WO2015132959A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
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- WO2015132959A1 WO2015132959A1 PCT/JP2014/055982 JP2014055982W WO2015132959A1 WO 2015132959 A1 WO2015132959 A1 WO 2015132959A1 JP 2014055982 W JP2014055982 W JP 2014055982W WO 2015132959 A1 WO2015132959 A1 WO 2015132959A1
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- refrigerant
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- heat exchanger
- gas
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B45/00—Arrangements for charging or discharging refrigerant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/32—Responding to malfunctions or emergencies
- F24F11/37—Resuming operation, e.g. after power outages; Emergency starting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B2400/0415—Refrigeration circuit bypassing means for the receiver
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B2400/16—Receivers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B2400/23—Separators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/15—Control issues during shut down
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2519—On-off valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2523—Receiver valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1931—Discharge pressures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction pressures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
Definitions
- the present invention relates to an air conditioner including a refrigerant circuit in which a compressor, a heat source side heat exchanger, an expansion valve, and a use side heat exchanger are connected by piping and the refrigerant circulates.
- the refrigeration apparatus described in Patent Literature 1 includes a heat source side unit, a use side unit, and a control unit.
- the heat source side unit has a compressor, a heat source side heat exchanger, an expansion valve, a large-diameter pipe, a liquid refrigerant side closing valve, and a gas refrigerant side closing valve, which are connected by a refrigerant pipe.
- the utilization side unit has a utilization side heat exchanger, and one end of the utilization side heat exchanger is connected to the liquid refrigerant side shut-off valve via the liquid refrigerant communication pipe, and the other end is connected to the gas via the gas refrigerant communication pipe. Connected to the refrigerant side closing valve.
- the control unit performs a pump-down operation for collecting the refrigerant in the heat source side unit.
- the refrigerant in the pump-down operation, is stored in a large-diameter pipe provided between the heat source side heat exchanger and the liquid refrigerant side shut-off valve.
- the present invention has been made against the background of the above problems, and suppresses a decrease in the refrigerating capacity without increasing the amount of refrigerant charged in the refrigerant circuit, and suitably stores the refrigerant during the pump-down operation. It aims at obtaining the air conditioning apparatus which can be performed.
- An air conditioner according to the present invention is an air conditioner provided with a refrigerant circuit in which a compressor, a heat source side heat exchanger, an expansion valve, and a use side heat exchanger are connected by piping and the refrigerant circulates, A first on-off valve provided in the pipe between the expansion valve and the use side heat exchanger, the pipe between the expansion valve and the first on-off valve, or the heat source side heat exchanger and the A bypass circuit for branching the pipe between the expansion valve and connected to the pipe on the suction side of the compressor; and a refrigerant storage means for storing the refrigerant flowing through the bypass circuit.
- the refrigerant that has flowed out of the heat source side heat exchanger flows into the bypass circuit, and the refrigerant is stored in the refrigerant storage means. is there.
- the present invention can suppress a decrease in the refrigerating capacity without increasing the amount of refrigerant charged in the refrigerant circuit, and can suitably store the refrigerant during the pump-down operation.
- FIG. 2 is a refrigerant circuit diagram of the air-conditioning apparatus 100 according to Embodiment 1.
- FIG. 6 is a ph diagram at the time of pump down operation of the air-conditioning apparatus 100 according to Embodiment 1.
- FIG. 6 is a refrigerant circuit diagram of an air-conditioning apparatus 100 according to Embodiment 2.
- FIG. 6 is a ph diagram at the time of pump down operation of the air-conditioning apparatus 100 according to Embodiment 2.
- FIG. 6 is a refrigerant circuit diagram of an air-conditioning apparatus 100 according to Embodiment 3.
- FIG. 10 is a ph diagram during cooling operation of the air-conditioning apparatus 100 according to Embodiment 3.
- 6 is a refrigerant circuit diagram of an air-conditioning apparatus 100 according to Embodiment 4.
- FIG. 10 is a ph diagram during heating operation of the air-conditioning apparatus 100 according to Embodiment 4.
- FIG. 1 is a refrigerant circuit diagram of an air-conditioning apparatus 100 according to Embodiment 1.
