[go: up one dir, main page]

WO2025046855A1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

Info

Publication number
WO2025046855A1
WO2025046855A1 PCT/JP2023/031908 JP2023031908W WO2025046855A1 WO 2025046855 A1 WO2025046855 A1 WO 2025046855A1 JP 2023031908 W JP2023031908 W JP 2023031908W WO 2025046855 A1 WO2025046855 A1 WO 2025046855A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
heat source
source side
operation mode
Prior art date
Application number
PCT/JP2023/031908
Other languages
English (en)
Japanese (ja)
Inventor
聖也 稲田
拓也 松田
龍一 永田
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2023/031908 priority Critical patent/WO2025046855A1/fr
Publication of WO2025046855A1 publication Critical patent/WO2025046855A1/fr

Links

Images

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
    • F25B1/00—Compression machines, plants or systems with non-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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • 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

Definitions

  • This disclosure relates to a refrigeration cycle device.
  • Patent Document 1 discloses a forced convection heat exchanger for refrigeration and air conditioning in which the cross-sectional shape of the refrigerant pipes is elliptical or flattened in order to reduce the amount of refrigerant charged.
  • the main objective of this disclosure is to provide a refrigeration cycle device that can simultaneously reduce the amount of refrigerant charged and the amount of refrigerant leakage.
  • a refrigeration cycle device is a refrigeration cycle device including a refrigerant circuit in which a refrigerant circulates.
  • the refrigerant circuit includes a heat source side refrigerant flow path including a compressor and a heat source side heat exchanger, a utilization side refrigerant flow path including a utilization side heat exchanger, and a first extension pipe and a second extension pipe connecting between the heat source side refrigerant flow path and the utilization side refrigerant flow path.
  • the refrigeration cycle device further includes a control device that switches between a cooling operation mode and a recovery operation mode in which the refrigerant is recovered to the heat source side refrigerant flow path.
  • the heat source side heat exchanger acts as a condenser
  • the utilization side heat exchanger acts as an evaporator
  • the refrigerant flows through the compressor, the heat source side heat exchanger, the first extension pipe, the utilization side heat exchanger, and the second extension pipe in this order.
  • the heat source side refrigerant flow path includes a first control valve disposed between the heat source side heat exchanger and the first extension pipe. The first control valve is controlled to open in the cooling operation mode and to close in the recovery operation mode.
  • the total internal volume of the utilization side heat exchanger is Vin (unit: m3 )
  • the maximum inner diameter of the first extension pipe is dL (unit: m)
  • the maximum inner diameter of the second extension pipe is dG (unit: m)
  • the maximum pipe length of each of the first extension pipe and the second extension pipe is L (unit: m)
  • the saturated liquid density of the refrigerant at the same temperature as the upper limit value Tmax of the ambient temperature of the refrigerant circuit at which operation of the refrigeration cycle device is guaranteed is ⁇ L (unit: kg/ m3 )
  • the saturated gas density of the refrigerant at the same temperature as the upper limit value Tmax is ⁇ G (unit: kg/ m3 )
  • the total internal volume Vout (unit: m3 ) of the heat source side heat exchanger is expressed by the following relational equation (1).
  • a refrigeration cycle apparatus is a refrigeration cycle apparatus including a refrigerant circuit through which a refrigerant circulates.
  • the refrigerant circuit includes a heat source side refrigerant flow path including a compressor and a heat source side heat exchanger, a utilization side refrigerant flow path including a utilization side heat exchanger, and a first extension pipe and a second extension pipe connecting the heat source side refrigerant flow path and the utilization side refrigerant flow path.
  • the refrigeration cycle apparatus further includes a control device that switches between a cooling operation mode and a recovery operation mode in which the refrigerant is recovered to the heat source side refrigerant flow path.
  • the heat source side heat exchanger acts as a condenser and the utilization side heat exchanger acts as an evaporator, and the refrigerant flows through the compressor, the heat source side heat exchanger, the first extension pipe, the utilization side heat exchanger, and the second extension pipe in this order.
  • the heat source side refrigerant flow path includes a first control valve arranged between the heat source side heat exchanger and the first extension pipe, a first branch path branched from the first refrigerant flow path connecting the heat source side heat exchanger and the first control valve, at least one on-off valve for opening and closing the first branch path, and a container connected to the first refrigerant flow path via the first branch path and the at least one on-off valve and capable of recovering refrigerant.
  • the first control valve is controlled to open in the cooling operation mode and to close in the recovery operation mode.
  • the at least one on-off valve is controlled to close in the cooling operation mode and to open in the recovery operation mode.
  • a refrigeration cycle apparatus is a refrigeration cycle apparatus including a refrigerant circuit through which a refrigerant circulates.
  • the refrigerant circuit includes a heat source side refrigerant flow path including a compressor and a heat source side heat exchanger, a utilization side refrigerant flow path including a utilization side heat exchanger, and a first extension pipe and a second extension pipe connecting the heat source side refrigerant flow path and the utilization side refrigerant flow path.
  • the refrigeration cycle apparatus further includes a control device that switches between a heating operation mode and a recovery operation mode in which the refrigerant is recovered to the heat source side refrigerant flow path.
  • the utilization side heat exchanger acts as a condenser and the heat source side heat exchanger acts as an evaporator, and the refrigerant flows through the compressor, the second extension pipe, the utilization side heat exchanger, the first extension pipe, and the heat source side heat exchanger in this order.
