WO2022013975A1 - Cold heat source unit and refrigeration cycle device - Google Patents

Cold heat source unit and refrigeration cycle device Download PDF

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Publication number
WO2022013975A1
WO2022013975A1 PCT/JP2020/027519 JP2020027519W WO2022013975A1 WO 2022013975 A1 WO2022013975 A1 WO 2022013975A1 JP 2020027519 W JP2020027519 W JP 2020027519W WO 2022013975 A1 WO2022013975 A1 WO 2022013975A1
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WIPO (PCT)
Prior art keywords
refrigerant
flow path
cooling
source unit
heat source
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PCT/JP2020/027519
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French (fr)
Japanese (ja)
Inventor
智隆 石川
素 早坂
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三菱電機株式会社
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Priority to JP2022536042A priority Critical patent/JP7438363B2/en
Priority to PCT/JP2020/027519 priority patent/WO2022013975A1/en
Publication of WO2022013975A1 publication Critical patent/WO2022013975A1/en

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    • 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

Definitions

  • This disclosure relates to a cold heat source unit and a refrigeration cycle device.
  • a refrigeration cycle device using a refrigerant for example, carbon dioxide
  • a refrigerant for example, carbon dioxide
  • the compressor discharge side pressure at the rated output is the supercritical pressure. Since the refrigerant near the critical point has a characteristic that the change in thermal characteristics is relatively large, the opening control of the expansion valve may become unstable.
  • Patent Document 1 states that the refrigerant state on the outlet side of the radiator changes along a control line set to avoid the critical point of the refrigerant on the Moriel diagram. Discloses a supercritical heat pump cycle that controls the opening degree of an expansion valve.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 2015-28401
  • Patent Document 1 the opening degree of the expansion valve is controlled to avoid the critical point.
  • the opening control of the expansion valve itself becomes unstable, and it becomes difficult to control the opening of the expansion valve so as to avoid the critical point. ..
  • the present disclosure has been made to solve the above problems, and the purpose of the present disclosure is to introduce a cold heat source unit and a refrigerating cycle device having improved control stability.
  • the present disclosure relates to a cold heat source unit of a refrigeration cycle device configured to be connected to a load device including a first inflator and an evaporator.
  • the cold heat source unit includes a first flow path that forms a circulation flow path through which the refrigerant circulates by being connected to the load device, and a compressor, a condenser, and a refrigerant cooling device that are sequentially arranged in the first flow path.
  • a pressure sensor and a temperature sensor that detect the pressure and temperature of the refrigerant sent from the refrigerant cooling device to the first expansion device, respectively, and a control device that changes the cooling performance of the refrigerant cooling device based on the outputs of the pressure sensor and the temperature sensor. And prepare.
  • the cold heat source unit of the present disclosure it is possible to stably control the compressor discharge pressure even when it approaches the critical point due to disturbance.
  • FIG. It is an overall block diagram of the refrigeration cycle apparatus of Embodiment 1.
  • FIG. It is a figure which shows an example of a cooling range. It is a figure which showed the cooling range in a ph diagram. It is a ph diagram which shows the change of the refrigerating cycle before and after cooling. It is a flowchart for demonstrating the control of the refrigerant cooling apparatus which the control apparatus 100 executes.
  • FIG. It is an overall block diagram of the modification of the refrigerating cycle apparatus of Embodiment 2.
  • FIG. 1 is an overall configuration diagram of the refrigeration cycle apparatus of the first embodiment. Note that FIG. 1 functionally shows the connection relationship and the arrangement configuration of each device in the refrigeration cycle apparatus, and does not necessarily show the arrangement in the physical space.
  • the refrigeration cycle device 1 includes a cold heat source unit 2, a load device 3, and pipes 84 and 88.
  • the cold heat source unit 2 has a refrigerant outlet port and a refrigerant inlet port for connecting to the load device 3. Since the cold heat source unit 2 is often arranged outdoors, it may also be referred to as an indoor unit or an outdoor unit.
  • the load device 3 has a refrigerant outlet port and a refrigerant inlet port for connecting to the cold heat source unit 2.
  • the pipe 84 connects the refrigerant outlet port of the cold heat source unit 2 and the refrigerant inlet port of the load device 3.
  • the pipe 88 connects the refrigerant outlet port of the load device 3 and the refrigerant inlet port of the cold heat source unit 2.
  • the cold heat source unit 2 of the refrigeration cycle device 1 is configured to be connected to the load device 3.
  • the cold heat source unit 2 includes a compressor 10 having a suction port G1 and a discharge port G2, a condenser 20, a fan 22, a refrigerant cooling device 30, and pipes 80 to 83, 89.
  • the refrigerant cooling device 30 includes a heat exchanger 72 and a switching unit 74 for switching the flow path of the refrigerant.
  • the heat exchanger 72 has a first passage H1 and a second passage H2, and is configured to exchange heat between the refrigerant flowing through the first passage H1 and the refrigerant flowing through the second passage H2.
  • the load device 3 includes a first expansion device 50, an evaporator 60, and pipes 85, 86, 87.
  • the evaporator 60 is configured to exchange heat between air and the refrigerant. In the refrigeration cycle device 1, the evaporator 60 evaporates the refrigerant by endothermic heat from the air in the cooling target space.
  • the first expansion device 50 is, for example, a temperature expansion valve controlled independently of the cold heat source unit 2.
  • the first expansion device 50 may be an electronic expansion valve capable of reducing the pressure of the refrigerant.
  • the compressor 10 compresses the refrigerant sucked from the pipe 89 and discharges it to the pipe 80.
  • the drive frequency of the compressor 10 can be arbitrarily changed by inverter control.
  • the compressor 10 is configured to adjust the rotation speed according to a control signal from the control device 100. By adjusting the rotation speed of the compressor 10, the circulation amount of the refrigerant is adjusted, and the capacity of the refrigerating cycle device 1 can be adjusted.
  • Various types of compressors 10 can be adopted, and for example, scroll type, rotary type, screw type and the like can be adopted.
  • the condenser 20 is configured so that the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 exchanges heat (heat dissipation) with the outside air. By this heat exchange, the refrigerant is condensed and changed into a liquid phase.
  • the refrigerant discharged from the compressor 10 to the pipe 80 is condensed and liquefied in the condenser 20 and flows out to the pipe 81.
  • a fan 22 for sending outside air is attached to the condenser 20 in order to improve the efficiency of heat exchange.
  • the fan 22 supplies the outside air to the condenser 20 through which the refrigerant exchanges heat in the condenser 20. By adjusting the rotation speed of the fan 22, the refrigerant pressure (high pressure side pressure) on the discharge side of the compressor 10 can be adjusted.
  • the refrigerant used in the refrigerant circuit of the refrigeration cycle device 1 is CO 2 , but if a state in which it is difficult to secure the degree of supercooling occurs, another refrigerant may be used.
  • the condenser 20 works as a radiator that dissipates heat from the refrigerant to the outside air.
  • a refrigerant such as CO 2 in a supercritical state
  • the degree of supercooling the degree of supercooling.
  • the first flow path F1 from the refrigerant inlet port of the cold heat source unit 2 to the refrigerant outlet port via the compressor 10, the condenser 20, and the first passage H1 of the heat exchanger 72 is the first expansion device 50 and the evaporator. Together with the load device 3 in which the 60 is arranged, a circulation flow path through which the refrigerant circulates is formed.
  • this circulation flow path is also referred to as a "main refrigerant circuit" of the refrigeration cycle.
  • the cold heat source unit 2 further includes a second flow path F2 that branches from the branch point BP of the first flow path F1 downstream of the evaporator 60 in the direction in which the refrigerant circulates.
  • the second flow path F2 is configured such that the refrigerant that has passed through the evaporator 60 returns to the compressor 10 via the refrigerant cooling device 30.
  • the refrigerant cooling device 30 includes a switching unit 74 for switching whether or not to flow the refrigerant from the branch point BP to the second flow path F2, and the first passage H1 and the second flow path F2 which are a part of the first flow path F1. It has a second passage H2 which is a part thereof, and includes a heat exchanger 72 configured to exchange heat between the refrigerant flowing through the first passage H1 and the refrigerant flowing through the second passage H2.
  • the cold heat source unit 2 further includes pressure sensors 110 to 112, temperature sensors 120 and 121, and a control device 100 that controls the compressor 10 and the switching unit 74.
  • the pressure sensor 110 detects the pressure Ps in the suction port portion of the compressor 10 and outputs the detected value to the control device 100.
  • the pressure sensor 111 detects the discharge pressure Pd of the compressor 10 and outputs the detected value to the control device 100.
  • the pressure sensor 112 detects the refrigerant pressure P1 in the pipe 83 in front of the first expansion device 50, and outputs the detected value to the control device 100.
  • the temperature sensor 120 detects the discharge temperature TH of the compressor 10 and outputs the detected value to the control device 100.
  • the temperature sensor 121 detects the refrigerant temperature T1 of the pipe 83 in front of the first expansion device 50, and outputs the detected value to the control device 100.
  • the control device 100 includes a CPU (Central Processing Unit) 102, a memory 104 (ROM (Read Only Memory) and RAM (Random Access Memory)), an input / output buffer (not shown) for inputting / outputting various signals, and the like. Consists of including.
  • the CPU 102 expands the program stored in the ROM into a RAM or the like and executes the program.
  • the program stored in the ROM is a program in which the processing procedure of the control device 100 is described.
  • the control device 100 executes control of each device in the cold heat source unit 2 according to these programs. This control is not limited to software processing, but can also be processed by dedicated hardware (electronic circuit).
  • the control device 100 controls the flow of the refrigerant in the switching unit 74 according to the outputs of the pressure sensor 112 and the temperature sensor 121.
  • the switching unit 74 includes on-off valves 76 and 77. When the on-off valve 76 is closed and the on-off valve 77 is opened, the refrigerant flows from the load device 3 to the suction port G1 of the compressor 10 without flowing through the second flow path F2. On the contrary, when the on-off valve 76 is opened and the on-off valve 77 is closed, the refrigerant flows from the load device 3 to the suction port G1 of the compressor 10 via the second flow path F2.
  • the second flow path F2 is a refrigerant that flows out from the condenser 20 to the pipe 81 by flowing the low-temperature refrigerant that has passed through the first expansion device 50 and the evaporator 60 into the heat exchanger 72. Is provided to cool the water and stabilize the state of the refrigerant flowing into the first expansion device 50 through the pipes 82 to 85.
  • the refrigerant in front of the first expansion device 50 is cooled by the refrigerant cooling device 30 to change the state of the refrigerant to the critical point. Avoid from the vicinity. As a result, it is possible to suppress the density fluctuation due to the temperature change, stabilize the expansion valve flow rate, and supply a stable refrigerating capacity.
  • the main refrigerant circuit passes from the compressor 10 through the condenser 20, the refrigerant cooling device 30, the first expansion device 50, and the evaporator 60 in this order.
  • the refrigerant is configured to return to the compressor 10.
  • the refrigerant cooling device 30 uses the refrigerant itself in the refrigerating cycle after passing through the evaporator 60 as a cold heat source.
  • a pressure sensor 112 and a temperature sensor 121 are provided in front of the inlet of the first expansion device 50.
  • the control device 100 increases the cooling capacity of the refrigerant cooling device 30 to cool the refrigerant.
  • the refrigerant is not limited to CO 2, but is particularly effective if CO 2.
  • the cooling range is the pressure range / temperature range in which the density fluctuates greatly with a slight temperature change.
  • the cooling range may be, for example, a range in which the density of the refrigerant changes by 10% or more with respect to a temperature change of 0.5 K of the refrigerant when the refrigerant pressure is a supercritical pressure.
