EP3121539B1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

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Publication number
EP3121539B1
EP3121539B1 EP15759078.7A EP15759078A EP3121539B1 EP 3121539 B1 EP3121539 B1 EP 3121539B1 EP 15759078 A EP15759078 A EP 15759078A EP 3121539 B1 EP3121539 B1 EP 3121539B1
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EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
expansion valve
refrigeration cycle
compressor
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.)
Active
Application number
EP15759078.7A
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German (de)
English (en)
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EP3121539A4 (fr
EP3121539A1 (fr
Inventor
Kensaku HATANAKA
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP3121539A4 publication Critical patent/EP3121539A4/fr
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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-conditioning apparatus, and more particularly, to a refrigeration cycle apparatus configured to suppress an increase in temperature of refrigerant discharged from a compressor while suppressing an increase in an amount of filled refrigerant.
  • R410A has a property in which a global warming potential (hereinafter referred to as "GWP") is high while an ozone depletion potential (hereinafter referred to as "ODP”) is zero and does not deplete the ozone layer unlike an "HCFC refrigerant", e.g., R22 that has been used up to now.
  • GWP global warming potential
  • ODP ozone depletion potential
  • HFC refrigerant that does not have a carbon-carbon double bond in its composition
  • R32 CH 2 F 2 ; difluoromethane
  • a halogenated hydrocarbon which is one type of HFC refrigerant similar to R32 and has a carbon-carbon double bond in its composition.
  • HFC refrigerant having a carbon-carbon double bond in its composition is expressed as an "HFO refrigerant" in many cases through use of "O" standing for olefin (unsaturated hydrocarbon having a carbon-carbon double bond is called “olefin”).
  • HFC refrigerant and HFO refrigerant are not as highly combustible as HC refrigerants, e.g., R290 (C 3 H 8 ; propane) that is a natural refrigerant, those refrigerants are slightly combustible unlike R410A that is non-combustible.
  • refrigerant that is even slightly combustible is referred to as "combustible refrigerant”.
  • a refrigeration apparatus using an R32 refrigerant or a mixed refrigerant whose proportion of R32 is 70% or more which is configured to calculate a target discharge temperature based on a condensing temperature, an evaporating temperature, and an opening degree of a subcooling expansion valve, and control an opening degree of a main expansion value such that the target discharge temperature is reached (see, for example, Patent Literature 1).
  • Patent Literature 1 While the increase in the temperature of refrigerant discharged from the compressor can be suppressed, the subcooling heat exchanger is used irrespective of an operation condition.
  • the amount of filled refrigerant disadvantageously increases due to an increase in a capacity of a heat exchanger installed at the outlet of the condenser and a decrease in a quality at an inlet of the evaporator. Therefore, when the refrigerant leaks, the leakage of refrigerant not only causes a safety problem, but also disadvantageously contributes to the global warming.
  • Patent Literature 2 in a cooling operation under a state in which an outside-air temperature and a load are high, the increase in the refrigerant discharge temperature of the compressor can be suppressed, but the quality at the inlet of the evaporator cannot be reduced. As a result, the refrigerant cannot be held in the evaporator, and a condensing pressure increases. Thus, the property of the refrigerant may change due to the increase in the condensing pressure. When the property of the refrigerant changes, proper performance of the refrigerant can no longer be exerted.
  • US 2006/0123840 A1 discloses a refrigeration cycle apparatus comprising a main refrigerant circuit formed by connecting a compressor, a first heat exchanger, a first expansion valve, and a second heat exchanger; a branch circuit and an injection circuit, the refrigeration cycle apparatus being operable in a normal operation mode of causing the refrigerant to flow through the main refrigerant circuit; and a high-outside-air-temperature operation mode of causing the refrigerant to flow through the branch circuit and the injection circuit to use the subcooling heat exchanger, and of injecting the refrigerant having flowed through the secondary side of the subcooling heat exchanger into the compressor, the refrigeration cycle apparatus being configured to perform the high-outside-air-temperature operation mode when an outside-air temperature is equal to or higher than a predetermined temperature.
  • the present invention has been made in order to overcome the above-mentioned problems, and it is an object of the present invention to provide a refrigeration cycle apparatus capable of suppressing an increase in refrigerant discharge temperature of a compressor while suppressing an increase in an amount of filled refrigerant.
  • a refrigeration cycle apparatus including: a main refrigerant circuit formed by connecting a compressor, a first heat exchanger, a first expansion valve, and a second heat exchanger; a branch circuit formed by connecting the first heat exchanger, a primary side of a subcooling heat exchanger installed on a downstream side of refrigerant flow in a case where the first heat exchanger serves as a condenser, a second expansion valve, and the second heat exchanger; and an injection circuit formed by connecting, with an injection pipe branching from a downstream side of the primary side of the subcooling heat exchanger, a third expansion valve, a secondary side of the subcooling heat exchanger, and the compressor, the refrigeration cycle apparatus being operable in a normal operation mode of causing the refrigerant to flow through the main refrigerant circuit; and a high-outside-air-temperature operation mode of causing the refrigerant to flow through the branch circuit and the injection circuit to use the subcooling heat exchanger, and of inject
  • the increase in the amount of filled refrigerant can be suppressed by suppressing a decrease in a quality at the inlet of the second heat exchanger serving as the evaporator in a predetermined normal operation. Further, the discharge temperature and the increase in the condensing pressure can be suppressed by injecting the refrigerant into the compressor during the high-outside-air-temperature cooling operation.
  • Fig. 1 is a refrigerant circuit configuration diagram for schematically illustrating 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. Referring to Fig. 1 , the refrigeration cycle apparatus 100A is described.
  • 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 to each other with a liquid pipe 7 and a gas pipe 9.
  • the number of the connected outdoor units 1 and the number of the connected indoor units 2 are not limited to one, and any one or both of the numbers may be two or more.
  • the outdoor unit (heat source apparatus) 1 includes a compressor 3 configured to compress refrigerant, an outdoor heat exchanger (first heat exchanger) 5 configured to exchange heat between the refrigerant and ambient air of the outdoor unit 1 sent by an outdoor blower device 5a, a first electronic expansion valve (first expansion valve) 6 configured to control a flow rate of the refrigerant, an opening-closing valve 21 configured to control a flow of the refrigerant, a subcooling heat exchanger 22 configured to exchange heat between refrigerant and refrigerant, a second electronic expansion valve (second expansion valve) 23 configured to control a flow rate of the refrigerant, and a third electronic expansion valve (third expansion valve) 24 configured to control a flow rate of the refrigerant.