  • the heat source side refrigerant flow path includes a second control valve arranged between the second extension pipe and the suction port of the compressor, a second branch path branched from the second refrigerant flow path connecting between the second control valve and the suction port, at least one on-off valve for opening and closing the second branch path, and a container connected to the second refrigerant flow path via the second branch path and the at least one on-off valve and capable of recovering refrigerant.
  • the second control valve is controlled to open in the heating operation mode and to close in the recovery operation mode.
  • the at least one on-off valve is controlled to close in the heating operation mode and to open in the recovery operation mode.
  • This disclosure provides a refrigeration cycle device that can simultaneously reduce the amount of refrigerant filled and the amount of refrigerant leaking.
  • FIG. 1 is a diagram for explaining a refrigeration cycle device according to a first embodiment.
  • FIG. 11 is a diagram for explaining a modified example of the refrigeration cycle device according to the first embodiment.
  • FIG. 11 is a diagram for explaining a refrigeration cycle device according to a second embodiment.
  • FIG. 11 is a diagram for explaining a first modified example of the refrigeration cycle device according to the second embodiment.
  • FIG. 11 is a diagram for explaining a second modified example of the refrigeration cycle device according to the second embodiment.
  • FIG. 11 is a diagram for explaining a refrigeration cycle device according to a third embodiment.
  • FIG. 11 is a diagram for explaining a first modified example of the refrigeration cycle device according to the third embodiment.
  • FIG. 11 is a diagram for explaining a second modified example of the refrigeration cycle device according to the third embodiment.
  • a refrigeration cycle apparatus 100 includes a refrigerant circuit 110 through which a refrigerant circulates, and a control device 200 .
  • the refrigerant circuit 110 includes a heat source side refrigerant flow path 111, a utilization side refrigerant flow path 112, and a first extension pipe 113 and a second extension pipe 114 that connect between the heat source side refrigerant flow path 111 and the utilization side refrigerant flow path 112.
  • the refrigerant is a refrigerant with a lower GWP than R32, for example a mixed refrigerant containing R32 and R1234yf, a mixed refrigerant containing R32 and R1123, a mixed refrigerant containing R32 and R1132(E), a mixed refrigerant containing R290 and R1123, a mixed refrigerant containing R290 and R1132(E), or R290.
  • the heat source side refrigerant flow path 111 is housed in the heat source side unit 121.
  • the heat source side refrigerant flow path 111 includes a compressor 1, a heat source side heat exchanger 2, a flow path switching device 4, an expansion device 5, a first shutoff valve 6 (first control valve), and a second shutoff valve 7.
  • the user-side refrigerant flow path 112 is housed within the user-side unit 122.
  • the user-side refrigerant flow path 112 includes the user-side heat exchanger 3.
  • Compressor 1 compresses the refrigerant and is, for example, a rotary compressor, scroll compressor, screw compressor, or reciprocating compressor.
  • the heat source side heat exchanger 2 is provided so that the refrigerant circulating through the refrigerant circuit exchanges heat with the air outside the room.
  • the refrigeration cycle device 100 is equipped with a heat source side fan (not shown) for supplying the air outside the room to the heat source side heat exchanger 2.
  • the utilization side heat exchanger 3 is arranged so that the refrigerant circulating in the refrigerant circuit exchanges heat with the air in the living room.
  • the refrigeration cycle device 100 is equipped with a utilization side fan (not shown) for supplying the air in the living room to the utilization side heat exchanger 3.
  • Each of the heat source side heat exchanger 2 and the utilization side heat exchanger 3 has, as a flow path through which the refrigerant flows, for example, a pair of headers and a number of heat transfer tubes connected in parallel to the pair of headers.
  • the total volume of the flow paths through which the refrigerant flows in the heat source side heat exchanger 2 or the utilization side heat exchanger 3 is referred to as the total internal volume of the heat source side heat exchanger 2 or the total internal volume of the utilization side heat exchanger 3.
  • the flow path switching device 4 switches between a first state in which the discharge port of the compressor 1 is connected to the heat source side heat exchanger 2 and the suction port of the compressor 1 is connected to the utilization side heat exchanger 3, and a second state in which the discharge port of the compressor 1 is connected to the utilization side heat exchanger 3 and the suction port of the compressor 1 is connected to the heat source side heat exchanger 2.
  • the above switching by the flow path switching device 4 is controlled by the control device 200, which will be described later.
  • the flow path switching device 4 is, for example, a four-way valve or a six-way valve.
  • the expansion device 5 expands the refrigerant to reduce its pressure.
  • the expansion device 5 is, for example, an electric expansion valve.
  • the expansion device 5 is not limited to an electric expansion valve, and may be a mechanical expansion valve that uses a diaphragm in the pressure receiving section, or a capillary tube, etc.
  • the first shutoff valve 6 is disposed between the heat source side heat exchanger 2 and the first extension pipe 113.
  • the first shutoff valve 6 is disposed, for example, between the expansion device 5 and the first extension pipe 113.
  • the first shutoff valve 6 is disposed near the connection between the heat source side refrigerant flow path 111 and the first extension pipe 113.
  • the second shutoff valve 7 is disposed between the second extension pipe 114 and the compressor 1.
  • the second shutoff valve 7 is disposed, for example, between the second extension pipe 114 and the flow path switching device 4.
  • the second shutoff valve 7 is disposed near the connection between the heat source side refrigerant flow path 111 and the second extension pipe 114.
  • Each of the first shutoff valve 6 and the second shutoff valve 7 is a control valve whose opening is controlled by the control device 200 described later.
  • the first shutoff valve 6 is fully open in a normal operation mode described later, and is fully closed in a recovery operation mode described later.
  • the second shutoff valve 7 is fully open in the normal operation mode described later, and is fully closed after the end of the recovery operation mode described later.