  • FIG. 2 is a diagram showing an example of a cooling range.
  • FIG. 3 is a diagram showing the cooling range in the ph diagram. 2 and 3 show an example when the refrigerant is CO 2.
  • the temperature range A1 when the pressure is 7.0 MPa is 28.5 to 29.5 ° C.
  • the temperature range A2 when the pressure is 7.2 MPa is 29.5 to 30.5 ° C.
  • the temperature range A3 when the pressure is 7.4 MPa is 31.0 to 32.0 ° C.
  • the temperature range A4 when the pressure is 7.6 MPa is 32.0 to 33.0 ° C.
  • the temperature range A5 when the pressure is 7.8 MPa is 33.0 to 34.0 ° C.
  • the temperature range A6 when the pressure is 8.0 MPa is 34.0 to 35.0 ° C.
  • the temperature range A7 when the pressure is 8.2 MPa is 35.5 to 36.5 ° C.
  • FIG. 4 is a ph diagram showing changes in the refrigeration cycle before and after cooling. Since it is difficult to see the change in the refrigeration cycle when displayed in FIG. 3, it is shown in a simplified manner as shown in FIG.
  • the state of the inlet portion of the first expansion device 50 is within the cooling range A.
  • the control device 100 cools the refrigerant by using the refrigerant cooling device 30.
  • the point indicating the state of the inlet portion of the first expansion device 50 moves to the left in FIG. 4, that is, in the direction in which the specific enthalpy becomes smaller because the refrigerant has been cooled.
  • FIG. 5 is a flowchart for explaining the control of the refrigerant cooling device executed by the control device 100. The processing of this flowchart is called and executed from the main control routine of the refrigeration cycle apparatus at regular intervals.
  • step S1 the control device 100 determines whether or not the refrigerant cooling device 30 is cooling the refrigerant.
  • the on-off valves 76 and 77 are controlled in the switching unit 74 so that the refrigerant flows through the second flow path F2. At this time, the on-off valve 76 is in the open state and the on-off valve 77 is in the closed state.
  • the on-off valves 76 and 77 are controlled in the switching unit 74 so that the refrigerant does not flow to the second flow path F2. At this time, the on-off valve 76 is in the closed state and the on-off valve 77 is in the open state.
  • step S1 when the refrigerant cooling device 30 is not cooling the refrigerant (NO in S1), in step S2, in the control device 100, the state of the refrigerant at the inlet portion of the first expansion device 50 is the cooling described with reference to FIGS. 2 and 3. Determine if it falls within the range.
  • step S3 the control device 100 sets the on-off valve 76 inside the switching unit 74 to the open state and the on-off valve 77 to the closed state to cool the refrigerant. Start.
  • the control device 100 returns the control to the main control routine without performing the control in step S3.
  • step S1 when the refrigerant cooling device 30 is cooling the refrigerant (YES in S1), in step S4, the control device 100 determines whether or not cooling is continued for 5 minutes or more from the start of cooling.
  • step S5 If cooling has been continued for 5 minutes or more from the start of cooling (YES in S4), the transition from the refrigeration cycle C1 to C2 in FIG. 4 has been completed, so that the control device 100 ends the cooling in step S5. That is, the on-off valves 76 and 77 are controlled in the switching unit 74 so that the refrigerant does not flow to the second flow path F2, the on-off valve 76 is set to the closed state, and the on-off valve 77 is set to the open state.
  • step S4 is only an example because it is affected by the circulation amount of the refrigerant and the like.
  • FIG. 6 is an overall configuration diagram of the refrigeration cycle apparatus of the second embodiment. Note that FIG. 2 functionally shows the connection relationship and the arrangement configuration of each device in the refrigeration cycle apparatus, and does not necessarily show the arrangement in the physical space.
  • the refrigeration cycle device 1A includes a cold heat source unit 2A, a load device 3, and pipes 84 and 88. Since the load device 3 has the same configuration as that in FIG. 1, the description will not be repeated.
  • the cold heat source unit 2A includes a compressor 10A instead of the compressor 10, a refrigerant cooling device 30A instead of the refrigerant cooling device 30, and a second flow path F2.
  • the second flow path F2A is included in place of the control device 100, and the control device 100A is included in place of the control device 100. Since the configuration of the other parts of the cold heat source unit 2A is the same as that of the cold heat source unit 2, the description will not be repeated.
  • the refrigerant cooling device 30A includes an on-off valve 70, a second expansion device 71, and a heat exchanger 72.
  • the second flow path F2A branches from the branch point BPA of the first flow path F1 downstream of the refrigerant cooling device 30A in the direction in which the refrigerant circulates, and the refrigerant that has passed through the condenser 20 and the refrigerant cooling device 30A is compressed. It is configured to return to 10.
  • the second expansion device 71 is an electronic expansion valve capable of reducing the refrigerant in the high pressure portion of the main refrigerant circuit to an intermediate pressure.
  • the on-off valve 70 may be omitted and the electronic expansion valve may be closed instead of closing the on-off valve 70.
  • the compressor 10A is provided with the intermediate pressure port G3, and the refrigerant from the intermediate pressure port G3 can flow into the middle part of the compression process.
  • the second flow path F2A includes pipes 91, 92, 94 for flowing the refrigerant from the branch point BPA of the pipe 82 connected to the outlet of the first passage H1 of the circulation flow path to the inlet of the second passage H2, and the second passage. Further, a pipe 96 for flowing a refrigerant from the outlet of H2 to the intermediate pressure port G3 of the compressor 10A is provided.
  • the second flow path F2A that branches from the main refrigerant circuit and sends the refrigerant to the compressor 10A via the second passage H2 is also referred to as an “injection flow path”.
  • the on-off valve 70, the second expansion device 71, and the heat exchanger 72 are arranged in the second flow path F2A in order from the branch point BPA.
  • the first passage H1 of the heat exchanger 72 is a part of the first passage F1.
  • the second passage H2 of the heat exchanger 72 is a part of the second passage F2A.
  • the control device 100A controls the amount of refrigerant flowing through the second expansion device 71 according to the outputs of the pressure sensor 112 and the temperature sensor 121.
  • the control device 100A executes the process shown in the flowchart of FIG. 5 as in the first embodiment.
  • the control device 100A opens the on-off valve 70 when the refrigerant cooling device 30A starts cooling the refrigerant in step S3. Further, the control device 100A closes the on-off valve 70 when the cooling of the refrigerant by the refrigerant cooling device 30A is completed in step S5.
  • FIG. 7 is an overall configuration diagram of a modified example of the refrigeration cycle apparatus according to the second embodiment.
  • the refrigerating cycle apparatus 1B shown in FIG. 7 includes a refrigerating heat source unit 2B instead of the refrigerating heat source unit 2A in the configuration of the refrigerating cycle apparatus 1A shown in FIG.
  • the second flow path F2A is the second flow path F2B.
  • the pipe 96 is connected to the intermediate pressure port G3 of the compressor 10A, but in the second flow path F2B, the pipe 96 is connected to the suction port G1 of the compressor 10. Since the configuration of the other parts of the cold heat source unit 2B is the same as that of the cold heat source unit 2A, the description will not be repeated.
  • Embodiment 3 the refrigerant flowing into the first expansion device 50 is cooled by the low temperature portion of the refrigerant itself circulating in the refrigeration cycle device, but it may be cooled by another method.
  • FIG. 8 is an overall configuration diagram of the refrigeration cycle apparatus according to the third embodiment. Note that FIG. 3 functionally shows the connection relationship and the arrangement configuration of each device in the refrigeration cycle apparatus, and does not necessarily show the arrangement in the physical space.
  • the refrigeration cycle device 1C includes a cold heat source unit 2C, a load device 3, and pipes 84 and 88. Since the load device 3 has the same configuration as that in FIG. 1, the description will not be repeated.
  • the second flow path F2 is deleted, and the refrigerant cooling device 30C is included instead of the refrigerant cooling device 30, and the control device 100 is replaced with the control device 100. Includes 100C. Since the configuration of the other parts of the cold heat source unit 2C is the same as that of the cold heat source unit 2, the description will not be repeated.
  • the refrigerant cooling device 30C includes a heat exchanger 202 that exchanges heat between the refrigerant and the heat medium, and a supply device 204 that sends the heat medium to the heat exchanger 202.
  • the supply device 204 is a fan.
  • the supply device is a pump or valve.
  • the control device 100C controls the amount of heat medium supplied to the heat exchanger 202 by the supply device 204 according to the outputs of the pressure sensor 112 and the temperature sensor 121. Thereby, the cooling performance of the refrigerant cooling device 30C can be changed.
  • the control device 100C executes the process shown in the flowchart of FIG. 5 as in the first embodiment.
  • the control device 100C operates the supply device 204 when the refrigerant cooling device 30C starts cooling the refrigerant in step S3. Further, the control device 100C stops the supply device 204 when the cooling of the refrigerant by the refrigerant cooling device 30C is completed in step S5.
  • the present disclosure relates to a cold heat source unit 2 configured to be connected to a load device 3 including a first expansion device 50 and an evaporator 60.
  • the cold heat source unit 2 includes a first flow path F1, a compressor 10, a condenser 20, a refrigerant cooling device 30, a pressure sensor 112, a temperature sensor 121, and a control device 100.
  • the first flow path F1 is connected to the load device 3 to form a circulation flow path through which the refrigerant circulates.
  • the compressor 10, the condenser 20, and the refrigerant cooling device 30 are arranged in order in the first flow path F1.
  • the pressure sensor 112 and the temperature sensor 121 detect the pressure and temperature of the refrigerant sent from the refrigerant cooling device 30 to the first expansion device 50, respectively.
  • the control device 100 changes the cooling performance of the refrigerant cooling device 30 based on the outputs of the pressure sensor 112 and the temperature sensor 121.
  • the refrigerant cooling device 30 is controlled based on the outputs of the pressure sensor 112 and the temperature sensor 121 in this way, it is possible to accurately prevent the refrigerant sent to the first expansion device 50 from being in a state near the critical point. can.
  • control device 100 controls the refrigerant cooling device 30 when the outputs of the pressure sensor 112 and the temperature sensor 121 indicate that the state of the refrigerant has entered the predetermined cooling range A. Increases the cooling performance of.
  • control device 100 cools the refrigerant by the refrigerant cooling device 30 for a certain period of time (for example, 5 minutes) in step S4 when the state of the refrigerant enters the predetermined cooling range A. do.
  • the cooling range A (A1 to A7) shown in FIGS. 2 and 3 is a temperature and pressure range in which the density of the refrigerant changes by 10% or more with respect to a temperature change of 0.5 Kelvin of the refrigerant.
  • the cooling range A (A1 to A7) may be a temperature and pressure range in which the evaporation temperature of the refrigerant in the evaporator changes by 1 Kelvin or more with respect to the temperature change of 0.5 Kelvin of the refrigerant.
  • the cold heat source unit 2 shown in FIG. 1 further includes a second flow path F2 that branches from the branch point BP of the first flow path F1 downstream of the evaporator 60 in the direction in which the refrigerant circulates.
  • the second flow path F2 is configured such that the refrigerant that has passed through the evaporator 60 returns to the compressor 10 via the refrigerant cooling device 30.
  • the refrigerant cooling device 30 includes a switching unit 74 for switching whether or not to flow the refrigerant from the branch point BP to the second flow path F2, and a heat exchanger 72.
  • the heat exchanger 72 has a first passage H1 that is a part of the first flow path F1 and a second passage H2 that is a part of the second flow path F2.
  • the heat exchanger 72 is configured to exchange heat between the refrigerant flowing through the first passage H1 and the refrigerant flowing through the second passage H2.
