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WO2015132967A1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

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Publication number
WO2015132967A1
WO2015132967A1 PCT/JP2014/056024 JP2014056024W WO2015132967A1 WO 2015132967 A1 WO2015132967 A1 WO 2015132967A1 JP 2014056024 W JP2014056024 W JP 2014056024W WO 2015132967 A1 WO2015132967 A1 WO 2015132967A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
expansion valve
compressor
refrigeration cycle
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2014/056024
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English (en)
Japanese (ja)
Inventor
謙作 畑中
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to PCT/JP2014/056024 priority Critical patent/WO2015132967A1/fr
Priority to EP15759078.7A priority patent/EP3121539B1/fr
Priority to PCT/JP2015/055855 priority patent/WO2015133398A1/fr
Priority to JP2016506459A priority patent/JP6188916B2/ja
Publication of WO2015132967A1 publication Critical patent/WO2015132967A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves

Definitions

  • the present invention relates to an air conditioner using a combustible refrigerant as a main component, and more particularly to a refrigeration cycle apparatus that suppresses an increase in discharge temperature from a compressor while suppressing an increase in the amount of refrigerant charged. .
  • HFC refrigerant having no carbon double bond in the composition for example, R32 (CH 2 F 2 ; difluoromethane) having a lower GWP than R410A.
  • a halogenated hydrocarbon having a carbon double bond in the composition which is a kind of HFC refrigerant like R32.
  • HFO-1234yf CF 3 CF ⁇ CH 2 ; tetrafluoropropene
  • HFO-1234ze CF 3 —CH ⁇ CHF
  • an HFC refrigerant having a carbon double bond is changed to an olefin (unsaturated hydrocarbon having a carbon double bond). It is often expressed as “HFO refrigerant” using “O” (called olefin).
  • Such low GWP refrigerants are not as flammable as HC refrigerants such as natural refrigerant R290 (C 3 H 8 ; propane), but are different from non-flammable R410A, It has flammability of a slight burn level.
  • coolant which has flammability even if it is a slight combustion level is called "flammable refrigerant
  • a refrigeration cycle apparatus using a flammable refrigerant R32 refrigerant or a mixed refrigerant with R32 of 70% or more is used, and a target discharge temperature is calculated according to the condensation temperature, evaporation temperature, and opening degree of the supercooling heat exchange expansion valve.
  • a refrigeration apparatus in which the opening of a main expansion valve is adjusted so as to achieve a target discharge temperature (see, for example, Patent Document 1).
  • a refrigeration circuit that uses a refrigerant that may be denatured depending on the temperature in the compressor, branches a part of the refrigerant discharged from the outlet of the condenser, and supplies the branched refrigerant to the inside of the compressor. (For example, refer to Patent Document 2).
  • the present invention has been made to solve the above-described problems, and suppresses an increase in discharge temperature from a compressor while suppressing an increase in the amount of charged refrigerant even when a flammable refrigerant is used.
  • An object of the present invention is to provide a refrigeration cycle apparatus capable of performing the above.
  • a refrigeration cycle apparatus includes a main refrigerant circuit to which a compressor, a first heat exchanger, a first expansion valve, and a second heat exchanger are connected, the first heat exchanger, and the first heat exchange.
  • an increase in the amount of refrigerant charged can be suppressed by suppressing a decrease in the dryness of the inlet of the second heat exchanger that acts as an evaporator during a predetermined normal operation. It is possible to suppress the discharge temperature and suppress the increase in the condensation pressure by injecting into the compressor during the cooling operation.
  • FIG. 1 is a refrigerant circuit configuration diagram schematically showing an example of a refrigerant circuit configuration of a refrigeration cycle apparatus (hereinafter referred to as refrigeration cycle apparatus 100A) according to Embodiment 1 of the present invention.
  • refrigeration cycle apparatus 100A a refrigeration cycle apparatus
  • the refrigeration cycle apparatus 100A is assumed to use a combustible refrigerant as a main component, and includes an outdoor unit 1 and an indoor unit 2.
  • the outdoor unit 1 and the indoor unit 2 are connected via a liquid pipe 7 and a gas pipe 9.
  • the connection algebra of the outdoor unit 1 and the indoor unit 2 is not limited to one, and any one or each may be a plurality.
  • the outdoor unit (heat source unit) 1 is an outdoor heat exchanger (first heat exchanger) that exchanges heat between the compressor 3 that compresses the refrigerant and the refrigerant and the air around the outdoor unit 1 that is conveyed by the outdoor fan 5a.
  • First electronic expansion valve (first expansion valve) 6 for controlling the flow rate of the refrigerant
  • on-off valve 21 for controlling the flow of the refrigerant
  • supercooling heat exchanger 22 for exchanging heat between the refrigerant and the refrigerant
  • a second electronic expansion valve (second expansion valve) 23 to be controlled and a third electronic expansion valve (third expansion valve) 24 to control the flow rate of the refrigerant are provided.
