WO2024189697A1 - 冷凍サイクル装置 - Google Patents

冷凍サイクル装置 Download PDF

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Publication number
WO2024189697A1
WO2024189697A1 PCT/JP2023/009413 JP2023009413W WO2024189697A1 WO 2024189697 A1 WO2024189697 A1 WO 2024189697A1 JP 2023009413 W JP2023009413 W JP 2023009413W WO 2024189697 A1 WO2024189697 A1 WO 2024189697A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
pressure
flows
flow path
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2023/009413
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
琢朗 松尾
元輝 高木
保則 田林
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Europe NV
Daikin Industries Ltd
Original Assignee
Daikin Europe NV
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 Europe NV, Daikin Industries Ltd filed Critical Daikin Europe NV
Priority to EP23927321.2A priority Critical patent/EP4679009A1/en
Priority to PCT/JP2023/009413 priority patent/WO2024189697A1/ja
Priority to JP2025506253A priority patent/JPWO2024189697A1/ja
Publication of WO2024189697A1 publication Critical patent/WO2024189697A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F25B2313/003—Indoor unit with water as a heat sink or heat source
    • 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
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0253—Compressor control by controlling speed with variable speed
    • 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
    • F25B2700/193—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

Definitions

  • Patent Document 1 JP Patent Publication No. 2009-085568 discloses a refrigeration cycle device (refrigeration circuit) that includes a refrigerant circuit having a compressor, a condenser, an evaporator, an internal heat exchanger, and an expansion mechanism, and that is filled with a non-azeotropic refrigerant mixture.
  • This disclosure provides a refrigeration cycle device that can accurately grasp the state of the refrigerant in the evaporator even when it is equipped with an internal heat exchanger.
  • the refrigeration cycle device of the first aspect includes a refrigerant circuit and a temperature detection unit.
  • the refrigerant circuit has a compressor, a radiator, a pressure reducing means, an internal heat exchanger, and an evaporator.
  • the temperature detection unit detects the temperature of the refrigerant.
  • the refrigerant circuit is filled with a non-azeotropic refrigerant mixture.
  • the internal heat exchanger exchanges heat between the refrigerant flowing from the evaporator to the compressor and the refrigerant flowing from the radiator to the evaporator.
  • the temperature detection unit detects the temperature of the refrigerant that flows out of the evaporator and before it flows into the internal heat exchanger.
  • This refrigeration cycle device can detect the temperature of the refrigerant flowing out of the evaporator before it flows into the internal heat exchanger. Therefore, even though this refrigeration cycle device is equipped with an internal heat exchanger, it can accurately grasp the state of the refrigerant in the evaporator.
  • the refrigeration cycle device of the second aspect is the refrigeration cycle device of the first aspect, further comprising a pressure detection unit that detects the pressure of the refrigerant before it flows out of the internal heat exchanger and into the compressor.
  • This refrigeration cycle device takes into account the refrigerant temperature detected by the temperature detection unit as well as the refrigerant pressure before it flows into the compressor, allowing for more accurate understanding of the state of the refrigerant in the evaporator.
  • the refrigeration cycle device of the third aspect is the refrigeration cycle device of the second aspect, further comprising a control unit that calculates the wetness of the refrigerant before it flows into the internal heat exchanger based on the detection results of the temperature detection unit and the pressure detection unit.
  • This control unit can calculate the wetness of the refrigerant before it flows into the internal heat exchanger based on the two detection results obtained from the temperature detection unit and the pressure detection unit.
  • the refrigeration cycle device of the fourth aspect is the refrigeration cycle device of the third aspect, in which the pressure reducing means reduces the pressure of the refrigerant flowing from the radiator to the evaporator.
  • the control unit controls the opening degree of the pressure reducing means based on the wetness.
  • the control unit can utilize temperature glide to efficiently exchange heat with the refrigerant in the internal heat exchanger. Therefore, the refrigeration cycle device can efficiently perform heating and cooling operations.
  • FIG. 1 is a schematic configuration diagram of a refrigeration cycle device 1.
  • FIG. FIG. 2 is a block diagram of a control unit 100. 2 is a Mollier diagram showing the relationship between temperature T, pressure P, and specific enthalpy H.
  • FIG. 1 is a schematic configuration diagram of a refrigeration cycle device 1 according to one embodiment.
  • the refrigeration cycle device 1 includes a refrigerant circuit 90 and a control unit 100.
