EP3457049B1 - Kältekreislaufvorrichtung - Google Patents

Kältekreislaufvorrichtung Download PDF

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Publication number
EP3457049B1
EP3457049B1 EP18198946.8A EP18198946A EP3457049B1 EP 3457049 B1 EP3457049 B1 EP 3457049B1 EP 18198946 A EP18198946 A EP 18198946A EP 3457049 B1 EP3457049 B1 EP 3457049B1
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EP
European Patent Office
Prior art keywords
heat source
refrigerant
reducing device
pressure reducing
heat
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Application number
EP18198946.8A
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English (en)
French (fr)
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EP3457049A1 (de
Inventor
Nobuya ISHIHARA
Tomotaka Ishikawa
Takashi Umeki
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Priority to EP18198946.8A priority Critical patent/EP3457049B1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/89—Arrangement or mounting of control or safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/12—Sound
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/191—Pressures near an expansion valve
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/197—Pressures of the evaporator
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part

Definitions

  • the present invention relates to a refrigeration cycle apparatus. Specifically it relates to a refrigeration cycle apparatus in which a local pipe can be used.
  • Patent Literature 1 As a related-art refrigeration cycle apparatus in which a local pipe can be used, for example, there has been known a binary refrigeration apparatus in which refrigerant flowing from an outdoor unit to a liquid pipe being a local pipe is reduced in pressure by a flow control device and brought into a two-phase gas-liquid state to result in reduction in refrigerant cost (Patent Literature 1, for example).
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2012-112622
  • EP 2 787 305 A1 discloses refrigerating/air-conditioning device.
  • EP 2 511 630 A1 discloses air conditioner and refrigerant amount detection method for air conditioner.
  • EP 2 765 370 A1 discloses refrigeration cycle apparatus and hot water generator provided with the same.
  • the present invention has been made to solve the above-mentioned problem, and has an object to provide a refrigeration cycle apparatus that enables reduction in pressure loss and reduction in noise in a liquid pipe.
  • the present invention provides a refrigeration cycle apparatus as set forth in claim 1.
  • the first refrigerant can be caused to flow into the first connection pipe as liquid refrigerant having a pressure less than the design pressure of the first connection pipe by regulating the opening degree of the first heat source-side pressure reducing device.
  • liquid refrigerant can be employed as the refrigerant flowing into the first connection pipe. Therefore, the refrigeration cycle apparatus enabling reduction in pressure loss and noise in the first connection pipe can be provided.
  • FIG. 1 is a schematic refrigerant circuit diagram for illustrating an example of the refrigeration cycle apparatus 1 according to Construction 1. In some cases, the dimensional relationships among components and their shapes in the following drawings including Fig. 1 differ from the actual ones.
  • the refrigeration cycle apparatus 1 includes a heat source-side unit 100 (for example, an outdoor unit), and a load-side unit 200 (for example, an indoor unit) arranged in parallel with the heat source-side unit 100.
  • the heat source-side unit 100 and the load-side unit 200 are connected to each other by a first connection pipe 300 (liquid pipe) and a second connection pipe 400 (gas pipe), which are local pipes.
  • a first connection pipe 300 liquid pipe
  • a second connection pipe 400 gas pipe
  • the refrigeration cycle apparatus 1 includes a first refrigeration cycle 500 in which a first compressor 2, a first heat source-side heat exchanger 3, a first heat source-side pressure reducing device 4, a load-side pressure reducing device 5, and a load side heat exchanger 6 are connected by a refrigerant pipe and through which first refrigerant circulates.
  • a first compressor 2 a first heat source-side heat exchanger 3
  • a first heat source-side pressure reducing device 4 a load-side pressure reducing device 5
  • a load side heat exchanger 6 a load side heat exchanger 6
  • any type of refrigerant can be selected in accordance with the purpose for which the refrigeration cycle apparatus 1 is used.
  • first refrigerant examples include natural refrigerant, such as CO 2 , hydrofluorocarbon, such as R32, hydrofluoroolefins, such as 2,3,3,3-tetrafluoro-1-propene (HFO-1234yf), and a mixed refrigerant, such as R410A.
  • natural refrigerant such as CO 2
  • hydrofluorocarbon such as R32
  • hydrofluoroolefins such as 2,3,3,3-tetrafluoro-1-propene (HFO-1234yf)
  • R410A examples of first refrigerant that can be used include natural refrigerant, such as CO 2 , hydrofluorocarbon, such as R32, hydrofluoroolefins, such as 2,3,3,3-tetrafluoro-1-propene (HFO-1234yf), and a mixed refrigerant, such as R410A.
  • the first compressor 2 is housed in the heat source-side unit 100, and is a variable-frequency type fluid machine that compresses sucked low-pressure first refrigerant into high-pressure first refrigerant and discharges the compressed refrigerant.
  • a scroll compressor having a rotational frequency controlled by an inverter can be used.
  • the first heat source-side heat exchanger 3 is a heat exchanger functioning as a radiator (condenser) and is housed in the heat source-side unit 100.
  • the first heat source-side heat exchanger 3 exchanges heat between the first refrigerant flowing through the inside of the first heat source-side heat exchanger 3 and outside air (for example, outdoor air) sent by a heat source-side heat exchanger fan (not shown).
  • the first heat source-side heat exchanger 3 is configured as a fin-and-tube type heat exchanger of a cross-fin type including a heat transfer tube and a plurality of fins, for example.
  • the first heat source-side pressure reducing device 4 expands high-pressure liquid refrigerant flowing in from the first heat source-side heat exchanger 3 and reduces pressure of the refrigerant, and causes the refrigerant to flow into the first connection pipe 300, which is a local pipe, as the first refrigerant having a pressure less than a design pressure of the first connection pipe 300.
  • a design pressure of the first connection pipe 300 is set to a withstand pressure reference value of the first connection pipe 300.
