WO2002099343A1 - Dispositif frigorifique - Google Patents

Dispositif frigorifique Download PDF

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Publication number
WO2002099343A1
WO2002099343A1 PCT/JP2002/003233 JP0203233W WO02099343A1 WO 2002099343 A1 WO2002099343 A1 WO 2002099343A1 JP 0203233 W JP0203233 W JP 0203233W WO 02099343 A1 WO02099343 A1 WO 02099343A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
compressor
refrigerant
refrigeration
heating
Prior art date
Application number
PCT/JP2002/003233
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 WO2002099343A1 publication Critical patent/WO2002099343A1/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
    • F25B2313/02331—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements during cooling
    • 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 including an air conditioning heat exchanger and a cooling heat exchanger.
  • a refrigerating apparatus that performs a refrigerating cycle has been known, and is widely used as an air conditioner for heating and heating a room or a refrigerator for storing food 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 present invention has been made in view of the above, and an object of the present invention is to efficiently exhibit the heating capacity of an air conditioning heat exchanger and the cooling capacity of a cooling heat exchanger. Disclosure of the invention More specifically, as shown in FIG. 1, the first invention comprises a compressor (2B), a heat source side heat exchanger (4), an expansion mechanism (26, 46,...), And air conditioning of the room.
  • the air-conditioning heat exchanger (41) and the cooling heat exchanger (45) for cooling the inside of the refrigerator are connected to form a refrigerant circuit (1E) through which the refrigerant circulates.
  • the refrigerant discharged from the compressor (2B) condenses in the air-conditioning heat exchanger (41), passes through the expansion mechanism (26), and evaporates in the heat source side heat exchanger (4).
  • Heating operation in which the refrigerant returns to the compressor (2B) and the refrigerant discharged from the compressor (2B) condenses in the air-conditioning heat exchanger (41) and passes through the expansion mechanism (46) to the cooling heat exchanger (46).
  • Heat recovery operation in which the refrigerant evaporates in step 45) and returns to the compressor (2B), and the refrigerant discharged from the compressor (2B) condenses in the heat source side heat exchanger (4) and expands (46).
  • ) through the cooling heat exchanger (4 5) is configured to at least selectively perform the freezing operation for performing circulation back to the evaporation and the compressor (2B) by.
  • the second invention is a compressor (2B), a heat source side heat exchanger (4), and an expansion mechanism.
  • an air conditioning heat exchanger (41) for air-conditioning the room and a cooling heat exchanger (45) for cooling the interior of the refrigerator, and a refrigerant circuit (1E) through which the refrigerant circulates Is configured.
  • the refrigerant discharged from the compressor (2B) condenses in the air-conditioning heat exchanger (41), passes through the expansion mechanism (26), and flows through the heat source-side heat exchanger (4).
  • a heating operation in which the refrigerant evaporates and returns to the compressor (2B); a part of the refrigerant discharged from the compressor (2B) condenses in the air-conditioning heat exchanger (41); Excessive heating capacity operation in which the refrigerant condensed in the heat exchanger (4) and the condensed total liquid refrigerant evaporates in the cooling heat exchanger (45) via the expansion mechanism (46) and returns to the compressor (2B) And the compressor
  • Condenses refrigerant discharged from (2B) is a heat source side heat exchanger (4), the circulation back to the cooling heat exchanger through the expansion mechanism (46) (4 5) evaporated to compressor (2B)
  • the refrigeration operation is configured to be performed at least selectively.
  • the third invention is a compressor (2B), a heat source side heat exchanger (4), and an expansion mechanism.
  • the refrigerant circuit (1E) condenses the refrigerant discharged from the compressor (2B) in the air-conditioning heat exchanger (41), evaporates in the heat source side heat exchanger (4) through the expansion mechanism (26).
  • the gas refrigerant evaporates in the heat source side heat exchanger (4) and returns to the compressor (2B) for circulation. Heating capacity is insufficient, and the refrigerant discharged from the compressor (2B) is used as the heat source side.
  • a refrigeration operation that condenses in the heat exchanger (4), evaporates in the cooling heat exchanger (45) via the expansion mechanism (46), and circulates back to the compressor (2B) is at least selectively performed. Have been.
  • the refrigerant circuit (1E) is characterized in that the refrigerant discharged from the compressor (2B) is condensed in the air conditioning heat exchanger (41), and the condensed liquid Part of the refrigerant evaporates in the cooling heat exchanger (45) via the expansion mechanism (46), and other liquid refrigerant evaporates in the heat source side heat exchanger (4) via the expansion mechanism (26) and evaporates. Insufficient heating operation is selected to circulate the gas refrigerant back to the compressor (2B).
  • the refrigerant circuit (1E) is configured such that the refrigerant discharged from the compressor (2B) is condensed in the air-conditioning heat exchanger (41), and the expansion mechanism (46) After that, the heat recovery operation that circulates through the cooling heat exchanger (45) and returns to the compressor (2B) is selectable.
  • a part of the refrigerant discharged from the compressor (2B) is condensed in the air-conditioning heat exchanger (41), and another refrigerant is discharged.
  • Excessive heating capacity that condenses in the heat source side heat exchanger (4) and evaporates in the cooling heat exchanger (45) via the expansion mechanism (46) and evaporates in the cooling heat exchanger (45) and returns to the compressor (2B)
  • the refrigerant discharged from the compressor (2B) condenses in the air-conditioning heat exchanger (41), and part of the condensed liquid refrigerant evaporates in the cooling heat exchanger (45) via the expansion mechanism (46).
  • Other liquid coolant evaporates in the heat source-side heat exchanger (4) via the expansion mechanism (26), and the heating capacity can be switched to insufficient heating operation to circulate the evaporated gas refrigerant back to the compressor (2B). It is configured.
  • the refrigerant circuit (1E) includes a plurality of compressors (2B, 2C,...); ) Can be selected as a refrigerant recovery operation that recovers the excess refrigerant to the compressor (2 ⁇ ).