  • Each of the first shutoff valve 6 and the second shutoff valve 7 is, for example, an electrically operated shutoff valve. Note that the method of shutoff operation of each of the first shutoff valve 6 and the second shutoff valve 7 is not limited to being electrically operated.
  • Each of the first shutoff valve 6 and the second shutoff valve 7 may be capable of shutting off only refrigerant flowing in one direction, or may be capable of shutting off refrigerant flowing in both directions.
  • each of the first shutoff valve 6 and the second shutoff valve 7 has the ability to shut off only refrigerant flowing in one direction
  • each of the first shutoff valve 6 and the second shutoff valve 7 is installed in a direction that prevents refrigerant from moving from the heat source side refrigerant flow path 111 to the user side refrigerant flow path 112.
  • the first extension pipe 113 and the second extension pipe 114 are each provided between the heat source unit 121 and the user side unit 122.
  • the first extension pipe 113 connects one end of the heat source side refrigerant flow path 111 to one end of the user side refrigerant flow path 112.
  • the first extension pipe 113 is disposed in the refrigerant circuit between an expansion device 5 (described later) included in the heat source side refrigerant flow path 111 and the user side heat exchanger 3.
  • the second extension pipe 114 connects the other end of the heat source side refrigerant flow path 111 to the other end of the user side refrigerant flow path 112.
  • the second extension pipe 114 is disposed in the refrigerant circuit between the user side heat exchanger 3 and the compressor 1.
  • the piping length of each of the first extension pipe 113 and the second extension pipe 114 may be adjustable in the specifications of the refrigeration cycle apparatus 100 (for example, specifications described in the user guide of the refrigeration cycle apparatus 100, etc.). As with known refrigeration cycle apparatuses in which the piping length of the extension pipes is adjustable, if the piping length of each of the first extension pipe 113 and the second extension pipe 114 is adjustable, the maximum piping length of each of the first extension pipe 113 and the second extension pipe 114 is set in the above specifications. Note that the piping length of each of the first extension pipe 113 and the second extension pipe 114 may not be adjustable in the specifications of the refrigeration cycle apparatus 100.
  • the refrigerant circuit 110 does not include an accumulator or a receiver.
  • the volume of the heat source side heat exchanger 2 is, for example, the largest among the components of the heat source side refrigerant flow path 111.
  • the control device 200 switches the operation mode of the refrigeration cycle device 100.
  • the control device 200 switches between a normal operation mode and a recovery operation mode.
  • the control device 200 can switch between, for example, a cooling operation mode and a heating operation mode.
  • the cooling operation mode, heating operation mode, and recovery operation mode will be described later.
  • the control device 200 includes a processor 201 and a memory 202.
  • the processor 201 is a computing entity that executes various programs.
  • the memory 202 provides a storage area for storing program codes or various variables when the processor 201 executes various programs.
  • the control device 200 is connected to each component of the refrigeration cycle device 100 and various sensors that detect the state of each component, and controls each component based on the operating conditions set by the user via a remote control and the signals output from each sensor.
  • the control device 200 controls, for example, the frequency of the compressor 1, the rotation speed of the fans near the heat source side heat exchanger 2 and the user side heat exchanger 3, the switching of the flow path switching device 4, the opening and closing of the first shutoff valve 6 and the second shutoff valve 7, and the opening degree of the expansion device 5.
  • the refrigeration cycle device 100 further includes at least one sensor 300 for detecting leakage of refrigerant from the user-side refrigerant flow path 112 in the room.
  • the at least one sensor 300 outputs a signal to the control device 200.
  • the control device 200 detects leakage of refrigerant based on the signal output from the sensor 300.
  • At least one sensor 300 is housed, for example, in the user unit 122. At least one sensor 300 is, for example, at least one of a gas detection sensor that detects gas contained in the refrigerant and a pressure sensor that detects pressure changes in the user-side refrigerant flow path 112.
  • the refrigeration cycle device 100 may be equipped with multiple sensors 300 of the same or different types.
  • the refrigeration cycle apparatus 100 has, as its operation modes, a cooling operation mode, a heating operation mode, and a recovery operation mode.
  • the first shutoff valve 6 and the second shutoff valve 7 are opened, and the flow path switching device 4 is in the first state.
  • the heat source side heat exchanger 2 acts as a condenser
  • the utilization side heat exchanger 3 acts as an evaporator.
  • the solid arrows in FIG. 1 indicate the flow direction of the refrigerant in the cooling operation mode.
  • the refrigerant flows through the compressor 1, the heat source side heat exchanger 2, the expansion device 5, the first shutoff valve 6, the first extension pipe 113, the user side heat exchanger 3, the second extension pipe 114, and the second shutoff valve 7 in that order.
  • the high-pressure gas refrigerant discharged from the compressor 1 flows into the heat source side heat exchanger 2 through the flow path switching device 4, where it exchanges heat with the air outside the room and condenses to become a high-pressure liquid refrigerant.
  • the liquid refrigerant condensed in the heat source side heat exchanger 2 is reduced in pressure by passing through the expansion device 5, becoming a low-pressure two-phase refrigerant.
  • the low-pressure two-phase refrigerant flows into the user side heat exchanger 3 through the first extension pipe 113, where it exchanges heat with the air inside the room and evaporates to become a low-pressure gas refrigerant.
  • the low-pressure gas refrigerant is sucked into the compressor 1 through the second extension pipe 114 and the flow path switching device 4.
  • the first shutoff valve 6 and the second shutoff valve 7 are opened, and the flow path switching device 4 is in the second state.
  • the user side heat exchanger 3 acts as a condenser
  • the heat source side heat exchanger 2 acts as an evaporator.