  • the first heat source-side pressure reducing device 4 is housed in the heat source-side unit 100, and is configured as an electronic expansion valve, such as a linear electronic expansion valve (LEV), which has an opening degree capable of being regulated in a plurality of stages or continuously.
  • LEV linear electronic expansion valve
  • the load-side pressure reducing device 5 further expands the first refrigerant flowing in from the first connection pipe 300 and having a pressure less than the design pressure of the first connection pipe 300 and reduces pressure of the refrigerant, and causes the refrigerant to flow into the load side heat exchanger 6.
  • the load-side pressure reducing device 5 is housed in the load-side unit 200, and is configured as an electronic expansion valve, such as a linear electronic expansion valve, which has an opening degree capable of being regulated in a plurality of stages or continuously.
  • the load side heat exchanger 6 is a heat exchanger functioning as an evaporator (cooler) and is housed in the load-side unit 200.
  • the load side heat exchanger 6 exchanges heat between refrigerant flowing through the inside of the load side heat exchanger 6 and outside air (for example, indoor air), for example.
  • the load side heat exchanger 6 can be configured as a fin-and-tube type heat exchanger of a cross-fin type formed of a heat transfer tube and a plurality of fins, for example.
  • the load side heat exchanger 6 may be configured so that outside air is supplied by a load side heat exchanger fan (not shown) sending air.
  • cooling operation an operation of the refrigeration cycle apparatus 1 in which the load side heat exchanger 6 functions as an evaporator is referred to as "cooling operation”.
  • a first heat source-side connection valve 7a for connection with the first connection pipe 300 is provided in a heat source-side refrigerant pipe housed in the heat source-side unit 100 and arranged between the first heat source-side pressure reducing device 4 and the first connection pipe 300.
  • a second heat source-side connection valve 7b for connection with the second connection pipe 400 is provided in a heat source-side refrigerant pipe housed in the heat source-side unit 100 and arranged between the first compressor 2 and the second connection pipe 400 .
  • a second heat source-side connection valve 7b for connection with the second connection pipe 400 is provided in a load side refrigerant pipe housed in the load-side unit 200 and arranged between the load-side pressure reducing device 5 and the first connection pipe 300.
  • a second load side connection valve 8b for connection with the second connection pipe 400 is provided.
  • the first heat source-side connection valve 7a, the second heat source-side connection valve 7b, the first load side connection valve 8a, and the second load side connection valve 8b are each formed of a two-way valve, such as a two-way solenoid valve, capable of being switched between open and closed states.
  • the subcooling heat exchanger 10 is arranged between the first heat source-side heat exchanger 3 and the first heat source-side pressure reducing device 4.
  • the subcooling heat exchanger 10 includes a first heat transfer tube 10a and a second heat transfer tube 10b, and is housed in the heat source-side unit 100.
  • the subcooling heat exchanger 10 is a heat exchanger that exchanges heat between the high-pressure first refrigerant flowing through the first heat transfer tube 10a and first refrigerant having been reduced in pressure and flowing through the second heat transfer tube 10b during cooling operation.
  • the subcooling heat exchanger 10 can be configured as a fin-and-tube type heat exchanger of a cross-fin type formed of the first heat transfer tube 10a, the second heat transfer tube 10b, and a plurality of fins, for example.
  • first heat transfer tube 10a and the first heat source-side pressure reducing device 4 are connected to each other by a first heat source-side refrigerant pipe 12.
  • the other end of the first heat transfer tube 10a and the first heat source-side heat exchanger 3 are connected to each other by a second heat source-side refrigerant pipe 13.
  • a branch joint portion 12a arranged in the first heat source-side refrigerant pipe 12 and one end of the second heat transfer tube 10b are connected to each other by a first heat source-side branched refrigerant pipe 16.
  • the other end of the second heat transfer tube 10b and an intermediate-pressure portion of the first compressor 2 are connected to each other by a second heat source-side branched refrigerant pipe 18.
  • the first heat source-side refrigerant pipe 12 and the second heat source-side refrigerant pipe 13 are some of refrigerant pipes forming the first refrigeration cycle 500.
  • the first heat source-side refrigerant pipe 12, the second heat source-side refrigerant pipe 13, the first heat source-side branched refrigerant pipe 16, and the second heat source-side branched refrigerant pipe 18 are housed in the heat source-side unit 100.
  • the second heat source-side pressure reducing device 20 is arranged in the first heat source-side branched refrigerant pipe 16.
  • the second heat source-side pressure reducing device 20 expands high-pressure liquid refrigerant that has been branched from the first heat source-side refrigerant pipe 12 to flow into the first heat source-side branched refrigerant pipe 16 and reduces pressure of the ,refrigerant and causes the refrigerant to flow into the second heat transfer tube 10b.
  • the second heat source-side pressure reducing device 20 is housed in the heat source-side unit 100, and is configured as an electronic expansion valve, such as a linear electronic expansion valve (LEV), which has an opening degree capable of being regulated in a plurality of stages or continuously.
  • LEV linear electronic expansion valve
  • the refrigeration cycle apparatus 1 includes a first temperature sensor 30, a second temperature sensor 35, a first pressure sensor 40, and a second pressure sensor 45.
  • the first temperature sensor 30 is arranged on the first heat source-side refrigerant pipe 12 and between the branch joint portion 12a and the first heat source-side pressure reducing device 4.
  • the first temperature sensor 30 is a temperature sensor that detects, during cooling operation, a temperature of the first refrigerant having flowed out from the first heat transfer tube 10a of the subcooling heat exchanger 10 and flowing into the first heat source-side pressure reducing device 4 with the refrigerant pipe interposed between the first temperature sensor 30 and the first refrigerant.
  • the second temperature sensor 35 is arranged on the second heat source-side branched refrigerant pipe 18.
  • the second temperature sensor 35 is a temperature sensor that detects, during cooling operation, a temperature of the first refrigerant having flowed out from the second heat transfer tube 10b of the subcooling heat exchanger 10 and being injected into the intermediate-pressure portion of the first compressor 2 with the refrigerant pipe interposed between the second temperature sensor 35 and the first refrigerant.