  • the control device 100 controls the flow of the refrigerant in the switching unit 74 according to the outputs of the pressure sensor 112 and the temperature sensor 121.
  • the cold heat source unit 2A shown in FIG. 6 and the cold heat source unit 2B shown in FIG. 7 branch from the branch point BPA of the first flow path F1 downstream of the refrigerant cooling device 30A in the direction in which the refrigerant circulates.
  • a second flow path F2A or F2B configured to return the refrigerant that has passed through the condenser 20 and the refrigerant cooling device 30A to the compressor 10 is further provided.
  • the refrigerant cooling device 30A includes a second expansion device 71 and a heat exchanger 72 arranged in the second flow path F2A or F2B in order from the branch point BPA.
  • the heat exchanger 72 has a first passage H1 that is a part of the first flow path F1 and a second passage H2 that is a part of the second flow path F2A or F2B.
  • the heat exchanger 72 is configured to exchange heat between the refrigerant flowing through the first passage H1 and the refrigerant flowing through the second passage H2.
  • the control device 100A controls the amount of refrigerant flowing through the second expansion device 71 according to the outputs of the pressure sensor 112 and the temperature sensor 121.
  • the refrigerant cooling device 30C shown in FIG. 8 includes a heat exchanger 202 for heat exchange between the refrigerant and the heat medium, and a supply device 204 for sending the heat medium to the heat exchanger 202.
  • the supply device 204 is a fan.
  • the supply device is a pump or valve.
  • the control device 100C controls the amount of heat medium supplied to the heat exchanger 202 by the supply device 204 according to the outputs of the pressure sensor 112 and the temperature sensor 121.
  • the refrigerant is carbon dioxide or a mixed refrigerant containing carbon dioxide.
  • the present disclosure relates to refrigerating cycle devices 1, 1A to 1C including any of the above-mentioned cold heat source units 2, 2A to 2C and a load device 3 in another aspect.
  • the refrigeration cycle devices 1, 1A to 1C may be used for an air conditioner or the like.
  • 1,1A, 1B, 1C refrigeration cycle device 1,2A, 2B, 2C cold heat source unit, 3 load device, 10 compressor, 20 condenser, 22 fan, 30, 30A, 30C refrigerant cooling device, 50 first expansion Equipment, 60 evaporator, 70,76,77 on-off valve, 71 second expansion device, 72,202 heat exchanger, 74 switching unit, 80,81,82,83,84,85,88,89,91,92 , 94,96 piping, 100,100A, 100C control device, 102 CPU, 104 memory, 110,111,112 pressure sensor, 120,121 temperature sensor, 204 supply device, BP, BPA branch point, F1 first flow path, F2, F2A, F2B second flow path, G1 suction port, G2 discharge port, G3 intermediate pressure port, H1 first passage, H2 second passage.

Abstract

This cold heat source unit (2) is configured so as to be connected to a load device (3) that includes a first expansion device (50) and an evaporator (60). The cold heat source unit (2) comprises: a first flow path (F1) that is connected to the load device (3), thereby forming a refrigerant flow path in which a refrigerant circulates; a compressor (10), and condenser (20), and a refrigerant cooling device (30) that are positioned in sequence in the first flow path (F1); a pressure sensor (112) and a temperature sensor (121) that respectively detect the pressure and the temperature of the refrigerant sent from the refrigerant cooling device (30) to the first expansion device (50); and a control device (100). The control device (100) modifies the cooling performance of the refrigerant cooling device (30) on the basis of the outputs from the pressure sensor (112) and the temperature sensor (121).

Description

冷熱源ユニットおよび冷凍サイクル装置Cold heat source unit and refrigeration cycle equipment
　本開示は、冷熱源ユニットおよび冷凍サイクル装置に関する。 This disclosure relates to a cold heat source unit and a refrigeration cycle device.
　従来、高圧側で超臨界状態となり得る冷媒（例えば、二酸化炭素など）を用いた冷凍サイクル装置が知られている。このような冷凍サイクル装置では、定格出力時の圧縮機吐出側圧力が超臨界圧力となる。臨界点付近の冷媒は、熱物性の変化が比較的大きい特性を有するため、膨張弁の開度制御が不安定となる可能性がある。 Conventionally, a refrigeration cycle device using a refrigerant (for example, carbon dioxide) that can be in a supercritical state on the high pressure side is known. In such a refrigeration cycle device, the compressor discharge side pressure at the rated output is the supercritical pressure. Since the refrigerant near the critical point has a characteristic that the change in thermal characteristics is relatively large, the opening control of the expansion valve may become unstable.
　特開２０１５－２８４０１号公報（特許文献１）には、放熱器の出口側における冷媒状態が、モリエル線図上において冷媒の臨界点を回避するように設定された制御線に沿って変化するように、膨張弁の開度を制御する超臨界式ヒートポンプサイクルが開示されている。 Japanese Patent Application Laid-Open No. 2015-28401 (Patent Document 1) states that the refrigerant state on the outlet side of the radiator changes along a control line set to avoid the critical point of the refrigerant on the Moriel diagram. Discloses a supercritical heat pump cycle that controls the opening degree of an expansion valve.
特開２０１５－２８４０１号公報Japanese Unexamined Patent Publication No. 2015-28401
　特開２０１５－２８４０１号公報（特許文献１）では、膨張弁の開度を制御して臨界点を回避している。しかし、外乱によって圧縮機吐出側圧力が臨界点付近になった場合などは、膨張弁の開度制御自身が不安定となるので、臨界点を回避するような膨張弁の開度制御も難しくなる。 In Japanese Patent Application Laid-Open No. 2015-28401 (Patent Document 1), the opening degree of the expansion valve is controlled to avoid the critical point. However, when the pressure on the discharge side of the compressor becomes near the critical point due to disturbance, the opening control of the expansion valve itself becomes unstable, and it becomes difficult to control the opening of the expansion valve so as to avoid the critical point. ..
　本開示は、上記課題を解決するためになされたものであって、その目的は制御の安定性が向上した冷熱源ユニットおよび冷凍サイクル装置を紹介することである。 The present disclosure has been made to solve the above problems, and the purpose of the present disclosure is to introduce a cold heat source unit and a refrigerating cycle device having improved control stability.
　本開示は、第１膨張装置および蒸発器を含む負荷装置に接続されるように構成された冷凍サイクル装置の冷熱源ユニットに関する。冷熱源ユニットは、負荷装置に接続されることによって、冷媒が循環する循環流路を形成する第１流路と、第１流路に順に配置される、圧縮機、凝縮器および冷媒冷却装置と、冷媒冷却装置から第１膨張装置に送られる冷媒の圧力および温度をそれぞれ検出する圧力センサおよび温度センサと、圧力センサおよび温度センサの出力に基づいて、冷媒冷却装置の冷却性能を変化させる制御装置とを備える。 The present disclosure relates to a cold heat source unit of a refrigeration cycle device configured to be connected to a load device including a first inflator and an evaporator. The cold heat source unit includes a first flow path that forms a circulation flow path through which the refrigerant circulates by being connected to the load device, and a compressor, a condenser, and a refrigerant cooling device that are sequentially arranged in the first flow path. , A pressure sensor and a temperature sensor that detect the pressure and temperature of the refrigerant sent from the refrigerant cooling device to the first expansion device, respectively, and a control device that changes the cooling performance of the refrigerant cooling device based on the outputs of the pressure sensor and the temperature sensor. And prepare.
　本開示の冷熱源ユニットによれば、圧縮機吐出圧力が外乱によって臨界点に近づいたときでも安定的に制御することができる。 According to the cold heat source unit of the present disclosure, it is possible to stably control the compressor discharge pressure even when it approaches the critical point due to disturbance.
実施の形態１の冷凍サイクル装置の全体構成図である。It is an overall block diagram of the refrigeration cycle apparatus of Embodiment 1. FIG. 冷却範囲の一例を示す図である。It is a figure which shows an example of a cooling range. 冷却範囲をｐ－ｈ線図中に示した図である。It is a figure which showed the cooling range in a ph diagram. 冷却前と冷却後の冷凍サイクルの変化を示すｐ－ｈ線図である。It is a ph diagram which shows the change of the refrigerating cycle before and after cooling. 制御装置１００が実行する冷媒冷却装置の制御を説明するためのフローチャートである。It is a flowchart for demonstrating the control of the refrigerant cooling apparatus which the control apparatus 100 executes. 実施の形態２の冷凍サイクル装置の全体構成図である。It is an overall block diagram of the refrigeration cycle apparatus of Embodiment 2. FIG. 実施の形態２の冷凍サイクル装置の変形例の全体構成図である。It is an overall block diagram of the modification of the refrigerating cycle apparatus of Embodiment 2. 実施の形態３の冷凍サイクル装置の全体構成図である。It is an overall block diagram of the refrigeration cycle apparatus of Embodiment 3. FIG.
　以下、本開示の実施の形態について、図面を参照しながら詳細に説明する。以下では、複数の実施の形態について説明するが、各実施の形態で説明された構成を適宜組み合わせることは出願当初から予定されている。なお、図中同一または相当部分には同一符号を付してその説明は繰返さない。 Hereinafter, embodiments of the present disclosure will be described in detail with reference to the drawings. Hereinafter, a plurality of embodiments will be described, but it is planned from the beginning of the application to appropriately combine the configurations described in the respective embodiments. The same or corresponding parts in the drawings are designated by the same reference numerals and the description thereof will not be repeated.
　実施の形態１．
　図１は、実施の形態１の冷凍サイクル装置の全体構成図である。なお、図１では、冷凍サイクル装置における各機器の接続関係および配置構成を機能的に示しており、物理的な空間における配置を必ずしも示すものではない。 Embodiment 1.
FIG. 1 is an overall configuration diagram of the refrigeration cycle apparatus of the first embodiment. Note that FIG. 1 functionally shows the connection relationship and the arrangement configuration of each device in the refrigeration cycle apparatus, and does not necessarily show the arrangement in the physical space.
　図１を参照して、冷凍サイクル装置１は、冷熱源ユニット２と、負荷装置３と、配管８４，８８とを備える。冷熱源ユニット２は、負荷装置３と接続するための冷媒出口ポートおよび冷媒入口ポートを有する。冷熱源ユニット２は、屋外に配置されることが多いので、室内ユニット、または屋外ユニットとも呼ばれる場合がある。負荷装置３は、冷熱源ユニット２と接続するための冷媒出口ポートおよび冷媒入口ポートを有する。配管８４は、冷熱源ユニット２の冷媒出口ポートと負荷装置３の冷媒入口ポートとを接続する。配管８８は、負荷装置３の冷媒出口ポートと冷熱源ユニット２の冷媒入口ポートとを接続する。 With reference to FIG. 1, the refrigeration cycle device 1 includes a cold heat source unit 2, a load device 3, and pipes 84 and 88. The cold heat source unit 2 has a refrigerant outlet port and a refrigerant inlet port for connecting to the load device 3. Since the cold heat source unit 2 is often arranged outdoors, it may also be referred to as an indoor unit or an outdoor unit. The load device 3 has a refrigerant outlet port and a refrigerant inlet port for connecting to the cold heat source unit 2. The pipe 84 connects the refrigerant outlet port of the cold heat source unit 2 and the refrigerant inlet port of the load device 3. The pipe 88 connects the refrigerant outlet port of the load device 3 and the refrigerant inlet port of the cold heat source unit 2.