  • the heating circuit (1E) is provided with a floor heating heat exchanger (36) in series with the air conditioning heat exchanger (41). Configuration ing.
  • the operation is performed by switching between the heating operation, the heat recovery operation, and the refrigeration operation.
  • efficient operation is performed without exhausting heat from the heat source side heat exchanger (4).
  • the operation is performed by switching between a heating operation, a heating overcapacity operation, and a refrigeration operation.
  • this excess capacity operation heat of condensation is released from the heat source side heat exchanger (4), which suppresses the excess operation of the air conditioning heat exchanger (41) and the reduction in capacity of the cooling heat exchanger (45).
  • the operation is performed by switching between the heating operation, the insufficient heating insufficient operation, and the refrigeration operation.
  • the insufficient capacity operation the evaporation heat is released from the heat source side heat exchanger (4), and the deterioration of the capacity of the air conditioning heat exchanger (41) and the excessive operation of the cooling heat exchanger (45) are suppressed.
  • the excess refrigerant in the heat exchanger and the pipes is recovered by the compressor (2B).
  • a refrigerant is caused to flow through the floor heating heat exchanger (36) to perform floor heating.
  • the heating operation and the heat recovery operation are selectively performed, the operation corresponding to the operation condition can be performed. As a result, energy-saving operation with less waste can be performed.
  • the cooling capacity of the cooling heat exchanger (45) is always It can be kept at a predetermined value. As a result, the quality of products such as refrigerators can be reliably maintained.
  • the condensed heat is released from the heat source-side heat exchanger (4), which suppresses the over-operation of the air-conditioning heat exchanger (41) and the deterioration of the capacity of the cooling heat exchanger (45). be able to.
  • the heat source side heat exchanger (4) emits evaporative heat to suppress the deterioration of the capacity of the air conditioning heat exchanger (41) and the excessive operation of the cooling heat exchanger (45). be able to.
  • FIG. 1 to 24 show Embodiment 1 of the present invention
  • FIG. 1 is a circuit diagram showing a refrigerant circuit.
  • FIG. 2 is a refrigerant circuit diagram showing a refrigerant flow during a cooling operation.
  • FIG. 3 is a refrigerant circuit diagram showing a refrigerant flow during a refrigeration operation.
  • FIG. 4 is a refrigerant circuit diagram showing a refrigerant flow during the first cooling and freezing operation.
  • FIG. 5 is a refrigerant circuit diagram showing a refrigerant flow during the second cooling and freezing operation.
  • FIG. 6 is a refrigerant circuit diagram showing a refrigerant flow during the heating operation.
  • FIG. 7 is a refrigerant circuit diagram illustrating a refrigerant flow during the first heating and refrigeration operation.
  • FIG. 8 is a refrigerant circuit diagram illustrating a refrigerant flow during the second heating and refrigeration operation.
  • FIG. 9 is a refrigerant circuit diagram showing a refrigerant flow during the third heating / refrigeration operation (part 1).
  • FIG. 10 is a refrigerant circuit diagram showing a refrigerant flow during the third heating / refrigeration operation (part 2).
  • FIG. 11 is a control flowchart showing operation switching in the cooling mode.
  • FIG. 12 is a control flowchart showing capacity control during cooling operation.
  • FIG. 13 is a performance characteristic diagram showing a change characteristic of the compressor capacity during the cooling operation.
  • FIG. 14 is a control flowchart showing the capacity control during the refrigeration operation.
  • FIG. 15 is a performance characteristic diagram showing a change characteristic of the compressor capacity during the refrigeration operation.
  • FIG. 16 is a Mollier chart showing refrigerant behavior during the first cooling and freezing operation.
  • FIG. 17 is a control port diagram showing operation switching between the first cooling and freezing operation and the first cooling and freezing operation.
  • FIG. 18 is a control flowchart showing operation switching in the heating mode.
  • FIG. 19 is a control flowchart showing control of the compressor capacity during the heating operation.
  • FIG. 20 is a control flowchart showing capacity control during the first heating and refrigeration operation.
  • FIG. 21 is a control flowchart showing capacity control during the second heating and refrigeration operation.
  • FIG. 22 is a control flowchart showing the capacity control in the third heating / refrigeration operation 1.
  • FIG. 23 is a control flowchart showing the capacity control in the third heating / refrigeration operation No. 2.
  • FIG. 24 is a control flowchart showing operation switching in the heating mode.
  • FIG. 25 is a circuit diagram showing Embodiment 2 of the present invention and showing a main part of a refrigerant circuit. BEST MODE FOR CARRYING OUT THE INVENTION
  • a refrigeration apparatus (1) As shown in FIG. 1, a refrigeration apparatus (1) according to the present embodiment is provided in a convenience store, and is used for cooling a showcase in a refrigerator and cooling and heating a store in a room. .
  • the refrigeration system (1) has an outdoor unit (1A), an indoor unit (1B), a refrigeration unit (1C), and a refrigeration unit (1D), and performs a refrigerant 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 and cools the air inside the showcase.
  • the outdoor unit (1A) includes a non-inverter compressor (2A), a first invertor compressor (2B), and a second invertor compressor (2C), and a first four-way switching valve (3A). ) And a second four-way switching valve (3B) and an outdoor heat exchanger (4) as a heat source side heat exchanger.
  • Each compressor (2A, 2B 5 2C), for example, is composed of a hermetic high-pressure dome type scroll compressor.
  • the non-inverter compressor (2A) is of a constant displacement type in which the motor is always driven at a constant speed.
  • the first inverter compressor (2B) and the second inverter compressor (2C) are configured such that the electric motors are controlled in the inverter and the capacities are varied stepwise or continuously.
  • the Non'inba Isseki compressor (2A) and the first inverter evening compressor (2 B) and the second inverter evening compressor (2C) and the first system compression mechanism (2D) second It constitutes the system compression mechanism (2E). That is, the non-inverter compressor (2A) and the first invertor compressor (2B) constitute the first system compression mechanism (2D), and the second invertor compressor (2C) constitutes the second system.
