0711365B2 (ja) * 1986-04-03 1995-02-08 日本電装株式会社 冷房冷蔵装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6160346B2 (fr) * 1980-05-13 1986-12-20 Nakano Reiki Kk
JPS6227817Y2 (fr) * 1981-12-22 1987-07-16
JPH062447B2 (ja) * 1985-04-29 1994-01-12 日本電装株式会社 冷凍車用冷凍冷房装置
JPH06221698A (ja) * 1993-01-26 1994-08-12 Sanyo Electric Co Ltd 冷凍装置
JPH0783520A (ja) * 1993-09-16 1995-03-28 Hitachi Ltd 空気調和機

Also Published As

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JP2002349980A (ja) 2002-12-04
JP3855683B2 (ja) 2006-12-13

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