　冷凍サイクル装置１の冷熱源ユニット２は、負荷装置３に接続されるように構成される。冷熱源ユニット２は、吸入ポートＧ１および吐出ポートＧ２を有する圧縮機１０と、凝縮器２０と、ファン２２と、冷媒冷却装置３０と、配管８０～８３，８９とを備える。冷媒冷却装置３０は、熱交換器７２と、冷媒の流路を切替える切替部７４とを含む。熱交換器７２は、第１通路Ｈ１および第２通路Ｈ２を有し、第１通路Ｈ１を流れる冷媒と第２通路Ｈ２を流れる冷媒との間で熱交換を行なうように構成される。 The cold heat source unit 2 of the refrigeration cycle device 1 is configured to be connected to the load device 3. The cold heat source unit 2 includes a compressor 10 having a suction port G1 and a discharge port G2, a condenser 20, a fan 22, a refrigerant cooling device 30, and pipes 80 to 83, 89. The refrigerant cooling device 30 includes a heat exchanger 72 and a switching unit 74 for switching the flow path of the refrigerant. The heat exchanger 72 has a first passage H1 and a second passage H2, and is configured to exchange heat between the refrigerant flowing through the first passage H1 and the refrigerant flowing through the second passage H2.
　負荷装置３は、第１膨張装置５０と、蒸発器６０と、配管８５、８６，８７とを含む。蒸発器６０は空気と冷媒との間で熱交換を行なうように構成される。冷凍サイクル装置１では、蒸発器６０は、冷却対象空間の空気からの吸熱によって冷媒を蒸発させる。第１膨張装置５０は、たとえば、冷熱源ユニット２と独立して制御される温度膨張弁である。なお、第１膨張装置５０は冷媒を減圧することができる電子膨張弁であってもよい。 The load device 3 includes a first expansion device 50, an evaporator 60, and pipes 85, 86, 87. The evaporator 60 is configured to exchange heat between air and the refrigerant. In the refrigeration cycle device 1, the evaporator 60 evaporates the refrigerant by endothermic heat from the air in the cooling target space. The first expansion device 50 is, for example, a temperature expansion valve controlled independently of the cold heat source unit 2. The first expansion device 50 may be an electronic expansion valve capable of reducing the pressure of the refrigerant.
　圧縮機１０は、配管８９から吸入される冷媒を圧縮して配管８０へ吐出する。圧縮機１０は、インバータ制御により駆動周波数を任意に変更することができる。圧縮機１０は、制御装置１００からの制御信号に従って回転速度を調整するように構成される。圧縮機１０の回転速度を調整することで冷媒の循環量が調整され、冷凍サイクル装置１の能力を調整することができる。圧縮機１０には種々のタイプのものを採用可能であり、たとえば、スクロールタイプ、ロータリータイプ、スクリュータイプ等のものを採用し得る。 The compressor 10 compresses the refrigerant sucked from the pipe 89 and discharges it to the pipe 80. The drive frequency of the compressor 10 can be arbitrarily changed by inverter control. The compressor 10 is configured to adjust the rotation speed according to a control signal from the control device 100. By adjusting the rotation speed of the compressor 10, the circulation amount of the refrigerant is adjusted, and the capacity of the refrigerating cycle device 1 can be adjusted. Various types of compressors 10 can be adopted, and for example, scroll type, rotary type, screw type and the like can be adopted.
　凝縮器２０は、圧縮機１０から吐出された高温高圧のガス冷媒が外気と熱交換（放熱）を行なうように構成される。この熱交換により、冷媒は凝縮されて液相に変化する。圧縮機１０から配管８０に吐出された冷媒は、凝縮器２０において凝縮および液化され配管８１へ流出する。熱交換の効率を上げるため外気を送るファン２２が凝縮器２０に取り付けられている。ファン２２は、凝縮器２０において冷媒が熱交換を行なう外気を凝縮器２０に供給する。ファン２２の回転速度を調整することにより、圧縮機１０の吐出側の冷媒圧力（高圧側圧力）を調整することができる。 The condenser 20 is configured so that the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 exchanges heat (heat dissipation) with the outside air. By this heat exchange, the refrigerant is condensed and changed into a liquid phase. The refrigerant discharged from the compressor 10 to the pipe 80 is condensed and liquefied in the condenser 20 and flows out to the pipe 81. A fan 22 for sending outside air is attached to the condenser 20 in order to improve the efficiency of heat exchange. The fan 22 supplies the outside air to the condenser 20 through which the refrigerant exchanges heat in the condenser 20. By adjusting the rotation speed of the fan 22, the refrigerant pressure (high pressure side pressure) on the discharge side of the compressor 10 can be adjusted.
　ここで、冷凍サイクル装置１の冷媒回路に使用する冷媒はＣＯ２とするが、過冷却度が確保しにくい状態が生じる場合は、他の冷媒を使用しても良い。 Here, the refrigerant used in the refrigerant circuit of the refrigeration cycle device 1 is CO 2 , but if a state in which it is difficult to secure the degree of supercooling occurs, another refrigerant may be used.
　なお、凝縮器２０は、冷媒からの熱を外気に放熱する放熱器として働く。本明細書では、説明の容易のため、超臨界状態のＣＯ２のような冷媒を冷却する場合も凝縮器２０と呼ぶこととする。また、本明細書では、説明の容易のため、超臨界状態の冷媒の基準温度からの低下量も過冷却度と呼ぶこととする。 The condenser 20 works as a radiator that dissipates heat from the refrigerant to the outside air. In the present specification, for the sake of simplicity, the case of cooling a refrigerant such as CO 2 in a supercritical state is also referred to as a condenser 20. Further, in the present specification, for the sake of simplicity, the amount of decrease of the refrigerant in the supercritical state from the reference temperature is also referred to as the degree of supercooling.
　冷熱源ユニット２の冷媒入口ポートから圧縮機１０、凝縮器２０、熱交換器７２の第１通路Ｈ１を経由して冷媒出口ポートに至る第１流路Ｆ１は、第１膨張装置５０および蒸発器６０が配置される負荷装置３とともに、冷媒が循環する循環流路を形成する。以下、この循環流路を冷凍サイクルの「主冷媒回路」とも言う。 The first flow path F1 from the refrigerant inlet port of the cold heat source unit 2 to the refrigerant outlet port via the compressor 10, the condenser 20, and the first passage H1 of the heat exchanger 72 is the first expansion device 50 and the evaporator. Together with the load device 3 in which the 60 is arranged, a circulation flow path through which the refrigerant circulates is formed. Hereinafter, this circulation flow path is also referred to as a "main refrigerant circuit" of the refrigeration cycle.
　冷熱源ユニット２は、冷媒が循環する方向において、蒸発器６０よりも下流の第１流路Ｆ１の分岐点ＢＰから分岐する第２流路Ｆ２をさらに備える。第２流路Ｆ２は、蒸発器６０を通過した冷媒が冷媒冷却装置３０を経由して圧縮機１０に戻るように構成される。冷媒冷却装置３０は、分岐点ＢＰから第２流路Ｆ２に冷媒を流すか否かを切替える切替部７４と、第１流路Ｆ１の一部である第１通路Ｈ１と第２流路Ｆ２の一部である第２通路Ｈ２とを有し、第１通路Ｈ１を流れる冷媒と第２通路Ｈ２を流れる冷媒との間で熱交換を行なうように構成された熱交換器７２とを備える。 The cold heat source unit 2 further includes a second flow path F2 that branches from the branch point BP of the first flow path F1 downstream of the evaporator 60 in the direction in which the refrigerant circulates. The second flow path F2 is configured such that the refrigerant that has passed through the evaporator 60 returns to the compressor 10 via the refrigerant cooling device 30. The refrigerant cooling device 30 includes a switching unit 74 for switching whether or not to flow the refrigerant from the branch point BP to the second flow path F2, and the first passage H1 and the second flow path F2 which are a part of the first flow path F1. It has a second passage H2 which is a part thereof, and includes a heat exchanger 72 configured to exchange heat between the refrigerant flowing through the first passage H1 and the refrigerant flowing through the second passage H2.
　冷熱源ユニット２は、さらに、圧力センサ１１０～１１２と、温度センサ１２０，１２１と、圧縮機１０および切替部７４を制御する制御装置１００とを備える。 The cold heat source unit 2 further includes pressure sensors 110 to 112, temperature sensors 120 and 121, and a control device 100 that controls the compressor 10 and the switching unit 74.
　圧力センサ１１０は、圧縮機１０の吸入ポート部分の圧力Ｐｓを検出し、その検出値を制御装置１００へ出力する。圧力センサ１１１は、圧縮機１０の吐出圧力Ｐｄを検出し、その検出値を制御装置１００へ出力する。圧力センサ１１２は、第１膨張装置５０の手前の配管８３の冷媒圧力Ｐ１を検出し、その検出値を制御装置１００へ出力する。 The pressure sensor 110 detects the pressure Ps in the suction port portion of the compressor 10 and outputs the detected value to the control device 100. The pressure sensor 111 detects the discharge pressure Pd of the compressor 10 and outputs the detected value to the control device 100. The pressure sensor 112 detects the refrigerant pressure P1 in the pipe 83 in front of the first expansion device 50, and outputs the detected value to the control device 100.
　温度センサ１２０は、圧縮機１０の吐出温度ＴＨを検出し、その検出値を制御装置１００へ出力する。温度センサ１２１は、第１膨張装置５０の手前の配管８３の冷媒温度Ｔ１を検出し、その検出値を制御装置１００へ出力する。 The temperature sensor 120 detects the discharge temperature TH of the compressor 10 and outputs the detected value to the control device 100. The temperature sensor 121 detects the refrigerant temperature T1 of the pipe 83 in front of the first expansion device 50, and outputs the detected value to the control device 100.
　制御装置１００は、ＣＰＵ（Central　Processing　Unit）１０２と、メモリ１０４（ＲＯＭ（Read　Only　Memory）およびＲＡＭ（Random　Access　Memory））と、各種信号を入出力するための入出力バッファ（図示せず）等を含んで構成される。ＣＰＵ１０２は、ＲＯＭに格納されているプログラムをＲＡＭ等に展開して実行する。ＲＯＭに格納されるプログラムは、制御装置１００の処理手順が記されたプログラムである。制御装置１００は、これらのプログラムに従って、冷熱源ユニット２における各機器の制御を実行する。この制御については、ソフトウェアによる処理に限られず、専用のハードウェア（電子回路）で処理することも可能である。 The control device 100 includes a CPU (Central Processing Unit) 102, a memory 104 (ROM (Read Only Memory) and RAM (Random Access Memory)), an input / output buffer (not shown) for inputting / outputting various signals, and the like. Consists of including. The CPU 102 expands the program stored in the ROM into a RAM or the like and executes the program. The program stored in the ROM is a program in which the processing procedure of the control device 100 is described. The control device 100 executes control of each device in the cold heat source unit 2 according to these programs. This control is not limited to software processing, but can also be processed by dedicated hardware (electronic circuit).
　制御装置１００は、圧力センサ１１２および温度センサ１２１の出力に応じて切替部７４の冷媒の流れを制御する。切替部７４は、開閉弁７６，７７を含む。開閉弁７６を閉じ開閉弁７７を開くと、冷媒は、第２流路Ｆ２を流れずに、負荷装置３から圧縮機１０の吸入ポートＧ１に流れる。逆に開閉弁７６を開き開閉弁７７を閉じると、冷媒は、負荷装置３から第２流路Ｆ２を経由して圧縮機１０の吸入ポートＧ１に流れる。 The control device 100 controls the flow of the refrigerant in the switching unit 74 according to the outputs of the pressure sensor 112 and the temperature sensor 121. The switching unit 74 includes on-off valves 76 and 77. When the on-off valve 76 is closed and the on-off valve 77 is opened, the refrigerant flows from the load device 3 to the suction port G1 of the compressor 10 without flowing through the second flow path F2. On the contrary, when the on-off valve 76 is opened and the on-off valve 77 is closed, the refrigerant flows from the load device 3 to the suction port G1 of the compressor 10 via the second flow path F2.