  • the compression mechanism (2E) is configured, the non-inverter compressor (2A) configures the first system compression mechanism (2D), and the first invertor compressor (2B) and the second invertor compressor (2B). and a case where the compressor (2 C) and constitutes a pressure compression mechanism (2E) of the second system.
  • the present invention includes a first-stage compressor and a second-system compressor.
  • the non-inverting evening compressor (2A), the discharge pipe of the first inverter Isseki compressor (2B) and the second I Nba Isseki compressor (2C) (5 a, 5b , 5c) is one of high pressure gas is connected to the tube (8), the high-pressure gas pipe (8) is connected to one port of the first four-way selector valve (3A).
  • the Non'inba Isseki compressor discharge pipe (2A) (5 a) and the second inverter one evening compressor discharge pipe (2C) to (5c), the check valve (7) is provided.
  • 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).
  • the liquid tube (10) A receiver (14) is provided in the middle of the pipe, and the other end of the liquid pipe (10) is connected to the first connecting liquid pipe.
  • the outdoor heat exchanger (4) is, for example, a cross-fin type fin and
  • An outdoor fan (4F) which is a tube heat exchanger and is a heat source fan, is located in close proximity.
  • the suction pipes (6a, 6b) of the non-inverter compressor (2A) and the first invar compressor (2B) are connected to a low-pressure gas pipe (15).
  • the suction pipe (6c) of the second inverter 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).
  • One port of the second four-way switching valve (3B) is connected to the discharge pipe of the auxiliary gas pipe (19) by the second inverter Isseki compressor (2C) (5 c).
  • One port of the second 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 first four-way switching valve (3A) is in the first state (where the high-pressure gas pipe (8) communicates with the outdoor gas pipe (9) and the connection pipe (18) communicates with the communication gas pipe (17)).
  • the second state in which the high pressure gas pipe (8) communicates with the connecting gas pipe (17), and the connecting pipe (18) communicates with the outdoor gas pipe (9) (see the solid line in Fig. 1) (see the broken line in Fig. 1). (See).
  • 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).
  • each of the discharge pipes (, 5b 5 5c) and high-pressure gas pipe (8) an outdoor gas pipe and (9) constitute a high-pressure gas line (1L) at the time of cooling operation.
  • the low-pressure gas pipe (15) and the suction pipes (6a, 6b) of the first system compression mechanism (2D) are connected to the first low-pressure gas pipe.
  • Line (1M) the connecting gas pipe (17) and the suction pipe (6c) of the second 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. Further, a check valve (7) is provided in the outdoor unit (1A) at the branch end of the second communication liquid pipe (12). The check valve (7) extends from the receiver (14) toward the closing valve (20). The medium is configured to flow.
  • 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.
  • the communication pipe (21) includes a main pipe (22), and a first sub pipe (23) and a second sub pipe (24) branched from the main pipe (22).
  • the main pipe (22) is connected to the suction pipe (6c) of the second invertor compressor (2C).
  • the first sub pipe (23) and the second sub pipe (24) are connected to a low-pressure gas pipe (15).
  • the first sub pipe (23) and the second sub pipe (24) are provided with solenoid valves (7a, 7b) and check valves (7), respectively, which are opening and closing mechanisms. That is, the first auxiliary pipe (23), the first system compression mechanism (2D) of Non'inba Isseki compressor (2 A) or the first inverter evening compressor from (2B) a second system compression mechanism (2E ), 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), or 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 connected to the liquid pipe (10). It is located between the connection of the auxiliary liquid pipe (25) and the receiver (14).
  • a liquid injection pipe (27) is connected between the auxiliary liquid pipe (2 ⁇ ) and the low-pressure gas pipe (1 ⁇ ).
  • the liquid injection pipe (27) is provided with a solenoid valve (7c).
  • gas vent pipe (28) is connected between the discharge pipe (5 a) of the Residencial ICHIBA (14) of the upper and Non'in inverter compressor (2.alpha).
  • the gas vent pipe (28) is a check valve (7) is provided for allowing only refrigerant flows toward the discharge pipe from the receiver (1 4) ().
  • the high-pressure gas pipe (8) is provided with an oil separator (30). 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 equalizing pipe (32) is connected between the dome of the non-invar evening compressor (2A) and the suction pipe (6c) of the second invar evening compressor (2C).
  • the first oil equalizing pipe (32) is provided with a check valve (7) and a solenoid valve (7e) that allow oil flow from the non-inverter compressor (2A) to the second inverter compressor (2C). 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 equalizing pipe (33) is connected between the check valve (7) and the solenoid valve (7e) of the first oil equalizing pipe (32).
  • a third oil equalizing pipe ( 34 ) is connected between the dome of the second invar overnight 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). It has been.
  • 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).
  • the first pipe (37) is provided with a check valve (7) that allows only the flow of the refrigerant toward the floor heating heat exchanger (36). 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 heat exchanger, and an indoor fan (43), which is a use-side fan, is disposed close to the indoor heat exchanger (41).
  • the refrigeration unit (1C) includes a refrigeration heat exchanger (45) 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 first-stage compression mechanism (2D), while the indoor heat exchanger (41) communicates with the second inverter compressor (2C) during cooling operation. To the suction side. Therefore, 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). As a result, the refrigerant evaporation temperature of the refrigeration heat exchanger (45) is, for example, ⁇ 10 ° C., and the refrigerant evaporation temperature of the indoor heat exchanger (41) is, for example, + 5 ° C.
  • the refrigerant 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 type heat exchanger, and a refrigerating fan (47), which is a cooling fan, is arranged in close proximity.
  • the refrigeration unit (1D) is a cooling heat exchanger freezing heat exchanger (5 1) and Rise freezing expansion valve is Zhang mechanism (52) and the refrigeration compressor in a booth evening compressor and (53) Have.
  • 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 booster compressor (53).