  • the refrigerant circuit 90 mainly includes a compressor 10, a switching mechanism 20, a first pressure reducing means 41, a second pressure reducing means 42, a bridge circuit 50, a first heat exchanger 61, a second heat exchanger 62, an internal heat exchanger 63, an economizer heat exchanger 64, an accumulator 80, a liquid refrigerant flow path 71, an injection flow path 72, a first branch flow path 73, and a second branch flow path 74.
  • the refrigeration cycle device 1 performs heating and cooling operations. More specifically, the refrigeration cycle device 1 causes the refrigerant circuit 90 to perform a refrigeration cycle to heat or cool the water circulating through the water circuit 200, and performs heating and cooling operations in a target space (not shown) using this water.
  • Refrigerant circuit 90 The refrigerant circuit 90 is filled with a non-azeotropic refrigerant mixture as a refrigerant. Although not limited thereto, the refrigerant circuit 90 is filled with R454C.
  • (2-1-1) Compressor 10 The compressor 10 compresses a low-pressure refrigerant in a refrigeration cycle to a high pressure. More specifically, the compressor 10 is a two-stage compressor that draws in the low-pressure refrigerant in the refrigeration cycle, compresses it to an intermediate pressure in the refrigeration cycle, and then further compresses the intermediate-pressure refrigerant to a high pressure and discharges it.
  • the compressor 10 has a casing 10a, a first compression element 10b, a second compression element 10c, a drive motor 10d, a first suction section 10e, a second suction section 10f, and a discharge section 10g.
  • the casing 10a houses the first compression element 10b and the second compression element 10c.
  • the first compression element 10b and the second compression element 10c are connected to a single drive shaft (not shown).
  • the drive motor 10d drives and rotates the first compression element 10b and the second compression element 10c via the drive shaft.
  • the compressor 10 has a single-shaft two-stage compression structure.
  • the rotation speed of the drive motor 10d is controlled by the control unit 100.
  • the first suction section 10e draws in low-pressure refrigerant from the refrigerant circuit 90.
  • the second suction section 10f draws in intermediate-pressure refrigerant from the refrigerant circuit 90.
  • the discharge section 10g discharges high-pressure refrigerant to the refrigerant circuit 90.
  • the second suction section 10f is an example of a suction section.
  • the first compression element 10b compresses the refrigerant sucked into the first suction section 10e to an intermediate pressure and discharges it to the second compression element 10c.
  • the second compression element 10c compresses both the intermediate pressure refrigerant discharged by the first compression element 10b and the intermediate pressure refrigerant sucked into the second suction section 10f to a high pressure and discharges it to the discharge section 10g.
  • the structure of the compressor 10 is not limited to a single-shaft, two-stage compression structure.
  • the structure of the compressor 10 may be configured with a compression element driven by a separate drive motor, for example.
  • the switching mechanism 20 switches the direction in which the refrigerant flows in the refrigerant circuit 90 between two states.
  • the switching mechanism 20 is a four-way switching valve.
  • the switching mechanism 20 has a first port P1, a second port P2, and It has a third port P3 and a fourth port P4.
  • the switching mechanism 20 switches between a first state (indicated by a dashed line in FIG. 1) and a second state (indicated by a solid line in FIG. 1).
  • the switching mechanism 20 connects the first port P1 to the second port P2, and connects the third port P3 to the fourth port P4.
  • the switching mechanism 20 connects the first port P1 to the fourth port P4, and connects the second port P2 to the third port P3.
  • the state of the switching mechanism 20 is controlled by the control unit 100.
  • the switching mechanism 20 is not limited to a four-way switching valve.
  • the switching mechanism 22 may be configured, for example, by combining multiple solenoid valves and refrigerant flow paths.
  • the first heat exchanger 61 exchanges heat between the refrigerant flowing through the refrigerant circuit 90 and the water circulating through the water circuit 200.
  • the first heat exchanger 61 functions as a refrigerant radiator in heating operation and as a refrigerant evaporator in cooling operation.
  • the first heat exchanger 61 has a refrigerant flow path 61a and a water flow path 61b. Note that FIG. 1 shows only a portion of the water circuit 200.
  • the refrigerant flow path 61a is provided in the refrigerant circuit 90.
  • the water flow path 61b is provided in the water circuit 200.
  • the refrigerant flowing through the refrigerant flow path 61a exchanges heat with the water flowing through the water flow path 61b.