  • the dashed arrows in Figure 1 indicate the flow direction of the refrigerant in the heating operation mode.
  • the refrigerant flows through the compressor 1, the second shutoff valve 7, the second extension pipe 114, the user side heat exchanger 3, the first extension pipe 113, the first shutoff valve 6, the expansion device 5, and the heat source side heat exchanger 2 in that order.
  • the high-pressure gas refrigerant discharged from the compressor 1 flows into the user side heat exchanger 3 through the flow path switching device 4 and the second extension pipe 114, where it exchanges heat with the air in the room and condenses to become a high-pressure liquid refrigerant.
  • the liquid refrigerant condensed in the user side heat exchanger 3 flows into the expansion device 5 through the first extension pipe 113, where it is reduced in pressure by passing through the expansion device 5, becoming a low-pressure two-phase refrigerant.
  • the low-pressure two-phase refrigerant flows into the heat source side heat exchanger 2, where it exchanges heat with the air outside the room in the heat source side heat exchanger 2, evaporating to become a low-pressure gas refrigerant.
  • the low-pressure gas refrigerant is sucked into the compressor 1 through the flow path switching device 4.
  • the first shutoff valve 6 is closed, the second shutoff valve 7 is opened, and the flow path switching device 4 is in the first state.
  • the heat source side heat exchanger 2 acts as a container for recovering the refrigerant.
  • the refrigerant is recovered in a portion of the heat source side refrigerant flow path 111 located between the discharge port of the compressor 1 and the first shutoff valve 6.
  • the heat source side fan for blowing air to the heat source side heat exchanger 2 described above continues to be driven.
  • the control device 200 detects a refrigerant leak, only the first shutoff valve 6 is closed.
  • the compressor 1 is kept operating at a predetermined frequency, the flow path switching device 4 is maintained in the first state, and the second shutoff valve 7 is maintained in an open state.
  • control device 200 When the control device 200 detects a refrigerant leak while the refrigeration cycle device 100 is operating in the heating operation mode, the control device 200 controls each component of the refrigeration cycle device 100 to start the recovery operation mode.
  • the flow path switching device 4 is switched to the first state.
  • the first shutoff valve 6 is closed.
  • the compressor 1 is placed in a state in which it is operating at a predetermined frequency.
  • the second shutoff valve 7 is maintained in an open state.
  • the recovery operation mode is performed until the pressure in the user-side refrigerant flow path 112 falls below atmospheric pressure or a predetermined time has elapsed since the start of the recovery operation mode. After the recovery operation mode ends, the compressor 1 stops and the second shutoff valve 7 is closed. At the end of the recovery operation mode, the refrigerant is recovered in the portion of the heat source-side refrigerant flow path 111 that is located between the discharge port of the compressor 1 and the first shutoff valve 6. After the recovery operation mode ends and the replacement work of the piping or heat transfer tube where the refrigerant leaked has been completed, the compressor 1 is driven again and the first shutoff valve 6 and the second shutoff valve 7 are opened, allowing the refrigeration cycle device 100 to operate normally again.
  • the total internal volume of the heat source side heat exchanger 2 is set to be equal to or greater than the volume of the refrigerant in the refrigerant circuit 110 at the end of the recovery operation mode.
  • the heat source side heat exchanger 2 is provided so that the total internal volume V out (unit: m 3 ) satisfies the following relational expression (1).
  • V in (unit: m 3 ) is the total internal volume of the user side heat exchanger 3
  • d L (unit: m) is the maximum inner diameter of the first extension pipe 113
  • d G (unit: m) is the maximum inner diameter of the second extension pipe 114
  • L (unit: m) is the maximum pipe length of each of the first extension pipe 113 and the second extension pipe 114
  • ⁇ L (unit: kg/m 3 ) is the saturated liquid density of the refrigerant at the same temperature as the upper limit value T max of the ambient temperature of the refrigerant circuit at which operation of the refrigeration cycle device is guaranteed
  • ⁇ G (unit: kg/m 3 ) is the saturated gas density of the refrigerant at the same temperature as the upper limit value T max .
  • the maximum length L of each of the first extension pipe 113 and the second extension pipe 114 means the maximum length of each of the first extension pipe 113 and the second extension pipe 114 specified in the above specifications if the length of each of the first extension pipe 113 and the second extension pipe 114 is adjustable.
  • the maximum length L of each of the first extension pipe 113 and the second extension pipe 114 means the maximum length of each of the first extension pipe 113 and the second extension pipe 114 specified in the above specifications if the length of each of the first extension pipe 113 and the second extension pipe 114 is not adjustable.
  • the above relational expression (1) is derived as follows. First, the amount of refrigerant charged in the refrigerant circuit 110 of the refrigeration cycle apparatus 100 increases or decreases depending on the piping length of each of the first extension pipe 113 and the second extension pipe 114, and is maximum when the piping length of each of the first extension pipe 113 and the second extension pipe 114 is maximum value L.
  • the refrigerant amount Mref unit: kg
  • the refrigerant amount Mref unit: kg
  • the term including Vin indicates the amount of refrigerant for realizing the required amount of heat exchange in the user-side heat exchanger 3 in the normal operation mode
  • the term including Vout indicates the amount of refrigerant for realizing the required amount of heat exchange in the heat-source-side heat exchanger 2 in the normal operation mode
  • the term including L indicates the amount of refrigerant flowing through each of the first extension pipe 113 and the second extension pipe 114, assuming that single-phase liquid refrigerant flows through the first extension pipe 113 and single-phase gas refrigerant flows through the second extension pipe 114 in the normal operation mode.
  • the appropriate amount M out (unit: kg) of refrigerant recovered in the heat source side heat exchanger 2 in the recovery operation mode is set so as to satisfy the following relational expression (5) with the total internal volume V out of the heat source side heat exchanger 2.