  • first temperature sensor 30 and the second temperature sensor 35 for example, a semiconductor (for example, a thermistor), or metal (for example, a resistance temperature detector) is used.
  • the first temperature sensor 30 and the second temperature sensor 35 may be formed of the same material or may be formed of different materials.
  • the first pressure sensor 40 is arranged on the second heat source-side branched refrigerant pipe 18.
  • the first pressure sensor 40 is a pressure sensor that detects, during cooling operation, a pressure of the first refrigerant having flowed out from the second heat transfer tube 10b of the subcooling heat exchanger 10 and being injected into the intermediate-pressure portion of the first compressor 2.
  • the second pressure sensor 45 is housed in the load-side unit 200 and arranged on the load side refrigerant pipe arranged between the first load side connection valve 8a and the load-side pressure reducing device 5.
  • the second pressure sensor 45 is a pressure sensor that detects, during cooling operation, a pressure of the first refrigerant having passed through the first connection pipe 300 and flowing into the second pressure sensor 45.
  • first pressure sensor 40 and the second pressure sensor 45 for example, a quartz crystal piezoelectric pressure sensor, a semiconductor sensor, or a pressure transducer is used.
  • the first pressure sensor 40 and the second pressure sensor 45 may be formed of the same type of sensor or may be formed of different types of sensors.
  • Fig. 2 is a control block diagram for illustrating part of control performed in the controller 50 of the refrigeration cycle apparatus 1 according to Construction 1.
  • the controller 50 of Construction 1 controls the first refrigeration cycle 500 and includes a microcomputer including a CPU, memory (for example, ROM, RAM, and other memory), and an I/O port. As illustrated in Fig. 2 , the controller 50 receives electrical signals of temperature information detected by the first temperature sensor 30 and the second temperature sensor 35, and electrical signals of pressure information detected by the first pressure sensor 40 and the second pressure sensor 45. The controller 50 transmits control signals based on the electrical signals of temperature information and the electrical signals of pressure information to the first heat source-side pressure reducing device 4, the load-side pressure reducing device 5, and the second heat source-side pressure reducing device 20.
  • a microcomputer including a CPU, memory (for example, ROM, RAM, and other memory), and an I/O port.
  • the controller 50 receives electrical signals of temperature information detected by the first temperature sensor 30 and the second temperature sensor 35, and electrical signals of pressure information detected by the first pressure sensor 40 and the second pressure sensor 45.
  • the controller 50 transmits control signals based on the electrical signals of temperature information and the electrical signals
  • the opening degree of the first heat source-side pressure reducing device 4 is regulated in accordance with a transmitted control signal.
  • the opening degree of the load-side pressure reducing device 5 is regulated in accordance with a transmitted control signal.
  • the opening degree of the second heat source-side pressure reducing device 20 is regulated in accordance with a transmitted control signal.
  • the controller 50 can be configured to control other components of the first refrigeration cycle 500.
  • the controller 50 can be configured to control operation states, such as the starting and stopping of the operation of the heat source-side unit 100 and the load-side unit 200, and the regulation of an operating frequency of the first compressor 2.
  • the controller 50 includes a storage unit (not shown) that can store various pieces of data, such as the design pressure of the first connection pipe 300. Further, the controller 50 can be configured to include an interface unit (not shown) through which various pieces of data, such as the design pressure of the first connection pipe 300, can be input.
  • the first refrigerant is discharged from the first compressor 2 as high-temperature high-pressure gas refrigerant and flows into the first heat source-side heat exchanger 3.
  • the high-temperature high-pressure gas refrigerant having flowed into the first heat source-side heat exchanger 3 is subjected to heat exchange by transferring heat to a low-temperature medium, such as outdoor air, and the first refrigerant turns into high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant flows into the first heat transfer tube 10a of the subcooling heat exchanger 10, and is subjected to heat exchange with the first refrigerant flowing through the second heat transfer tube 10b, thereby being subcooled. Then, the first refrigerant turns into subcooled high-pressure liquid refrigerant.
  • the first refrigerant flowing through the second heat transfer tube 10b is (intermediate-pressure, for example) liquid refrigerant or two-phase refrigerant into which the high-pressure liquid refrigerant has been branched at the branch joint portion 12a of the first heat source-side refrigerant pipe 12 to flow into the first heat source-side branched refrigerant pipe 16 and has been expanded and reduced in pressure by the second heat source-side pressure reducing device 20 to turn.
  • the first refrigerant having flowed out from the second heat transfer tube 10b is injected into the intermediate-pressure portion of the first compressor 2 through the second heat source-side branched refrigerant pipe 18.
  • the high-pressure liquid refrigerant subcooled in the subcooling heat exchanger 10 flows into the first heat source-side pressure reducing device 4, and is expanded and reduced in pressure by the first heat source-side pressure reducing device 4, and the first refrigerant turns into (intermediate-pressure, for example) liquid refrigerant or two-phase refrigerant reduced in pressure.
  • the liquid refrigerant or two-phase refrigerant reduced in pressure flows out from the heat source-side unit 100, and flows into the load-side unit 200 through the first connection pipe 300.
  • the liquid refrigerant or two-phase refrigerant reduced in pressure having flowed into the load-side pressure reducing device 5 is further expanded and reduced in pressure, and the first refrigerant turns into low-temperature low-pressure two-phase refrigerant.
  • the low-temperature low-pressure two-phase refrigerant flows into the load side heat exchanger 6, and receives heat from a high-temperature medium, such as indoor air, and the first refrigerant evaporates to turn into high-quality two-phase refrigerant or low-temperature low-pressure gas refrigerant.
  • the high-quality two-phase refrigerant or low-temperature low-pressure gas refrigerant having flowed out from the load side heat exchanger 6 flows out from the load-side unit 200, and flows into the heat source-side unit 100 through the second connection pipe 400.
  • the high-quality two-phase refrigerant or low-temperature low-pressure gas refrigerant having flowed into the load-side unit 200 is sucked into the first compressor 2.