  • the water that has exchanged heat with the refrigerant circulates through the water circuit 200 to heat or cool the air in the target space.
  • the end of the refrigerant flow path 61a into which the refrigerant flows is referred to as the first end 61aa
  • the end of the refrigerant flow path 61a from which the refrigerant flows out is referred to as the second end 61ab.
  • the second heat exchanger 62 exchanges heat between the refrigerant flowing through the refrigerant circuit 90 and the air in the location where the second heat exchanger 62 is installed.
  • the second heat exchanger 62 functions as a refrigerant evaporator in heating operation and as a refrigerant radiator in cooling operation.
  • the second heat exchanger 62 has a refrigerant flow path (not shown) 62a.
  • the second heat exchanger 62 is provided in the refrigerant circuit 90.
  • the refrigerant flowing through the refrigerant passage of the second heat exchanger 62 exchanges heat with the air in the location where the second heat exchanger 62 is installed.
  • the end of the refrigerant flow path of the second heat exchanger 62 into which the refrigerant flows is referred to as the first end 62aa
  • the end of the refrigerant flow path 61a from which the refrigerant flows out is referred to as the second end 62ab.
  • first heat exchanger 61 and the second heat exchanger 62 may be collectively referred to as the main heat exchanger 60.
  • the bridge circuit 50 allows the refrigerant flowing out of the first heat exchanger 61 and the second heat exchanger 62 and flowing through the liquid refrigerant flow path 71 to flow into the first branch flow path 73.
  • the bridge circuit 50 allows the refrigerant flowing out of the internal heat exchanger 63 and flowing through the second branch flow path 74 to flow into the liquid refrigerant flow path 71.
  • the bridge circuit 50 has a first check valve 51, a second check valve 52, a third check valve 53, and a fourth check valve 54.
  • the first check valve 51 has an outlet side connected to the outlet side of the second check valve 52, and an inlet side connected to the outlet side of the fourth check valve 54.
  • the third check valve 53 has an outlet side connected to the inlet side of the second check valve 52, and an inlet side connected to the inlet side of the fourth check valve 54.
  • connection between the outflow side of the first check valve 51 and the outflow side of the second check valve 52 is referred to as the first connection part C1.
  • the connection between the inflow side of the second check valve 52 and the outflow side of the third check valve 53 is referred to as the second connection part C2.
  • the connection between the inflow side of the third check valve 53 and the inflow side of the fourth check valve 54 is referred to as the third connection part C3.
  • the connection between the outflow side of the fourth check valve 54 and the inflow side of the first check valve 51 is referred to as the fourth connection part C4.
  • the liquid refrigerant flow path 71 is a refrigerant flow path that connects a first end 61aa of the refrigerant flow path 61a of the first heat exchanger 61 and a first end 62aa of the refrigerant flow path of the second heat exchanger 62 to the bridge circuit 50.
  • the liquid refrigerant flow path 71 has a first portion 71a and a second portion 71b.
  • the first part 71a connects the first end 61aa of the first heat exchanger 61 to the second connection part C2 of the bridge circuit 50.
  • the second part 71b connects the first end 62aa of the second heat exchanger 62 to the fourth connection part C4 of the bridge circuit 50.
  • the internal heat exchanger 63 is a pre-cooling heat exchanger that cools the refrigerant flowing from the main heat exchanger 60 functioning as a radiator to the main heat exchanger 60 functioning as an evaporator.
  • the internal heat exchanger 63 has a heat transfer tube 63a and a second heat transfer tube 63b.
  • the internal heat exchanger 63 exchanges heat between the refrigerant passing through the first heat transfer tube 63a and the refrigerant passing through the second heat transfer tube 63b.
  • the first heat transfer pipe 63a carries the refrigerant that flows from the main heat exchanger 60, which functions as an evaporator, to the first suction section 10e of the compressor 10.
  • One end of the first heat transfer pipe 63a is connected to the third port P3 of the switching mechanism 20.
  • the other end of the first heat transfer pipe 63a is connected to the first suction section 10e of the compressor 10 via the accumulator 80.
  • the second heat transfer tube 63b is used for refrigerant flowing from the main heat exchanger 60 functioning as a radiator to the main heat exchanger 60 functioning as an evaporator.
  • One end of the second heat transfer tube 63b is connected to the third connection C3 of the bridge circuit 50.
  • the other end of the second heat transfer tube 63b is connected to the first connection C1 of the bridge circuit 50.