  • the left side indicating the lower limit of the above-mentioned appropriate amount Mout is set from the viewpoint of suppressing a decrease in performance caused by an excess total internal volume Vout of the heat source side heat exchanger 2 resulting in a shortage of the amount of refrigerant during normal operation, or from the viewpoint of eliminating the need to change the product specifications (for example, shorten the maximum piping length L) to suppress such a decrease in performance.
  • the right side indicating the upper limit of the above-mentioned appropriate amount Mout is set as the total internal volume Vout of the heat source side heat exchanger 2 necessary to retain the refrigerant inside the heat source side heat exchanger 2 in the recovery operation mode.
  • the above relational expression (1) is derived by substituting Mref of the above relational expression (4) for Mout of the above relational expression (5).
  • the total internal volume V out (unit: m 3 ) of the heat source side heat exchanger 2 is set so as to satisfy the above relational expression (1), so the amount of refrigerant charged can be reduced compared to when the total internal volume V out is larger than the right side of the above relational expression (1). Furthermore, in the refrigeration cycle apparatus 100, the total internal volume V out (unit: m 3 ) of the heat source side heat exchanger 2 is set so as to satisfy the above relational expression (1), so the heat source side heat exchanger 2 can recover a large amount of refrigerant, and the amount of refrigerant leakage can be reduced compared to when the total internal volume V out is smaller than the left side of the above relational expression (1).
  • the gas refrigerant discharged from the compressor 1 flows into the heat source side heat exchanger 2, and the gas refrigerant can be sufficiently condensed in the heat source side heat exchanger 2.
  • the total internal volume Vout (unit: m3 ) of the heat source side heat exchanger 2 is set to satisfy the above relational expression (1), so that an accumulator and a receiver are not required from the viewpoint of reducing the amount of refrigerant leakage. Since the refrigerant circuit 110 of the refrigeration cycle apparatus 100 does not include an accumulator and a receiver, the amount of refrigerant charged in the refrigerant circuit 110 can be reduced compared to the amount of refrigerant charged in a refrigerant circuit that includes an accumulator and a receiver.
  • the entire heat source side refrigerant flow path 111 is accommodated in one heat source side unit 121, but this is not limited thereto.
  • the compressor 1, the flow path switching device 4, and the expansion device 5 may be accommodated in a unit different from the heat source side heat exchanger 2.
  • the refrigerant circuit 110 does not need to include a flow path switching device 4. In this case, it is sufficient that the discharge port of the compressor 1 is connected to the heat source side heat exchanger 2, and the suction port of the compressor 1 is connected to the utilization side heat exchanger 3. In other words, the refrigeration cycle device 100 is required to be at least capable of switching between a cooling operation mode and a recovery operation mode.
  • control device 200 is included in the heat source side unit 121, but this is not limited to the above.
  • the control device 200 may be included in the user side unit 122, or the control device 200 may be divided so that a part of the control device 200 is included in the heat source side unit 121 and the remaining part of the control device 200 is included in the user side unit 122.
  • the control device 200 may also be disposed outside the heat source side unit 121 and the user side unit 122.
  • the expansion device 5 may be included in the user unit 122 instead of the heat source unit 121.
  • the user side unit 122 may include at least one of a shutoff valve arranged near the connection between the user side refrigerant flow path 112 and the first extension pipe 113, and a shutoff valve arranged near the connection between the user side refrigerant flow path 112 and the second extension pipe 114.
  • the refrigerant circuit 110 may include, for example, a plurality of heat source side heat exchangers 2 connected in series with each other.
  • the total internal volume V out of the heat source side heat exchanger 2 in the above relational expression (1) is the sum of the total internal volumes of the plurality of heat source side heat exchangers 2.
  • the refrigerant circuit 110 may include, for example, a plurality of use side heat exchangers 3 connected in series or in parallel with each other. In this case, the total internal volume V in of the use side heat exchanger 3 in the above relational expression (1) is the sum of the total internal volumes of the plurality of use side heat exchangers 3.
  • FIG. 2 shows a refrigeration cycle apparatus 101, which is a modified example of the refrigeration cycle apparatus 100.
  • the refrigerant circuit 110 of the refrigeration cycle apparatus 101 does not have to include the first shutoff valve 6.
  • the expansion device 5 is controlled as the first control valve in the recovery operation mode in the same manner as the first shutoff valve 6 of the refrigeration cycle apparatus 100. In this case, it is preferable that the expansion device 5 is disposed near the connection between the heat source side refrigerant flow path 111 and the first extension pipe 113.
  • the refrigeration cycle apparatus 102 according to the second embodiment has the same configuration as the refrigeration cycle apparatus 100 according to the first embodiment and exerts the same effects.
  • the refrigerant circuit 110 further includes a first branch path 116, an on-off valve 8, and a container 9.
  • the heat source side refrigerant flow path 111 includes a first refrigerant flow path that connects the heat source side heat exchanger 2 and a first shutoff valve 6 serving as a first control valve.
  • the first refrigerant flow path includes a third refrigerant flow path 115A that connects the heat source side heat exchanger 2 and the expansion device 5, and a fourth refrigerant flow path 115B that connects the expansion device 5 and the first shutoff valve 6.
  • the first branch path 116 branches off from the fourth refrigerant flow path 115B. Only one end of the first branch path 116 is connected to the fourth refrigerant flow path 115B.
  • the on-off valve 8 opens and closes the first branch path 116.
  • the on-off valve 8 is, for example, a solenoid valve or an electric valve.
  • the opening and closing operation of the on-off valve 8 is controlled, for example, by the control device 200.