  • the refrigerant sucked into the first compressor 2 is compressed, and the first refrigerant turns into high-temperature high-pressure gas refrigerant, and is discharged from the first compressor 2.
  • the above-described cycle is repeated.
  • the controller 50 of the refrigeration cycle apparatus 1 regulates the opening degree of the first heat source-side pressure reducing device 4 to cause the first refrigerant to flow into the first connection pipe 300 as liquid refrigerant having a pressure less than the design pressure of the first connection pipe 300.
  • the controller 50 of the refrigeration cycle apparatus 1 according to Construction 1 can be configured to regulate the opening degree of the second heat source-side pressure reducing device 20 to increase a degree of subcooling so that the temperature of the first refrigerant flowing into the first heat source-side pressure reducing device 4 falls below a saturated liquid temperature of the first refrigerant at the design pressure.
  • an opening degree DH1 of the first heat source-side pressure reducing device 4 can be regulated in a range of 0 ⁇ DH1 ⁇ 1.
  • An opening degree DH2 of the second heat source-side pressure reducing device 20 can be regulated in a range of 0 ⁇ DH2 ⁇ 1.
  • Fig. 3 is a flowchart for illustrating an example of a control process during cooling operation performed in the controller 50 of the refrigeration cycle apparatus 1 according to Construction 1.
  • the control process illustrated in Fig. 3 may be performed at all times during cooling operation, or may be performed whenever variations in parameter of the refrigeration cycle apparatus 1, such as variations in frequency of the first compressor 2, are detected.
  • Step S11 the controller 50 determines whether a temperature Tc of the first refrigerant flowing into the first heat source-side pressure reducing device 4 detected by the first temperature sensor 30 is not less than a saturated liquid temperature Ta of the first refrigerant at the design pressure Pm.
  • the saturated liquid temperature Ta is a temperature value calculated by the controller 50 based on a value of the design pressure Pm.
  • the controller 50 controls, in Step S12, the opening degree DH2 of the second heat source-side pressure reducing device 20 to open the second heat source-side pressure reducing device 20 by a regulation value ⁇ DH2.
  • the regulation value ⁇ DH2 is a certain constant determined in view of specifications of, for example, the structure of the second heat source-side pressure reducing device 20.
  • the regulation value ⁇ DH2 can be set to 0.02.
  • the controller 50 determines in Step S13 whether a pressure P of the first refrigerant flowing into the load-side pressure reducing device 5 is not greater than a saturated liquid pressure Ps.
  • the pressure P of the first refrigerant flowing into the load-side pressure reducing device 5 is detected by the second pressure sensor 45.
  • the saturated liquid pressure Ps is a pressure value calculated by the controller 50 based on a value of the temperature Tc of the first refrigerant.
  • the saturated liquid pressure Ps is represented as a point on a saturated liquid line obtained through an isenthalpic change from the temperature Tc of the first refrigerant.
  • the controller 50 controls, in Step S14, the opening degree DH1 of the first heat source-side pressure reducing device 4 to open the first heat source-side pressure reducing device 4 by a regulation value ⁇ DH1.
  • the regulation value ⁇ DH1 is a certain constant determined in view of specifications of, for example, the structure of the first heat source-side pressure reducing device 4.
  • the regulation value ⁇ DH1 can be set to 0.01.
  • the refrigeration cycle apparatus 1 includes: the heat source-side unit 100 which receives the first compressor 2, the first heat source-side heat exchanger 3, and the first heat source-side pressure reducing device 4; the load-side unit 200, which receives the load-side pressure reducing device 5 and the load side heat exchanger 6, and is connected to the heat source-side unit 100 by the first connection pipe 300 arranged between the first heat source-side pressure reducing device 4 and the load-side pressure reducing device 5 and by the second connection pipe 400 arranged between the first compressor 2 and the load side heat exchanger 6; and the controller 50.
  • the first compressor 2, the first heat source-side heat exchanger 3, the first heat source-side pressure reducing device 4, the load-side pressure reducing device 5, and the load side heat exchanger 6 are connected by a refrigerant pipe and form the first refrigeration cycle 500 through which first refrigerant circulates.
  • the controller 50 regulates the opening degree of the first heat source-side pressure reducing device 4 to cause the first refrigerant to flow into the first connection pipe 300 as liquid refrigerant having a pressure less than a design pressure of the first connection pipe 300.
  • a related-art refrigeration apparatus for example, as a binary refrigeration apparatus, there is a typical refrigeration apparatus that causes two-phase refrigerant to pass through a local liquid pipe, to thereby reduce the amount of refrigerant in the overall refrigeration apparatus and reduce refrigerant cost and product cost.
  • a first expansion valve is provided in an outdoor unit to reduce the pressure and expand refrigerant, and to cause two-phase refrigerant to flow into the local liquid pipe.
  • a second expansion valve is provided in an indoor unit to reduce the pressure of and expand the two-phase refrigerant flowing in from the local liquid pipe further and to cause the refrigerant to flow into an indoor side heat exchanger functioning as an evaporator.
  • the related-art refrigeration apparatus has a so-called two-stage expansion structure in which the first expansion valve and the second expansion valve are provided in front of and behind the local liquid pipe.
  • the two-phase refrigerant is caused to flow into the local liquid pipe, and hence pressure loss and noise in the local pipe increase.
  • the two-phase refrigerant having flowed in from the local liquid pipe is not evenly distributed into the indoor side heat exchangers, and an increase in the number of the indoor side heat exchangers causes uneven distribution of the refrigerant.
  • the configuration according to Construction 1 enables, during cooling operation, the first refrigerant to flow into the first connection pipe 300 as liquid refrigerant having a pressure less than the design pressure of the first connection pipe 300 by regulating the opening degree of the first heat source-side pressure reducing device 4.