  • First branch flow path 73 and second branch flow path 74 are refrigerant flow paths that branch off from the liquid refrigerant flow path 71 via the bridge circuit 50 and connect to the second heat transfer tube 63b.
  • One end of the first branch flow path 73 is connected to the first connection part C1 of the bridge circuit 50.
  • the other end of the first branch flow path 73 is connected to the second heat transfer tube 63b.
  • the second heat transfer tube 64b (described later) of the economizer heat exchanger 64 is provided midway along the first branch flow path 73.
  • One end of the second branch flow path 74 is connected to the third connection part C3 of the bridge circuit 50.
  • the other end of the second branch flow path 74 is connected to the end of the second heat transfer tube 63b opposite to the first branch flow path 73.
  • First pressure reducing means 41 reduces the pressure of the refrigerant flowing from the main heat exchanger 60 functioning as a radiator to the main heat exchanger 60 functioning as an evaporator.
  • the first pressure reducing means 41 is provided midway through the second branch flow path 74.
  • the opening degree of the first pressure reducing means 41 is controlled by the control unit 100.
  • the first pressure reducing means 41 is an example of a pressure reducing means.
  • the first pressure reducing means 41 is an electric expansion valve.
  • the injection flow passage 72 is a refrigerant flow passage that branches off from a portion of the first branch flow passage 73 between the economizer heat exchanger 64 and the second heat transfer tube 63b of the internal heat exchanger 63, and is connected to the second suction section 10f of the compressor 10.
  • a first heat transfer tube 64a (described later) of the economizer heat exchanger 64 is provided midway through the injection flow passage 72, as will be described in detail later.
  • Second pressure reducing means 42 reduces the pressure of the refrigerant passing therethrough to an intermediate pressure.
  • the second pressure reducing means 42 is provided in the middle of the injection flow path 72. More specifically, the second pressure reducing means 42 is provided between a connection portion of the injection flow path 72 with the first branch flow path 73 and a connection portion of the injection flow path 72 with the economizer heat exchanger 64.
  • the opening degree of the second pressure reducing means 42 is controlled by the control unit 100.
  • the second pressure reducing means 42 is an electric expansion valve.
  • Economizer heat exchanger 64 exchanges heat between the refrigerant depressurized by the second depressurizing means 42 passing through the injection flow path 72 and the refrigerant flowing from the main heat exchanger 60 functioning as a radiator to the main heat exchanger 60 functioning as an evaporator.
  • the economizer heat exchanger 64 has a first heat transfer tube 64a and a second heat transfer tube 64b. The economizer heat exchanger 64 exchanges heat between the refrigerant passing through the first heat transfer tube 64a and the refrigerant passing through the second heat transfer tube 64b.
  • the first heat transfer tube 64a is connected to the injection flow path 72 by the refrigerant.
  • the first heat transfer tube 64a is provided in the injection flow path 72.
  • One end of the first heat transfer tube 64a is connected to the second pressure reducing means 42 and the first branch flow path 73 via the injection flow path 72.
  • the other end of the first heat transfer tube 64a is connected to the second suction section 10f of the compressor 10 via the injection flow path 72.
  • the second heat transfer tube 64b passes through the refrigerant flowing through the first branch flow path 73.
  • the second heat transfer tube 64b is provided in the first branch flow path 73.
  • One end of the second heat transfer tube 64b is connected to the first connection part C1 of the bridge circuit 50 via the first branch flow path 73.
  • the other end of the second heat transfer tube 64b is connected to the second heat transfer tube 63b of the internal heat exchanger 63 via the first branch flow path 73.
  • the accumulator 80 separates the refrigerant flowing out of the first heat transfer tube 63a and flowing into the first suction section 10e of the compressor 10 into a gas refrigerant and a liquid refrigerant.
  • the accumulator 80 is provided in a refrigerant flow path connecting the other end of the first heat transfer tube 63a and the first suction section 10e of the compressor 10.
  • Temperature detection unit 81 detects the temperature T of the refrigerant before it flows out of the main heat exchanger 60 functioning as an evaporator and flows into the first heat transfer tube 63a of the internal heat exchanger 63.
  • the temperature detection unit 81 is provided in a refrigerant flow path that connects one end of the first heat transfer tube 63a and the third port P3 of the switching mechanism 20.
  • the control unit 100 acquires the temperature of the refrigerant detected by the temperature detection unit 81.
  • the temperature detection unit 81 is a thermistor.