  • the outdoor heat exchanger 5 has the outdoor air blower 5a which supplies air.
  • the indoor unit (use-side unit) 2 exchanges heat between the refrigerant and the air around the indoor unit 2 conveyed by the indoor blower 8a, and cools or heats the indoor space by, for example, cooling or heating the indoor space.
  • a heat exchanger (second heat exchanger) 8 is provided.
  • the indoor heat exchanger 8 has an indoor blower 8a that supplies air.
  • the compressor 3 for compressing the refrigerant it is preferable to use a positive displacement compressor of a type in which the rotation speed is controlled by an inverter circuit and the capacity is controlled.
  • the positive displacement compressor include a rotary compressor, a scroll compressor, a screw compressor, and a reciprocating compressor.
  • a discharge pipe 3 a is connected to the compressor 3.
  • the outdoor heat exchanger 5 functions as a condenser or an evaporator, and can be constituted by, for example, a cross-fin type fin-and-tube heat exchanger constituted by a heat transfer tube and a large number of fins.
  • the outdoor blower 5a supplies air to the outdoor heat exchanger 5, and is configured to be capable of changing the air flow rate.
  • a centrifugal fan or a multiblade fan driven by a motor such as a DC fan motor can be used as the outdoor fan 5a.
  • the opening of the first electronic expansion valve 6 is controlled by a control device 30 to be described later, and the refrigerant flow rate is adjusted while the refrigerant pressure is reduced.
  • the indoor heat exchanger 8 functions as an evaporator or a condenser, and can be constituted by, for example, a cross-fin type fin-and-tube heat exchanger constituted by heat transfer tubes and a large number of fins.
  • the indoor blower 8a supplies air to the indoor heat exchanger 8, and is configured to be capable of changing the air flow rate.
  • a centrifugal fan or a multiblade fan driven by a motor such as a DC fan motor can be used as the indoor fan 8a.
  • the compressor 3, the outdoor heat exchanger 5, the first electronic expansion valve 6, and the indoor heat exchanger 8 are connected by a main refrigerant pipe 31 including the discharge pipe 3 a, the liquid pipe 7, and the gas pipe 9. This constitutes the main refrigerant circuit.
  • the outdoor unit 1 was branched from the main refrigerant pipe 31 between the outdoor heat exchanger 5 and the first electronic expansion valve 6 and connected between the first electronic expansion valve 6 and the indoor heat exchanger 8.
  • a branch pipe 25 is provided.
  • the outdoor heat exchanger 5, the primary side of the supercooling heat exchanger 22 (the refrigerant side flowing through the branch pipe 25), the second electronic expansion valve 23, and the indoor heat exchanger 8 are connected to the branch pipe 25 and the main refrigerant pipe 31.
  • a branch circuit is configured by connecting them with each other.
  • the outdoor unit 1 has an injection pipe 26 branched from a branch pipe 25 between the supercooling heat exchanger 22 and the second electronic expansion valve 23 and connected to the suction side of the compressor 3.
  • the injection side is configured by connecting the third electronic expansion valve 24, the secondary side of the subcooling heat exchanger 22 (the refrigerant side flowing through the injection pipe 26), and the suction side of the compressor 3 through the injection pipe 26. .
  • the on-off valve 21 is provided between the outdoor heat exchanger 5 and the supercooling heat exchanger 22 of the branch pipe 25, and is controlled to be opened and closed by a control device 30 described later to open and close the branch pipe 25.
  • the supercooling heat exchanger 22 performs heat exchange between the refrigerant flowing through the branch pipe 25 and the refrigerant flowing through the injection pipe 26.
  • a microchannel heat exchanger a shell and tube heat exchanger, a heat A pipe heat exchanger, a double pipe heat exchanger, a plate heat exchanger, or the like may be used.
  • the second electronic expansion valve 23 is provided on the downstream side of the subcooling heat exchanger 22 in the branch pipe 25, the opening degree is controlled by a control device 30 described later, and the pressure of the refrigerant flowing through the branch pipe 25 is reduced. It is possible to adjust the flow rate of the refrigerant.
  • the third electronic expansion valve 24 is provided on the upstream side of the supercooling heat exchanger 22 of the injection pipe 26, the opening degree of which is controlled by a control device 30 described later, and the pressure of the refrigerant flowing through the injection pipe 26 is reduced. It is possible to adjust the flow rate of the refrigerant.
  • the refrigeration cycle apparatus 100A includes a control device 30 that performs overall control of the refrigeration cycle apparatus 100A. Based on the detection values from the detectors, the control device 30 controls each actuator (compressor 3, outdoor blower 5a, first electronic expansion valve 6, on-off valve 21, second electronic expansion valve 23, third electronic expansion valve 24). , Driving components such as the indoor fan 8a) are controlled.
  • the control device 30 can be configured by hardware such as a circuit device that realizes the function, or can be configured by an arithmetic device such as a microcomputer or a CPU and software executed thereon.