- the air conditioner 100 includes an outdoor unit 1 and an indoor unit 2, and the outdoor unit 1 and the indoor unit 2 are connected by a liquid pipe 8 and a gas pipe 5.
- the outdoor unit 1 includes the compressor 3, the four-way valve 4, the heat source side heat exchanger 9, the expansion valve 7, the heat source side blower 91 that blows air to the heat source side heat exchanger 9, and the operation of each part constituting the air conditioner 100.
- the control apparatus 40 which controls is provided.
- the indoor unit 2 includes a use side heat exchanger 6 and a use side blower 61 that blows air to the use side heat exchanger 6.
- the compressor 3, the four-way valve 4, the heat source side heat exchanger 9, the expansion valve 7, and the use side heat exchanger 6 are sequentially connected by a pipe to form a refrigerant circuit in which the refrigerant circulates.
- the outdoor unit 1 further includes a bypass circuit 20 that branches a pipe between the expansion valve 7 and the first on-off valve 11 and connects to a pipe on the suction side of the compressor 3.
- the bypass circuit 20 is provided with a first bypass opening / closing valve 21, a second bypass opening / closing valve 22, and a container 30 for storing refrigerant.
- the compressor 3 is a type in which the number of revolutions is controlled by an inverter, for example, and the capacity is controlled.
- the expansion valve 7 is an electronic expansion valve whose opening degree is variably controlled, for example.
- the heat source side heat exchanger 9 exchanges heat with the outside air blown by the heat source side blower 91.
- the use side heat exchanger 6 exchanges heat with room air blown by the use side blower 61.
- the first bypass on-off valve 21 is provided on the refrigerant inflow side of the bypass circuit 20 (the pipe side between the expansion valve 7 and the first on-off valve 11).
- the second bypass on-off valve 22 is provided on the refrigerant outflow side of the bypass circuit 20 (the piping side on the suction side of the compressor 3).
- the first bypass on-off valve 21 and the second bypass on-off valve 22 are on-off valves that open and close the refrigerant flow path of the bypass circuit 20.
- the container 30 is a container that stores a refrigerant.
- the container 30 corresponds to “refrigerant storage means” in the present invention.
- the gas pipe 5 and the liquid pipe 8 are connection pipes that connect the outdoor unit 1 and the indoor unit 2.
- the first on-off valve 11 and the second on-off valve 12 are connected to the liquid pipe 8 and the gas pipe 5, respectively.
- the liquid pipe 8 connects between the use side heat exchanger 6 of the indoor unit 2 and the first on-off valve 11 of the outdoor unit 1.
- the gas pipe 5 connects between the use side heat exchanger 6 of the indoor unit 2 and the second on-off valve 12 of the outdoor unit 1.
- the first on-off valve 11, the second on-off valve 12, the first bypass on-off valve 21, and the second bypass on-off valve 22 may be manual valves that are manually opened and closed, and the open / close state is controlled by the control device 40. It may be a solenoid valve.
- the outdoor unit 1 further includes a discharge temperature sensor 41, a discharge pressure sensor 51, and a suction pressure sensor 52.
- the discharge temperature sensor 41 detects the temperature of the refrigerant discharged from the compressor 3.
- the discharge pressure sensor 51 detects the pressure of the refrigerant discharged from the compressor 3.
- the suction pressure sensor 52 detects the pressure of the refrigerant sucked into the compressor 3. Note that the pressure of the refrigerant circulating in the refrigerant circuit is lowest on the suction side of the compressor 3 and highest on the discharge side of the compressor 3. Therefore, in the following description, the pressure on the suction side of the compressor 3 is referred to as a low pressure, and the pressure on the discharge side of the compressor 3 is referred to as a high pressure.
- a slightly flammable (R32, HFO1234yf, HFO1234ze, etc.) and flammable (HC) refrigerant is used.
- the substance to be mixed to generate the mixed refrigerant include tetrafluoropropene (HFO1234yf which is 2,3,3,3-tetrafluoropropene, 1,3,3,3-tetrafluoro-1-propene. HFO1234ze etc.), difluoromethane (HFC32) etc. are used, but not limited to these, HC290 (propane) etc.
- coolant used in this invention is not limited to said refrigerant
- a refrigerant such as R410A may be used.