  • Pressure detection unit 82 detects the pressure P of the refrigerant flowing out from the first heat transfer tube 63a of the internal heat exchanger 63 and before flowing into the first suction section 10e of the compressor 10.
  • the pressure detection unit 82 is provided in a refrigerant flow path that connects the accumulator 80 and the first suction section 10e of the compressor 10.
  • the control unit 100 acquires the refrigerant pressure detected by the pressure detection unit 82.
  • Control Unit 100 1 is a block diagram of a control unit 100.
  • the control unit 100 controls each device of the refrigerant circuit 90 to cause the refrigerant circuit 90 to perform a refrigeration cycle.
  • the control unit 100 is electrically connected to the compressor 10, the switching mechanism 20, the first pressure reducing means 41, the second pressure reducing means 42, the temperature detection unit 81, and the pressure detection unit 82 so as to be able to transmit and receive signals to and from them.
  • the control unit 100 is realized by a computer.
  • the control unit 100 includes a control arithmetic unit and a storage device (both not shown).
  • the control arithmetic unit can be a processor such as a CPU or a GPU.
  • the control arithmetic unit reads a program stored in the storage device and performs predetermined arithmetic processing in accordance with the program. Furthermore, the control arithmetic unit can write the results of calculations to the storage device and read information stored in the storage device in accordance with the program.
  • control unit 100 controls each device as described below.
  • control unit 100 controls each part of the refrigerant circuit 90 as follows.
  • the control unit 100 starts the compressor 10 and controls the rotation speed of the drive motor 10d.
  • the switching mechanism 20 is controlled to be in the first state.
  • the opening degree of the first pressure reducing means 41 is controlled based on the temperature detection unit 81 and the pressure detection unit 82. Details of the control of the first pressure reducing means 41 will be described later.
  • the opening degree of the second pressure reducing means 42 is controlled.
  • the control unit 100 controls the opening degree of the second pressure reducing means 42 so that the degree of superheat of the refrigerant flowing out of the second pressure reducing means 42 approaches a predetermined target degree of superheat.
  • the high-pressure gas refrigerant flowing out from the discharge port 10g passes through the switching mechanism 22, in the order of the first port P1 and the second port P2, and flows into the refrigerant flow path 61a of the first heat exchanger 61 from the second end 61ab.
  • the refrigerant that flows into the first heat exchanger 61 exchanges heat with the water flowing through the water flow path 61b, condensing, and becoming a high-pressure liquid refrigerant that flows out from the first end 61aa.
  • the first heat exchanger 61 functions as a radiator.
  • the high-pressure refrigerant flowing out of the first heat exchanger 61 flows through the first section 71a of the liquid refrigerant flow path 71.
  • the refrigerant flowing through the first section 71a of the liquid refrigerant flow path 71 flows into the bridge circuit 50 from the second connection section C2.
  • the refrigerant that flows into the bridge circuit 50 flows through the second check valve 52 and the first connection section C1 into the first branch flow path 73.
  • the refrigerant that flows into the first branch flow path 73 flows into the second heat transfer tube 64b of the economizer heat exchanger 64.
  • the refrigerant that flows into the second heat transfer tube 64b of the economizer heat exchanger 64 exchanges heat with the refrigerant passing through the first heat transfer tube 64a of the economizer heat exchanger 64, and flows out from the second heat transfer tube 64b.
  • a portion of the refrigerant that flows out from the second heat transfer tube 64b flows into the injection flow path 72, and the remainder flows through the first branch flow path 73 into the second heat transfer tube 63b of the internal heat exchanger 63.
  • the refrigerant that flows into the injection flow passage 72 is reduced in pressure to intermediate pressure as it flows through the second pressure reducing means 42.
  • the intermediate pressure refrigerant flows into the first heat transfer tube 64a of the economizer heat exchanger 64, exchanges heat with the refrigerant passing through the second heat transfer tube 64b of the economizer heat exchanger 64, and flows out from the first heat transfer tube 64a.
  • the refrigerant that flows out from the first heat transfer tube 64a is again sucked into the compressor 10 from the second suction section 10f.
  • the refrigerant that flows into the second heat transfer tube 63b of the internal heat exchanger 63 exchanges heat with the refrigerant passing through the first heat transfer tube 63a of the internal heat exchanger 63, and flows out into the second branch flow path 74.
  • the refrigerant that flows out into the second branch flow path 74 passes through the first pressure reducing means 41 and flows into the bridge circuit 50 from the third connection part C3.