  • the liquid pipe 7 connecting the outdoor unit 1 and the indoor unit 2 is connected via a liquid side stop valve 32.
  • the gas pipe 9 connecting the outdoor unit 1 and the indoor unit 2 is connected via a gas-side stop valve 33. That is, the outdoor unit 1 and the indoor unit 2 can be separated from each other through the liquid side stop valve 32 and the gas side stop valve 33.
  • FIG. 2 is a control pattern of each actuator (here, the on-off valve 21, the first electronic expansion valve 6, the second electronic expansion valve 23, and the third electronic expansion valve 24) corresponding to the operation mode executed by the refrigeration cycle apparatus 100A. It is explanatory drawing for demonstrating. Based on FIG.1 and FIG.2, operation
  • the refrigeration cycle apparatus 100A determines the use of the supercooling heat exchanger 22 according to the outside air temperature.
  • the operation mode when the subcooling heat exchanger 22 is not used during normal outside air is referred to as “normal operation mode”
  • normal operation mode the operation mode when the subcooling heat exchanger 22 is used during high outside air
  • high outside air operation mode the operation mode when the subcooling heat exchanger 22 is used during high outside air
  • the normal outside air time cannot be determined in a strict temperature range, but is assumed to be within the normal temperature range of the area where the refrigeration cycle apparatus 100A is used. It shall be. Moreover, although the exact temperature range cannot be defined as the time of high outside air, it is assumed that the temperature is equal to or higher than the upper limit (for example, 40 ° C. or higher) of the predetermined normal outside air temperature of the refrigeration cycle apparatus 100A. .
  • ⁇ Normal operation mode> In the normal operation mode, as shown in FIG. 2, the on-off valve 21 is closed, the second electronic expansion valve 23 is fully opened, and the third electronic expansion valve 24 is fully closed, and the first electronic expansion valve 6 controls the compressor 3.
  • the temperature of the refrigerant discharged from is controlled. That is, during normal outdoor air, the refrigeration cycle apparatus 100A suppresses a decrease in the dryness of the inlet of the indoor heat exchanger 8 that functions as an evaporator, and suppresses an increase in the amount of refrigerant necessary for the indoor heat exchanger 8. Then, the supercooling heat exchanger 22 is bypassed.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 3 flows into the outdoor heat exchanger 5 acting as a condenser, and dissipates heat to the outdoor air blown by the outdoor blower 5a.
  • This refrigerant is decompressed by the first electronic expansion valve 6 to become a low-pressure two-phase refrigerant, and the indoor air is cooled by the indoor heat exchanger 8 acting as an evaporator to become a low-pressure gas refrigerant. Thereafter, the gas is again sucked into the compressor 3 through the gas pipe 9.
  • ⁇ High outdoor air operation mode> In the high outside air operation mode, as shown in FIG. 2, the on-off valve 21 is opened, the first electronic expansion valve 6 is fully closed, and the temperature of the refrigerant discharged from the compressor 3 is controlled by the second electronic expansion valve 23.
  • the third electronic expansion valve 24 controls the supercooling degree (SC) of the refrigerant at the outlet of the supercooling heat exchanger 22. That is, at the time of high outside air, the refrigeration cycle apparatus 100A causes the refrigerant to flow through the branch circuit and uses the supercooling heat exchanger 22 to lower the inlet dryness of the indoor heat exchanger 8 that functions as an evaporator. By holding a large amount of refrigerant in the indoor heat exchanger 8, an increase in the high pressure of the refrigerant discharged from the compressor 3 is suppressed.
  • SC supercooling degree
  • the refrigeration cycle apparatus 100A injects the refrigerant that has passed through the supercooling heat exchanger 22 to the suction side of the compressor 3, and suppresses an increase in the discharge temperature of the refrigerant discharged from the compressor 3. is doing.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 3 flows into the outdoor heat exchanger 5 acting as a condenser, and dissipates heat to the outdoor air blown by the outdoor blower 5a.
  • This refrigerant flows into the supercooling heat exchanger 22 through the on-off valve 21.
  • This refrigerant is cooled by the low-pressure refrigerant in the supercooling heat exchanger 22 and then depressurized by the second electronic expansion valve 23 to become a low-pressure two-phase refrigerant.
  • the indoor heat exchanger 8 acting as an evaporator the indoor air Is cooled to become a low-pressure gas refrigerant. Thereafter, the gas is again sucked into the compressor 3 through the gas pipe 9.
  • the refrigerant in the injection circuit that has flowed into the injection pipe 26 is heated by the high-pressure refrigerant in the supercooling heat exchanger 22 after being depressurized by the third electronic expansion valve 24.
  • This refrigerant is injected into the suction side of the compressor 3 and merges with the refrigerant flowing through the gas pipe 9. Thereafter, the gas is again sucked into the compressor 3 through the gas pipe 9.