　本実施の形態では第２流路Ｆ２は、第１膨張装置５０および蒸発器６０を通過して低温になった冷媒を熱交換器７２へ流入させることによって凝縮器２０から配管８１に流出する冷媒を冷却し、配管８２～８５を通過して第１膨張装置５０に流入する冷媒の状態を安定させるために設けられる。 In the present embodiment, the second flow path F2 is a refrigerant that flows out from the condenser 20 to the pipe 81 by flowing the low-temperature refrigerant that has passed through the first expansion device 50 and the evaporator 60 into the heat exchanger 72. Is provided to cool the water and stabilize the state of the refrigerant flowing into the first expansion device 50 through the pipes 82 to 85.
　この点についてより詳細に説明する。たとえば、ＣＯ２などの高圧側で超臨界状態となり得る冷媒を使用する場合、冷媒状態が臨界点（臨界圧力、臨界温度）付近のとき、少しの温度変化に対して密度が大きく変動する。第１膨張装置５０の入口側の冷媒密度が大きく変化すると、第１膨張装置５０の冷媒流量が安定せず、冷凍サイクル装置の冷凍能力不足などを引き起こす。 This point will be described in more detail. For example, when a refrigerant that can be in a supercritical state on the high pressure side such as CO 2 is used, when the refrigerant state is near a critical point (critical pressure, critical temperature), the density fluctuates greatly with a slight temperature change. If the refrigerant density on the inlet side of the first expansion device 50 changes significantly, the refrigerant flow rate of the first expansion device 50 becomes unstable, causing a shortage of the refrigerating capacity of the refrigeration cycle device.
　そこで、本実施の形態では、第１膨張装置５０の入口側の冷媒状態が臨界点付近の場合、第１膨張装置５０の手前の冷媒を冷媒冷却装置３０によって冷却して冷媒の状態を臨界点付近から回避させる。これにより、温度変化に対する密度変動を抑制して膨張弁流量を安定化させ、安定した冷凍能力を供給することができる。 Therefore, in the present embodiment, when the refrigerant state on the inlet side of the first expansion device 50 is near the critical point, the refrigerant in front of the first expansion device 50 is cooled by the refrigerant cooling device 30 to change the state of the refrigerant to the critical point. Avoid from the vicinity. As a result, it is possible to suppress the density fluctuation due to the temperature change, stabilize the expansion valve flow rate, and supply a stable refrigerating capacity.
　このような冷却を実現するために、図１に示す構成では、主冷媒回路は、圧縮機１０から、凝縮器２０、冷媒冷却装置３０、第１膨張装置５０、蒸発器６０を順に経由して、圧縮機１０に冷媒が戻るように構成される。 In order to realize such cooling, in the configuration shown in FIG. 1, the main refrigerant circuit passes from the compressor 10 through the condenser 20, the refrigerant cooling device 30, the first expansion device 50, and the evaporator 60 in this order. , The refrigerant is configured to return to the compressor 10.
　冷媒冷却装置３０は、実施の形態１では、蒸発器６０を通過した後の冷凍サイクルの冷媒自体を冷熱源として使用する。冷媒の状態を観測するために、第１膨張装置５０の入口手前に圧力センサ１１２と温度センサ１２１が設けられている。制御装置１００は、第１膨張装置５０の冷媒入口側の冷媒状態（圧力、温度）が冷却範囲となったら、冷媒冷却装置３０の冷却能力を増加させ冷媒冷却を行なう。なお、冷媒は、ＣＯ２には限定されないが、ＣＯ２であれば特に効果的である。 In the first embodiment, the refrigerant cooling device 30 uses the refrigerant itself in the refrigerating cycle after passing through the evaporator 60 as a cold heat source. In order to observe the state of the refrigerant, a pressure sensor 112 and a temperature sensor 121 are provided in front of the inlet of the first expansion device 50. When the refrigerant state (pressure, temperature) on the refrigerant inlet side of the first expansion device 50 falls within the cooling range, the control device 100 increases the cooling capacity of the refrigerant cooling device 30 to cool the refrigerant. Incidentally, the refrigerant is not limited to CO 2, but is particularly effective if CO 2.
　冷却範囲は、少しの温度変化に対して密度が大きく変動する状態の圧力範囲/温度範囲である。冷却範囲は、たとえば、冷媒圧力が超臨界圧力であるとき冷媒の温度変化０．５Ｋに対して冷媒の密度が１０％以上変化する範囲にすると良い。 The cooling range is the pressure range / temperature range in which the density fluctuates greatly with a slight temperature change. The cooling range may be, for example, a range in which the density of the refrigerant changes by 10% or more with respect to a temperature change of 0.5 K of the refrigerant when the refrigerant pressure is a supercritical pressure.
　図２は、冷却範囲の一例を示す図である。図３は、冷却範囲をｐ－ｈ線図中に示した図である。図２、図３では、冷媒がＣＯ２である場合の例を示す。 FIG. 2 is a diagram showing an example of a cooling range. FIG. 3 is a diagram showing the cooling range in the ph diagram. 2 and 3 show an example when the refrigerant is CO 2.
　図２の例では、圧力を７．０ＭＰａから８．２ＭＰａまで０．２ＭＰａ刻みで変化させた場合の冷却範囲に該当する温度範囲Ａ１～Ａ７が示されている。 In the example of FIG. 2, the temperature ranges A1 to A7 corresponding to the cooling range when the pressure is changed from 7.0 MPa to 8.2 MPa in 0.2 MPa increments are shown.
　図２に示すように、圧力が７．０ＭＰａである場合の温度範囲Ａ１は、２８．５～２９．５℃である。圧力が７．２ＭＰａである場合の温度範囲Ａ２は、２９．５～３０．５℃である。圧力が７．４ＭＰａである場合の温度範囲Ａ３は、３１．０～３２．０℃である。圧力が７．６ＭＰａである場合の温度範囲Ａ４は、３２．０～３３．０℃である。圧力が７．８ＭＰａである場合の温度範囲Ａ５は、３３．０～３４．０℃である。圧力が８．０ＭＰａである場合の温度範囲Ａ６は、３４．０～３５．０℃である。圧力が８．２ＭＰａである場合の温度範囲Ａ７は、３５．５～３６．５℃である。 As shown in FIG. 2, the temperature range A1 when the pressure is 7.0 MPa is 28.5 to 29.5 ° C. The temperature range A2 when the pressure is 7.2 MPa is 29.5 to 30.5 ° C. The temperature range A3 when the pressure is 7.4 MPa is 31.0 to 32.0 ° C. The temperature range A4 when the pressure is 7.6 MPa is 32.0 to 33.0 ° C. The temperature range A5 when the pressure is 7.8 MPa is 33.0 to 34.0 ° C. The temperature range A6 when the pressure is 8.0 MPa is 34.0 to 35.0 ° C. The temperature range A7 when the pressure is 8.2 MPa is 35.5 to 36.5 ° C.
　このように、圧力と温度で規定される範囲Ａ１～Ａ７の集合で表わされる冷却範囲Ａをｐ－ｈ線図上に図示すると、図３のようになる。 As described above, when the cooling range A represented by the set of the ranges A1 to A7 defined by the pressure and the temperature is illustrated on the ph diagram, it becomes as shown in FIG.
　制御装置１００は、第１膨張装置５０の冷媒入口側の冷媒状態（圧力、温度）が冷却範囲となったら、冷媒冷却装置３０の冷却能力を増加させ冷媒冷却を行なう。図４は、冷却前と冷却後の冷凍サイクルの変化を示すｐ－ｈ線図である。なお、冷凍サイクルの変化を図３中に表示すると見にくいため、図４のように簡略化して示している。 When the refrigerant state (pressure, temperature) on the refrigerant inlet side of the first expansion device 50 falls within the cooling range, the control device 100 increases the cooling capacity of the refrigerant cooling device 30 to cool the refrigerant. FIG. 4 is a ph diagram showing changes in the refrigeration cycle before and after cooling. Since it is difficult to see the change in the refrigeration cycle when displayed in FIG. 3, it is shown in a simplified manner as shown in FIG.
　冷媒冷却前の冷凍サイクルＣ１は、第１膨張装置５０の入口部分の状態が冷却範囲Ａに入っている。このような状態となると、制御装置１００は、冷媒冷却装置３０を用いて冷媒を冷却する。冷媒冷却装置３０の作動後の冷凍サイクルＣ２では、冷媒が冷却されたため第１膨張装置５０の入口部分の状態を示す点が図４の左方向すなわち比エンタルピが小さくなる方向に移動する。 In the refrigerating cycle C1 before cooling the refrigerant, the state of the inlet portion of the first expansion device 50 is within the cooling range A. In such a state, the control device 100 cools the refrigerant by using the refrigerant cooling device 30. In the refrigerating cycle C2 after the operation of the refrigerant cooling device 30, the point indicating the state of the inlet portion of the first expansion device 50 moves to the left in FIG. 4, that is, in the direction in which the specific enthalpy becomes smaller because the refrigerant has been cooled.
　図５は、制御装置１００が実行する冷媒冷却装置の制御を説明するためのフローチャートである。このフローチャートの処理は、一定時間ごとに冷凍サイクル装置の主制御ルーチンから呼び出されて実行される。 FIG. 5 is a flowchart for explaining the control of the refrigerant cooling device executed by the control device 100. The processing of this flowchart is called and executed from the main control routine of the refrigeration cycle apparatus at regular intervals.
　まず、ステップＳ１において制御装置１００は、冷媒冷却装置３０が冷媒冷却中であるか否かを判断する。冷媒冷却装置３０が冷媒冷却中の場合には、切替部７４において第２流路Ｆ２に冷媒が流通するように開閉弁７６，７７が制御される。このとき、開閉弁７６は開状態、開閉弁７７は閉状態である。一方、冷媒冷却装置３０が冷媒冷却中でない場合には、切替部７４において第２流路Ｆ２に冷媒が流通しないように開閉弁７６，７７が制御される。このとき、開閉弁７６は閉状態、開閉弁７７は開状態である。 First, in step S1, the control device 100 determines whether or not the refrigerant cooling device 30 is cooling the refrigerant. When the refrigerant cooling device 30 is cooling the refrigerant, the on-off valves 76 and 77 are controlled in the switching unit 74 so that the refrigerant flows through the second flow path F2. At this time, the on-off valve 76 is in the open state and the on-off valve 77 is in the closed state. On the other hand, when the refrigerant cooling device 30 is not cooling the refrigerant, the on-off valves 76 and 77 are controlled in the switching unit 74 so that the refrigerant does not flow to the second flow path F2. At this time, the on-off valve 76 is in the closed state and the on-off valve 77 is in the open state.
　ステップＳ１において、冷媒冷却装置３０が冷媒冷却中でない場合（Ｓ１でＮＯ）、ステップＳ２において制御装置１００は、第１膨張装置５０の入口部分の冷媒の状態が図２，図３で説明した冷却範囲内に該当するか否かを判断する。 In step S1, when the refrigerant cooling device 30 is not cooling the refrigerant (NO in S1), in step S2, in the control device 100, the state of the refrigerant at the inlet portion of the first expansion device 50 is the cooling described with reference to FIGS. 2 and 3. Determine if it falls within the range.