  • the refrigerant that passes through the first pressure reducing means 41 is reduced in pressure to a low level and becomes a gas-liquid two-phase refrigerant.
  • the refrigerant that flows into the bridge circuit 50 branches into the third check valve 53 and the fourth check valve 54 at the third connection C3.
  • the refrigerant that flows into the third check valve 53 flows into the second check valve 52 through the second connection C2.
  • the refrigerant that flows into the second check valve 52 flows into the first branch flow path 73 through the first connection C1 as described above.
  • the refrigerant that flows into the fourth check valve 54 flows into the second part 71b of the liquid refrigerant flow path 71 through the fourth connection C4.
  • the refrigerant that flows into the liquid refrigerant flow path 71 flows into the refrigerant flow path of the second heat exchanger 62 from the first end 62aa.
  • the refrigerant that flows into the second heat exchanger 62 evaporates through heat exchange with the air in the location where the second heat exchanger 62 is installed, becoming a low-pressure gas refrigerant that flows out from the second end 62ab.
  • the second heat exchanger 62 functions as an evaporator.
  • the low-pressure refrigerant flowing out of the second heat exchanger 62 passes through the switching mechanism 22 in the order of the fourth port P4 and the third port P3, and flows into the first heat transfer tube 63a of the internal heat exchanger 63.
  • the refrigerant that flows into the first heat transfer tube 63a exchanges heat with the refrigerant passing through the second heat transfer tube 63b of the internal heat exchanger 63, and flows out of the first heat transfer tube 63a.
  • the refrigerant that flows out of the first heat transfer tube 63a passes through the accumulator 80, and is again sucked into the compressor 10 from the first suction section 10e.
  • control unit 100 controls each part of the refrigerant circuit 90 as follows.
  • the control unit 100 starts the compressor 10 and controls the rotation speed of the drive motor 10d.
  • the switching mechanism 20 is controlled to be in the second state.
  • the control unit 100 controls the opening degree of the first pressure reducing means 41 based on the temperature detection unit 81 and the pressure detection unit 82. Details of the control of the first pressure reducing means 41 will be described later.
  • the opening degree of the second pressure reducing means 42 is controlled.
  • the control unit 100 controls the opening degree of the second pressure reducing means 42 so that the superheat degree of the refrigerant flowing out of the second pressure reducing means 42 approaches a predetermined target superheat degree.
  • the high-pressure gas refrigerant flowing out from the discharge port 10g passes through the switching mechanism 22, in the order of the first port P1 and the fourth port P4, and flows into the refrigerant flow path of the second heat exchanger 62 from the second end 62ab.
  • the refrigerant that flows into the second heat exchanger 62 exchanges heat with the air in the location where the second heat exchanger 62 is installed, condenses, and becomes high-pressure liquid refrigerant, which flows out from the first end 62aa.
  • the second heat exchanger 62 functions as a radiator.
  • the high-pressure refrigerant flowing out of the second heat exchanger 62 flows through the second part 71b of the liquid refrigerant flow path 71 and enters the bridge circuit 50 from the fourth connection part C4.
  • the refrigerant that flows into the bridge circuit 50 passes through the first check valve 51 and the first connection part C1 and flows into the first branch flow path 73.
  • the refrigerant that flows into the first branch flow path 73 flows into the second heat transfer tube 64b of the economizer heat exchanger 64.
  • the refrigerant that flows into the second heat transfer tube 64b of the economizer heat exchanger 64 exchanges heat with the refrigerant passing through the first heat transfer tube 64a of the economizer heat exchanger 64, and flows out from the second heat transfer tube 64b.
  • a portion of the refrigerant that flows out from the second heat transfer tube 64b flows into the injection flow path 72, and the remainder flows through the first branch flow path 73 into the second heat transfer tube 63b of the internal heat exchanger 63.
  • the refrigerant that flows into the injection flow passage 72 is reduced in pressure to intermediate pressure as it flows through the second pressure reducing means 42.
  • the intermediate pressure refrigerant flows into the first heat transfer tube 64a of the economizer heat exchanger 64, exchanges heat with the refrigerant passing through the second heat transfer tube 64b of the economizer heat exchanger 64, and flows out from the first heat transfer tube 64a.
  • the refrigerant that flows out from the first heat transfer tube 64a is again sucked into the compressor 10 from the second suction section 10f.