  • the degree of supercooling (SC) of the refrigerant at the outlet of the supercooling heat exchanger 22 is the saturation temperature on the high pressure side of the refrigerant obtained from the value of the refrigerant discharge pressure discharged from the compressor 3, and the supercooling heat exchange. It can be calculated by the difference between the temperature of the refrigerant after passing through the vessel 22.
  • ⁇ Switching operation mode> The filling amount of the refrigerant sealed in the refrigerant circuit is normally determined at the time of outside air. Therefore, in the refrigeration cycle apparatus 100A, the normal operation mode is executed, the supercooling heat exchanger 22 is bypassed, the dryness of the inlet refrigerant of the indoor heat exchanger 8 functioning as an evaporator is kept high, and charging is performed. An increase in the amount of refrigerant is suppressed. On the other hand, since the increase in the refrigerant charging amount is suppressed, there is a possibility that the high pressure will increase under high outside air conditions.
  • the refrigeration cycle apparatus 100A executes the high outside air operation mode and uses the supercooling heat exchanger 22 to set the dryness of the inlet refrigerant of the indoor heat exchanger 8 functioning as an evaporator. It is possible to suppress an increase in high pressure by setting a low state and holding a large amount of refrigerant in the indoor heat exchanger 8.
  • the refrigerant that has passed through the supercooling heat exchanger 22 is injected into the suction side of the compressor 3, and the refrigerant discharged from the compressor 3 is injected. It is possible to suppress an increase in discharge temperature.
  • the refrigeration cycle apparatus 100A determines the use of the supercooling heat exchanger 22 depending on whether the outside air temperature is a high outside temperature. Therefore, according to the refrigeration cycle apparatus 100A, the filling amount of the refrigerant sealed in the refrigerant circuit is determined according to the normal operation mode, and the increase in the filling refrigerant amount is suppressed. Further, according to the refrigeration cycle apparatus 100A, the supercooling heat exchanger 22 is used as necessary. Therefore, when the supercooling heat exchanger 22 is not used, the high pressure side of the supercooling heat exchanger 22 is used. The amount of refrigerant charged can be reduced without causing a decrease in pressure.
  • the supercooling heat exchanger 22 and the injection pipe 26 are used by executing the high outside air operation mode.
  • the refrigeration cycle apparatus 100A is assumed to use a refrigerant whose main component is a combustible refrigerant.
  • combustible refrigerants include R32, HFO-1234yf, HFO-1234ze, R290 (C 3 H 8 ; propane), R1270 (C 3 H 6 ; propylene), and the like.
  • the content of other refrigerants to be mixed may be a plurality of types of refrigerants), including that the combustible refrigerant exemplified above is used alone, It means that the content of the combustible refrigerant is not exceeded by mass%.
  • a circuit in which the injection pipe 26 is connected to the suction side of the compressor 3 is shown as an example, but an intermediate in which the injection pipe 26 communicates with the intermediate pressure portion of the compressor 3. You may make it connect to a port.
  • the refrigeration cycle apparatus 100A can suppress an increase in discharge temperature while suppressing an increase in the amount of refrigerant charged. Therefore, according to the refrigeration cycle apparatus 100A, the increase in the amount of charged refrigerant is suppressed, so that safety is taken into consideration even when the refrigerant leaks, the influence on global warming can be reduced, and the refrigerant can be reduced by suppressing the increase in discharge temperature. It is possible to continue high-efficiency operation without degeneration.
  • FIG. FIG. 3 is a refrigerant circuit configuration diagram schematically showing an example of a refrigerant circuit configuration of a refrigeration cycle apparatus (hereinafter referred to as refrigeration cycle apparatus 100B) according to Embodiment 2 of the present invention.
  • the refrigeration cycle apparatus 100B will be described based on FIG.
  • differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted.
  • the refrigeration cycle apparatus 100B is assumed to use a combustible refrigerant as a main component.
  • the refrigeration cycle apparatus 100B is different from the refrigeration cycle apparatus 100A according to Embodiment 1 in the configuration of the outdoor unit 1. Also.
  • the configuration of the main refrigerant pipe 31 and the branch pipe 25 is different from that of the refrigeration cycle apparatus 100A according to the first embodiment.
  • the outdoor unit (heat source unit) 1 includes a compressor 3, an outdoor heat exchanger 5, a three-way valve 27, a supercooling heat exchanger 22, a second electronic expansion valve 23, and a third electronic expansion valve 24. That is, the refrigeration cycle apparatus 100B includes the three-way valve 27 instead of the first electronic expansion valve 6 and the on-off valve 21 that the outdoor unit 1 of the refrigeration cycle apparatus 100A according to Embodiment 1 includes. . Therefore, the second electronic expansion valve 23 functions as the “first electronic expansion valve” of the present invention.
  • the three-way valve 27 has a function as a flow path switching device, is provided on the downstream side of the outdoor heat exchanger 5, and is provided in either the main refrigerant pipe 31 (main refrigerant circuit) or the branch pipe 25 (branch circuit).