  • the branch gas pipe (16) is provided with a check valve (7) and an oil separator (55). Between the Oirusepare Isseki (5Deruta) and the connecting gas pipe (5, oil return pipe having Kiyabirari tube (56) (5 ⁇ ) 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, 140 ° 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 refrigerating heat exchanger (51) is, for example, a cross-fin type fin 'and' tube type heat exchanger, and a refrigerating fan (58) serving as a cooling fan is arranged in close proximity. '
  • the booth evening compressor (3) of the connecting gas pipe is the suction side (54) and the blanking one scan evening a discharge side is branch gas pipe of the compressor (53) (16) of the check valve (7) between the downstream side of the bypass pipe having a check valve) (5 9) is connected.
  • the bypass pipe (59) is configured to allow the refrigerant to bypass the booth and evening compressor (53) when the booth and evening 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). Above second invar compression
  • the discharge pipe (5c) of the machine (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 chamber compressor (2B) and the second chamber compressor (2C).
  • a pressure switch (64) that opens when the pressure reaches a predetermined value is provided.
  • Each of the suction pipes (6b, 6c) of the first invar compressor (2B) and the second invar compressor (2C) has a low pressure sensor (65) serving as a pressure detecting means for detecting a low pressure refrigerant pressure.
  • a low pressure sensor (65) serving as a pressure detecting means for detecting a low pressure refrigerant pressure.
  • 66 a suction temperature sensor
  • 67 , 68 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 outdoor 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) is provided with a room temperature sensor (73) as temperature detecting means for detecting the indoor 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 and the like of the first inverter compressor (2B) and the second inverter compressor (2C).
  • controller (80) controls the operation of the refrigerant circuit (1E), It is configured to switch and control the operation, the freezing operation, the first cooling / freezing operation, the second cooling / freezing operation, the heating operation, the first heating / cooling operation, the excess heating operation of the heating, and the third heating / 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 sensor (65, 66) is higher than 98 kPa is satisfied in the state of the air conditioning thermostat ON.
  • step ST2 it is determined whether or not the condition 2 that the condition of the air conditioning system 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 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 refrigerant does not flow through the indoor heat exchanger (41), and the indoor fan (43) is driven to suspend cooling operation.
  • step ST1 When the operation in the cooling mode is started, first, the determination in step ST1 is performed. If the condition 1 of step ST1 is satisfied, the process proceeds to step ST4, where the first cooling / freezing operation or the second cooling / refrigerating operation for performing cooling, refrigeration, and freezing is performed, and the process returns. If the condition 1 in step ST1 is not satisfied and the condition 2 in 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 compressor (2A) constitutes the first system compression mechanism (2D)
  • the compressor (2C) constitutes the second system compression mechanism (2E). Then, only the first invertime compressor (2B) and the second invertime compressor (2C), which are the 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 line in FIG. Further, while the solenoid valve (7b) of the second sub pipe (24) of the communication pipe (21) is connected, the solenoid valve (7a) of the first sub pipe (23) of the communication pipe (21) is connected to the outdoor expansion valve. Valve (2e), solenoid valve (7g) of refrigeration unit (1C) and solenoid valve (7h) of refrigeration unit (1D) are closed.
  • the refrigerant discharged from the first inverter compressor (2B) and the second inverter compressor (2C) passes through the outdoor gas pipe (9) through the outdoor gas pipe (9) from the first four-way switching valve (3A). It flows into 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.
  • the evaporated gas refrigerant flows from the connecting gas pipe (17) through the first four-way switching valve (3A) and the second four-way switching valve (3B) to the suction pipe (6c) of the second Invar evening compressor (2C). And return to the No.
  • 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. If the condition 1 of step ST11 is satisfied, the process proceeds to step ST13, where the capacity of the first inverter compressor (2 ⁇ ) or the second inverter compressor (2C) is increased and the process returns. .
  • step ST 11 If the condition 1 in step ST 11 above is not satisfied and the condition 2 in step ST 12 is satisfied, the process proceeds to step ST 14 and the first invertor overnight compressor (2 ⁇ ) or the second invertor compressor is used. Increase the capacity of the compressor (2C) and return. If the condition 2 in step ST12 is not satisfied, the current compressor capacity is satisfied, so the routine returns and the above operation is repeated.
  • the compressor capacity increase control is performed by first raising the first inverter compressor (2 ⁇ ) from the stopped state to the minimum capacity (see point ⁇ ), The second inverter compressor (2C) is driven from a stopped state while maintaining the minimum capacity of the overnight compressor (2 ⁇ ) to increase the capacity. Thereafter, when the load further increases, the capacity of the first invar overnight compressor (2 ⁇ ) is increased while the second invar overnight compressor (2C) is maintained at the maximum capacity (see point)).
  • 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.
  • This refrigeration operation is an operation that only cools the refrigeration unit (1C) and the refrigeration unit (1D).
  • the non-inverter overnight compressor (2 ⁇ ) and the first inverter compressor (2 ⁇ ) constitute a first system compression mechanism (2D)
  • the second inverter The overnight compressor (2C) constitutes the second system compression mechanism (2 ⁇ ).
  • the first evening compressor (53) is also driven. Drive
  • the first four-way switching valve (3 ⁇ ) switches to the first state as shown by the solid line in FIG.
  • 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) are opened.
  • the outdoor expansion valve (26) and the indoor expansion valve (42) are closed.
  • the refrigerant discharged from the non-inverter and evening compressors (2A) and the first invertor and evening compressor (2B) exchanges outdoor heat through the outdoor gas pipe (9) from the first four-way switching valve (3A). 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 flows through the refrigeration expansion valve (46) to the refrigeration heat exchanger (45). Flow and evaporate.
  • the gas refrigerant evaporated in the refrigeration heat exchanger (45) and the gas refrigerant discharged from the booth compressor (53) are combined in the low-pressure gas pipe ( 15 ), and are combined in the non-inverter compressor (2A) and the second compressor. 1 Return to the Invar overnight compressor (2B). This circulation is repeated to cool the inside of the refrigerator, which is a refrigeration showcase and a freezer showcase.