  • the refrigerant that flows into the second heat transfer tube 63b of the internal heat exchanger 63 exchanges heat with the refrigerant passing through the first heat transfer tube 63a of the internal heat exchanger 63, and flows out into the second branch flow path 74.
  • the refrigerant that flows out into the second branch flow path 74 passes through the first pressure reducing means 41 and flows into the bridge circuit 50 from the third connection part C3.
  • the refrigerant that passes through the first pressure reducing means 41 is reduced in pressure to a low level and becomes a gas-liquid two-phase refrigerant.
  • the refrigerant that flows into the bridge circuit 50 branches into the third check valve 53 and the fourth check valve 54 at the third connection C3.
  • the refrigerant that flows into the fourth check valve 54 flows into the first check valve 51 through the fourth connection C4.
  • the refrigerant that flows into the first check valve 51 flows into the first branch flow path 73 through the first connection C1 as described above.
  • the refrigerant that flows into the third check valve 53 flows into the first part 71a of the liquid refrigerant flow path 71 through the second connection C2.
  • the refrigerant that flows into the liquid refrigerant flow path 71 flows into the refrigerant flow path 61a of the first heat exchanger 61 from the first end 61aa.
  • the refrigerant that flows into the first heat exchanger 61 evaporates through heat exchange with the water flowing through the water flow path 61b, becoming a low-pressure gas refrigerant that flows out from the second end 61ab.
  • the first heat exchanger 61 functions as an evaporator.
  • the low-pressure refrigerant flowing out of the first heat exchanger 61 passes through the switching mechanism 22, in the order of the second port P2 and the third port P3, and flows into the first heat transfer tube 63a of the internal heat exchanger 63.
  • the refrigerant flowing out of the first heat transfer tube 63a passes through the accumulator 80 and is again sucked into the compressor 10 from the first suction section 10e.
  • Control of the aperture of the first pressure reducing means 41 The control unit 100 calculates the wetness W of the refrigerant before it flows into the first heat transfer tube 63a of the internal heat exchanger 63 from the detection results of the temperature detection unit 18 and the pressure detection unit 82.
  • the control unit 100 controls the aperture of the first pressure reducing means 41 based on the calculated wetness W. For example, the control unit 100 can increase the aperture of the first pressure reducing means 41 when the wetness W increases, and decrease the aperture of the first pressure reducing means 41 when the wetness W decreases.
  • the control unit 100 controls the opening degree of the first pressure reducing means 41 so that the wetness W of the refrigerant before flowing into the first heat transfer tube 63a becomes a predetermined target wetness W (for example, about 0.2).
  • control unit 100 obtains the specific enthalpy H from the position where the isothermal line of temperature T detected by the temperature detection unit 81 intersects with the isobaric line of pressure P detected by the pressure detection unit 82 in the Mollier diagram of the refrigerant filled in the refrigerant circuit 90.
  • the control unit 100 uses this specific enthalpy H to calculate the wetness W.
  • Figure 3 is a Mollier diagram showing the relationship between temperature T, pressure P, and specific enthalpy H.
  • the control unit 100 can determine one specific enthalpy H for a refrigerant in a gas-liquid two-phase state based on one set of temperature T and pressure P, and can use this specific enthalpy H to calculate the wetness W of the refrigerant before it flows into the first heat transfer tube 63a.
  • the refrigeration cycle apparatus 1 includes a refrigerant circuit 90 and a temperature detection unit 81.
  • the refrigerant circuit 90 includes a compressor 10, a main heat exchanger 60 (specifically, a first heat exchanger 61 and a second heat exchanger 62) functioning as a radiator and an evaporator, a first pressure reducing means 41, and an internal heat exchanger 63.
  • the temperature detection unit 81 detects the temperature of the refrigerant.
  • the refrigerant circuit 90 is filled with a non-azeotropic refrigerant mixture.
  • the internal heat exchanger 63 exchanges heat between the refrigerant flowing from the main heat exchanger 60 functioning as an evaporator to the compressor 10 and the refrigerant flowing from the main heat exchanger 60 functioning as a radiator to the main heat exchanger 60 functioning as an evaporator.
  • the temperature detection unit 81 detects the temperature of the refrigerant that flows out of the main heat exchanger 60 functioning as an evaporator and before it flows into the internal heat exchanger 63.
  • the refrigeration cycle device 1 can detect the temperature of the refrigerant flowing out of the main heat exchanger 60, which functions as an evaporator, before it flows into the internal heat exchanger 63. Therefore, even though the refrigeration cycle device 1 is equipped with an internal heat exchanger 63, it can accurately grasp the state of the refrigerant in the evaporator.