- the air conditioner 100 configured as described above can perform a cooling operation or a heating operation by switching the four-way valve 4.
- the air conditioner 100 can perform a pump-down operation for collecting the refrigerant in the indoor unit 2 in the outdoor unit 1.
- the air conditioner 100 only needs to be capable of at least a cooling operation and a pump-down operation. Therefore, the four-way valve 4 is not necessarily an essential configuration and can be omitted.
- the solid line indicates the flow during cooling
- the dotted line indicates the flow during heating
- the low-pressure two-phase refrigerant that has flowed out of the expansion valve 7 passes through the liquid pipe 8 and flows into the indoor unit 2, evaporates by exchanging heat with indoor air in the use-side heat exchanger 6, and flows out as low-pressure gas refrigerant. To do.
- the low-pressure gas refrigerant that has flowed out of the use-side heat exchanger 6 passes through the gas pipe 5, flows into the outdoor unit 1, and returns to the compressor 3 through the four-way valve 4.
- the first bypass opening / closing valve 21 is in a closed state, so that no refrigerant flows into the bypass circuit 20.
- the liquid sealing of the container 30 can be prevented by opening the second bypass on-off valve 22.
- the heating operation in the normal operation will be described.
- the four-way valve 4 is switched to the heating side (state indicated by a dotted line).
- the 1st on-off valve 11, the 2nd on-off valve 12, and the 2nd bypass on-off valve 22 are an open state.
- the first bypass on-off valve 21 is in a closed state.
- the high-pressure and high-temperature gas refrigerant flows into the use side heat exchanger 6 of the indoor unit 2 through the four-way valve 4 and the gas pipe 5. Dissipates heat by exchanging heat with room air and flows out as high-pressure liquid refrigerant.
- the high-pressure liquid refrigerant that has flowed out of the use-side heat exchanger 6 passes through the liquid pipe 8 and flows into the expansion valve 7 to become a low-pressure two-phase refrigerant.
- the low-pressure two-phase refrigerant that has flowed out of the expansion valve 7 flows into the heat source side heat exchanger 9 and evaporates by heat exchange with outdoor air, and flows out as low-pressure gas refrigerant.
- the low-pressure gas refrigerant that has flowed out of the heat source side heat exchanger 9 returns to the compressor 3 via the four-way valve 4.
- the first bypass opening / closing valve 21 is in the closed state, so that no refrigerant flows into the bypass circuit 20.
- the liquid sealing of the container 30 can be prevented by opening the second bypass on-off valve 22.
- FIG. 2 is a ph diagram during the pump-down operation of the air-conditioning apparatus 100 according to Embodiment 1.
- the horizontal axis of FIG. 2 shows the specific enthalpy of the refrigerant, and the vertical axis shows the pressure.
- points a to c in FIG. 5 indicate the refrigerant state at the positions shown in FIG.
- the four-way valve 4 is switched to the cooling side (state indicated by the solid line).
- the second on-off valve 12 and the first bypass on-off valve 21 are open.
- the first on-off valve 11 and the second bypass on-off valve 22 are closed.
- the control device 40 fully opens the opening of the expansion valve 7. Further, the control device 40 operates the heat source side blower 91 and the use side blower 61.
- the low-pressure gas refrigerant (state a) is compressed by the compressor 3 and discharged as a high-temperature and high-pressure gas refrigerant (state b).
- the high-pressure and high-temperature gas refrigerant discharged from the compressor 3 flows into the heat source side heat exchanger 9 through the four-way valve 4 and radiates heat by exchanging heat with outdoor air to become high-pressure liquid refrigerant (state c) and flows out. To do.
- the high-pressure liquid refrigerant that has flowed out of the heat source side heat exchanger 9 passes through the expansion valve 7 and flows into the bypass circuit 20.
- the high-pressure liquid refrigerant (state c) flowing into the bypass circuit 20 passes through the first bypass opening / closing valve 21 and flows into the container 30. Since the second bypass opening / closing valve 22 is in the closed state, the high-pressure liquid refrigerant (state c) flowing into the bypass circuit 20 is stored in the container 30.