  • the on-off valve 8 may be configured to open in response to physical factors such as pressure changes or temperature changes of the refrigerant flowing through the first branch path 116.
  • the container 9 is connected to the fourth refrigerant flow path 115B via the first branch path 116 and the on-off valve 8.
  • the internal pressure of the container 9 is set lower than the internal pressure of the refrigerant circuit 110 when the refrigeration cycle device 102 is shipped.
  • the cooling operation mode, heating operation mode, and recovery operation mode of the refrigeration cycle device 102 are performed in the same manner as those of the refrigeration cycle device 100.
  • the on-off valve 8 is closed in the normal operation mode.
  • the container 9 is isolated from the refrigerant circuit 110 by the on-off valve 8 in the normal operation mode.
  • the on-off valve 8 is opened in the recovery operation mode.
  • the container 9 communicates with the refrigerant circuit 110 only in the recovery operation mode when the on-off valve 8 is open, and the refrigerant filled in the refrigerant circuit 110 can be recovered.
  • the maximum inner diameter of the first extension pipe 113 is dL (unit: m)
  • the maximum inner diameter of the second extension pipe 114 is dG (unit: m)
  • the maximum pipe length of each of the first extension pipe 113 and the second extension pipe 114 is L (unit: m)
  • the saturated liquid density of the refrigerant at the same temperature as the upper limit value Tmax of the ambient temperature of the refrigerant circuit 110 at which operation of the refrigeration cycle device 102 is guaranteed is ⁇ L (unit: kg/ m3 )
  • the saturated gas density of the refrigerant at the same temperature as the upper limit value Tmax is ⁇ G (unit: kg/ m3 )
  • the total internal volume Vout (unit: m3 ) of the heat source side heat exchanger 2 and the internal volume VC of the container 9 are expressed by the following relational equation (2).
  • the above-mentioned relational expression (2) is derived from the above-mentioned relational expressions (4) and (5) in the same manner as the above-mentioned relational expression (1).
  • the appropriate amount M out (unit: kg) of refrigerant recovered in the heat source side heat exchanger 2 and the container 9 in the recovery operation mode only needs to be equal to or greater than the left side of the above-mentioned relational expression (5), and the relationship with the right side of the above-mentioned relational expression (5) is not particularly limited.
  • the appropriate amount M out (unit: kg) of refrigerant recovered in the heat source side heat exchanger 2 and the container 9 in the recovery operation mode is equal to or less than the right side of the above-mentioned relational expression (5).
  • the total internal volume V out (unit: m 3 ) of the heat source side heat exchanger 2 and the internal volume V C of the container 9 are expressed by the following relational expression (6).
  • the refrigerant circuit 110 includes a container 9, which is separated from the refrigerant circuit 110 in the normal operation mode, but is connected to the refrigerant circuit 110 in the recovery operation mode. Therefore, in the refrigeration cycle device 102, the amount of refrigerant recovered can be increased without increasing the amount of refrigerant charged.
  • the heat source side heat exchanger 2 can recover a large amount of refrigerant, and the amount of refrigerant leakage can be reduced, compared to when the total internal volume Vout is smaller than the left side of the above relational expression (2).
  • the sum of the total internal volume Vout (unit: m3 ) of the heat source side heat exchanger 2 and the internal volume Vc of the container 9 is set so as to satisfy the above relational expression (2), so it is possible to use a heat source side heat exchanger 2 having an even smaller total internal volume V than that of the refrigeration cycle apparatus 100.
  • the first branch passage 116 may branch off from a third refrigerant passage 115A of the first refrigerant passage that connects between the heat source side heat exchanger 2 and the expansion device 5.
  • FIG. 4 shows a refrigeration cycle apparatus 103 which is a first modified example of the refrigeration cycle apparatus 102.
  • the refrigerant circuit 110 of the refrigeration cycle apparatus 103 does not have to include the first shutoff valve 6.
  • the expansion device 5 is controlled as a first control valve in the recovery operation mode in the same manner as the first shutoff valve 6 of the refrigeration cycle apparatuses 100 and 102.
  • a first branch passage 116 branches off from a first refrigerant flow passage 115 which connects between the heat source side heat exchanger 2 and the expansion device 5 which serves as the first control valve.
  • FIG. 5 shows a refrigeration cycle device 104, which is a second modified example of the refrigeration cycle device 102.
  • the first branch path 116 is connected in parallel with the first refrigerant flow path.
  • One end and the other end of the first branch path 116 are connected to the first refrigerant flow path.
  • One end and the other end of the first branch path 116 are connected to, for example, the fourth refrigerant flow path 115B.
  • the heat source side refrigerant flow path 111 includes a first on-off valve 8a arranged between the container 9 and one end of the first branch passage 116, and a second on-off valve 8b arranged between the container 9 and the other end of the first branch passage 116.
  • the first and second on-off valves 8a and 8b are each closed in the normal operation mode. At least one of the first and second on-off valves 8a and 8b is opened in the recovery operation mode.
  • one end and the other end of the first branch path 116 may be connected to the third refrigerant flow path 115A.
  • One end of the first branch path 116 may be connected to the third refrigerant flow path 115A, and the other end of the first branch path 116 may be connected to the fourth refrigerant flow path 115B.
  • the refrigeration cycle devices 102 to 104 according to the second embodiment can be modified in the same manner as the refrigeration cycle devices 100 and 101 according to the first embodiment.
  • the refrigeration cycle apparatus 105 according to the third embodiment has the same configuration as the refrigeration cycle apparatus 100 according to the first embodiment and exerts the same effects.
  • the refrigerant circuit 110 further includes a second branch path 118, an on-off valve 8, and a container 9.
  • the heat source side refrigerant flow path 111 includes a second refrigerant flow path 117 that connects between the compressor 1 and a second shutoff valve 7 serving as a second control valve.