  • the refrigeration cycle apparatus 1 further includes a pressure detection unit 82.
  • the pressure detection unit 82 detects the pressure of the refrigerant that flows out of the internal heat exchanger 63 and before flowing into the compressor 10.
  • the refrigeration cycle device 1 can more accurately grasp the state of the refrigerant in the evaporator by taking into account the refrigerant temperature detected by the temperature detection unit 81 and the pressure of the refrigerant before it flows into the compressor 10.
  • the refrigeration cycle apparatus 1 further includes a control unit 100.
  • the control unit 100 calculates the wetness of the refrigerant before it flows into the internal heat exchanger 63, based on the detection results of the temperature detection unit 81 and the pressure detection unit 82.
  • the control unit 100 can calculate the wetness of the refrigerant before it flows into the internal heat exchanger 63 based on the two detection results (temperature T, pressure P) obtained from the temperature detection unit 81 and the pressure detection unit 82.
  • the first pressure reducing means 41 reduces the pressure of the refrigerant flowing from the main heat exchanger 60 functioning as a radiator to the main heat exchanger 60 functioning as an evaporator.
  • the control unit 100 controls the opening degree of the first pressure reducing means 41 based on the wetness W.
  • the control unit 100 can utilize temperature glide to efficiently perform heat exchange of the refrigerant in the internal heat exchanger 63 by flowing a gas-liquid two-phase refrigerant with a low humidity level W into the internal heat exchanger 63. Therefore, the refrigeration cycle device 1 can efficiently perform heating and cooling operations.
  • the heat source with which the refrigerant flowing through the refrigerant passage 61a exchanges heat is not limited to water, and the refrigerant may exchange heat with, for example, air in the target space.
  • the first heat exchanger 61 can be disposed in the target space.
  • the refrigerant filled in the refrigerant circuit 90 is not limited to R454C as long as it is a non-azeotropic refrigerant mixture.
  • Refrigeration cycle device 10 Compressor 20 Switching mechanism 41 First pressure reducing means (pressure reducing means) 61 First heat exchanger (radiator or evaporator) 62 Second heat exchanger (radiator or evaporator) 63 Internal heat exchanger 63a First heat transfer tube 63b Second heat transfer tube 81 Temperature detector 82 Pressure detector 90 Refrigerant circuit 100 Control unit P Pressure T Temperature W Humidity

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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)
PCT/JP2023/009413 2023-03-10 2023-03-10 冷凍サイクル装置 Ceased WO2024189697A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP23927321.2A EP4679009A1 (en) 2023-03-10 2023-03-10 Refrigeration cycle device
PCT/JP2023/009413 WO2024189697A1 (ja) 2023-03-10 2023-03-10 冷凍サイクル装置
JP2025506253A JPWO2024189697A1 (https=) 2023-03-10 2023-03-10

Applications Claiming Priority (1)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01102254A (ja) * 1987-10-14 1989-04-19 Technol Res Assoc Super Heat Pump Energ Accum Syst ヒートポンプ
JP2002130856A (ja) * 2000-10-23 2002-05-09 Matsushita Seiko Co Ltd 冷凍サイクル装置及び冷凍サイクルの制御方法
JP2009085568A (ja) 2007-10-03 2009-04-23 Sanden Corp 冷凍回路
JP2010048498A (ja) * 2008-08-22 2010-03-04 Tgk Co Ltd 冷凍サイクル
JP2016125746A (ja) * 2014-12-26 2016-07-11 株式会社前川製作所 冷凍又は空調装置及びその制御方法

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01102254A (ja) * 1987-10-14 1989-04-19 Technol Res Assoc Super Heat Pump Energ Accum Syst ヒートポンプ
JP2002130856A (ja) * 2000-10-23 2002-05-09 Matsushita Seiko Co Ltd 冷凍サイクル装置及び冷凍サイクルの制御方法
JP2009085568A (ja) 2007-10-03 2009-04-23 Sanden Corp 冷凍回路
JP2010048498A (ja) * 2008-08-22 2010-03-04 Tgk Co Ltd 冷凍サイクル
JP2016125746A (ja) * 2014-12-26 2016-07-11 株式会社前川製作所 冷凍又は空調装置及びその制御方法

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP4679009A1

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EP4679009A1 (en) 2026-01-14

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