  • the refrigerant flow path is switched.
  • the flow path switching device is the three-way valve 27 will be described as an example, but the flow path switching device is not limited to the three-way valve 27.
  • the flow path switching device only needs to switch the refrigerant flow path.
  • the flow path switching device may be configured by combining two-way valves, or may be configured to close one flow path of the four-way valve. it can.
  • the compressor 3, the outdoor heat exchanger 5, the three-way valve 27, the second electronic expansion valve 23, and the indoor heat exchanger 8 include the discharge pipe 3a, the liquid pipe 7, and the gas pipe 9.
  • the main refrigerant circuit is configured by being connected by the main refrigerant pipe 31.
  • the branch pipe 25 branches from the main refrigerant pipe 31 via the three-way valve 27, passes through the supercooling heat exchanger 22, and is connected between the three-way valve 27 and the second electronic expansion valve 23. .
  • the outdoor heat exchanger 5, the three-way valve 27, the primary side of the supercooling heat exchanger 22 (the refrigerant side flowing through the branch pipe 25), the second electronic expansion valve 23, and the indoor heat exchanger 8 are connected to the branch pipe 25 and A branch circuit is configured by being connected by the main refrigerant pipe 31.
  • the outdoor unit 1 is branched from the branch pipe 25 between the supercooling heat exchanger 22 and the second electronic expansion valve 23, and is sucked into the compressor 3. It has an injection pipe 26 connected to the side.
  • the injection circuit is configured by connecting the third electronic expansion valve 24, the secondary side of the supercooling heat exchanger (the refrigerant side flowing through the injection pipe 26), and the suction side of the compressor 3 through the injection pipe 26.
  • FIG. 4 is an explanatory diagram for explaining a control pattern of each actuator (here, the three-way valve 27, the second electronic expansion valve 23, and the third electronic expansion valve 24) according to the operation mode executed by the refrigeration cycle apparatus 100B. It is. Based on FIG.3 and FIG.4, operation
  • each actuator here, the three-way valve 27, the second electronic expansion valve 23, and the third electronic expansion valve 24
  • the refrigeration cycle apparatus 100B determines the use of the supercooling heat exchanger 22 according to the outside air temperature.
  • the definitions of the normal operation mode and the high outside air operation mode are the same as in the first embodiment.
  • ⁇ Normal operation mode> In the normal operation mode, as shown in FIG. 4, the three-way valve 27 is switched to connect the outdoor heat exchanger 5 and the second electronic expansion valve 23, and the third electronic expansion valve 24 is controlled to be fully closed, The temperature of the refrigerant discharged from the compressor 3 is controlled by the second electronic expansion valve 23.
  • the refrigeration cycle apparatus 100B suppresses a decrease in the dryness of the inlet of the indoor heat exchanger 8 that functions as an evaporator, and suppresses an increase in the amount of refrigerant necessary for the indoor heat exchanger 8. Then, the supercooling heat exchanger 22 is bypassed.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 3 flows into the outdoor heat exchanger 5 acting as a condenser, and dissipates heat to the outdoor air blown by the outdoor blower 5a.
  • This refrigerant flows into the second electronic expansion valve 23 via the three-way valve 27. Then, the pressure is reduced by the second electronic expansion valve 23 to become a low pressure two-phase refrigerant, and the indoor air is cooled by the indoor heat exchanger 8 acting as an evaporator to become a low pressure gas refrigerant. Thereafter, the gas is again sucked into the compressor 3 through the gas pipe 9.
  • the three-way valve 27 is switched to connect the outdoor heat exchanger 5 and the supercooling heat exchanger 22, and the second electronic expansion valve 23 outputs from the compressor 3.
  • the temperature of the discharged refrigerant is controlled, and the third electronic expansion valve 24 controls the supercooling degree (SC) of the refrigerant at the outlet of the supercooling heat exchanger 22.
  • SC supercooling degree
  • the refrigeration cycle apparatus 100B causes the refrigerant to flow through the branch circuit and uses the supercooling heat exchanger 22 to lower the inlet dryness of the indoor heat exchanger 8 that functions as an evaporator.
  • the refrigeration cycle apparatus 100B injects the refrigerant of the injection circuit that has passed through the supercooling heat exchanger 22 to the suction side of the compressor 3, and the discharge temperature of the refrigerant discharged from the compressor 3 The rise is suppressed.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 3 flows into the outdoor heat exchanger 5 acting as a condenser, and dissipates heat to the outdoor air blown by the outdoor blower 5a.
  • This refrigerant flows into the supercooling heat exchanger 22 via the three-way valve 27.
  • This refrigerant is cooled by the low-pressure refrigerant in the supercooling heat exchanger 22 and then depressurized by the second electronic expansion valve 23 to become a low-pressure two-phase refrigerant.
  • the indoor heat exchanger 8 acting as an evaporator the indoor air Is cooled to become a low-pressure gas refrigerant. Thereafter, the gas is again sucked into the compressor 3 through the gas pipe 9.