- the refrigerant in the use side heat exchanger 6, the liquid pipe 8, and the gas pipe 5 is sucked by the operation of the compressor 3, discharged from the compressor 3, and then stored in the container 30 by the above operation.
- the refrigerant in the indoor unit 2 is recovered to the outdoor unit 1 side.
- the second on-off valve 12 is closed and, for example, the indoor unit 2 is removed.
- the refrigerant that has flowed out of the heat source side heat exchanger 9 is caused to flow into the bypass circuit 20, and this refrigerant is stored in the container 30.
- coolant can be suitably collect
- the amount of refrigerant charged in the refrigerant circuit can be reduced, an increase in manufacturing cost can be suppressed, and the influence on the environment when the refrigerant leaks can be reduced.
- the bypass circuit 20 branches the piping between the expansion valve 7 and the first on-off valve 11 and connects to the suction-side piping of the compressor 3.
- the piping between the exchanger 9 and the expansion valve 7 may be branched. Even in such a configuration, the same effect can be obtained by performing the same operation as described above.
- Embodiment 2 the difference from the first embodiment will be mainly described, and the same components as those in the first embodiment will be denoted by the same reference numerals and the description thereof will be omitted.
- FIG. 3 is a refrigerant circuit diagram of the air-conditioning apparatus 100 according to Embodiment 2.
- the air-conditioning apparatus 100 according to Embodiment 2 is provided with an accumulator 10 that stores excess refrigerant on the suction side of the compressor 3.
- the bypass circuit 20 is connected to a pipe on the suction side of the accumulator 10.
- the bypass circuit 20 is provided with a third bypass opening / closing valve 23.
- the first bypass opening / closing valve 21, the second bypass opening / closing valve 22, and the container 30 are not provided.
- the third bypass opening / closing valve 23 has a function of opening / closing the flow path of the bypass circuit 20 and expanding (depressurizing) the refrigerant passing therethrough.
- the refrigerant passing through the third bypass opening / closing valve 23 is expanded by making the pipe diameter of the bypass circuit 20 downstream of the third bypass opening / closing valve 23 (accumulator 10 side) smaller than that of the upstream side.
- the configuration of the third bypass opening / closing valve 23 is not limited to this.
- an electronic expansion valve whose opening degree is variably controlled may be used as the third bypass opening / closing valve 23.
- the two-way valve and the capillary tube may be connected in series. That is, any configuration can be used as long as the refrigerant flow in the bypass circuit 20 can be opened and closed and the refrigerant passing therethrough is expanded (depressurized).
- the third bypass on-off valve 23 corresponds to the “second expansion valve” in the present invention.
- the third bypass on-off valve 23 is closed. In this state, the cooling operation and the heating operation are performed by the same operation as in the first embodiment. Since the third bypass opening / closing valve 23 is in a closed state, the refrigerant does not flow into the bypass circuit 20.
- the accumulator 10 separates the gas refrigerant into the liquid refrigerant and the gas refrigerant is sucked into the compressor 3.
- FIG. 4 is a ph diagram during the pump-down operation of the air-conditioning apparatus 100 according to Embodiment 2.
- the horizontal axis of FIG. 4 shows the specific enthalpy of the refrigerant, and the vertical axis shows the pressure. Further, points a to e in FIG. 4 indicate refrigerant states at the positions shown in FIG.
- the four-way valve 4 is switched to the cooling side (state indicated by the solid line).
- the 2nd on-off valve 12 and the 3rd bypass on-off valve 23 are an open state.
- the first on-off valve 11 is in a closed state. Further, the control device 40 fully opens the opening of the expansion valve 7.
- control device 40 operates the heat source side blower 91 and the use side blower 61.
- the heat source side air blower 91 may be stopped or the air flow rate may be reduced to reduce the heat exchange amount of the heat source side heat exchanger 9.
- the low-pressure gas refrigerant (state a) is compressed by the compressor 3 and discharged as a high-temperature and high-pressure gas refrigerant (state b).
- the high-pressure and high-temperature gas refrigerant discharged from the compressor 3 flows into the heat source side heat exchanger 9 through the four-way valve 4, and becomes a high-pressure two-phase refrigerant (state c) by dissipating heat by exchanging heat with outdoor air. leak.