  • the refrigerant pressure in the refrigerating heat exchanger (51) is sucked 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) becomes ⁇ 10 ° 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 sensor (6 ⁇ , 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 invertor compressor (2B) or the non-inverter compressor (2A) is increased, and the process 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-evening compressor (2B) or non-inverting overnight compression is performed. (2A) and return You. If 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, while the non-inverter compressor (2 ⁇ ) is stopped, the first invertor compressor (2 ⁇ ) is driven (see point ⁇ ). ), Increase the capacity. After the capacity of the first Invar evening compressor (2 ⁇ ) has increased to the maximum capacity (see point ⁇ ), if the load further increases, the non-inverting evening compressor (2 ⁇ ) is driven and at the same time, the first Invar evening compressor (2 ⁇ ) is driven. 2)) to the minimum capacity (see point C). After that, when the load further increases, the capacity of the 1st Invar overnight compressor (2 ⁇ ) 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 ( ⁇ 2) is controlled by a temperature-sensitive cylinder, and is the same in each operation.
  • This first cooling / refrigeration operation is an operation that simultaneously cools the indoor unit (1 ⁇ ) and cools the refrigerator unit (1C) and the refrigeration unit (1D).
  • the non-inverter evening compressor (2 ⁇ ) and the first invertor evening compressor (2 ⁇ ) constitute the first system compression mechanism (2D).
  • the two-inverter compressor (2C) forms the second system compression mechanism (2 ⁇ ).
  • the Non'inba Isseki compressor (2.alpha) together with the first inverter Isseki compressor (2 beta) and a second inverter evening compressor (2C) is driven, the booster compressor (53) is also driven.
  • first four-way switching valve (3 ⁇ ) and the second four-way switching valve (3 ⁇ ) switch to the first state, respectively, as shown by the solid line in FIG. Further, while the solenoid valve of the refrigerating unit (1C) (7 g) and refrigeration Yuni' preparative (1 D) solenoid valve (7h) is opened, the communicating pipe (2 1) two electromagnetic valves (7a, 7b) And the outdoor expansion valve (2 ⁇ ) is closed.
  • the refrigerant discharged from the non-inverter compressor (2 ⁇ ), the first invar evening compressor (2 ⁇ ), and the second invar evening compressor (2C) merges in the high-pressure gas pipe (8), 1 Flow from the four-way switching valve (3 ⁇ ) to the outdoor heat exchanger (4) via the outdoor gas pipe (9), and condense.
  • 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) passes through the indoor expansion valve (42) and is It flows into the heat exchanger (41) and evaporates.
  • 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 (4 ⁇ ) 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.
  • the gas refrigerant evaporated in the refrigerating heat exchanger (51) is sucked and compressed by the booth compressor (53) and 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). Further, the refrigerant is compressed to the point B by the non-inverter compressor (2A) and the first inverter 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.
  • 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 () is sucked by 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 system compression mechanism (2D) and the second system compression mechanism (2E), and further by the booth mixer (53). Two types of evaporation temperature are obtained by two-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 and refrigeration operation in that it is opened.
  • the non-inverter compressor (28), the first invar compressor (2B), and the second invar compressor (2C) ) Is condensed in the outdoor heat exchanger (4) and evaporated in the indoor heat exchanger (41), the refrigeration heat exchanger (45), and the refrigeration heat exchanger (51).
  • the refrigerant evaporated in the indoor heat exchanger (41) returns to the second inverter compressor (2C), and the refrigerant evaporated in the refrigeration heat exchanger (45) and the refrigeration heat exchanger (51) becomes non-refrigerated. It returns to the Invar evening compressor (2A) and the 1st Invar evening compressor (2B).
  • the second sub pipe (24) in the communicating pipe (21) is in communication, the above indoor heat exchange
  • the refrigerant pressure of the compressor (41) drops to the suction pressure of the non-inverter compressor (2A) and the first invertor 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 above-described first cooling and refrigeration operation 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 condition 2 that the first invar compressor (2B) is operated at the maximum capacity (maximum frequency) is satisfied.
  • Step ST 3 In 5 it determines whether the capacity of the non-inverting evening compressor (2 A) and the first inverter evening compressor (2B) are satisfied the condition 3 that not the maximum.
  • step ST37 opens the solenoid valve (7b) of the second sub pipe (24), 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 ST41 If the condition 5 of step ST41 is satisfied, the process moves to step ST43, where the first-stage compression mechanism of the non-inverter compressor (2A) and the first invar-night compressor (2B) is used. Improve (2D) ability. If the condition of step ST41 above is satisfied 6, the process proceeds to step ST44, where the first-stage compression mechanism of the non-inverter compressor (2A) and the first invar compressor (2B) is used. Reduces (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 is satisfied while the air conditioner is ON. I do.
  • step ST52 it is determined whether or not the condition 2 that the air-conditioning thermo-ON is in a state 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 thermo-OFF.
  • the above-mentioned air-conditioning thermo ON means the state where the refrigerant is condensed in the indoor heat exchanger (41) and heating operation is being performed
  • the air-conditioning thermo OFF means that the indoor expansion valve (42) is closed. Means that 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. When the condition 1 of step ST51 is satisfied, the process proceeds to step ST54, where the first heating / refrigeration operation or the second heating / refrigeration operation in heating mode 1 is performed, and the process returns. If the condition 1 of step ST51 is not satisfied and the condition 2 of step ST52 is satisfied, the process proceeds to step ST55 to perform the heating operation or the third heating / refrigeration operation and return. If the condition 2 of step ST53 is not satisfied and the condition 3 of step ST53 is satisfied, the process proceeds to step ST56, performs the freezing operation, and returns. If condition 3 of step ST53 is not satisfied, the operation is continued and the operation returns.
  • the refrigeration operation is the same as the refrigeration operation in the cooling mode.
  • This heating operation only heats the indoor unit (1B) and the floor heating circuit (35).