  • the second branch path 118 branches off from the second refrigerant flow path 117.
  • the second branch path 118 branches off, for example, from a portion of the second refrigerant flow path 117 that connects between the flow path switching device 4 and the second shutoff valve 7. Only one end of the second branch path 118 is connected to the second refrigerant flow path 117.
  • the on-off valve 8 opens and closes the second branch passage 118.
  • the on-off valve 8 may have the same configuration as the on-off valve 8 described above.
  • the container 9 is connected to the second refrigerant flow path 117 via the second branch path 118 and the on-off valve 8.
  • the internal pressure of the container 9 is set lower than the internal pressure of the refrigerant circuit 110 when the refrigeration cycle device 105 is shipped.
  • the on-off valve 8 is closed in the normal operation mode.
  • the container 9 is isolated from the refrigerant circuit 110 by the on-off valve 8 in the normal operation mode.
  • the on-off valve 8 is opened in the recovery operation mode.
  • the container 9 communicates with the refrigerant circuit 110 only in the recovery operation mode when the on-off valve 8 is open, and the refrigerant filled in the refrigerant circuit 110 can be recovered.
  • the cooling and heating operation modes of the refrigeration cycle device 105 are performed in the same manner as those of the refrigeration cycle device 100.
  • the recovery operation mode of the refrigeration cycle device 105 is different from that of the refrigeration cycle device 100.
  • the second shutoff valve 7 is closed, the first shutoff valve 6 is opened, and the flow path switching device 4 is in the second state.
  • the container 9 acts as a container for recovering the refrigerant.
  • the refrigerant is recovered in a portion of the heat source side refrigerant flow path 111 located between the discharge port of the compressor 1 and the second shutoff valve 7.
  • the control device 200 detects a refrigerant leak, only the second shutoff valve 7 is closed.
  • the compressor 1 is kept operating at a predetermined frequency, the flow path switching device 4 is maintained in the second state, and the first shutoff valve 6 is maintained in an open state.
  • control device 200 When the control device 200 detects a refrigerant leak while the refrigeration cycle device 105 is operating in the cooling operation mode, the control device 200 controls each component of the refrigeration cycle device 100 to start the recovery operation mode.
  • the flow path switching device 4 is switched to the second state.
  • the second shutoff valve 7 is closed.
  • the compressor 1 is placed in a state in which it is operating at a predetermined frequency.
  • the first shutoff valve 6 is maintained in an open state. After the recovery operation mode ends, the compressor 1 is stopped and the first shutoff valve 6 is closed.
  • the refrigerant is recovered in a portion of the heat source side refrigerant flow path 111 that is located between the discharge port of the compressor 1 and the second shutoff valve 7.
  • the inner volume Vc of the container 9 is set to be equal to or larger than the volume of the refrigerant in the refrigerant circuit 110 at the end of the recovery operation mode.
  • the internal volume VC of the container 9 is expressed by the following relational equation (3).
  • the right-hand side indicating the upper limit of the above-mentioned appropriate amount M C is set taking into consideration that a portion of the gas refrigerant recovered in the container 9 is likely to remain without being condensed.
  • M ref M C.
  • the above relational expression (3) is derived by substituting M ref of the above relational expression (4) for M C of the above relational expression (7).
  • the refrigerant circuit 110 includes a container 9, which is separated from the refrigerant circuit 110 in the normal operation mode, but is connected to the refrigerant circuit 110 in the recovery operation mode. Therefore, in the refrigeration cycle device 105, as in the refrigeration cycle device 102, the amount of refrigerant recovered can be increased without increasing the amount of refrigerant charged.
  • the container 9 can recover a larger amount of refrigerant, and the amount of refrigerant leakage can be reduced, compared to a case in which the internal volume V C is smaller than the left side of the above-mentioned relational expression (3).
  • the container 9 is preferably provided so that the refrigerant recovered therein exchanges heat with the outside air of the container 9 or with the refrigerant drawn into the compressor 1.
  • Fig. 7 shows a refrigeration cycle apparatus 106 which is a first modified example of the refrigeration cycle apparatus 105.
  • the container 9 shown in Fig. 7 is provided so that the refrigerant recovered therein exchanges heat with the refrigerant drawn into the compressor 1. In this way, condensation of the gas refrigerant discharged from the compressor 1 to the container 9 in the recovery operation mode can be promoted.
  • the container 9 may include fins capable of coming into contact with air flowing around the container 9.
  • FIG. 8 shows a refrigeration cycle device 107, which is a second modified example of the refrigeration cycle device 105.
  • the second branch path 118 is connected in parallel with the second refrigerant flow path 117.
  • One end and the other end of the second branch path 118 are connected to the second refrigerant flow path 117.
  • the heat source side refrigerant flow path 111 includes a first on-off valve 8a arranged between the container 9 and one end of the second branch passage 118, and a second on-off valve 8b arranged between the container 9 and the other end of the second branch passage 118.
  • Each of the first on-off valve 8a and the second on-off valve 8b is closed in the normal operation mode. At least one of the first on-off valve 8a and the second on-off valve 8b is opened in the recovery operation mode.
  • the refrigerant circuit 110 does not need to include a flow path switching device 4. In this case, it is sufficient that the discharge port of the compressor 1 is connected to the utilization side heat exchanger 3, and the suction port of the compressor 1 is connected to the heat source side heat exchanger 2. In other words, in the refrigeration cycle devices 105 to 107, it is sufficient that at least the heating operation mode and the recovery operation mode can be switched.
  • the refrigeration cycle devices 105 to 107 according to embodiment 3 can be modified in the same manner as the refrigeration cycle devices 100 and 101 according to embodiment 1 or the refrigeration cycle devices 102 and 103 according to embodiment 2.