- the high-pressure two-phase refrigerant that has flowed out of the heat source side heat exchanger 9 passes through the expansion valve 7 and flows into the bypass circuit 20.
- the high-pressure liquid refrigerant (state c) that has flowed into the bypass circuit 20 is expanded (depressurized) when passing through the third bypass on-off valve 23 to become a low-pressure two-phase refrigerant (state d).
- This low-pressure two-phase refrigerant flows into the accumulator 10 from the bypass circuit 20 and is separated into a gas refrigerant (state a) and a liquid refrigerant (state e).
- the gas refrigerant in the accumulator 10 is sucked into the compressor 3.
- the liquid refrigerant is stored in the accumulator 10.
- the refrigerant in the use side heat exchanger 6, the liquid pipe 8, and the gas pipe 5 is sucked by the operation of the compressor 3, flows into the accumulator 10, is separated into the gas refrigerant and the liquid refrigerant, and the liquid refrigerant is the accumulator 10. It is stored in.
- the refrigerant in the indoor unit 2 is recovered to the outdoor unit 1 side.
- the second on-off valve 12 is closed and, for example, the indoor unit 2 is removed.
- the third bypass opening / closing valve 23 is provided in the bypass circuit 20, the refrigerant flowing into the bypass circuit 20 is expanded (depressurized), and the refrigerant is stored in the accumulator 10.
- the refrigerant stored in the accumulator 10 is an expanded (depressurized) low-pressure liquid refrigerant (see TACC in FIG. 4). Therefore, as compared with the case of storing the high-pressure refrigerant (refer to T C of FIG. 4), the temperature of the coolant is lowered, it is possible to increase the refrigerant density. Therefore, the capacity
- the bypass circuit 20 branches the piping between the expansion valve 7 and the first on-off valve 11 and connects to the suction-side piping of the compressor 3.
- the piping between the exchanger 9 and the expansion valve 7 may be branched. Even in such a configuration, the same effect can be obtained by performing the same operation as described above.
- Embodiment 3 FIG. In this Embodiment 3, it demonstrates centering on difference with Embodiment 2, the same code
- FIG. 5 is a refrigerant circuit diagram of the air-conditioning apparatus 100 according to Embodiment 3.
- the air-conditioning apparatus 100 according to Embodiment 3 further includes a gas-liquid separator 32 in addition to the configuration of Embodiment 2 above.
- the gas-liquid separator 32 is provided in a pipe between the expansion valve 7 and the first on-off valve 11.
- the gas-liquid separator 32 separates the inflowing refrigerant into a gas refrigerant and a liquid phase refrigerant.
- the bypass circuit 20 connects the gas-side connection port of the gas-liquid separator 32 and the suction-side piping of the compressor 3.
- FIG. 6 is a ph diagram during the cooling operation of the air-conditioning apparatus 100 according to Embodiment 3.
- the horizontal axis of FIG. 6 shows the specific enthalpy of the refrigerant, and the vertical axis shows the pressure.
- points a to f in FIG. 6 indicate refrigerant states at the positions shown in FIG.
- a pressure difference is generated between the state e and the state a in FIG. 6, but in actuality, it is about a decrease due to pressure loss in the refrigerant flow path.
- the four-way valve 4 is switched to the cooling side (state indicated by a solid line). Moreover, the 1st on-off valve 11, the 2nd on-off valve 12, and the 3rd bypass on-off valve 23 are an open state.
- the compressor 3 When the compressor 3 is started in this state, the low-pressure gas refrigerant (state a) is compressed by the compressor 3 and discharged as a high-temperature and high-pressure gas refrigerant (state b).
- the high-pressure and high-temperature gas refrigerant discharged from the compressor 3 flows into the heat source side heat exchanger 9 through the four-way valve 4 and radiates heat by exchanging heat with outdoor air to become high-pressure liquid refrigerant (state c) and flows out.
- the high-pressure liquid refrigerant that has flowed out of the heat source side heat exchanger 9 flows into the expansion valve 7 and becomes a low-pressure two-phase refrigerant (state d).
- the low-pressure two-phase refrigerant that has flowed out of the expansion valve 7 flows into the gas-liquid separator 32 and is separated into a gas refrigerant (state f) and a liquid refrigerant (state e).