　冷媒の状態が冷却範囲内に該当する場合（Ｓ２でＹＥＳ）、ステップＳ３において制御装置１００は、切替部７４の内部の開閉弁７６を開状態、開閉弁７７を閉状態として、冷媒の冷却を開始する。一方、冷媒の状態が冷却範囲内に該当しない場合（Ｓ２でＮＯ）、制御装置１００は、ステップＳ３の制御を行なわずに制御を主制御ルーチンに戻す。 When the state of the refrigerant falls within the cooling range (YES in S2), in step S3, the control device 100 sets the on-off valve 76 inside the switching unit 74 to the open state and the on-off valve 77 to the closed state to cool the refrigerant. Start. On the other hand, when the state of the refrigerant does not fall within the cooling range (NO in S2), the control device 100 returns the control to the main control routine without performing the control in step S3.
　ステップＳ１において、冷媒冷却装置３０が冷媒冷却中である場合（Ｓ１でＹＥＳ）、ステップＳ４において制御装置１００は、冷却開始から５分以上冷却を継続しているか否かを判断する。 In step S1, when the refrigerant cooling device 30 is cooling the refrigerant (YES in S1), in step S4, the control device 100 determines whether or not cooling is continued for 5 minutes or more from the start of cooling.
　冷却開始から５分以上冷却を継続していた場合（Ｓ４でＹＥＳ）、図４の冷凍サイクルＣ１からＣ２への移行が完了しているので、ステップＳ５において制御装置１００は、冷却を終了させる。すなわち、切替部７４において第２流路Ｆ２に冷媒が流通しないように開閉弁７６，７７が制御され、開閉弁７６は閉状態、開閉弁７７は開状態に設定される。 If cooling has been continued for 5 minutes or more from the start of cooling (YES in S4), the transition from the refrigeration cycle C1 to C2 in FIG. 4 has been completed, so that the control device 100 ends the cooling in step S5. That is, the on-off valves 76 and 77 are controlled in the switching unit 74 so that the refrigerant does not flow to the second flow path F2, the on-off valve 76 is set to the closed state, and the on-off valve 77 is set to the open state.
　なお、ステップＳ４における「５分」については、冷媒の循環量などにも影響を受けるので、あくまでも例示である。 Note that "5 minutes" in step S4 is only an example because it is affected by the circulation amount of the refrigerant and the like.
　以上のように冷媒冷却装置３０を制御することによって、温度変化に対する密度変動を抑制して第１膨張装置５０の冷媒流量を安定化させることができ、安定した冷凍能力を供給することが可能となる。 By controlling the refrigerant cooling device 30 as described above, it is possible to suppress the density fluctuation due to the temperature change and stabilize the refrigerant flow rate of the first expansion device 50, and it is possible to supply a stable refrigerating capacity. Become.
　実施の形態２．
　図６は、実施の形態２の冷凍サイクル装置の全体構成図である。なお、図２では、冷凍サイクル装置における各機器の接続関係および配置構成を機能的に示しており、物理的な空間における配置を必ずしも示すものではない。 Embodiment 2.
FIG. 6 is an overall configuration diagram of the refrigeration cycle apparatus of the second embodiment. Note that FIG. 2 functionally shows the connection relationship and the arrangement configuration of each device in the refrigeration cycle apparatus, and does not necessarily show the arrangement in the physical space.
　図６を参照して、冷凍サイクル装置１Ａは、冷熱源ユニット２Ａと、負荷装置３と、配管８４，８８とを備える。負荷装置３については、図１の構成と同じであるので、説明は繰返さない。 With reference to FIG. 6, the refrigeration cycle device 1A includes a cold heat source unit 2A, a load device 3, and pipes 84 and 88. Since the load device 3 has the same configuration as that in FIG. 1, the description will not be repeated.
　冷熱源ユニット２Ａは、図１に示した冷熱源ユニット２の構成において、圧縮機１０に代えて圧縮機１０Ａを含み、冷媒冷却装置３０に代えて冷媒冷却装置３０Ａを含み、第２流路Ｆ２に代えて第２流路Ｆ２Ａを含み、制御装置１００に代えて制御装置１００Ａを含む。冷熱源ユニット２Ａの他の部分の構成は、冷熱源ユニット２と同様であるので説明は繰返さない。 In the configuration of the cold heat source unit 2 shown in FIG. 1, the cold heat source unit 2A includes a compressor 10A instead of the compressor 10, a refrigerant cooling device 30A instead of the refrigerant cooling device 30, and a second flow path F2. The second flow path F2A is included in place of the control device 100, and the control device 100A is included in place of the control device 100. Since the configuration of the other parts of the cold heat source unit 2A is the same as that of the cold heat source unit 2, the description will not be repeated.
　冷媒冷却装置３０Ａは、開閉弁７０と、第２膨張装置７１と、熱交換器７２とを含む。第２流路Ｆ２Ａは、冷媒が循環する方向において、冷媒冷却装置３０Ａよりも下流の第１流路Ｆ１の分岐点ＢＰＡから分岐し、凝縮器２０および冷媒冷却装置３０Ａを通過した冷媒を圧縮機１０に戻すように構成される。 The refrigerant cooling device 30A includes an on-off valve 70, a second expansion device 71, and a heat exchanger 72. The second flow path F2A branches from the branch point BPA of the first flow path F1 downstream of the refrigerant cooling device 30A in the direction in which the refrigerant circulates, and the refrigerant that has passed through the condenser 20 and the refrigerant cooling device 30A is compressed. It is configured to return to 10.
　第２膨張装置７１は主冷媒回路の高圧部の冷媒を中間圧力まで低下させることができる電子膨張弁である。なお、第２膨張装置７１が完全に閉止することが可能な電子膨張弁である場合には、開閉弁７０を閉じる代わりに、開閉弁７０を省略し、電子膨張弁を閉じても良い。 The second expansion device 71 is an electronic expansion valve capable of reducing the refrigerant in the high pressure portion of the main refrigerant circuit to an intermediate pressure. When the second expansion device 71 is an electronic expansion valve that can be completely closed, the on-off valve 70 may be omitted and the electronic expansion valve may be closed instead of closing the on-off valve 70.
　実施の形態２では、圧縮機１０Ａに中間圧ポートＧ３が設けられており中間圧ポートＧ３からの冷媒を圧縮工程の途中部分に流入させることができる。 In the second embodiment, the compressor 10A is provided with the intermediate pressure port G3, and the refrigerant from the intermediate pressure port G3 can flow into the middle part of the compression process.
　第２流路Ｆ２Ａは、循環流路の第１通路Ｈ１の出口に接続される配管８２の分岐点ＢＰＡから、第２通路Ｈ２の入口に冷媒を流す配管９１，９２，９４と、第２通路Ｈ２の出口から圧縮機１０Ａの中間圧ポートＧ３に冷媒を流す配管９６とをさらに備える。以下において、主冷媒回路から分岐して第２通路Ｈ２を経由して圧縮機１０Ａに冷媒を送る第２流路Ｆ２Ａを、「インジェクション流路」とも言う。 The second flow path F2A includes pipes 91, 92, 94 for flowing the refrigerant from the branch point BPA of the pipe 82 connected to the outlet of the first passage H1 of the circulation flow path to the inlet of the second passage H2, and the second passage. Further, a pipe 96 for flowing a refrigerant from the outlet of H2 to the intermediate pressure port G3 of the compressor 10A is provided. In the following, the second flow path F2A that branches from the main refrigerant circuit and sends the refrigerant to the compressor 10A via the second passage H2 is also referred to as an “injection flow path”.
　開閉弁７０、第２膨張装置７１および熱交換器７２は、分岐点ＢＰＡから順に第２流路Ｆ２Ａに配置される。熱交換器７２の第１通路Ｈ１は、第１流路Ｆ１の一部である。熱交換器７２の第２通路Ｈ２は、第２流路Ｆ２Ａの一部である。制御装置１００Ａは、圧力センサ１１２および温度センサ１２１の出力に応じて第２膨張装置７１の冷媒流通量を制御する。 The on-off valve 70, the second expansion device 71, and the heat exchanger 72 are arranged in the second flow path F2A in order from the branch point BPA. The first passage H1 of the heat exchanger 72 is a part of the first passage F1. The second passage H2 of the heat exchanger 72 is a part of the second passage F2A. The control device 100A controls the amount of refrigerant flowing through the second expansion device 71 according to the outputs of the pressure sensor 112 and the temperature sensor 121.
　制御装置１００Ａは、実施の形態１と同様に、図５のフローチャートで示した処理を実行する。この場合、制御装置１００Ａは、ステップＳ３において冷媒冷却装置３０Ａによる冷媒の冷却を開始する場合には、開閉弁７０を開く。また、制御装置１００Ａは、ステップＳ５において冷媒冷却装置３０Ａによる冷媒の冷却を終了する場合には、開閉弁７０を閉じる。 The control device 100A executes the process shown in the flowchart of FIG. 5 as in the first embodiment. In this case, the control device 100A opens the on-off valve 70 when the refrigerant cooling device 30A starts cooling the refrigerant in step S3. Further, the control device 100A closes the on-off valve 70 when the cooling of the refrigerant by the refrigerant cooling device 30A is completed in step S5.
　図７は、実施の形態２の冷凍サイクル装置の変形例の全体構成図である。図７に示す冷凍サイクル装置１Ｂは、図６に示した冷凍サイクル装置１Ａの構成において、冷熱源ユニット２Ａに代えて冷熱源ユニット２Ｂを備える。 FIG. 7 is an overall configuration diagram of a modified example of the refrigeration cycle apparatus according to the second embodiment. The refrigerating cycle apparatus 1B shown in FIG. 7 includes a refrigerating heat source unit 2B instead of the refrigerating heat source unit 2A in the configuration of the refrigerating cycle apparatus 1A shown in FIG.
　冷熱源ユニット２Ｂは、第２流路Ｆ２Ａが第２流路Ｆ２Ｂとなっている。第２流路Ｆ２Ａでは、配管９６が圧縮機１０Ａの中間圧ポートＧ３に接続されていたが、第２流路Ｆ２Ｂでは、配管９６が圧縮機１０の吸入ポートＧ１に接続されている。冷熱源ユニット２Ｂの他の部分の構成は、冷熱源ユニット２Ａと同様であるので、説明は繰返さない。 In the cold heat source unit 2B, the second flow path F2A is the second flow path F2B. In the second flow path F2A, the pipe 96 is connected to the intermediate pressure port G3 of the compressor 10A, but in the second flow path F2B, the pipe 96 is connected to the suction port G1 of the compressor 10. Since the configuration of the other parts of the cold heat source unit 2B is the same as that of the cold heat source unit 2A, the description will not be repeated.
　図７に示すように構成を変形しても、図１および図６の構成と同様な効果を得ることができる。 Even if the configuration is modified as shown in FIG. 7, the same effect as that of the configurations of FIGS. 1 and 6 can be obtained.
　実施の形態３．
　実施の形態１および２では、冷凍サイクル装置を循環する冷媒自体の低温部分によって、第１膨張装置５０に流入する冷媒を冷却したが、他の方法で冷却しても良い。 Embodiment 3.
In the first and second embodiments, the refrigerant flowing into the first expansion device 50 is cooled by the low temperature portion of the refrigerant itself circulating in the refrigeration cycle device, but it may be cooled by another method.
　図８は、実施の形態３の冷凍サイクル装置の全体構成図である。なお、図３では、冷凍サイクル装置における各機器の接続関係および配置構成を機能的に示しており、物理的な空間における配置を必ずしも示すものではない。 FIG. 8 is an overall configuration diagram of the refrigeration cycle apparatus according to the third embodiment. Note that FIG. 3 functionally shows the connection relationship and the arrangement configuration of each device in the refrigeration cycle apparatus, and does not necessarily show the arrangement in the physical space.