  • the refrigerant that has flowed into the injection pipe 26 is heated by the high-pressure refrigerant in the supercooling heat exchanger 22 after being depressurized by the third electronic expansion valve 24.
  • This refrigerant is injected into the suction side of the compressor 3 and merges with the refrigerant flowing through the gas pipe 9. Thereafter, the gas is again sucked into the compressor 3 through the gas pipe 9.
  • refrigeration cycle apparatus 100B like refrigeration cycle apparatus 100A according to Embodiment 1, suppresses an increase in the amount of charged refrigerant and suppresses an increase in discharge temperature and indoor heat exchange functions as an evaporator. It is possible to suppress the increase in the condensation pressure due to the decrease in the dryness of the refrigerant at the inlet of the vessel 8. Therefore, according to the refrigeration cycle apparatus 100B, safety is taken into consideration even when the refrigerant leaks by suppressing the increase in the amount of refrigerant charged, the effect on global warming can be reduced, and the refrigerant can be reduced by suppressing the increase in discharge temperature. It is possible to continue high-efficiency operation without degeneration.
  • the number of valves can be reduced as compared with the refrigeration cycle apparatus 100A according to the first embodiment.
  • FIG. FIG. 5 is a refrigerant circuit configuration diagram schematically showing an example of a refrigerant circuit configuration of a refrigeration cycle apparatus (hereinafter referred to as refrigeration cycle apparatus 100C) according to Embodiment 3 of the present invention.
  • the refrigeration cycle apparatus 100C will be described based on FIG.
  • differences from the first and second embodiments will be mainly described, and the same parts as those in the first and second embodiments will be denoted by the same reference numerals and the description thereof will be omitted.
  • the refrigeration cycle apparatus 100C is assumed to use a combustible refrigerant as a main component.
  • the refrigeration cycle apparatus 100C is different from the refrigeration cycle apparatus 100A according to Embodiment 1 in the configuration of the outdoor unit 1. Also.
  • the configuration of the main refrigerant pipe 31 and the branch pipe 25 is different from that of the refrigeration cycle apparatus 100A according to the first embodiment.
  • the outdoor unit (heat source unit) 1 includes a compressor 3, a refrigerant flow switching device 28, an outdoor heat exchanger 5, a fourth electronic expansion valve (fourth expansion valve) 29, a supercooling heat exchanger 22, and a second electron.
  • An expansion valve 23 and a third electronic expansion valve 24 are provided. That is, the refrigeration cycle apparatus 100C is not provided with the first electronic expansion valve 6 and the on-off valve 21 provided in the outdoor unit 1 of the refrigeration cycle apparatus 100A according to Embodiment 1, A fourth electronic expansion valve 29 is provided. Therefore, the fourth electronic expansion valve 29 functions as the “first electronic expansion valve” of the present invention.
  • the branch pipe 25 is not branched from the main refrigerant pipe 31 provided in the outdoor unit 1 of the refrigeration cycle apparatus 100A according to Embodiment 1, and the branch pipe 25 is connected to the main refrigerant pipe 31.
  • the connected structure is adopted.
  • the refrigerant flow switching device 28 is provided on the discharge side of the compressor 3 and switches the flow of the refrigerant.
  • the refrigerant flow switching device 28 can be constituted by a four-way valve, for example, as shown in FIG.
  • the refrigerant flow switching device 28 is not limited to a four-way valve, and a two-way valve or a three-way valve may be combined to form the refrigerant flow switching device 28.
  • the opening degree of the fourth electronic expansion valve 29 is controlled by the control device 30, and the refrigerant flow rate is adjusted while the pressure of the refrigerant is reduced.
  • the fourth electronic expansion valve 29 is provided between the outdoor heat exchanger 5 and the supercooling heat exchanger 22.
  • the compressor 3, the refrigerant flow switching device 28, the outdoor heat exchanger 5, the fourth electronic expansion valve 29, the supercooling heat exchanger 22, and the indoor heat exchanger 8 are connected to the discharge pipe 3a,
  • the main refrigerant circuit is configured by being connected by the main refrigerant pipe 31 including the branch pipe 25, the liquid pipe 7 and the gas pipe 9. That is, the branch pipe 25 constitutes a part of the main refrigerant pipe 31.
  • the outdoor heat exchanger 5, the fourth electronic expansion valve 29, the primary side of the supercooling heat exchanger 22 (the refrigerant side flowing through the branch pipe 25), the second electronic expansion valve 23, and the indoor heat exchanger 8 are
  • the branch circuit is configured by being connected by the branch pipe 25 and the main refrigerant pipe 31.
  • the outdoor unit 1 is branched from the branch pipe 25 between the supercooling heat exchanger 22 and the second electronic expansion valve 23, and is sucked into the compressor 3. It has an injection pipe 26 connected to the side.