- the gas refrigerant flowing into the bypass circuit 20 from the gas-liquid separator 32 passes through the third bypass opening / closing valve 23 and flows into the accumulator 10.
- the liquid refrigerant (state e) separated by the gas-liquid separator 32 flows into the indoor unit 2 through the liquid pipe 8, evaporates by exchanging heat with indoor air in the use side heat exchanger 6, It flows out as a low-pressure gas refrigerant.
- the low-pressure gas refrigerant that has flowed out of the use-side heat exchanger 6 passes through the gas pipe 5 and flows into the outdoor unit 1, and returns to the compressor 3 through the four-way valve 4 and the accumulator 10.
- Heating operation In the heating operation, the third bypass on-off valve 23 is closed. In this state, the heating operation is performed by the same operation as in the second embodiment. Since the third bypass opening / closing valve 23 is in a closed state, the refrigerant does not flow into the bypass circuit 20.
- the gaseous refrigerant separated by the gas-liquid separator 32 flows into the bypass circuit 20.
- the gas refrigerant separated by the gas-liquid separator 32 is caused to flow into the bypass circuit 20, so that the dryness of the refrigerant flowing into the use side heat exchanger 6 acting as an evaporator is reduced, and the refrigerant Pressure loss can be reduced.
- refrigeration performance can be improved by bypassing a gas refrigerant that contributes little to heat exchange. Therefore, the energy saving property at the time of cooling operation can be improved.
- Embodiment 4 FIG. In the fourth embodiment, the difference from the second embodiment will be mainly described.
- the same components as those in the second embodiment are denoted by the same reference numerals, and the description thereof will be omitted.
- FIG. 7 is a refrigerant circuit diagram of the air-conditioning apparatus 100 according to Embodiment 4.
- the air conditioning apparatus 100 according to the fourth embodiment further includes a gas-liquid separator 32 in addition to the configuration of the second embodiment.
- the gas-liquid separator 32 is provided in a pipe between the heat source side heat exchanger 9 and the expansion valve 7.
- the gas-liquid separator 32 separates the inflowing refrigerant into a gas refrigerant and a liquid phase refrigerant.
- the bypass circuit 20 connects the gas-side connection port of the gas-liquid separator 32 and the suction-side piping of the compressor 3.
- FIG. 8 is a ph diagram when the air-conditioning apparatus 100 according to Embodiment 4 is in the heating operation.
- the horizontal axis of FIG. 8 shows the specific enthalpy of the refrigerant, and the vertical axis shows the pressure. Further, points a to f in FIG. 8 indicate refrigerant states at the positions shown in FIG. For convenience of illustration, a pressure difference is generated between the state c and the state a in FIG. 8, but in actuality, it is about a drop due to pressure loss in the refrigerant flow path.
- the four-way valve 4 is switched to the heating side (state indicated by a dotted line). Moreover, the 1st on-off valve 11, the 2nd on-off valve 12, and the 3rd bypass on-off valve 23 are an open state.
- the compressor 3 When the compressor 3 is started in this state, the low-pressure gas refrigerant (state a) is compressed by the compressor 3 and discharged as a high-temperature and high-pressure gas refrigerant (state b).
- the high-pressure and high-temperature gas refrigerant discharged from the compressor 3 flows into the use side heat exchanger 6 of the indoor unit 2 through the four-way valve 4 and the gas pipe 5 and dissipates heat by heat exchange with the indoor air.
- the low-pressure two-phase refrigerant that has flowed out of the expansion valve 7 flows into the gas-liquid separator 32 and is separated into a gas refrigerant (state f) and a liquid refrigerant (state c).
- the gas refrigerant flowing into the bypass circuit 20 from the gas-liquid separator 32 passes through the third bypass opening / closing valve 23 and flows into the accumulator 10.
- the liquid refrigerant (state c) separated by the gas-liquid separator 32 flows into the heat source side heat exchanger 9 and evaporates by heat exchange with the outdoor air to become a low-pressure gas refrigerant (state f). leak.
- the low-pressure gas refrigerant that has flowed out of the heat source side heat exchanger 9 returns to the compressor 3 via the four-way valve 4.