  • the operation to be performed as shown in Fig. 6, the non-inverter compressor (2A) forms the first system compression mechanism (2D), and the first inverter compressor (2B) and the second inverter compressor (2B).
  • the compressor (2C) constitutes the second system compression mechanism (2E). Then, only the first inverter compressor (2B) and the second inverter compressor (2C), which are the second-system compression mechanisms (2E), are driven.
  • first four-way switching valve (3A) switches to the second state as shown by the solid line in FIG. 6, and the second four-way switching valve (3B) as shown by the solid line in FIG. Switch to the first state.
  • solenoid valve (7b) of the second sub pipe (24) of the communication pipe (21) is open, the solenoid valve (7a) of the first sub pipe (23) of the communication pipe (21) and the refrigeration unit ( The solenoid valve (7g) of 1C) and the solenoid valve (7h) of refrigeration unit (1D) are closed.
  • the refrigerant discharged from the first invar overnight compressor (2B) and the second invar evening compressor (2C) passes through the connecting gas pipe (17) from the first four-way switching valve (3A) to the indoor heat source. It flows to the exchanger (41) and condenses.
  • the condensed liquid refrigerant flows through the second connecting liquid pipe (12), flows through the floor heating circuit (35), and flows through the floor heating heat exchanger (36) to the receiver (14). Thereafter, the liquid refrigerant flows through the outdoor expansion valve (26) of the auxiliary liquid pipe (25) to the room heat exchanger (4) and evaporates.
  • Evaporated gas refrigerant flows from the connecting gas pipe (17) through the first four-way switching valve (3A) and the second four-way switching valve (3B) to the second invar- evening compressor (2C) suction pipe (6c). And return to the No. 1 Invernox compressor (2B) and No. 2 Invero compressor (2C). This circulation is repeated to heat the interior of the store and to heat the floor at the same time.
  • a part of the low-pressure gas refrigerant is diverted from the suction pipe (6c) of the second inverter-evening compressor (2C) to the communication pipe (21), and is diverted from the second sub pipe (24) to the first inverter. Return to the compressor (2B).
  • 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 6 Move to 3 and raise the capacity of the 1st Inver / Empressor (2B) or the 2nd Inver / Empressor (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-evening 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 degree of superheat based on the saturation temperature corresponding to the pressure based on the low pressure pressure sensor (65, 66) and the temperature detected by the suction temperature sensor (67, 68).
  • the degree 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 does not use the outdoor heat exchanger (4) but heats the indoor unit (1B) and cools the refrigeration unit (1C) and the refrigeration unit (1D). is there.
  • 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 non-inverter compressor (2A) and the 1st inverter compressor (2B) are driven together with the booth compressor (3 ⁇ 4).
  • 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. 7
  • the second four-way switching valve (3B) switches to the second state as shown by the solid line in FIG. Switch to the first state.
  • the solenoid valve (7g) of the refrigerator 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 non-inverter overnight compressor (2A) and the first inverter compressor The refrigerant discharged from (2B) flows from the first four-way switching valve (3A) to the indoor heat exchanger (41) via the connecting gas pipe (17) 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) between 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. 0% heat recovery is performed.
  • the compressor capacity and the like during the first heating and refrigeration operation are controlled as shown in FIG. 20. In this control, the following four determinations 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 ST 7 Go to 5 and raise the capacity of the No. 1 Inverter overnight compressor (2B) or Non-inverter overnight compressor (2A) and return. 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 / refrigeration operation described later, that is, the operation of insufficient heating capacity 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 ST73 If the condition 3 of step ST73 is not satisfied and the condition 4 of step ST74 is satisfied, the process proceeds to step ST78, where the first invertor compressor (2B) or the non-inverter compressor ( 2A) Increase your ability and return. If 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. 8, it constitutes a non-inverting evening compressor (2 A) and the first inverter evening compressor (2B) and the first system compression mechanism (2D),
  • the second invar compressor (2C) constitutes the second system compression mechanism (2E). Then, the above-mentioned non-invar evening 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 evening compressor (2C) is stopped.
  • the 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
  • part of the refrigerant discharged from the non-inverted overnight compressor (2A) and the first invared overnight compressor (2B) flows to the indoor heat exchanger (41) and condenses as in the first heating and refrigeration operation. I do.
  • 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 cooling capacity (the amount of heat of evaporation) between the refrigerator unit (1C) and the refrigeration unit (1D) and the heating capacity (the amount of heat of condensation) of the indoor unit (1B) and the floor heating circuit (35) are balanced. Instead, the excess heat of condensation is released outside by the outdoor heat exchanger (4).
  • the compressor capacity and outdoor fan (4F) air volume during the second heating / refrigeration operation are controlled as shown in FIG. 21 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 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 ST82 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 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 ST85 the capacity of the first inverter / night compressor (2B) or the non-inverter / night compressor (2A) is increased. I do. 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 and the outdoor fan (4F) The air flow is reduced and the operation 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 Click.
  • step ST83 the heat of condensation of the indoor heat exchanger (41) is given to the outdoor heat exchanger (4). If the condition 3 of step ST83 is not satisfied and the condition 4 of step ST84 is satisfied, the process proceeds to step ST88, where the first invar compressor (2B) or the non-invar compressor is used. Decrease (2A) ability and return. If condition 4 of step ST84 is not satisfied, the current compression function is satisfied, so that the operation 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.
  • the non-inverter compressor (2A) and the first invertor compressor (2B) use the first system compression mechanism (2D).
  • the second inverter compressor (2C) forms the second system compression mechanism (2E).
  • the non-inverter compressor (2A) and the first chamber compressor (2B) are driven, and the booster 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 freezing operation.
  • the refrigerant discharged from the non-inverting and evening compressors (2A) and the first inverting 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 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 vaporized 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 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 communicates with the gas refrigerant from the refrigeration unit (1C) and the refrigeration unit (1D). Merge and return to the non-inverter compressor (2A) and the first inverter 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 refrigeration unit (1C) and the refrigeration unit (1D) and the heating capacity (the amount of heat of condensation) of the indoor unit (1B) and the floor heating circuit (35) are balanced. Without this, the insufficient heat of evaporation is obtained from the outdoor heat exchanger (4).