  • the injection circuit is configured by connecting the third electronic expansion valve 24, the secondary side of the supercooling heat exchanger (the refrigerant side flowing through the injection pipe 26), and the suction side of the compressor 3 through the injection pipe 26.
  • FIG. 6 illustrates a control pattern of each actuator (here, the second electronic expansion valve 23, the third electronic expansion valve 24, and the fourth electronic expansion valve 29) corresponding to the operation mode executed by the refrigeration cycle apparatus 100C. It is explanatory drawing of. Based on FIG.5 and FIG.6, operation
  • the refrigeration cycle apparatus 100C determines the use of the supercooling heat exchanger 22 according to the outside air temperature.
  • the definitions of the normal operation mode and the high outside air operation mode are the same as in the first embodiment.
  • the operation mode when the refrigerant flow is reversed by the operation of the refrigerant flow switching device 28 is referred to as a “heating operation mode”.
  • ⁇ Normal operation mode> In the normal operation mode, as shown in FIG. 6, the second electronic expansion valve 23 is controlled to be fully open and the third electronic expansion valve 24 is fully closed, and the temperature of the refrigerant discharged from the compressor 3 is controlled by the fourth electronic expansion valve 29. Is to control. That is, during normal outdoor air, the refrigeration cycle apparatus 100C suppresses a decrease in the dryness of the inlet of the indoor heat exchanger 8 that functions as an evaporator, and suppresses an increase in the amount of refrigerant necessary for the indoor heat exchanger 8. Then, the supercooling heat exchanger 22 is bypassed.
  • the refrigerant flows through the supercooling heat exchanger 22, but since the refrigerant does not flow through the injection pipe 26, heat exchange between the refrigerants is not performed. Therefore, also in this case, it is expressed that the supercooling heat exchanger 22 is bypassed.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 3 flows into the outdoor heat exchanger 5 acting as a condenser, and dissipates heat to the outdoor air blown by the outdoor blower 5a.
  • This refrigerant flows into the fourth electronic expansion valve 29.
  • the pressure is reduced by the fourth electronic expansion valve 29 to become a low-pressure two-phase refrigerant, and the indoor air is cooled by the indoor heat exchanger 8 acting as an evaporator to become a low-pressure gas refrigerant.
  • the gas is again sucked into the compressor 3 through the gas pipe 9.
  • ⁇ High outdoor air operation mode> In the high outside air operation mode, as shown in FIG. 6, the temperature of the refrigerant discharged from the compressor 3 is controlled by the second electronic expansion valve 23, and the refrigerant at the outlet of the supercooling heat exchanger 22 is controlled by the third electronic expansion valve 24. The degree of supercooling (SC) is controlled, and the fourth electronic expansion valve 29 is controlled to be fully opened. That is, at the time of high outside air, the refrigeration cycle apparatus 100C causes the refrigerant to flow through the branch circuit and uses the supercooling heat exchanger 22 to lower the inlet dryness of the indoor heat exchanger 8 that functions as an evaporator. By holding a large amount of refrigerant in the indoor heat exchanger 8, an increase in the high pressure of the refrigerant discharged from the compressor 3 is suppressed.
  • the refrigeration cycle apparatus 100C injects the refrigerant in the injection circuit that has passed through the supercooling heat exchanger 22 to the suction side of the compressor 3, and the discharge temperature of the refrigerant discharged from the compressor 3 The rise is suppressed.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 3 flows into the outdoor heat exchanger 5 acting as a condenser, and dissipates heat to the outdoor air blown by the outdoor blower 5a.
  • This refrigerant flows into the supercooling heat exchanger 22 through the fourth electronic expansion valve 29.
  • This refrigerant is cooled by the low-pressure refrigerant in the supercooling heat exchanger 22 and then depressurized by the second electronic expansion valve 23 to become a low-pressure two-phase refrigerant.
  • the indoor heat exchanger 8 acting as an evaporator the indoor air Is cooled to become a low-pressure gas refrigerant. Thereafter, the gas is again sucked into the compressor 3 through the gas pipe 9.
  • the refrigerant that has flowed into the injection pipe 26 is heated by the high-pressure refrigerant in the supercooling heat exchanger 22 after being depressurized by the third electronic expansion valve 24.
  • This refrigerant is injected into the suction side of the compressor 3 and merges with the refrigerant flowing through the gas pipe 9. Thereafter, the gas is again sucked into the compressor 3 through the gas pipe 9.
  • ⁇ Heating operation mode> In the heating operation mode, as shown in FIG. 6, the temperature of the refrigerant discharged from the compressor 3 is controlled by the fourth electronic expansion valve 29, and the refrigerant at the outlet of the supercooling heat exchanger 22 is controlled by the third electronic expansion valve 24. The degree of supercooling (SC) is controlled, and the second electronic expansion valve 23 is controlled to be fully opened. That is, in the heating operation mode, the refrigeration cycle apparatus 100C uses the supercooling heat exchanger 22 to lower the inlet dryness of the indoor heat exchanger 8 that functions as an evaporator, and the indoor heat exchanger 8 By holding a large amount of refrigerant, the increase in the high pressure of the refrigerant discharged from the compressor 3 is suppressed.