- the gas-state refrigerant separated by the gas-liquid separator 32 flows into the bypass circuit 20 in the heating operation.
- the gas refrigerant separated by the gas-liquid separator 32 is caused to flow into the bypass circuit 20, so that the dryness of the refrigerant flowing into the heat source side heat exchanger 9 acting as an evaporator decreases, Pressure loss can be reduced.
- refrigeration performance can be improved by bypassing a gas refrigerant that contributes little to heat exchange. Therefore, the energy saving property at the time of heating operation can be improved.
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Abstract
Description
即ち、冷房運転に凝縮器として作用する熱源側熱交換器の出口に大径管を配置しているので、ポンプダウン運転時だけではなく冷房運転時にも大径管に冷媒が貯留されてしまう。このため、冷媒回路を循環する冷媒量が減少して冷凍能力が低下してしまうという課題がある。
一方、大径管に冷媒が貯留される冷媒量を考慮して冷媒の充填量を増加させると、これに伴い製造コストが増加してしまうという課題がある。また、冷媒回路に充填する冷媒量を多くすると、冷媒の漏洩時における環境への影響が大きくなってしまうという課題がある。特に、微燃性(R32,HFO1234yf,HFO1234ze等)及び可燃性(HC)の冷媒を適用する場合には、冷媒回路へ充填できる許容冷媒量がIEC規格(国際電気標準規格)によって制約されており、充填冷媒量を多くすることができないため、上記の課題は顕著となる。
図1は、実施の形態1に係る空気調和装置100の冷媒回路図である。
図1に示すように、空気調和装置100は、室外機1と室内機2とを備え、室外機1と室内機2とが液配管8及びガス配管5で接続されている。
室内機2は、利用側熱交換器6、及び利用側熱交換器6に空気を送風する利用側送風機61を備えている。
空気調和装置100は、圧縮機3、四方弁4、熱源側熱交換器9、膨張弁7、利用側熱交換器6が、順次配管で接続されて冷媒が循環する冷媒回路を形成する。
膨張弁7は、例えば開度が可変に制御される電子膨張弁である。
熱源側熱交換器9は、熱源側送風機91によって送風される外気と熱交換する。
利用側熱交換器6は、利用側送風機61によって送風される室内空気と熱交換する。
第2バイパス開閉弁22は、バイパス回路20の冷媒の流出側(圧縮機3の吸入側の配管側)に設けられている。
第1バイパス開閉弁21及び第2バイパス開閉弁22は、バイパス回路20の冷媒の流路を開閉する開閉弁である。
容器30は、冷媒を貯留する容器である。
なお、容器30は、本発明における「冷媒貯留手段」に相当する。
吐出温度センサー41は、圧縮機3から吐出された冷媒の温度を検出する。
吐出圧力センサー51は、圧縮機3から吐出された冷媒の圧力を検出する。
吸入圧力センサー52は、圧縮機3へ吸入される冷媒の圧力を検出する。
なお、冷媒回路を循環する冷媒の圧力は、圧縮機3の吸入側が最も低く、圧縮機3の吐出側が最も高い。よって、以下の説明では、圧縮機3の吸入側の圧力を低圧、圧縮機3の吐出側の圧力を高圧と言う。
混合冷媒を生成させるために混合させる物質としては、例えば、テトラフルオロプロペン(2,3,3,3-テトラフルオロプロペンであるHFO1234yf、1,3,3,3-テトラフルオロ-1-プロペンであるHFO1234ze等)、ジフルオロメタン(HFC32)等が用いられるが、これらに限るものではなく、HC290(プロパン)等を混合させてもよく、冷凍サイクル(冷媒回路)の冷媒として使用できる熱性能を有する物質であれば、どのようなものを用いてもよく、どのような混合比としてもよい。