  • a compressor 3 configured to compress refrigerant
  • an outdoor heat exchanger (first heat exchanger) 5 configured to exchange heat between the refrigerant and ambient air of the outdoor unit 1 sent by an outdoor blower device 5a
  • the outdoor heat exchanger 5 includes the outdoor blower device 5a configured to supply air and an outside-air temperature sensor T 1 configured to detect an outside-air temperature.
  • a discharge temperature sensor T 2 configured to detect a temperature of the refrigerant discharged from the compressor 3
  • a discharge pressure sensor P 1 configured to detect a pressure of the refrigerant discharged from the compressor 3.
  • a refrigerant temperature sensor T 3 configured to detect a temperature of the refrigerant that has passed through the subcooling heat exchanger 22.
  • the indoor unit (use-side device) 2 includes an indoor heat exchanger (second heat exchanger) 8 configured to exchange heat between the refrigerant and ambient air of the indoor unit 2 conveyed by an indoor blower device 8a to, for example, cool or heat an indoor space, to thereby implement cooling or heating.
  • the indoor heat exchanger 8 includes the indoor blower device 8a configured to supply air.
  • a positive-displacement compressor which is a type of compressor having a rotation speed and an operation capacity controlled by an inverter circuit.
  • Examples of the positive-displacement compressor include a rotary compressor, a scroll compressor, a screw compressor, and a reciprocating compressor.
  • a discharge pipe 3a is connected to the compressor 3.
  • the outdoor heat exchanger 5 serves as a condenser or an evaporator.
  • the outdoor heat exchanger 5 can be constructed with, for example, a cross fin-type fin- and-tube heat exchanger including heat transmission tubes and a large number of fins.
  • the outdoor blower device 5a is configured to supply the air to the outdoor heat exchanger 5.
  • the outdoor blower device 5a is constructed with a device capable of changing a flow rate of the air.
  • a centrifugal fan or a multiblade fan to be driven by a motor e.g., a DC fan motor, can be used.
  • the first electronic expansion valve 6 is configured to have an opening degree controlled by a controller 30 described later, and is configured to, for example, control the flow rate of the refrigerant while reducing the pressure of the refrigerant.
  • the indoor heat exchanger 8 functions as an evaporator or a condenser.
  • the indoor heat exchanger 8 can be constructed with, for example, a cross fin-type fin- and-tube heat exchanger including heat transmission tubes and a large number of fins.
  • the indoor blower device 8a is configured to supply the air to the indoor heat exchanger 8.
  • the indoor blower device 8a is constructed with a device capable of changing a flow rate of the air.
  • a centrifugal fan or a multiblade fan to be driven by a motor e.g., a DC fan motor, can be used.
  • the compressor 3, the outdoor heat exchanger 5, the first electronic expansion valve 6, and the indoor heat exchanger 8 form a main refrigerant circuit by being connected to one another with a main refrigerant pipe 31 including the discharge pipe 3a, the liquid pipe 7, and the gas pipe 9.
  • the outdoor unit 1 further includes a branch pipe 25, which branches from a portion of the main refrigerant pipe 31 between the outdoor heat exchanger 5 and the first electronic expansion valve 6 and is connected to a portion between the first electronic expansion valve 6 and the indoor heat exchanger 8.
  • the outdoor heat exchanger 5, a primary side of the subcooling heat exchanger 22 (side of the refrigerant flowing through the branch pipe 25), the second electronic expansion valve 23, and the indoor heat exchanger 8 form a branch circuit by being connected to one another with the branch pipe 25 and the main refrigerant pipe 31.
  • the outdoor unit 1 further includes an injection pipe 26, which branches from a portion of the branch pipe 25 between the subcooling heat exchanger 22 and the second electronic expansion valve 23 and is connected to a suction side of the compressor 3.
  • the third electronic expansion valve 24, a secondary side of the subcooling heat exchanger 22 (side of the refrigerant flowing through the injection pipe 26), and the suction side of the compressor 3 form an injection circuit by being connected to one another with the injection pipe 26.
  • the opening-closing valve 21 is arranged on the branch pipe 25 between the outdoor heat exchanger 5 and the subcooling heat exchanger 22, and is configured to open and close the branch pipe 25. Opening and closing of the opening-closing valve 21 is controlled by the controller 30 described later.
  • the subcooling heat exchanger 22 is configured to exchange heat between the refrigerant flowing through the branch pipe 25 and the refrigerant flowing through the injection pipe 26. It is preferred that the subcooling heat exchanger 22 be constructed with, for example, a microchannel heat exchanger, a shell and tube heat exchanger, a heat pipe heat exchanger, a double pipe heat exchanger, or a plate heat exchanger.
  • the second electronic expansion valve 23 is arranged on the branch pipe 25 on a downstream side of the subcooling heat exchanger 22.
  • the second electronic expansion valve 23 has an opening degree controlled by the controller 30 described later, and is capable of, for example, controlling the flow rate of the refrigerant while reducing the pressure of the refrigerant flowing through the branch pipe 25.
  • the third electronic expansion valve 24 is arranged on the injection pipe 26 on an upstream side of the subcooling heat exchanger 22.
  • the third electronic expansion valve 24 has an opening degree controlled by the controller 30 described later, and is capable of, for example, controlling the flow rate of the refrigerant while reducing the pressure of the refrigerant flowing through the injection pipe 26.
  • the refrigeration cycle apparatus 100A includes the controller 30 configured to generally control the refrigeration cycle apparatus 100A.
  • the controller 30 is configured to perform operation modes by controlling actuators (parts to be driven, including the compressor 3, the outdoor blower device 5a, the first electronic expansion valve 6, the opening-closing valve 21, the second electronic expansion valve 23, the third electronic expansion valve 24, and the indoor blower device 8a) based on detection values obtained by detectors including the outside-air temperature sensor T 1 , the discharge pressure sensor P 1 , the discharge temperature sensor T 2 , and the refrigerant temperature sensor T 3 .