  • refrigerant flowing into the first connection pipe 300 can serve as liquid refrigerant, and reductions in pressure loss and noise in the first connection pipe 300 can be achieved. Thus, reduction in the amount of energy consumption in the refrigeration cycle apparatus 1 can be achieved. Further, the refrigerant flowing from the first connection pipe 300 into the load-side unit 200 serves as liquid refrigerant. Thus, even when a plurality of load side heat exchangers 6 are installed in the refrigeration cycle apparatus 1, the refrigerant can be distributed evenly.
  • the pressure of the liquid refrigerant flowing into the first connection pipe 300 can be set to less than the design pressure of the first connection pipe 300.
  • the refrigeration cycle apparatus 1 in which an existing local pipe can be used can be provided.
  • any connection pipe that causes pressure loss of the first refrigerant to occur in a range where a saturation temperature of the refrigerant in the load side heat exchanger 6 does not fall below an evaporating temperature in the load side heat exchanger 6 can be used.
  • the heat source-side unit 100 further includes: the subcooling heat exchanger 10, which is arranged between the first heat source-side heat exchanger 3 and the first heat source-side pressure reducing device 4, and includes the first heat transfer tube 10a and the second heat transfer tube 10b; the first heat source-side refrigerant pipe 12 connecting the one end of the first heat transfer tube 10a to the first heat source-side pressure reducing device 4; the second heat source-side refrigerant pipe 13 connecting the other end of the first heat transfer tube 10a to the first heat source-side heat exchanger 3; the first heat source-side branched refrigerant pipe 16 connecting the branch joint portion 12a arranged in the first heat source-side refrigerant pipe 12 to the one end of the second heat transfer tube 10b; the second heat source-side branched refrigerant pipe 18 connecting the other end of the second heat transfer tube 10b to the intermediate-pressure portion of the first compressor 2; and the second heat source-side pressure reducing device 20 arranged in the first heat
  • the subcooling heat exchanger 10 exchanges heat between the first refrigerant flowing through the first heat transfer tube 10a and the first refrigerant flowing through the second heat transfer tube 10b.
  • the controller 50 regulates the opening degree of the second heat source-side pressure reducing device 20 to increase a degree of subcooling so that the temperature of the first refrigerant flowing into the first heat source-side pressure reducing device 4 can fall below a saturated liquid temperature of the first refrigerant at the design pressure.
  • the above-described configuration enables the temperature of the first refrigerant flowing into the first heat source-side pressure reducing device 4 to fall below a saturated liquid temperature of the first refrigerant at the design pressure, thereby facilitating the first refrigerant to be kept in a liquid state even after the first refrigerant is reduced in pressure and expanded by the first heat source-side pressure reducing device 4.
  • Fig. 4 is a Mollier diagram for illustrating an operation of the refrigeration cycle apparatus 1 according to Construction 1.
  • the vertical axis represents absolute pressure (MPa)
  • the horizontal axis represents specific enthalpy (kJ/kg).
  • a saturated liquid line, a saturated vapor line, and steps in the first refrigeration cycle 500 are illustrated.
  • the first heat source-side pressure reducing device 4 and the load-side pressure reducing device 5 are schematically represented at corresponding positions in an expansion step.
  • a bent dashed-dotted line represents the state of the refrigerant that is reduced in pressure and expanded by the second heat source-side pressure reducing device 20, and is subjected to heat exchange in the second heat transfer tube 10b of the subcooling heat exchanger 10.
  • a point A on the Mollier diagram of Fig. 4 represents a position of the saturated liquid temperature Ta of the first refrigerant calculated from the design pressure Pm.
  • a point B on the Mollier diagram of Fig. 4 represents a position in a condensation step in the first refrigeration cycle 500 that is equal in specific enthalpy to the point A.
  • a point C on the Mollier diagram of Fig. 4 represents a position of the temperature Tc of the first refrigerant flowing into the first heat source-side pressure reducing device 4 in the condensation step in the first refrigeration cycle 500.
  • a point D on the Mollier diagram of Fig. 4 represents a position in the expansion step in the first refrigeration cycle 500 that is equal in specific enthalpy to the point C and at which a pressure reaches the design pressure Pm.
  • a point E on the Mollier diagram of Fig. 4 represents a point of intersection of a straight line representing the expansion step in the first refrigeration cycle 500 and the saturated liquid line and is a position at which the pressure of the first refrigerant reaches the saturated liquid pressure Ps.
  • the above-described configuration enables an increase in degree of subcooling by regulating the opening degree of the second heat source-side pressure reducing device 20 and exchanging heat between the first refrigerant flowing through the first heat transfer tube 10a and the first refrigerant flowing through the second heat transfer tube 10b in the subcooling heat exchanger 10. That is, the above-described configuration enables adjustment to be performed so that the point C is located on the left side of the point B in the Mollier diagram of Fig. 4 .
  • the temperature of the first refrigerant at the point B is equal to or slightly higher than the saturated liquid temperature Ta at the point A.
  • the temperature Tc of the first refrigerant flowing into the first heat source-side pressure reducing device 4 is lower than the saturated liquid temperature Ta at all times.
  • the above-described configuration enables control to be performed so that a state is obtained in which the pressure P of the first refrigerant flowing into the first connection pipe 300 is greater than the saturated liquid pressure Ps and less than the design pressure Pm by regulating the opening degree of the first heat source-side pressure reducing device 4.
  • the state in which the pressure P of the first refrigerant is greater than the saturated liquid pressure Ps and less than the design pressure Pm corresponds to a position of the expansion step between the point D and the point E in Fig. 4 .
  • the point A is 38 degrees Celsius.
  • a condensing temperature is 50 degrees Celsius
  • a degree of subcooling is about 30 degrees Celsius
  • the point C is 20 degrees Celsius.
  • the pressure of the refrigerant may be less than the design pressure and the refrigerant may be in a liquid state
  • the pressure is controlled to be in a range of from 1.00 MPa to 1.64 MPa by the first heat source-side pressure reducing device 4.