  • SC degree of supercooling
  • the refrigeration cycle apparatus 100C injects the refrigerant that has passed through the supercooling heat exchanger 22 into the suction side of the compressor 3 to increase the discharge temperature of the refrigerant discharged from the compressor 3. Suppressed.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 3 flows into the indoor heat exchanger 8 acting as a condenser via the refrigerant flow switching device 28 and dissipates heat to the outdoor air blown by the indoor blower 8a.
  • This refrigerant flows into the supercooling heat exchanger 22 via the second electronic expansion valve 23.
  • This refrigerant is cooled by the low-pressure refrigerant in the supercooling heat exchanger 22 and then reduced in pressure by the fourth electronic expansion valve 29 to become a low-pressure two-phase refrigerant.
  • the outdoor heat exchanger 5 acting as an evaporator the outdoor air Is cooled to become a low-pressure gas refrigerant. Thereafter, the gas is again sucked into the compressor 3 through the gas pipe 9.
  • the refrigerant that has flowed into the injection pipe 26 is heated by the high-pressure refrigerant in the supercooling heat exchanger 22 after being depressurized by the third electronic expansion valve 24.
  • This refrigerant is injected into the suction side of the compressor 3 and merges with the refrigerant flowing through the gas pipe 9. Thereafter, the gas is again sucked into the compressor 3 through the gas pipe 9.
  • refrigeration cycle apparatus 100C like refrigeration cycle apparatus 100A according to Embodiment 1, suppresses an increase in the amount of refrigerant charged, suppresses an increase in discharge temperature, and performs indoor heat exchange that functions as an evaporator. It is possible to suppress the increase in the condensation pressure due to the decrease in the dryness of the refrigerant at the inlet of the vessel 8. Therefore, according to the refrigeration cycle apparatus 100C, safety is taken into consideration even when refrigerant leaks by suppressing an increase in the amount of charged refrigerant, the effect on global warming can be reduced, and refrigerant can be reduced by suppressing an increase in discharge temperature. It is possible to continue high-efficiency operation without degeneration.
  • the refrigeration cycle apparatus 100C compared with the refrigeration cycle apparatus 100A according to Embodiment 1, it is possible to suppress an increase in discharge temperature due to injection of the refrigerant that has passed through the supercooling heat exchanger 22 in the heating operation mode. become. Furthermore, according to the refrigeration cycle apparatus 100C, the two-phase refrigerant of the liquid pipe 7 can be realized even in the heating operation mode, which contributes to the reduction of the charged refrigerant amount.
  • the refrigeration cycle apparatus described in each embodiment is applied to an apparatus equipped with a refrigeration cycle, such as an air conditioner (for example, a refrigeration apparatus, a room air conditioner, a packaged air conditioner, a multi air conditioner for buildings), a heat pump water heater, and the like. Can be used.
  • a refrigeration cycle such as an air conditioner (for example, a refrigeration apparatus, a room air conditioner, a packaged air conditioner, a multi air conditioner for buildings), a heat pump water heater, and the like. Can be used.

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

Abstract

L'invention concerne un dispositif à cycle de réfrigération (100A) dans lequel, lorsqu'une température extérieure élevée est supérieure à la température extérieure normale, un fluide frigorigène circule dans un circuit de dérivation et un circuit d'injection, un échangeur de chaleur à sous-refroidissement (22) est utilisé, et le fluide frigorigène qui s'est écoulé par un côté secondaire de l'échangeur de chaleur à sous-refroidissement (22) est injecté dans un compresseur (3).
PCT/JP2014/056024 2014-03-07 2014-03-07 Dispositif à cycle de réfrigération Ceased WO2015132967A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
PCT/JP2014/056024 WO2015132967A1 (fr) 2014-03-07 2014-03-07 Dispositif à cycle de réfrigération
EP15759078.7A EP3121539B1 (fr) 2014-03-07 2015-02-27 Dispositif à cycle de réfrigération
PCT/JP2015/055855 WO2015133398A1 (fr) 2014-03-07 2015-02-27 Dispositif à cycle de réfrigération
JP2016506459A JP6188916B2 (ja) 2014-03-07 2015-02-27 冷凍サイクル装置

Applications Claiming Priority (1)

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PCT/JP2014/056024 WO2015132967A1 (fr) 2014-03-07 2014-03-07 Dispositif à cycle de réfrigération

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CN109442835A (zh) * 2018-10-17 2019-03-08 广东也节能科技有限公司 一种液化天然气冷能回收利用系统

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EP3121539B1 (fr) 2018-12-19
EP3121539A1 (fr) 2017-01-25
EP3121539A4 (fr) 2017-12-27
WO2015133398A1 (fr) 2015-09-11
JP6188916B2 (ja) 2017-08-30

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