  • the controller 30 can be constructed with hardware, e.g., a circuit device, for implementing its functions, or can be constructed with an arithmetic device, e.g., a microcontroller or a CPU, and software to be executed on the arithmetic device.
  • hardware e.g., a circuit device
  • arithmetic device e.g., a microcontroller or a CPU
  • Parts of the liquid pipe 7 connecting the outdoor unit 1 and the indoor unit 2 to each other are connected to each other via a liquid-side stop valve 32.
  • parts of the gas pipe 9 connecting the outdoor unit 1 and the indoor unit 2 to each other are connected to each other via a gas-side stop valve 33.
  • the outdoor unit 1 and the indoor unit 2 can be separated from each other via the liquid-side stop valve 32 and the gas-side stop valve 33.
  • Fig. 2 is an explanatory table for showing patterns of control by the controller 30 on actuators (in this case, the opening-closing valve 21, the first electronic expansion valve 6, the second electronic expansion valve 23, and the third electronic expansion valve 24) corresponding to operation modes executed by the refrigeration cycle apparatus 100A. Referring to Fig. 1 and Fig. 2 , the operation of the refrigeration cycle apparatus 100A is described.
  • the refrigeration cycle apparatus 100A is configured to determine whether or not to use the subcooling heat exchanger 22 depending on the outside-air temperature detected by the outside-air temperature sensor T 1 .
  • normal operation mode an operation mode at the time when the subcooling heat exchanger 22 is not used at a normal outside-air temperature
  • high-outside-air-temperature operation mode an operation mode at the time when the subcooling heat exchanger 22 is used at a high outside-air temperature
  • the opening-closing valve 21 is controlled to be closed, the second electronic expansion valve 23 is controlled to be fully opened, and the third electronic expansion valve 24 is controlled to be fully closed.
  • the first electronic expansion valve 6 controls the refrigerant discharge temperature of the compressor 3.
  • the refrigeration cycle apparatus 100A bypasses the refrigerant through the subcooling heat exchanger 22 in order to suppress a decrease in a quality at an inlet of the indoor heat exchanger 8 functioning as the evaporator and suppress an increase in an amount of refrigerant required for the indoor heat exchanger 8.
  • a high-temperature and high-pressure gas refrigerant discharged from the compressor 3 flows into the outdoor heat exchanger 5 serving as the condenser, and transfers its heat to outdoor air conveyed by the outdoor blower device 5a.
  • This refrigerant has its pressure reduced by the first electronic expansion valve 6 to turn into a low-pressure two-phase refrigerant, and the low-pressure two-phase refrigerant then cools indoor air in the indoor heat exchanger 8 serving as the evaporator to turn into a low-pressure gas refrigerant. After that, the low-pressure gas refrigerant passes through the gas pipe 9 to be sucked into the compressor 3 again.
  • the opening-closing valve 21 is controlled to be opened, and the first electronic expansion valve 6 is controlled to be fully closed. Further, based on the detection result obtained by the discharge temperature sensor T 2 , the second electronic expansion valve 23 controls the temperature of the refrigerant discharged from the compressor 3, and the third electronic expansion valve 24 controls a degree of subcooling (SC) of the refrigerant at an outlet of the subcooling heat exchanger 22.
  • SC subcooling
  • the refrigeration cycle apparatus 100A causes the refrigerant to flow into the branch circuit, uses the subcooling heat exchanger 22 to keep the quality at the inlet of the indoor heat exchanger 8 serving as the evaporator at a low level, and causes the indoor heat exchanger 8 to hold a large amount of refrigerant, to thereby suppress an increase in the high pressure of the refrigerant discharged from the compressor 3.
  • the refrigeration cycle apparatus 100A injects the refrigerant that has passed through the subcooling heat exchanger 22 into the suction side of the compressor 3, to thereby suppress the increase in the refrigerant discharge temperature from the compressor 3.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 3 flows into the outdoor heat exchanger 5 serving as the condenser, and transfers its heat to the outdoor air conveyed by the outdoor blower device 5a.
  • This refrigerant flows into the subcooling heat exchanger 22 via the opening-closing valve 21.
  • This refrigerant is cooled by a low-pressure refrigerant in the subcooling heat exchanger 22, and then has its pressure reduced by the second electronic expansion valve 23 to turn into the low-pressure two-phase refrigerant.
  • the low-pressure two-phase refrigerant cools the indoor air in the indoor heat exchanger 8 functioning as the evaporator to turn into the low-pressure gas refrigerant. After that, the low-pressure gas refrigerant passes through the gas pipe 9 to be sucked into the compressor 3 again.
  • the refrigerant of the injection circuit having flowed into the injection pipe 26 has its pressure reduced by the third electronic expansion valve 24, and is then heated by a high-pressure refrigerant in the subcooling heat exchanger 22.
  • This refrigerant is injected into the suction side of the compressor 3, and merges with the refrigerant having flowed through the gas pipe 9. After that, the refrigerant passes through the gas pipe 9 to be sucked into the compressor 3 again.
  • the degree of subcooling (SC) of the refrigerant at the outlet of the subcooling heat exchanger 22 can be calculated based on a difference between a high-pressure-side saturation temperature of the refrigerant and the temperature of the refrigerant that has passed through the subcooling heat exchanger 22.
  • the high-pressure-side saturation temperature of the refrigerant is obtained based on the pressure of the refrigerant discharged from the compressor 3, which is detected by the discharge pressure sensor P 1 .
  • the temperature of the refrigerant that has passed through the subcooling heat exchanger 22 is detected by the refrigerant temperature sensor T 3 .
  • An amount of refrigerant to be filled into a refrigerant circuit is defined at the normal outside-air temperature. Therefore, the refrigeration cycle apparatus 100A executes the normal operation mode to bypass the refrigerant through the subcooling heat exchanger 22 and to keep the quality of the refrigerant at a high level at the inlet of the indoor heat exchanger 8 functioning as the evaporator, to thereby suppress the increase in the amount of filled refrigerant. Meanwhile, however, because the increase in the amount of filled refrigerant is suppressed, at the high outside-air temperature, the high pressure may disadvantageously increase.