  • the configuration according to Construction 1 causes the temperature Tc of the first refrigerant flowing into the first heat source-side pressure reducing device 4 to be less than the saturated liquid temperature Ta, thereby enabling the first refrigerant to be kept in a liquid state even after the first refrigerant is reduced in pressure and expanded by the first heat source-side pressure reducing device 4.
  • Embodiment 1 of the present invention is a modification of the refrigeration cycle apparatus 1 according to Construction 1 described above.
  • Fig. 5 is a schematic refrigerant circuit diagram for illustrating an example of the refrigeration cycle apparatus 1 according to Embodiment 1.
  • the heat source-side unit 100 of the refrigeration cycle apparatus 1 according to Embodiment 1 includes a third heat source-side refrigerant pipe 14 connected between the second connection pipe 400 and the one end of the second heat transfer tube 10b of the subcooling heat exchanger 10 in place of the first heat source-side branched refrigerant pipe 16 of the refrigeration cycle apparatus 1 according to Construction 1 described above.
  • the heat source-side unit 100 of the refrigeration cycle apparatus 1 according to Embodiment 1 further includes a fourth heat source-side refrigerant pipe 15 connected between the other end of the second heat transfer tube 10b of the subcooling heat exchanger 10 and the first compressor 2 in place of the second heat source-side branched refrigerant pipe 18 of the refrigeration cycle apparatus 1 according to Construction 1 described above.
  • the heat source-side unit 100 of the refrigeration cycle apparatus 1 according to Embodiment 1 does not include the second heat source-side pressure reducing device 20.
  • the second temperature sensor 35 and the first pressure sensor 40 are provided on the fourth heat source-side refrigerant pipe 15.
  • the other components of the heat source-side unit 100 of the refrigeration cycle apparatus 1 according to Embodiment 1 are the same as those in the refrigeration cycle apparatus 1 according to Construction 1 described above.
  • Fig. 6 is a control block diagram for illustrating part of control performed in the controller 50 of the refrigeration cycle apparatus 1 according to Embodiment 1.
  • Fig. 6 is the same control block diagram as that of Fig. 2 except that it does not include the second heat source-side pressure reducing device 20.
  • the controller 50 of the refrigeration cycle apparatus 1 is configured to regulate the opening degree of the load-side pressure reducing device 5 to increase a degree of subcooling so that the temperature of the first refrigerant flowing into the first heat source-side pressure reducing device 4 falls below a saturated liquid temperature of the first refrigerant at the design pressure.
  • an opening degree DH1 of the first heat source-side pressure reducing device 4 can be regulated in a range of 0 ⁇ DH1 ⁇ 1.
  • An opening degree DL of the load-side pressure reducing device 5 can be regulated in a range of 0 ⁇ DL ⁇ 1.
  • Fig. 7 is a flowchart for illustrating an example of a control process during cooling operation performed in the controller 50 of the refrigeration cycle apparatus 1 according to Embodiment 1. Similarly to the control process illustrated in Fig. 3 , the control process illustrated in Fig. 7 may be performed at all times during cooling operation, or may be performed whenever variations in parameter of the refrigeration cycle apparatus 1, such as variations in frequency of the first compressor 2, are detected.
  • Step S21 as in Step S11 in Construction 1 described above, the controller 50 determines whether a temperature Tc of the first refrigerant flowing into the first heat source-side pressure reducing device 4 detected by the first temperature sensor 30 is not less than a saturated liquid temperature Ta of the first refrigerant at the design pressure Pm.
  • the controller 50 controls, in Step S22, the opening degree DL of the load-side pressure reducing device 5 to open the load-side pressure reducing device 5 by a regulation value ⁇ DL.
  • the regulation value ⁇ DL is a certain constant determined in view of specifications of, for example, the structure of the load-side pressure reducing device 5.
  • the regulation value ⁇ DL can be set to 0.02.
  • Step S23 as in Step S13 in Construction 1 described above, when the temperature Tc of the first refrigerant is less than the saturated liquid temperature Ta, the controller 50 determines whether a pressure P of the first refrigerant flowing into the load-side pressure reducing device 5 is not greater than a saturated liquid pressure Ps. When the pressure P of the first refrigerant is greater than the saturated liquid pressure Ps, the control process ends.
  • Step S24 as in Step S14 in Construction 1 described above, when the pressure P of the first refrigerant is not greater than the saturated liquid pressure Ps, the controller 50 controls the opening degree DH1 of the first heat source-side pressure reducing device 4 to open the first heat source-side pressure reducing device 4 by a regulation value ⁇ DH1.
  • the heat source-side unit 100 of the refrigeration cycle apparatus 1 further includes: the subcooling heat exchanger 10, which is arranged between the first heat source-side heat exchanger 3 and the first heat source-side pressure reducing device 4, and includes the first heat transfer tube 10a and the second heat transfer tube 10b; the first heat source-side refrigerant pipe 12 connecting the one end of the first heat transfer tube 10a to the first heat source-side pressure reducing device 4; the second heat source-side refrigerant pipe 13 connecting the other end of the first heat transfer tube 10a to the first heat source-side heat exchanger 3; the third heat source-side refrigerant pipe 14 connected between the second connection pipe 400 and the one end of the second heat transfer tube 10b; and the fourth heat source-side refrigerant pipe 15 connected between the other end of the second heat transfer tube 10b and the first compressor 2.
  • the subcooling heat exchanger 10 exchanges heat between the first refrigerant flowing through the first heat transfer tube 10a and the first refrigerant flowing through the second heat transfer tube 10b.
  • the controller 50 regulates the opening degree of the load-side pressure reducing device 5 to increase a degree of subcooling so that the temperature of the first refrigerant flowing into the first heat source-side pressure reducing device 4 falls below a saturated liquid temperature of the first refrigerant at the design pressure.
  • Fig. 8 is a Mollier diagram for illustrating an operation of the refrigeration cycle apparatus 1 according to Embodiment 1.