　図８を参照して、冷凍サイクル装置１Ｃは、冷熱源ユニット２Ｃと、負荷装置３と、配管８４，８８とを備える。負荷装置３については、図１の構成と同じであるので、説明は繰返さない。 With reference to FIG. 8, the refrigeration cycle device 1C includes a cold heat source unit 2C, a load device 3, and pipes 84 and 88. Since the load device 3 has the same configuration as that in FIG. 1, the description will not be repeated.
　冷熱源ユニット２Ｃは、図１に示した冷熱源ユニット２の構成において、第２流路Ｆ２は削除され、冷媒冷却装置３０に代えて冷媒冷却装置３０Ｃを含み、制御装置１００に代えて制御装置１００Ｃを含む。冷熱源ユニット２Ｃの他の部分の構成は、冷熱源ユニット２と同様であるので説明は繰返さない。 In the cold heat source unit 2C, in the configuration of the cold heat source unit 2 shown in FIG. 1, the second flow path F2 is deleted, and the refrigerant cooling device 30C is included instead of the refrigerant cooling device 30, and the control device 100 is replaced with the control device 100. Includes 100C. Since the configuration of the other parts of the cold heat source unit 2C is the same as that of the cold heat source unit 2, the description will not be repeated.
　冷媒冷却装置３０Ｃは、冷媒と熱媒体とを熱交換させる熱交換器２０２と、熱交換器２０２に熱媒体を送る供給装置２０４とを備える。たとえば、熱媒体が外気である場合、供給装置２０４はファンである。なお、熱媒体が水またはブラインである場合、供給装置はポンプまたは弁である。制御装置１００Ｃは、圧力センサ１１２および温度センサ１２１の出力に応じて供給装置２０４によって熱交換器２０２に供給される熱媒体の量を制御する。これにより、冷媒冷却装置３０Ｃの冷却性能を変化させることができる。 The refrigerant cooling device 30C includes a heat exchanger 202 that exchanges heat between the refrigerant and the heat medium, and a supply device 204 that sends the heat medium to the heat exchanger 202. For example, if the heat medium is outside air, the supply device 204 is a fan. If the heat medium is water or brine, the supply device is a pump or valve. The control device 100C controls the amount of heat medium supplied to the heat exchanger 202 by the supply device 204 according to the outputs of the pressure sensor 112 and the temperature sensor 121. Thereby, the cooling performance of the refrigerant cooling device 30C can be changed.
　制御装置１００Ｃは、実施の形態１と同様に、図５のフローチャートで示した処理を実行する。この場合、制御装置１００Ｃは、ステップＳ３において冷媒冷却装置３０Ｃによる冷媒の冷却を開始する場合には、供給装置２０４を作動させる。また、制御装置１００Ｃは、ステップＳ５において冷媒冷却装置３０Ｃによる冷媒の冷却を終了する場合には、供給装置２０４を停止する。 The control device 100C executes the process shown in the flowchart of FIG. 5 as in the first embodiment. In this case, the control device 100C operates the supply device 204 when the refrigerant cooling device 30C starts cooling the refrigerant in step S3. Further, the control device 100C stops the supply device 204 when the cooling of the refrigerant by the refrigerant cooling device 30C is completed in step S5.
　実施の形態３に示す構成としても、図１および図６の構成と同様な効果を得ることができる。 As the configuration shown in the third embodiment, the same effect as that of the configurations of FIGS. 1 and 6 can be obtained.
　（まとめ）
　最後に、本実施の形態について再び図面を参照して総括する。 (summary)
Finally, the present embodiment will be summarized again with reference to the drawings.
　本開示は、第１膨張装置５０および蒸発器６０を含む負荷装置３に接続されるように構成された冷熱源ユニット２に関する。冷熱源ユニット２は、第１流路Ｆ１と、圧縮機１０と、凝縮器２０と、冷媒冷却装置３０と、圧力センサ１１２と、温度センサ１２１と、制御装置１００とを備える。第１流路Ｆ１は、負荷装置３に接続されることによって、冷媒が循環する循環流路を形成する。圧縮機１０、凝縮器２０および冷媒冷却装置３０は、第１流路Ｆ１に順に配置される。圧力センサ１１２および温度センサ１２１は、冷媒冷却装置３０から第１膨張装置５０に送られる冷媒の圧力および温度をそれぞれ検出する。制御装置１００は、圧力センサ１１２および温度センサ１２１の出力に基づいて、冷媒冷却装置３０の冷却性能を変化させる。 The present disclosure relates to a cold heat source unit 2 configured to be connected to a load device 3 including a first expansion device 50 and an evaporator 60. The cold heat source unit 2 includes a first flow path F1, a compressor 10, a condenser 20, a refrigerant cooling device 30, a pressure sensor 112, a temperature sensor 121, and a control device 100. The first flow path F1 is connected to the load device 3 to form a circulation flow path through which the refrigerant circulates. The compressor 10, the condenser 20, and the refrigerant cooling device 30 are arranged in order in the first flow path F1. The pressure sensor 112 and the temperature sensor 121 detect the pressure and temperature of the refrigerant sent from the refrigerant cooling device 30 to the first expansion device 50, respectively. The control device 100 changes the cooling performance of the refrigerant cooling device 30 based on the outputs of the pressure sensor 112 and the temperature sensor 121.
　このように圧力センサ１１２および温度センサ１２１の出力に基づいて、冷媒冷却装置３０を制御するので、第１膨張装置５０に送られる冷媒が臨界点付近の状態となることを正確に回避することができる。 Since the refrigerant cooling device 30 is controlled based on the outputs of the pressure sensor 112 and the temperature sensor 121 in this way, it is possible to accurately prevent the refrigerant sent to the first expansion device 50 from being in a state near the critical point. can.
　好ましくは、図４に示すように、制御装置１００は、冷媒の状態が予め定められた冷却範囲Ａに入ったことを圧力センサ１１２および温度センサ１２１の出力が示す場合には、冷媒冷却装置３０の冷却性能を増加させる。 Preferably, as shown in FIG. 4, the control device 100 controls the refrigerant cooling device 30 when the outputs of the pressure sensor 112 and the temperature sensor 121 indicate that the state of the refrigerant has entered the predetermined cooling range A. Increases the cooling performance of.
　好ましくは、図５に示すように、制御装置１００は、冷媒の状態が予め定められた冷却範囲Ａに入った場合に、ステップＳ４において一定時間（たとえば５分）冷媒冷却装置３０によって冷媒を冷却する。 Preferably, as shown in FIG. 5, the control device 100 cools the refrigerant by the refrigerant cooling device 30 for a certain period of time (for example, 5 minutes) in step S4 when the state of the refrigerant enters the predetermined cooling range A. do.
　より好ましくは、図２、図３に示す冷却範囲Ａ（Ａ１～Ａ７）は、冷媒の温度変化０．５ケルビンに対して冷媒の密度が１０％以上変化する温度および圧力範囲である。 More preferably, the cooling range A (A1 to A7) shown in FIGS. 2 and 3 is a temperature and pressure range in which the density of the refrigerant changes by 10% or more with respect to a temperature change of 0.5 Kelvin of the refrigerant.
　なお、冷却範囲Ａ（Ａ１～Ａ７）は、冷媒の温度変化０．５ケルビンに対して蒸発器における冷媒の蒸発温度が１ケルビン以上変化する温度および圧力範囲であってもよい。 The cooling range A (A1 to A7) may be a temperature and pressure range in which the evaporation temperature of the refrigerant in the evaporator changes by 1 Kelvin or more with respect to the temperature change of 0.5 Kelvin of the refrigerant.
　好ましくは、図１に示す冷熱源ユニット２は、冷媒が循環する方向において、蒸発器６０よりも下流の第１流路Ｆ１の分岐点ＢＰから分岐する第２流路Ｆ２をさらに備える。第２流路Ｆ２は、蒸発器６０を通過した冷媒が冷媒冷却装置３０を経由して圧縮機１０に戻るように構成される。冷媒冷却装置３０は、分岐点ＢＰから第２流路Ｆ２に冷媒を流すか否かを切替える切替部７４と、熱交換器７２とを備える。熱交換器７２は、第１流路Ｆ１の一部である第１通路Ｈ１と第２流路Ｆ２の一部である第２通路Ｈ２とを有する。熱交換器７２は、第１通路Ｈ１を流れる冷媒と第２通路Ｈ２を流れる冷媒との間で熱交換を行なうように構成される。制御装置１００は、圧力センサ１１２および温度センサ１２１の出力に応じて切替部７４の冷媒の流れを制御する。 Preferably, the cold heat source unit 2 shown in FIG. 1 further includes a second flow path F2 that branches from the branch point BP of the first flow path F1 downstream of the evaporator 60 in the direction in which the refrigerant circulates. The second flow path F2 is configured such that the refrigerant that has passed through the evaporator 60 returns to the compressor 10 via the refrigerant cooling device 30. The refrigerant cooling device 30 includes a switching unit 74 for switching whether or not to flow the refrigerant from the branch point BP to the second flow path F2, and a heat exchanger 72. The heat exchanger 72 has a first passage H1 that is a part of the first flow path F1 and a second passage H2 that is a part of the second flow path F2. The heat exchanger 72 is configured to exchange heat between the refrigerant flowing through the first passage H1 and the refrigerant flowing through the second passage H2. The control device 100 controls the flow of the refrigerant in the switching unit 74 according to the outputs of the pressure sensor 112 and the temperature sensor 121.
　好ましくは、図６に示す冷熱源ユニット２Ａおよび図７に示す冷熱源ユニット２Ｂは、冷媒が循環する方向において、冷媒冷却装置３０Ａよりも下流の第１流路Ｆ１の分岐点ＢＰＡから分岐し、凝縮器２０および冷媒冷却装置３０Ａを通過した冷媒を圧縮機１０に戻すように構成された第２流路Ｆ２ＡまたはＦ２Ｂをさらに備える。冷媒冷却装置３０Ａは、分岐点ＢＰＡから順に第２流路Ｆ２ＡまたはＦ２Ｂに配置される第２膨張装置７１および熱交換器７２を含む。熱交換器７２は、第１流路Ｆ１の一部である第１通路Ｈ１と、第２流路Ｆ２ＡまたはＦ２Ｂの一部である第２通路Ｈ２とを有する。熱交換器７２は、第１通路Ｈ１を流れる冷媒と第２通路Ｈ２を流れる冷媒との間で熱交換を行なうように構成される。制御装置１００Ａは、圧力センサ１１２および温度センサ１２１の出力に応じて第２膨張装置７１の冷媒流通量を制御する。 Preferably, the cold heat source unit 2A shown in FIG. 6 and the cold heat source unit 2B shown in FIG. 7 branch from the branch point BPA of the first flow path F1 downstream of the refrigerant cooling device 30A in the direction in which the refrigerant circulates. A second flow path F2A or F2B configured to return the refrigerant that has passed through the condenser 20 and the refrigerant cooling device 30A to the compressor 10 is further provided. The refrigerant cooling device 30A includes a second expansion device 71 and a heat exchanger 72 arranged in the second flow path F2A or F2B in order from the branch point BPA. The heat exchanger 72 has a first passage H1 that is a part of the first flow path F1 and a second passage H2 that is a part of the second flow path F2A or F2B. The heat exchanger 72 is configured to exchange heat between the refrigerant flowing through the first passage H1 and the refrigerant flowing through the second passage H2. The control device 100A controls the amount of refrigerant flowing through the second expansion device 71 according to the outputs of the pressure sensor 112 and the temperature sensor 121.