  • the refrigeration cycle apparatus 100A executes the high-outside-air-temperature operation mode to keep the quality of the refrigerant at a low level at the inlet of the indoor heat exchanger 8 serving as the evaporator, through use of the subcooling heat exchanger 22 and to cause the indoor heat exchanger 8 to hold a large amount of refrigerant, to thereby enable suppression of the increase in the high pressure.
  • the refrigeration cycle apparatus 100A executes the high-outside-air-temperature operation mode to inject the refrigerant that has passed through the subcooling heat exchanger 22 into the suction side of the compressor 3, to thereby enable suppression of the increase in the discharge temperature of the refrigerant discharged from the compressor 3.
  • the refrigeration cycle apparatus 100A is configured to determine whether or not to use the subcooling heat exchanger 22 depending on whether the outside-air temperature is the high outside-air temperature. Therefore, with the refrigeration cycle apparatus 100A, the amount of refrigerant to be filled into the refrigerant circuit is determined based on the normal operation mode, to thereby suppress the increase in the amount of filled refrigerant. Further, with the refrigeration cycle apparatus 100A, the subcooling heat exchanger 22 is used as the need arises, and hence when the subcooling heat exchanger 22 is not used, the amount of filled refrigerant can be reduced without causing a decrease in a pressure on the high-pressure side of the subcooling heat exchanger 22.
  • the refrigeration cycle apparatus 100A is assumed to use the combustible refrigerant as the main component, and hence safety can be taken into consideration even if the refrigerant leaks by suppressing the increase in the amount of filled refrigerant, and the influence on global warming can be reduced.
  • the refrigeration cycle apparatus 100A executes the high-outside-air-temperature operation mode to achieve, through use of the subcooling heat exchanger 22 and the injection pipe 26, suppression of the increase in the discharge temperature and suppression of the increase in the condensing pressure due to the decrease in the quality of the refrigerant at the inlet of the indoor heat exchanger 8 serving as the evaporator. Therefore, the refrigeration cycle apparatus 100A can continue a highly efficient operation even at the high outside-air temperature.
  • the refrigeration cycle apparatus 100A is assumed to use the refrigerant that is the combustible refrigerant as the main component, but the refrigerant to be used in the refrigeration cycle apparatus 100A is not limited thereto.
  • the combustible refrigerant there are known, for example, R32, HFO-1234yf, HFO-1234ze, R290 (C 3 H 8 ; propane), and R1270 (C3H6; propylene).
  • combustible refrigerant as the main component
  • a contained amount of another refrigerant which may be a plurality of types of refrigerants
  • a contained amount of the combustible refrigerant in terms of mass% including a case where one of the combustible refrigerants exemplified above is used alone.
  • a circuit in which the injection pipe 26 is connected to the suction side of the compressor 3 is given as an example, but the injection pipe 26 may be connected to an intermediate port communicating to an intermediate pressure portion of the compressor 3.
  • the refrigeration cycle apparatus 100A can suppress the increase in the discharge temperature while suppressing the increase in the amount of filled refrigerant. Therefore, safety can be taken into consideration even for the case where the refrigerant leaks, with the refrigeration cycle apparatus 100A that can suppress the increase in the amount of filled refrigerant. Further, the influence on global warming can be reduced. Still further, a highly efficient operation can be continued without causing a change in the property of the refrigerant by suppressing the increase in the discharge temperature.
  • Fig. 3 is a refrigerant circuit configuration diagram for schematically illustrating 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 is described.
  • Embodiment 2 differences from Embodiment 1 are mainly described.
  • the same components as those of Embodiment 1 are denoted by the same reference numerals, and a description thereof is omitted.
  • the refrigeration cycle apparatus 100B is assumed to use the combustible refrigerant as the 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. Further, the refrigeration cycle apparatus 100B is different from the refrigeration cycle apparatus 100A according to Embodiment 1 in the configurations of the main refrigerant pipe 31 and the branch pipe 25.
  • the outdoor unit (heat source apparatus) 1 includes the compressor 3, the outdoor heat exchanger 5, a three-way valve 27, the subcooling heat exchanger 22, the second electronic expansion valve 23, and the third electronic expansion valve 24.
  • the refrigeration cycle apparatus 100B includes the three-way valve 27 instead of including the first electronic expansion valve 6 and the opening-closing valve 21 included in the outdoor unit 1 of the refrigeration cycle apparatus 100A according to Embodiment 1. 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 switching device, and is arranged on a downstream side of the outdoor heat exchanger 5.
  • the three-way valve is configured to, under the control of the controller 30, switch a refrigerant passage to any one of the main refrigerant pipe 31 (main refrigerant circuit) and the branch pipe 25 (branch circuit).
  • the following description discusses a case where the flow switching device is the three-way valve 27 as an example, but the flow switching device is not limited to the three-way valve 27.
  • the flow switching device only needs to be a device capable of switching the refrigerant passage.
  • the flow switching device may be constructed by using two-way valves in combination, or may be constructed by blocking one passage of a four-way valve.
  • 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 form the main refrigerant circuit by being connected to one another with the main refrigerant pipe 31 including the discharge pipe 3a, the liquid pipe 7, and the gas pipe 9.
  • the branch pipe 25 branches from the main refrigerant pipe 31 via the three-way valve 27 and passes through the subcooling heat exchanger 22.
  • the branch pipe 25 is then connected to a portion 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 subcooling heat exchanger 22 (side of the refrigerant flowing through the branch pipe 25), the second electronic expansion valve 23, and the indoor heat exchanger 8 form the branch circuit by being connected to one another with the branch pipe 25 and the main refrigerant pipe 31.
  • the outdoor unit 1 includes the injection pipe 26, which branches from the portion of the branch pipe 25 between the subcooling heat exchanger 22 and the second electronic expansion valve 23 and is connected to the suction side of the compressor 3.
  • the third electronic expansion valve 24, the secondary side of the subcooling heat exchanger 22 (side of the refrigerant flowing through the injection pipe 26), and the suction side of the compressor 3 form the injection circuit by being connected to one another with the injection pipe 26.
  • Fig. 4 is an explanatory table for showing patterns of control by the controller 30 on actuators (in this case, the three-way valve 27, the second electronic expansion valve 23, and the third electronic expansion valve 24) corresponding to the operation modes executed by the refrigeration cycle apparatus 100B. Referring to Fig. 3 and Fig. 4 , the operation of the refrigeration cycle apparatus 100B is described.