  • Fig. 8 is the same Mollier diagram as that of Fig. 4 except that there is not illustrated a bent dashed-dotted line representing the state of the refrigerant that is subjected to heat exchange in the second heat transfer tube 10b of the subcooling heat exchanger 10.
  • the configuration according to Embodiment 1 enables an increase in degree of subcooling by regulating the opening degree of the load-side pressure reducing device 5 and exchanging heat between the first refrigerant flowing through the first heat transfer tube 10a and the first refrigerant flowing through the second heat transfer tube 10b in the subcooling heat exchanger 10. Further, the configuration causes the temperature Tc of the first refrigerant flowing into the first heat source-side pressure reducing device 4 to be less than the saturated liquid temperature Ta, thereby enabling the first refrigerant to be kept in a liquid state even after the first refrigerant is reduced in pressure and expanded by the first heat source-side pressure reducing device 4.
  • the configuration according to Embodiment 1 enables an improvement in the reliability of the refrigeration cycle apparatus 1. Further, in the configuration according to Embodiment 1, all the first refrigerant flowing through the refrigeration cycle apparatus 1 can be used in heat exchange in the load side heat exchanger 6, thereby enabling an improvement in cooling capacity of the refrigeration cycle apparatus 1.
  • FIG. 9 is a schematic refrigerant circuit diagram for illustrating an example of the refrigeration cycle apparatus 1 according to Construction 2.
  • the heat source-side unit 100 further includes the second refrigeration cycle 600 in which a second compressor 62, a second heat source-side heat exchanger 63, a third heat source-side pressure reducing device 64, and the first heat source-side heat exchanger 3 are connected by a refrigerant pipe and through which second refrigerant circulates.
  • the first heat source-side heat exchanger 3 exchanges heat between the first refrigerant flowing in from the first compressor 2 and the second refrigerant flowing in from the third heat source-side pressure reducing device 64.
  • the second heat source-side heat exchanger 63 functions as a radiator.
  • the first heat source-side heat exchanger 3 functions as a cascade heat exchanger that exchanges heat between the first refrigerant flowing in from the first compressor 2 and the second refrigerant flowing in from the third heat source-side pressure reducing device 64 during cooling operation.
  • examples of second refrigerant that can be used include hydrofluorocarbon, such as R32, hydrofluoroolefins, such as 2,3,3,3-tetrafluoro-1-propene (HFO-1234yf), and a mixed refrigerant, such as R410A.
  • hydrofluorocarbon such as R32
  • hydrofluoroolefins such as 2,3,3,3-tetrafluoro-1-propene (HFO-1234yf)
  • R410A mixed refrigerant
  • Fig. 10 is a control block diagram for illustrating part of control performed in the controller 50 of the refrigeration cycle apparatus 1 according to Construction 2.
  • Fig. 10 is the same control block diagram as that of Fig. 2 except that the controller 50 controls the opening degree of the third heat source-side pressure reducing device 64.
  • Fig. 11 is a flowchart for illustrating an example of a control process during cooling operation performed in the controller 50 of the refrigeration cycle apparatus 1 according to Construction 2.
  • the control process illustrated in Fig. 11 is the same as the control process illustrated in Fig. 3
  • Step S31 to Step S34 in Fig. 11 correspond to Step S11 to Step S14 in Fig. 3 .
  • the other descriptions of the control process are also the same as those of the control process in Construction 1 described above.
  • Fig. 12 is a Mollier diagram for illustrating an operation of the refrigeration cycle apparatus 1 according to Construction 2.
  • Fig. 12 is the same Mollier diagram as that of Fig. 4 .
  • the configuration according to Construction 2 also enables, as in Construction 1 described above, an increase in degree of subcooling by regulating the opening degree of the second heat source-side pressure reducing device 20 and exchanging heat between the first refrigerant flowing through the first heat transfer tube 10a and the first refrigerant flowing through the second heat transfer tube 10b in the subcooling heat exchanger 10. Further, the configuration causes the temperature Tc of the first refrigerant flowing into the first heat source-side pressure reducing device 4 to be less than the saturated liquid temperature Ta, thereby enabling the first refrigerant to be kept in a liquid state even after the first refrigerant is reduced in pressure and expanded by the first heat source-side pressure reducing device 4.
  • CO 2 is used as the first refrigerant, and CO 2 can be used in a state equal to or below a supercritical state.
  • the refrigeration cycle apparatus 1 exhibiting excellent safety can be provided.
  • Embodiment 1 described above, and various modifications can be made, as long as the resulting embodiment comprises all features of appended independent claim 1.
  • the refrigeration cycle apparatus 1 according to Embodiment 1 described above can be used in an air-conditioning apparatus, a refrigerating machine, and other apparatus.
  • the refrigeration cycle apparatus 1 can be configured so that heating operation can be performed.
  • a refrigerant flow switching device for example, a four-way valve
  • the refrigeration cycle apparatus 1 thereby enabling switching between cooling operation and heating operation.
  • the opening degree of the second heat source-side pressure reducing device 20 or the load-side pressure reducing device 5 is regulated, thereby enabling control to be performed so that the amount of liquid return to the first compressor 2 is reduced.