　好ましくは、図８に示す冷媒冷却装置３０Ｃは、冷媒と熱媒体とを熱交換させる熱交換器２０２と、熱交換器２０２に熱媒体を送る供給装置２０４とを備える。たとえば、熱媒体が外気である場合、供給装置２０４はファンである。なお、熱媒体が水またはブラインである場合、供給装置はポンプまたは弁である。制御装置１００Ｃは、圧力センサ１１２および温度センサ１２１の出力に応じて供給装置２０４によって熱交換器２０２に供給される熱媒体の量を制御する。 Preferably, the refrigerant cooling device 30C shown in FIG. 8 includes a heat exchanger 202 for heat exchange between the refrigerant and the heat medium, and a supply device 204 for sending the heat medium to the heat exchanger 202. For example, if the heat medium is outside air, the supply device 204 is a fan. If the heat medium is water or brine, the supply device is a pump or valve. The control device 100C controls the amount of heat medium supplied to the heat exchanger 202 by the supply device 204 according to the outputs of the pressure sensor 112 and the temperature sensor 121.
　好ましくは、冷媒は、二酸化炭素、または二酸化炭素を含む混合冷媒である。
　本開示は、他の局面では、上記冷熱源ユニット２，２Ａ～２Ｃのいずれかと、負荷装置３とを備える冷凍サイクル装置１，１Ａ～１Ｃに関する。 Preferably, the refrigerant is carbon dioxide or a mixed refrigerant containing carbon dioxide.
The present disclosure relates to refrigerating cycle devices 1, 1A to 1C including any of the above-mentioned cold heat source units 2, 2A to 2C and a load device 3 in another aspect.
　以上、冷凍サイクル装置１を備える冷凍機を例示して本実施の形態を説明したが、冷凍サイクル装置１、１Ａ～１Ｃは、空気調和機などに利用されても良い。 Although the present embodiment has been described above by exemplifying a refrigerator equipped with the refrigeration cycle device 1, the refrigeration cycle devices 1, 1A to 1C may be used for an air conditioner or the like.
　今回開示された実施の形態は、すべての点で例示であって制限的なものではないと考えられるべきである。本開示の範囲は、上記した実施の形態の説明ではなくて請求の範囲によって示され、請求の範囲と均等の意味および範囲内でのすべての変更が含まれることが意図される。 The embodiments disclosed this time should be considered to be exemplary in all respects and not restrictive. The scope of the present disclosure is set forth by the scope of claims rather than the description of the embodiments described above, and is intended to include all modifications within the meaning and scope of the claims.
　１，１Ａ，１Ｂ，１Ｃ　冷凍サイクル装置、２，２Ａ，２Ｂ，２Ｃ　冷熱源ユニット、３　負荷装置、１０　圧縮機、２０　凝縮器、２２　ファン、３０，３０Ａ，３０Ｃ　冷媒冷却装置、５０　第１膨張装置、６０　蒸発器、７０，７６，７７　開閉弁、７１　第２膨張装置、７２，２０２　熱交換器、７４　切替部、８０，８１，８２，８３，８４，８５，８８，８９，９１，９２，９４，９６　配管、１００，１００Ａ，１００Ｃ　制御装置、１０２　ＣＰＵ、１０４　メモリ、１１０，１１１，１１２　圧力センサ、１２０，１２１　温度センサ、２０４　供給装置、ＢＰ，ＢＰＡ　分岐点、Ｆ１　第１流路、Ｆ２，Ｆ２Ａ，Ｆ２Ｂ　第２流路、Ｇ１　吸入ポート、Ｇ２　吐出ポート、Ｇ３　中間圧ポート、Ｈ１　第１通路、Ｈ２　第２通路。 1,1A, 1B, 1C refrigeration cycle device, 2,2A, 2B, 2C cold heat source unit, 3 load device, 10 compressor, 20 condenser, 22 fan, 30, 30A, 30C refrigerant cooling device, 50 first expansion Equipment, 60 evaporator, 70,76,77 on-off valve, 71 second expansion device, 72,202 heat exchanger, 74 switching unit, 80,81,82,83,84,85,88,89,91,92 , 94,96 piping, 100,100A, 100C control device, 102 CPU, 104 memory, 110,111,112 pressure sensor, 120,121 temperature sensor, 204 supply device, BP, BPA branch point, F1 first flow path, F2, F2A, F2B second flow path, G1 suction port, G2 discharge port, G3 intermediate pressure port, H1 first passage, H2 second passage.

Claims (10)

  1. 　第１膨張装置および蒸発器を含む負荷装置に接続されるように構成された冷凍サイクル装置の冷熱源ユニットであって、
    　前記負荷装置に接続されることによって、冷媒が循環する循環流路を形成する第１流路と、
    　前記第１流路に順に配置される、圧縮機、凝縮器および冷媒冷却装置と、
    　前記冷媒冷却装置から前記第１膨張装置に送られる冷媒の圧力および温度をそれぞれ検出する圧力センサおよび温度センサと、
    　前記圧力センサおよび前記温度センサの出力に基づいて、前記冷媒冷却装置の冷却性能を変化させる制御装置とを備える、冷熱源ユニット。     A cold heat source unit of a refrigeration cycle device configured to be connected to a load device including a first inflator and an evaporator.
    A first flow path that forms a circulation flow path through which the refrigerant circulates by being connected to the load device, and
    A compressor, a condenser, and a refrigerant cooling device, which are sequentially arranged in the first flow path,
    A pressure sensor and a temperature sensor that detect the pressure and temperature of the refrigerant sent from the refrigerant cooling device to the first expansion device, respectively.
    A cold heat source unit including a control device that changes the cooling performance of the refrigerant cooling device based on the output of the pressure sensor and the temperature sensor.
  2. 　前記制御装置は、冷媒の状態が予め定められた冷却範囲に入ったことを前記圧力センサおよび前記温度センサの出力が示す場合には、前記冷媒冷却装置の冷却性能を増加させる、請求項１に記載の冷熱源ユニット。 The control device increases the cooling performance of the refrigerant cooling device when the outputs of the pressure sensor and the temperature sensor indicate that the state of the refrigerant has entered a predetermined cooling range, according to claim 1. The cooling heat source unit described.
  3. 　前記制御装置は、冷媒の状態が予め定められた冷却範囲に入った場合に、一定時間前記冷媒冷却装置によって冷媒を冷却する、請求項１に記載の冷熱源ユニット。 The cooling heat source unit according to claim 1, wherein the control device cools the refrigerant by the refrigerant cooling device for a certain period of time when the state of the refrigerant enters a predetermined cooling range.
  4. 　前記冷却範囲は、冷媒の温度変化０．５ケルビンに対して冷媒の密度が１０％以上変化する温度および圧力範囲である、請求項２または３に記載の冷熱源ユニット。 The cold heat source unit according to claim 2 or 3, wherein the cooling range is a temperature and pressure range in which the density of the refrigerant changes by 10% or more with respect to a temperature change of 0.5 Kelvin of the refrigerant.
  5. 　前記冷却範囲は、冷媒の温度変化０．５ケルビンに対して前記蒸発器における冷媒の蒸発温度が１ケルビン以上変化する温度および圧力範囲である、請求項２または３に記載の冷熱源ユニット。 The cold heat source unit according to claim 2 or 3, wherein the cooling range is a temperature and pressure range in which the evaporation temperature of the refrigerant in the evaporator changes by 1 Kelvin or more with respect to a temperature change of 0.5 Kelvin of the refrigerant.
  6. 　冷媒が循環する方向において、前記蒸発器よりも下流の前記第１流路の分岐点から分岐する第２流路をさらに備え、前記第２流路は、前記蒸発器を通過した冷媒が前記冷媒冷却装置を経由して前記圧縮機に戻るように構成され、
    　前記冷媒冷却装置は、
    　前記分岐点から前記第２流路に冷媒を流すか否かを切替える切替部と、
    　前記第１流路の一部である第１通路と前記第２流路の一部である第２通路とを有し、前記第１通路を流れる冷媒と前記第２通路を流れる冷媒との間で熱交換を行なうように構成された熱交換器とを備え、
    　前記制御装置は、前記圧力センサおよび前記温度センサの出力に応じて前記切替部の冷媒の流れを制御する、請求項１に記載の冷熱源ユニット。     In the direction in which the refrigerant circulates, a second flow path that branches from the branch point of the first flow path downstream of the evaporator is further provided, and in the second flow path, the refrigerant that has passed through the evaporator is the refrigerant. It is configured to return to the compressor via a cooling device.
    The refrigerant cooling device is
    A switching unit that switches whether or not to flow the refrigerant from the branch point to the second flow path,
    It has a first passage that is a part of the first flow path and a second passage that is a part of the second flow path, and is between a refrigerant flowing through the first passage and a refrigerant flowing through the second passage. Equipped with a heat exchanger configured to exchange heat with
    The cold heat source unit according to claim 1, wherein the control device controls the flow of the refrigerant in the switching unit according to the outputs of the pressure sensor and the temperature sensor.
  7. 　冷媒が循環する方向において、前記冷媒冷却装置よりも下流の前記第１流路の分岐点から分岐し、前記凝縮器および前記冷媒冷却装置を通過した冷媒を前記圧縮機に戻すように構成された第２流路をさらに備え、
    　前記冷媒冷却装置は、前記分岐点から順に前記第２流路に配置される第２膨張装置および熱交換器を含み、
    　前記熱交換器は、前記第１流路の一部である第１通路と、前記第２流路の一部である第２通路とを有し、前記熱交換器は、前記第１通路を流れる冷媒と前記第２通路を流れる冷媒との間で熱交換を行なうように構成され、
    　前記制御装置は、前記圧力センサおよび前記温度センサの出力に応じて前記第２膨張装置の冷媒流通量を制御する、請求項１に記載の冷熱源ユニット。     In the direction in which the refrigerant circulates, it is configured to branch from the branch point of the first flow path downstream of the refrigerant cooling device and return the refrigerant passing through the condenser and the refrigerant cooling device to the compressor. Further equipped with a second flow path,
    The refrigerant cooling device includes a second expansion device and a heat exchanger arranged in the second flow path in order from the branch point.
    The heat exchanger has a first passage that is a part of the first flow path and a second passage that is a part of the second flow path, and the heat exchanger has the first passage. It is configured to exchange heat between the flowing refrigerant and the refrigerant flowing in the second passage.
    The cold heat source unit according to claim 1, wherein the control device controls the amount of refrigerant flowing through the second expansion device according to the outputs of the pressure sensor and the temperature sensor.
  8. 　前記冷媒冷却装置は、
    　前記冷媒と熱媒体とを熱交換させる熱交換器と、
    　前記熱交換器に前記熱媒体を送る供給装置とを備え、
    　前記制御装置は、前記圧力センサおよび前記温度センサの出力に応じて前記供給装置によって前記熱交換器に供給される熱媒体の量を制御する、請求項１に記載の冷熱源ユニット。     The refrigerant cooling device is
    A heat exchanger that exchanges heat between the refrigerant and the heat medium,
    The heat exchanger is provided with a supply device for sending the heat medium.
    The cold heat source unit according to claim 1, wherein the control device controls the amount of a heat medium supplied to the heat exchanger by the supply device according to the output of the pressure sensor and the temperature sensor.
  9. 　前記冷媒は、二酸化炭素または二酸化炭素を含む混合冷媒である、請求項１～７のいずれか１項に記載の冷熱源ユニット。 The cold heat source unit according to any one of claims 1 to 7, wherein the refrigerant is carbon dioxide or a mixed refrigerant containing carbon dioxide.
  10. 　請求項１～９のいずれか１項に記載の冷熱源ユニットと、前記負荷装置とを備える冷凍サイクル装置。 A refrigeration cycle device including the cold heat source unit according to any one of claims 1 to 9 and the load device.
PCT/JP2020/027519 2020-07-15 2020-07-15 Cold heat source unit and refrigeration cycle device WO2022013975A1 (en)

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