  • the refrigeration cycle apparatus 100B is configured to determine whether or not to use the subcooling heat exchanger 22 depending on the outside-air temperature detected by the outside-air temperature sensor T 1 .
  • Definitions of the normal operation mode and the high-outside-air-temperature operation mode are the same as those of Embodiment 1.
  • the three-way valve 27 is controlled to be switched such that the outdoor heat exchanger 5 and the second electronic expansion valve 23 communicate to each other.
  • the third electronic expansion valve 24 is controlled to be fully closed, and based on the detection result obtained by the discharge temperature sensor T 2 , the second electronic expansion valve 23 controls the temperature of the refrigerant discharged from the compressor 3.
  • the refrigeration cycle apparatus 100B bypasses the refrigerant through the subcooling heat exchanger 22 in order to suppress the decrease in the quality at the inlet of the indoor heat exchanger 8 functioning as the evaporator and suppress the increase in the amount of refrigerant required for the indoor heat exchanger 8.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 3 flows into the outdoor heat exchanger 5 operating as the condenser, and transfers its heat to the outdoor air sent by the outdoor blower device 5a.
  • This refrigerant flows into the second electronic expansion valve 23 via the three-way valve 27.
  • the refrigerant then has its pressure reduced by the second electronic expansion valve 23 to turn into the low-pressure two-phase refrigerant, and the low-pressure two-phase refrigerant then cools the indoor air in the indoor heat exchanger 8 operating as the evaporator to turn into the low-pressure gas refrigerant. After that, the low-pressure gas refrigerant passes through the gas pipe 9 to be sucked into the compressor 3 again.
  • the three-way valve 27 is controlled to be switched such that the outdoor heat exchanger 5 and the subcooling heat exchanger 22 communicate to each other, and based on the detection result obtained by the discharge temperature sensor T 2 , the second electronic expansion valve 23 controls the temperature of the refrigerant discharged from the compressor 3. Further, under the control of the controller 30, the third electronic expansion valve 24 controls the degree of subcooling (SC) of the refrigerant at the outlet of the subcooling heat exchanger 22.
  • SC subcooling
  • the refrigeration cycle apparatus 100B causes the refrigerant to flow into the branch circuit, uses the subcooling heat exchanger 22 to keep the quality at a low level at the inlet of the indoor heat exchanger 8 functioning as the evaporator, and causes the indoor heat exchanger 8 to hold a large amount of refrigerant, to thereby suppress the increase in the high pressure of the refrigerant discharged from the compressor 3.
  • the refrigeration cycle apparatus 100B injects the refrigerant of the injection circuit that has passed through the subcooling heat exchanger 22 into the suction side of the compressor 3, to thereby suppress the increase in the discharge temperature of the refrigerant discharged from the compressor 3.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 3 flows into the outdoor heat exchanger 5 operating as the condenser, and transfers its heat to the outdoor air sent by the outdoor blower device 5a.
  • This refrigerant flows into the subcooling heat exchanger 22 via the three-way valve 27.
  • This refrigerant is cooled by the low-pressure refrigerant in the subcooling heat exchanger 22, and then has its pressure reduced by the second electronic expansion valve 23 to turn into the low-pressure two-phase refrigerant.
  • the low-pressure two-phase refrigerant cools the indoor air in the indoor heat exchanger 8 operating as the evaporator to turn into the low-pressure gas refrigerant. After that, the low-pressure gas refrigerant passes through the gas pipe 9 to be sucked into the compressor 3 again.
  • the refrigerant having flowed into the injection pipe 26 has its pressure reduced by the third electronic expansion valve 24, and is then heated by the high-pressure refrigerant in the subcooling heat exchanger 22.
  • This refrigerant is injected into the suction side of the compressor 3, and merges with the refrigerant having flowed through the gas pipe 9. After that, the refrigerant passes through the gas pipe 9 to be sucked into the compressor 3 again.
  • the refrigeration cycle apparatus 100B can achieve suppression of the increase in the discharge temperature and suppression of the increase in the condensing pressure due to the decrease in the quality of the refrigerant at the inlet of the indoor heat exchanger 8 functioning as the evaporator while suppressing the increase in the amount of filled refrigerant. Therefore, with the refrigeration cycle apparatus 100B, safety can be taken into consideration even if the refrigerant leaks by suppressing the increase in the amount of filled refrigerant. Further, the influence on global warming can be reduced. Still further, a highly efficient operation can be continued without causing a change in the property of the refrigerant by suppressing the increase in the discharge temperature.
  • the number of valves can be made smaller than in the refrigeration cycle apparatus 100A according to Embodiment 1.
  • Fig. 5 is a refrigerant circuit configuration diagram for schematically illustrating 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 is described.
  • Embodiment 3 differences from Embodiments 1 and 2 are mainly described.
  • the same components as those of Embodiments 1 and 2 are denoted by the same reference numerals, and a description thereof is omitted.
  • the refrigeration cycle apparatus 100C is assumed to use the combustible refrigerant as the 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. Further, the refrigeration cycle apparatus 100C is different from the refrigeration cycle apparatus 100A according to Embodiment 1 in the configurations of the main refrigerant pipe 31 and the branch pipe 25.
  • the outdoor unit (heat source apparatus) 1 includes the compressor 3, a refrigerant flow switching device 28, the outdoor heat exchanger 5, a fourth electronic expansion valve (fourth expansion valve) 29, the subcooling heat exchanger 22, the second electronic expansion valve 23, and the third electronic expansion valve 24.
  • the refrigeration cycle apparatus 100C includes the refrigerant flow switching device 28 and the fourth electronic expansion valve 29 instead of including the first electronic expansion valve 6 and the opening-closing valve 21 included in the outdoor unit 1 of the refrigeration cycle apparatus 100A according to Embodiment 1. Therefore, the fourth electronic expansion valve 29 functions as the "first electronic expansion valve" of the present invention.
  • the branch pipe 25 does not branch from the main refrigerant pipe 31 included 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 refrigerant flow switching device 28 is arranged on the discharge side of the compressor 3, and is configured to switch the flow of the refrigerant under the control of the controller 30.