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Claims (3)

  1. Kühlkreislaufvorrichtung (1), die Folgendes umfasst:
    Wärmequellenseiteneinheit (100), in der ein erster Kompressor (2), ein erster Wärmequellenseitenwärmetauscher (3) und eine erste Wärmequellenseitendruckreduzierungsvorrichtung (4) aufgenommen sind;
    eine Lastseiteneinheit (200), in der eine Lastseitendruckreduzierungsvorrichtung (5) und ein Lastseitenwärmetauscher (6) aufgenommen sind und die über eine erste Verbindungsleitung (300), die zwischen der ersten Wärmequellenseitendruckreduzierungsvorrichtung (4) und der Lastseitendruckreduzierungsvorrichtung (5) angeordnet ist, und über eine zweite Verbindungsleitung (400), die zwischen dem ersten Kompressor (2) und dem Lastseitenwärmetauscher (6) angeordnet ist, mit der Wärmequellenseiteneinheit (100) verbunden ist; und
    eine Steuerung (50),
    wobei der erste Kompressor (2), der erste Wärmequellenseitenwärmetauscher (3), die erste Wärmequellenseitendruckreduzierungsvorrichtung (4), die Lastseitendruckreduzierungsvorrichtung (5) und der Lastseitenwärmetauscher (6) über eine Kühlmittelleitung miteinander verbunden sind und einen ersten Kühlkreislauf (500) ausbilden, durch den ein erstes Kühlmittel zirkuliert,
    wobei die Wärmequellenseiteneinheit (100) ferner Folgendes umfasst:
    einen Unterkühlungswärmetauscher (10), der zwischen dem ersten Wärmequellenseitenwärmetauscher (3) und der ersten Wärmequellenseitendruckreduzierungsvorrichtung (4) angeordnet ist und ein erstes Wärmetransportrohr (10a) und ein zweites Wärmetransportrohr (10b) umfasst,
    eine erste Wärmequellenseitenkühlmittelleitung (12), die ein Ende des ersten Wärmetransportrohrs (10a) mit der ersten Wärmequellenseitendruckreduzierungsvorrichtung (4) verbindet,
    eine zweite Wärmequellenseitenkühlmittelleitung (13), die das andere Ende des ersten Wärmetransportrohrs (10a) mit dem ersten Wärmequellenseitenwärmetauscher (3) verbindet,
    eine dritte Wärmequellenseitenkühlmittelleitung (14), die zwischen die zweite Verbindungsleitung (400) und ein Ende des zweiten Wärmetransportrohres (10b) geschaltet ist, und
    eine vierte Wärmequellenseitenkühlmittelleitung (15), die zwischen das andere Ende des zweiten Wärmetransportrohrs (10b) und den ersten Kompressor (2) geschaltet ist,
    wobei der Unterkühlungswärmetauscher (10) ausgelegt ist, während eines Kühlvorgangs, bei dem der Lastseitenwärmetauscher (6) als Verdampfer fungiert, Wärme zwischen dem ersten Kühlmittel, das durch das erste Wärmetransportrohr (10a) strömt, und dem ersten Kühlmittel, das durch das zweite Wärmetransportrohr (10b) strömt, auszutauschen,
    wobei die Steuerung (50) ausgelegt ist, um während des Kühlvorgangs ein Öffnungsausmaß der Lastseitendruckreduzierungsvorrichtung (5) zu regeln, um ein Unterkühlungsausmaß zu erhöhen, so dass die Temperatur des ersten Kühlmittels, das in die erste Wärmequellenseitendruckreduzierungsvorrichtung (4) strömt, unter die Gesättigte-Flüssigkeit-Temperatur des ersten Kühlmittels bei einem Auslegungsdruck der ersten Verbindungsleitung (300) fällt, und
    wobei die Steuerung (50) ausgelegt ist, um während des Kühlvorgangs ein Öffnungsausmaß der ersten Wärmequellenseitendruckreduzierungsvorrichtung (4) zu regeln, um zu bewirken, dass das erste Kühlmittel als flüssiges Kühlmittel mit einem Druck, der geringer ist als der Auslegungsdruck der ersten Verbindungsleitung (300), in die erste Verbindungsleitung (300) und in die Lastseitendruckreduzierungsvorrichtung (5), deren Druck größer ist als ein Gesättigte-Flüssigkeit-Druck, strömt.
  2. Kühlkreislaufvorrichtung (1) nach Anspruch 1,
    wobei die Wärmequellenseiteneinheit (100) ferner einen zweiten Kühlkreislauf (600) umfasst, in dem ein zweiter Kompressor (62), ein zweiter Wärmequellenseitenwärmetauscher (63), eine dritte Wärmequellenseitendruckreduzierungsvorrichtung (64) und der erste Wärmequellenseitenwärmetauscher (3) über eine Kühlmittelleitung miteinander verbunden sind, durch die ein zweites Kühlmittel zirkuliert,
    wobei der erste Wärmequellenseitenwärmetauscher (3) ausgelegt ist, um während des Kühlvorgangs Wärme zwischen dem ersten Kühlmittel, das aus dem ersten Kompressor (2) einströmt, und dem zweiten Kühlmittel, das aus der dritten Wärmequellenseitendruckreduzierungsvorrichtung (64) einströmt, auszutauschen, und
    wobei der zweite Wärmequellenseitenwärmetauscher (63) während des Kühlvorgangs als Kühler fungiert.
  3. Kühlkreislaufvorrichtung (1) nach Anspruch 1 oder 2, wobei das erste Kühlmittel CO2 umfasst.
EP18198946.8A 2015-06-18 2015-06-18 Kältekreislaufvorrichtung Active EP3457049B1 (de)

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US10655878B2 (en) * 2018-07-06 2020-05-19 Johnson Controls Technology Company Variable refrigerant flow system with sub-cooling temperature optimization using extremum-seeking control
CN110953699B (zh) * 2018-09-26 2021-05-18 杭州三花研究院有限公司 一种空调系统及其控制方法
US11828507B2 (en) 2018-09-25 2023-11-28 Hangzhou Sanhua Research Institute Co., Ltd. Air conditioning system and control method therefor
JP7469583B2 (ja) * 2019-06-12 2024-04-17 ダイキン工業株式会社 空調機
DE102020122713A1 (de) 2020-08-31 2022-03-03 Andreas Bangheri Wärmepumpe und Verfahren zum Betreiben einer Wärmepumpe
CN112033040B (zh) * 2020-09-15 2022-08-30 广东美的暖通设备有限公司 空调系统的控制方法和计算机可读存储介质
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JPWO2016203624A1 (ja) 2018-01-18
EP3312524A4 (de) 2018-07-04
EP3312524A1 (de) 2018-04-25
WO2016203624A1 (ja) 2016-12-22
JP6735744B2 (ja) 2020-08-05
EP3312524B1 (de) 2020-06-03

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