  • the compressor capacity and the outdoor fan (4F) air volume during the third heating / refrigeration operation are controlled as shown in FIG. 22, and the following four determinations are made.
  • 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). Is higher than 392 kPa, it is determined whether or not Condition 1 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 ST 9 Go to 5 and increase the capacity of the 1st inverter compressor (2B) or non-inverter compressor (2A) and return. If the condition 1 of step ST91 is not satisfied and the condition 2 of step ST92 is satisfied, the process proceeds to step ST96, and the heating capacity is not enough. Switch to operation 2 and return. If the condition 2 in step ST92 is not satisfied and the condition 3 in step ST93 is satisfied, the process proceeds to step ST97, in which the air flow of the outdoor fan (4F) is reduced and the process returns.
  • step ST93 If the condition 3 of step ST93 is not satisfied and the condition 4 of step ST94 is satisfied, the process proceeds to step ST98, where the first inverter 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 and evening compressor (2A) and the first invertor and evening compressor (2B) constitute a first system compression mechanism (2D).
  • the two-inverter compressor (2C) forms the second system compression mechanism (2E).
  • the co-Driving the Non'inba Isseki compressor (2A), the first inverter evening compressor (2B) and the second inverter evening compressor (2 C) Booth evening compressor () 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. This is the same as 1 in the third heating and refrigeration operation described above, except that the solenoid valve (7b) in the second sub pipe (24) is closed and the second inverter compressor (2C) is driven.
  • the refrigerant discharged from the non-inverter compressor (2A), the first invar overnight compressor (2B), and the second invar overnight compressor (2C) passes through the communication gas pipe (17) to the indoor heat exchanger. It flows to (41) and condenses.
  • the condensed liquid refrigerant flows through the floor heating circuit (3 ⁇ ) and flows from the floor heating heat exchanger (36) to the receiver (14). Thereafter, a part of the liquid refrigerant from the receiver (14) flows through the first communication liquid pipe (11), and a part of the liquid refrigerant flowing through the first communication liquid pipe (11) is cooled by the refrigeration heat exchanger (45). ) And evaporates.
  • the other liquid refrigerant flowing through the first communication liquid pipe (11) flows into the refrigeration heat exchanger (51) and evaporates.
  • the gas refrigerant evaporated in the refrigeration heat exchanger (45) and the gas refrigerant discharged from the pressure compressor (53) are combined in the low-pressure gas pipe (15), and are combined in the non-inverter compressor (2A) and Return to No. 1 Invar evening compressor (2B).
  • 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 is compressed by the second invar overnight. Return to the machine (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. That is, 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) Does not bun lance and the insufficient heat of evaporation is obtained from the outdoor heat exchanger (4).
  • Noninba Isseki compressor (2A) and the first inverter evening compressor (2 B) and the second inverter Isseki compressor (2C) and the driven warm tufts capability to ensure Noninba Isseki compressor (2A) and the first inverter evening compressor (2 B) and the second inverter Isseki compressor (2C) and the driven warm tufts capability.
  • the compressor capacity and the outdoor fan (4F) airflow in the second heating / refrigeration operation 2 are controlled as shown in FIG. 23, 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 medium pressure detected by the low-pressure pressure sensors (65, 66). It is determined whether the condition 1 that the LP 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. If the condition 1 of step ST101 is satisfied, the process proceeds to step S S105, where the capacity of the second inverter compressor (2C) is increased and the first inverter compressor (2C) is compressed. Increase the capacity of the compressor (2 ⁇ ) or the non-inverter compressor (2 ⁇ ) and return.
  • step S ⁇ 101 If the condition 1 of step S ⁇ 101 is not satisfied and the condition 2 of step S ⁇ 102 is satisfied, the process proceeds to step ST106, and the refrigeration unit (1C) and the refrigeration unit Since the capacity of (1D) is rather low, the capacity of the second inverter compressor (2C) is increased while the capacity of the first inverter compressor (2 ⁇ ) or the non-inverter compressor is increased.
  • step ST102 Reduces the ability and returns. If the condition 2 in step ST102 is not satisfied and the condition 3 in step S103 is satisfied, the process proceeds to step ST107 and the refrigeration unit (1C) and the refrigeration unit (1D) are not moved. The capacity of the 2nd Inver Evening Compressor (2C) was reduced due to the lack of capacity.
  • step S ⁇ 103 or increase the capacity of the non-inverter compressor (2 ⁇ ) and return. If the condition 3 of step S ⁇ 103 is not satisfied and the condition 4 of step S 4104 is satisfied, the process proceeds to step S ⁇ 108, and the second chamber overnight compressor (2C ) And reduce the capacity of the No. 1 Inverter compressor (2 ⁇ ) or the non-inverter overnight compressor (2 ⁇ ) and return. If the condition 4 of step ST104 is not satisfied, the current compression function is satisfied, so the routine returns and the above operation is repeated.
  • step STil 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 ST112 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 ST112 to step ST113, and the outdoor fan (4F Judgment is made as to whether the air volume of Wind of this outdoor fan (4F) If the amount is the minimum, 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 air flow 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 to resume operation.
  • 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 When the outdoor heat exchanger (4) is a condenser, for example, in a state such as the second heating and freezing operation, the process proceeds from step ST122 to step ST123, and the outdoor fan (4F) It is determined whether or not the air volume is the lowest. If the air flow of the outdoor fan (4F) is the minimum, the process proceeds from step ST123 to step ST124, and switches to the first heating / freezing operation and returns. If the airflow of the outdoor fan (4F) is not the lowest in step ST123, the process proceeds to step ST125, where the airflow 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.
  • the liquid refrigerant may accumulate in the outdoor heat exchanger (4) and the outdoor gas pipe (9), so the solenoid valve (7b) in the second sub pipe (24) of the communication pipe (21) Open for a few minutes, or drive the second inverter compressor (2C) for a predetermined time to collect the excess refrigerant.