  • the refrigerant flow switching device 28 may be constructed with, for example, a four-way valve as illustrated in Fig. 5 .
  • the refrigerant flow switching device 28 is not limited to the four-way valve, and a two-way valve and a three-way valve may be used in combination to form the refrigerant flow switching device 28.
  • the fourth electronic expansion valve 29 has its opening degree controlled by the controller 30, and is configured to, for example, control the flow rate of the refrigerant while reducing the pressure of the refrigerant.
  • the fourth electronic expansion valve 29 is arranged between the outdoor heat exchanger 5 and the subcooling heat exchanger 22.
  • the compressor 3, the refrigerant flow switching device 28, the outdoor heat exchanger 5, the fourth electronic expansion valve 29, the subcooling heat exchanger 22, and the indoor heat exchanger 8 form the main refrigerant circuit by being connected to one another with the main refrigerant pipe 31 including the discharge pipe 3a, the branch pipe 25, the liquid pipe 7, and the gas pipe 9.
  • the branch pipe 25 forms a part of the main refrigerant pipe 31.
  • the outdoor heat exchanger 5, the fourth electronic expansion valve 29, the primary side of the subcooling heat exchanger 22 (side of the refrigerant flowing through the branch pipe 25), the second electronic expansion valve 23, and the indoor heat exchanger 8 form the branch circuit by being connected to one another with the branch pipe 25 and the main refrigerant pipe 31.
  • the outdoor unit 1 includes the injection pipe 26, which branches from the portion of the branch pipe 25 between the subcooling heat exchanger 22 and the second electronic expansion valve 23 and is connected to the suction side of the compressor 3.
  • the third electronic expansion valve 24, the secondary side of the subcooling heat exchanger 22 (side of the refrigerant flowing through the injection pipe 26), and the suction side of the compressor 3 form the injection circuit by being connected to one another with the injection pipe 26.
  • Fig. 6 is an explanatory table for showing patterns of control by the controller 30 on actuators (in this case, the second electronic expansion valve 23, the third electronic expansion valve 24, and the fourth electronic expansion valve 29) corresponding to the operation modes executed by the refrigeration cycle apparatus 100C. Referring to Fig. 5 and Fig. 6 , the operation of the refrigeration cycle apparatus 100C is described.
  • the refrigeration cycle apparatus 100C is configured to determine whether or not to use the subcooling heat exchanger 22 depending on the outside-air temperature detected by the outside-air temperature sensor T 1 .
  • Definitions of the normal operation mode and the high-outside-air-temperature operation mode are the same as those of Embodiment 1.
  • an operation mode at the time when the flow of the refrigerant is inverted through the operation of the refrigerant flow switching device 28 is referred to as "heating operation mode".
  • the second electronic expansion valve 23 is controlled to be fully opened
  • the third electronic expansion valve 24 is controlled to be fully closed
  • the fourth electronic expansion valve 29 controls the temperature of the refrigerant discharged from the compressor 3.
  • the refrigeration cycle apparatus 100C bypasses the refrigerant through the subcooling heat exchanger 22 in order to suppress the decrease in the quality at the inlet of the indoor heat exchanger 8 functioning as the evaporator and suppress the increase in the amount of refrigerant required for the indoor heat exchanger 8.
  • the refrigerant flows through the subcooling heat exchanger 22 but the refrigerant does not flow through the injection pipe 26, and hence heat is not exchanged between the refrigerant of the subcooling heat exchanger 22 and the refrigerant of the injection pipe 26. Therefore, this case is also expressed as "bypasses the refrigerant through the subcooling heat exchanger 22".
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 3 flows into the outdoor heat exchanger 5 operating as the condenser, and transfers its heat to the outdoor air sent by the outdoor blower device 5a.
  • This refrigerant flows into the fourth electronic expansion valve 29.
  • this refrigerant has its pressure reduced by the fourth electronic expansion valve 29 to turn into the low-pressure two-phase refrigerant, and the low-pressure two-phase refrigerant then cools the indoor air in the indoor heat exchanger 8 operating as the evaporator to turn into the low-pressure gas refrigerant.
  • the low-pressure gas refrigerant passes through the gas pipe 9 to be sucked into the compressor 3 again.
  • the second electronic expansion valve 23 controls the temperature of the refrigerant discharged from the compressor 3 based on the detection result obtained by the discharge temperature sensor T 2
  • the third electronic expansion valve 24 controls the degree of subcooling (SC) of the refrigerant at the outlet of the subcooling heat exchanger 22, and the fourth electronic expansion valve 29 is controlled to be fully opened.
  • the refrigeration cycle apparatus 100C causes the refrigerant to flow into the branch circuit, uses the subcooling heat exchanger 22 to keep the quality at a low level at the inlet of the indoor heat exchanger 8 functioning as the evaporator, and causes the indoor heat exchanger 8 to hold a large amount of refrigerant, to thereby suppress the increase in the high pressure of the refrigerant discharged from the compressor 3.
  • the refrigeration cycle apparatus 100C injects the refrigerant of the injection circuit that has passed through the subcooling heat exchanger 22 into the suction side of the compressor 3, to thereby suppress the increase in the discharge temperature of the refrigerant discharged from the compressor 3.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 3 flows into the outdoor heat exchanger 5 operating as the condenser, and transfers its heat to the outdoor air sent by the outdoor blower device 5a.
  • This refrigerant flows into the subcooling heat exchanger 22 via the fourth electronic expansion valve 29.
  • This refrigerant is cooled by the low-pressure refrigerant in the subcooling heat exchanger 22, and then has its pressure reduced by the second electronic expansion valve 23 to turn into the low-pressure two-phase refrigerant.
  • the low-pressure two-phase refrigerant cools the indoor air in the indoor heat exchanger 8 operating as the evaporator to turn into the low-pressure gas refrigerant. After that, the low-pressure gas refrigerant passes through the gas pipe 9 to be sucked into the compressor 3 again.
  • the refrigerant having flowed into the injection pipe 26 has its pressure reduced by the third electronic expansion valve 24, and is then heated by the high-pressure refrigerant in the subcooling heat exchanger 22.