Landscapes

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

Abstract

L'invention concerne un dispositif à cycle de réfrigération comprenant un circuit de fluide frigorigène incluant : un canal de fluide frigorigène côté source de chaleur (111) qui inclut un échangeur de chaleur côté source de chaleur (2) ; un canal de fluide frigorigène côté utilisation (112) qui inclut un échangeur de chaleur côté utilisation (3) ; et une première conduite d'extension (113) et une seconde conduite d'extension (114). Le volume interne total Vout (unités : m3) de l'échangeur de chaleur côté source de chaleur est représenté par l'expression relationnelle (1), lorsque le volume interne total de l'échangeur de chaleur côté utilisation est Vin (unités : m3), le diamètre interne maximal de la première conduite d'extension est dL (unités : m), le diamètre interne maximal de la seconde conduite d'extension est dG (unités : m), la valeur maximale des longueurs de conduite de la première conduite d'extension et de la seconde conduite d'extension est L (unités : m), la densité de liquide saturé d'un fluide frigorigène à une température qui est la même que la valeur maximale Tmax de la température ambiante du circuit de fluide frigorigène lorsque le dispositif à cycle de réfrigération est actif de manière sûre est ρL (unités : kg/m3), et la densité de gaz saturé du fluide frigorigène à une température qui est la même que la valeur maximale Tmax est ρG (unités : kg/m3).
PCT/JP2023/031908 2023-08-31 2023-08-31 Dispositif à cycle de réfrigération WO2025046855A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2023/031908 WO2025046855A1 (fr) 2023-08-31 2023-08-31 Dispositif à cycle de réfrigération

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2023/031908 WO2025046855A1 (fr) 2023-08-31 2023-08-31 Dispositif à cycle de réfrigération

Publications (1)

Publication Number Publication Date
WO2025046855A1 true WO2025046855A1 (fr) 2025-03-06

Family

ID=94818483

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2023/031908 WO2025046855A1 (fr) 2023-08-31 2023-08-31 Dispositif à cycle de réfrigération

Country Status (1)

Country Link
WO (1) WO2025046855A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013080914A1 (fr) * 2011-11-29 2013-06-06 日立アプライアンス株式会社 Climatiseur
JP2013124791A (ja) * 2011-12-13 2013-06-24 Daikin Industries Ltd 冷凍装置
JP2015190712A (ja) * 2014-03-28 2015-11-02 株式会社富士通ゼネラル 空気調和機
JP2020143870A (ja) * 2019-03-08 2020-09-10 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． 空気調和機
US20230145115A1 (en) * 2020-05-20 2023-05-11 Daikin Industries, Ltd. Heat pump system and controller for controlling operation of the same

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013080914A1 (fr) * 2011-11-29 2013-06-06 日立アプライアンス株式会社 Climatiseur
JP2013124791A (ja) * 2011-12-13 2013-06-24 Daikin Industries Ltd 冷凍装置
JP2015190712A (ja) * 2014-03-28 2015-11-02 株式会社富士通ゼネラル 空気調和機
JP2020143870A (ja) * 2019-03-08 2020-09-10 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． 空気調和機
US20230145115A1 (en) * 2020-05-20 2023-05-11 Daikin Industries, Ltd. Heat pump system and controller for controlling operation of the same

Similar Documents

Publication Publication Date Title
EP3683524B1 (fr) Dispositif frigorifique
JP5318099B2 (ja) 冷凍サイクル装置、並びにその制御方法
CN103328909B (zh) 空气调节装置
JP7186845B2 (ja) 空気調和装置
JP5908183B1 (ja) 空気調和装置
JP4883201B2 (ja) 熱源ユニット
EP3217115B1 (fr) Appareil de climatisation
EP2354723A2 (fr) Système réfrigérant
JP2017142038A (ja) 冷凍サイクル装置
CN108954501A (zh) 空调机
CN108885029B (zh) 冷冻装置
JP6537629B2 (ja) 空気調和装置
WO2025046855A1 (fr) Dispositif à cycle de réfrigération
JP2004225928A (ja) 冷凍装置
JP7397286B2 (ja) 冷凍サイクル装置
WO2020202519A1 (fr) Dispositif à cycle frigorifique
CN119365737A (zh) 空调装置
KR20080072241A (ko) 차량용 공조 시스템