  • the heating operation, the first heating / refrigeration operation, the second heating / refrigeration operation, and the third heating / refrigeration operation are selected and performed, the operation corresponding to the operation condition is performed. It can be performed. As a result, energy-saving operation with less waste can be performed.
  • the excess or insufficient heating capacity of the indoor heat exchanger (41) can be adjusted by the outdoor heat exchanger (4), the cooling capacity of the refrigeration heat exchanger (45) and the like is always specified. Can be held to a value. As a result, the quality of products such as refrigerators can be reliably maintained.
  • the heat of condensation is released from the outdoor heat exchanger (4), and the excess operation of the air conditioning heat exchanger (41) and the refrigeration heat exchanger (45) and the refrigeration heat exchanger (51) are performed. ) Can be suppressed.
  • Embodiment 2 of One Invention Next, a second embodiment of the present invention will be described in detail with reference to the drawings.
  • 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.
  • 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).
  • One port of the four-way switching valve (91) is connected between the two check valves (7, 7) in the first auxiliary pipe (23) via the first passage (92). .
  • 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 state shown in FIG. 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) is switched to the solid state shown in FIG. And the second passage (93).
  • the gas refrigerant in the low-pressure gas pipe (15) flows from the first sub pipe (23) through the first passage (92), passes through the four-way switching valve (91), flows into the second passage (93), It flows into the suction pipe (6c) of the second chamber compressor (2C) via the second sub pipe (24).
  • 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.
  • one air-conditioning heat exchanger (41), one refrigeration heat exchanger (45), and one refrigeration heat exchanger (51) are provided.
  • a plurality of air conditioning heat exchangers (45) may be provided, a plurality of refrigeration heat exchangers (45) may be provided, and a plurality of refrigeration heat exchangers may be provided.
  • a container (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. Further, a plurality of refrigeration heat exchangers (51) may be connected in parallel with each other.
  • cooling and heating are performed.
  • the present invention may be configured to perform only heating mode operation.
  • 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

L'invention concerne un dispositif frigorifique, dans lequel, au cours d'une opération de récupération de chaleur, le fluide frigorigène libéré par un compresseur (2B) est condensé dans un échangeur thermique (41) d'un conditionneur d'air, acheminé à travers un détendeur (46), évaporé dans un échangeur thermique (45) d'un réfrigérateur et dans un échangeur thermique (51) d'un congélateur, puis renvoyé vers le compresseur (2B). Au cours d'une opération à plein débit de surchauffage, une partie du fluide frigorigène libéré par le compresseur (2B) est condensée dans l'échangeur thermique (41), le reste du fluide frigorigène est condensé dans un échangeur thermique extérieur (4), tout le fluide frigorigène condensé est acheminé à travers le détendeur (46), évaporé dans l'échangeur thermique (45) et dans l'échangeur thermique (51), puis renvoyé vers le compresseur (2B). Lors du chauffage au cours d'une exploitation à plein débit, le fluide frigorigène libéré par le compresseur (2B) est condensé dans l'échangeur thermique (41), une partie du fluide frigorigène liquide condensé est acheminé à travers le détendeur (46) puis évaporé dans l'échangeur thermique (45) et dans l'échangeur thermique (51), le reste du fluide frigorigène liquide est acheminé à travers le détendeur (26) puis évaporé dans l'échangeur thermique extérieur (4), le fluide frigorigène gazeux évaporé est renvoyé vers le compresseur (2B).
PCT/JP2002/003233 2001-05-31 2002-03-29 Dispositif frigorifique WO2002099343A1 (fr)

Applications Claiming Priority (2)

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JP2001-164816 2001-05-31
JP2001164816A JP3956649B2 (ja) 2001-05-31 2001-05-31 冷凍装置

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JP3953029B2 (ja) * 2001-06-26 2007-08-01 ダイキン工業株式会社 冷凍装置
JP4618313B2 (ja) * 2004-08-30 2011-01-26 ダイキン工業株式会社 冷凍装置
JP2009030937A (ja) * 2007-07-30 2009-02-12 Daikin Ind Ltd 冷凍装置
KR101900272B1 (ko) * 2018-05-15 2018-09-19 주식회사 이수에어텍 냉난방, 냉장 및 냉동 복합 기능을 구비한 가스엔진 구동 히트펌프 장치

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0340306B2 (fr) * 1983-02-15 1991-06-18
JPH0666456A (ja) * 1992-08-20 1994-03-08 Sanden Corp 店舗内及びその設備の温度管理システム
JPH08178447A (ja) * 1994-12-19 1996-07-12 Toshiba Ave Corp マルチシステム空気調和機
JPH10238879A (ja) * 1997-02-21 1998-09-08 Mitsubishi Heavy Ind Ltd マルチ型ヒートポンプ式空気調和機及びその運転方法
JPH10318620A (ja) * 1997-05-19 1998-12-04 Yamaha Motor Co Ltd エンジン駆動熱ポンプ式空調装置
JPH11182961A (ja) * 1997-12-24 1999-07-06 Sanyo Electric Co Ltd 空気調和機

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0340306B2 (fr) * 1983-02-15 1991-06-18
JPH0666456A (ja) * 1992-08-20 1994-03-08 Sanden Corp 店舗内及びその設備の温度管理システム
JPH08178447A (ja) * 1994-12-19 1996-07-12 Toshiba Ave Corp マルチシステム空気調和機
JPH10238879A (ja) * 1997-02-21 1998-09-08 Mitsubishi Heavy Ind Ltd マルチ型ヒートポンプ式空気調和機及びその運転方法
JPH10318620A (ja) * 1997-05-19 1998-12-04 Yamaha Motor Co Ltd エンジン駆動熱ポンプ式空調装置
JPH11182961A (ja) * 1997-12-24 1999-07-06 Sanyo Electric Co Ltd 空気調和機

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