  • This refrigerant is injected into the suction side of the compressor 3, and merges with the refrigerant having flowed through the gas pipe 9. After that, the refrigerant passes through the gas pipe 9 to be sucked into the compressor 3 again.
  • the fourth electronic expansion valve 29 controls the temperature of the refrigerant discharged from the compressor 3 based on the detection result obtained by the discharge temperature sensor T 2
  • the third electronic expansion valve 24 controls the degree of subcooling (SC) of the refrigerant at the outlet of the subcooling heat exchanger 22, and the second electronic expansion valve 23 is controlled to be fully opened.
  • the refrigeration cycle apparatus 100C uses the subcooling heat exchanger 22 to keep the quality at a low level at the inlet of the indoor heat exchanger 8 functioning as the evaporator, and causes the indoor heat exchanger 8 to hold a large amount of refrigerant, to thereby suppress the increase in the high pressure of the refrigerant discharged from the compressor 3.
  • the refrigeration cycle apparatus 100C injects the refrigerant that has passed through the subcooling heat exchanger 22 into the suction side of the compressor 3, to thereby suppress the increase in the discharge temperature of the refrigerant discharged from the compressor 3.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 3 flows into the indoor heat exchanger 8 operating as the condenser via the refrigerant flow switching device 28, and transfers its heat to the outdoor air sent by the indoor blower device 8a.
  • This refrigerant flows into the subcooling heat exchanger 22 via the second electronic expansion valve 23.
  • This refrigerant is cooled by the low-pressure refrigerant in the subcooling heat exchanger 22, and then has its pressure reduced by the fourth electronic expansion valve 29 to turn into the low-pressure two-phase refrigerant.
  • the low-pressure two-phase refrigerant cools the outdoor air in the outdoor heat exchanger 5 operating as the evaporator to turn into the low-pressure gas refrigerant. After that, the low-pressure gas refrigerant passes through the gas pipe 9 to be sucked into the compressor 3 again.
  • the refrigerant having flowed into the injection pipe 26 has its pressure reduced by the third electronic expansion valve 24, and is then heated by the high-pressure refrigerant in the subcooling heat exchanger 22.
  • This refrigerant is injected into the suction side of the compressor 3, and merges with the refrigerant having flowed through the gas pipe 9. After that, the refrigerant passes through the gas pipe 9 to be sucked into the compressor 3 again.
  • the refrigeration cycle apparatus 100C can achieve suppression of the increase in the discharge temperature and suppression of the increase in the condensing pressure due to the decrease in the quality of the refrigerant at the inlet of the indoor heat exchanger 8 functioning as the evaporator while suppressing the increase in the amount of filled refrigerant. Therefore, with the refrigeration cycle apparatus 100C, safety can be taken into consideration even if the refrigerant leaks by suppressing the increase in the amount of filled refrigerant. Further, the influence on global warming can be reduced. Still further, a highly efficient operation can be continued without causing a change in the property of the refrigerant by suppressing the increase in the discharge temperature.
  • the increase in the discharge temperature can be suppressed by injecting the refrigerant that has passed through the subcooling heat exchanger 22 in the heating operation mode. Still further, with the refrigeration cycle apparatus 100C, even in the heating operation mode, the refrigerant flowing through the liquid pipe 7 can be changed to a two-phase refrigerant. As a result, the refrigeration cycle apparatus 100C contributes to reduction in the amount of filled refrigerant.
  • the refrigeration cycle apparatus described in each of the embodiments is applicable, for use, to an apparatus including a refrigeration cycle, e.g., an air-conditioning apparatus (e.g., a refrigeration apparatus, a room air conditioner, a package air conditioner, or a multi-air conditioner for a building), or a heat pump water heater.
  • a refrigeration cycle e.g., an air-conditioning apparatus (e.g., a refrigeration apparatus, a room air conditioner, a package air conditioner, or a multi-air conditioner for a building), or a heat pump water heater.

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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)

Claims (6)

  1. Appareil à cycle de réfrigération, comprenant :
    un circuit principal de fluide frigorigène formé en raccordant un compresseur (3), un premier échangeur de chaleur (5), un premier détendeur (6) et un deuxième échangeur de chaleur (8) ;
    un circuit de dérivation formé en raccordant le premier échangeur de chaleur (5), un côté primaire d'un échangeur de chaleur à sous-refroidissement (22) installé côté aval du débit de fluide frigorigène dans le cas où le premier échangeur de chaleur (5) sert de condenseur, un deuxième détendeur (23), et le deuxième échangeur de chaleur (8) ; et
    un circuit d'injection formé en raccordant, avec un tuyau d'injection (26) partant en dérivation depuis un côté aval du côté primaire de l'échangeur de chaleur à sous-refroidissement (22), un troisième détendeur (24), un côté secondaire de l'échangeur de chaleur à sous-refroidissement (22), et le compresseur (3),
    l'appareil à cycle de réfrigération pouvant être utilisé dans
    un mode de fonctionnement normal qui amène le fluide frigorigène à s'écouler dans le circuit principal de fluide frigorigène ; et
    un mode de fonctionnement sous température extérieure élevée qui amène le fluide frigorigène à s'écouler dans le circuit de dérivation et le circuit d'injection pour utiliser l'échangeur de chaleur à sous-refroidissement (22), et qui injecte le fluide frigorigène qui s'est écoulé par le côté secondaire de l'échangeur de chaleur à sous-refroidissement (22) dans le compresseur (3),
    l'appareil à cycle de réfrigération étant configuré pour passer en mode de fonctionnement sous température extérieure élevée lorsque la température extérieure de l'air est supérieure ou égale à une température prédéterminée.
  2. Appareil à cycle de réfrigération selon la revendication 1, comprenant en outre un dispositif de commande (30) configuré pour passer en mode de fonctionnement normal et en mode de fonctionnement sous température extérieure élevée en commandant le circuit principal de fluide frigorigène, le circuit de dérivation et le circuit d'injection.
  3. Appareil à cycle de réfrigération selon la revendication 2, comprenant en outre une soupape d'ouverture et de fermeture (21) agencée entre le premier échangeur de chaleur (5) et l'échangeur de chaleur à sous-refroidissement (22),
    dans lequel le dispositif de commande (30) est configuré pour
    dans le mode de fonctionnement normal, amener la soupape d'ouverture et de fermeture (21) à se fermer, amener le deuxième détendeur (23) à s'ouvrir complètement, amener le troisième détendeur (24) à se fermer complètement, et commander la température du fluide frigorigène refoulé par le compresseur (3) avec le premier détendeur (6), et
    dans le mode de fonctionnement sous température extérieure élevée, amener la soupape d'ouverture et de fermeture (21) à s'ouvrir, amener le premier détendeur (6) à se fermer complètement, commander la température du fluide frigorigène refoulé par le compresseur (3) avec le deuxième détendeur (23), et commander un degré de sous-refroidissement du fluide frigorigène à une sortie de l'échangeur de chaleur à sous-refroidissement (22) avec le troisième détendeur (24).
  4. Appareil à cycle de réfrigération selon la revendication 2, comprenant en outre un dispositif de commutation de débit (27) agencé entre le premier échangeur de chaleur (5) et l'échangeur de chaleur à sous-refroidissement (22) et configuré pour commuter un passage de fluide frigorigène entre le circuit principal de fluide frigorigène et le circuit de dérivation,
    dans lequel le dispositif de commande (30) est configuré pour
    dans le mode de fonctionnement normal, commuter le dispositif de commutation de débit (27) de sorte que le premier échangeur de chaleur (5) et le deuxième détendeur (23) communiquent l'un avec l'autre pour amener le deuxième détendeur (23) à servir de premier détendeur (6), amener le troisième détendeur (24) à se fermer complètement, et commander la température du fluide frigorigène refoulé par le compresseur (3) avec le deuxième détendeur (23), et
    dans le mode de fonctionnement sous température extérieure élevée, commuter le dispositif de commutation de débit (27) de sorte que le premier échangeur de chaleur (5) et l'échangeur de chaleur à sous-refroidissement (22) communiquent l'un avec l'autre, commander la température du fluide frigorigène refoulé par le compresseur (3) avec le deuxième détendeur (23), et commander un degré de sous-refroidissement du fluide frigorigène à la sortie de l'échangeur de chaleur à sous-refroidissement (22) avec le troisième détendeur (24).
  5. Appareil à cycle de réfrigération selon la revendication 2, comprenant en outre un quatrième détendeur (29) agencé entre le premier échangeur de chaleur (5) et l'échangeur de chaleur à sous-refroidissement (22),
    dans lequel le dispositif de commande (30) est configuré pour
    dans le mode de fonctionnement normal, amener le deuxième détendeur (23) à s'ouvrir complètement, amener le troisième détendeur (24) à se fermer complètement, et amener le quatrième détendeur (29) à servir de premier détendeur (6) pour commander la température du fluide frigorigène refoulé par le compresseur (3) avec le quatrième détendeur (29),
    dans le mode de fonctionnement sous température extérieure élevée, amener le quatrième détendeur (29) à s'ouvrir complètement, commander la température du fluide frigorigène refoulé par le compresseur (3) avec le deuxième détendeur (23), et commander un degré de sous-refroidissement du fluide frigorigène à la sortie de l'échangeur de chaleur à sous-refroidissement (22) avec le troisième détendeur (24), et
    dans un fonctionnement à un moment où le premier échangeur de chaleur (5) sert d'évaporateur, amener le deuxième détendeur (23) à s'ouvrir complètement, amener le quatrième détendeur (29) à servir de premier détendeur (6) pour commander la température du fluide frigorigène refoulé par le compresseur (3) avec le quatrième détendeur (29), et commander le degré de sous-refroidissement du fluide frigorigène à la sortie de l'échangeur de chaleur à sous-refroidissement (22) avec le troisième détendeur (24).
  6. Appareil à cycle de réfrigération selon la revendication 5, comprenant en outre un dispositif de commutation de débit de fluide frigorigène (28) agencé côté refoulement du compresseur (3),
    dans lequel l'appareil à cycle de réfrigération est configuré pour amener le premier échangeur de chaleur (5) à servir de condenseur ou d'évaporateur avec le dispositif de commutation de débit de fluide frigorigène (28).
EP15759078.7A 2014-03-07 2015-02-27 Dispositif à cycle de réfrigération Active EP3121539B1 (fr)

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PCT/JP2014/056024 WO2015132967A1 (fr) 2014-03-07 2014-03-07 Dispositif à cycle de réfrigération
PCT/JP2015/055855 WO2015133398A1 (fr) 2014-03-07 2015-02-27 Dispositif à cycle de réfrigération

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WO2016009516A1 (fr) * 2014-07-16 2016-01-21 三菱電機株式会社 Dispositif de réfrigération et de climatisation
EP3187789A4 (fr) * 2015-10-27 2018-03-21 GD Midea Heating & Ventilating Equipment Co., Ltd. Système de climatisation par injection de vapeur amélioré
CN110494703A (zh) 2017-03-31 2019-11-22 大金工业株式会社 空调装置
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
US20220042727A1 (en) * 2019-09-13 2022-02-10 Carrier Corporation Hvac unit with expansion device

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JP3966262B2 (ja) * 2003-09-29 2007-08-29 三菱電機株式会社 冷凍冷蔵庫
JP4459776B2 (ja) * 2004-10-18 2010-04-28 三菱電機株式会社 ヒートポンプ装置及びヒートポンプ装置の室外機
US7114349B2 (en) * 2004-12-10 2006-10-03 Carrier Corporation Refrigerant system with common economizer and liquid-suction heat exchanger
JP4740984B2 (ja) * 2008-06-19 2011-08-03 三菱電機株式会社 冷凍空調装置
JP5593905B2 (ja) * 2010-07-16 2014-09-24 ダイキン工業株式会社 冷凍装置
JP5881282B2 (ja) * 2010-09-30 2016-03-09 三菱重工業株式会社 ターボ冷凍装置、その制御装置及びその制御方法
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JP5659909B2 (ja) * 2011-03-29 2015-01-28 株式会社富士通ゼネラル ヒートポンプ装置
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EP3121539A1 (fr) 2017-01-25
JPWO2015133398A1 (ja) 2017-04-06
JP6188916B2 (ja) 2017-08-30
WO2015132967A1 (fr) 2015-09-11
WO2015133398A1 (fr) 2015-09-11

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