なお、本発明において使用する冷媒は上記の冷媒に限定されない。例えば、R410A等の冷媒を使用しても良い。
なお、空気調和装置100は少なくとも冷房運転及びポンプダウン運転が可能であれば良い。よって、四方弁4は必ずしも必須の構成ではなく、省略可能である。
まず、通常運転における冷房運転について説明する。
冷房運転時において、四方弁4は冷房側(実線で示す状態)に切り換えられる。また、第1開閉弁11、第2開閉弁12、第2バイパス開閉弁22は、開状態である。第1バイパス開閉弁21は閉状態である。
この状態で圧縮機3から高圧高温のガス冷媒が吐出されると、その高圧高温のガス冷媒は、四方弁4を介して熱源側熱交換器9に流入し、室外空気との熱交換により放熱することで高圧液冷媒となり流出する。熱源側熱交換器9から流出した高圧液冷媒は、膨張弁7に流入し、低圧の二相冷媒となる。
なお、冷房運転時、第1バイパス開閉弁21は閉状態のため、バイパス回路20に冷媒が流入することはない。また、第2バイパス開閉弁22を開状態にすることで、容器30の液封を防止できる。
次に、通常運転における暖房運転について説明する。
暖房運転時において、四方弁4は暖房側(点線で示す状態)に切り換えられる。また、第1開閉弁11、第2開閉弁12、第2バイパス開閉弁22は、開状態である。第1バイパス開閉弁21は閉状態である。
この状態で圧縮機3から高圧高温のガス冷媒が吐出されると、その高圧高温のガス冷媒は、四方弁4及びガス配管5を介して室内機2の利用側熱交換器6に流入し、室内空気との熱交換により放熱することで高圧液冷媒となり流出する。利用側熱交換器6から流出した高圧液冷媒は、液配管8を通過して膨張弁7に流入し、低圧の二相冷媒となる。
なお、暖房運転時、第1バイパス開閉弁21は閉状態のため、バイパス回路20に冷媒が流入することはない。また、第2バイパス開閉弁22を開状態にすることで、容器30の液封を防止できる。
次に、ポンプダウン運転について説明する。
ポンプダウン運転時において、四方弁4は冷房側(実線で示す状態)に切り換えられる。また、第2開閉弁12、第1バイパス開閉弁21は開状態である。第1開閉弁11、第2バイパス開閉弁22は、閉状態である。更に、制御装置40は、膨張弁7の開度を全開にする。また、制御装置40は、熱源側送風機91及び利用側送風機61を運転させる。
バイパス回路20へ流入した高圧液冷媒(状態c)は、第1バイパス開閉弁21を通過して、容器30へ流入する。第2バイパス開閉弁22は閉状態であるので、バイパス回路20に流入した高圧液冷媒(状態c)は、容器30内に貯留される。
利用側熱交換器6、液配管8、及びガス配管5内の冷媒は、圧縮機3の運転によって吸引され、圧縮機3から吐出されたあと、上記動作によって、容器30内に貯留される。
このため、ポンプダウン運転時には好適に冷媒を室外機1へ回収することができる。また、熱源側熱交換器9(凝縮器)の出口側に大径管等の貯留容器を設ける必要が無く、冷媒回路に充填する冷媒量を増加させることなく冷凍能力の低下を抑制することができる。
また、冷媒回路へ充填する冷媒量を低減することができるので、製造コストの増加を抑制し、冷媒の漏洩時における環境への影響を低減することができる。
なお、上記の説明では、バイパス回路20は、膨張弁7と第1開閉弁11との間の配管を分岐し、圧縮機3の吸入側の配管に接続する場合を説明したが、熱源側熱交換器9と膨張弁7との間の配管を分岐しても良い。このような構成においても、上記と同様の動作を行うことで同様の効果を得ることができる。
本実施の形態2では実施の形態1との相違点を中心に説明し、実施の形態1と同一の構成には同一の符号を付して説明を省略する。
図3に示すように、実施の形態2に係る空気調和装置100は、圧縮機3の吸入側に、余剰冷媒を溜めるアキュムレータ10が設けられている。バイパス回路20は、アキュムレータ10の吸入側の配管に接続されている。
また、バイパス回路20には、第3バイパス開閉弁23を設けている。なお、本実施の形態2では、第1バイパス開閉弁21、第2バイパス開閉弁22、及び容器30を設けていない。
第3バイパス開閉弁23は、バイパス回路20の流路を開閉するとともに、通過する冷媒を膨張(減圧)させる機能を有している。例えば、第3バイパス開閉弁23の下流側(アキュムレータ10側)におけるバイパス回路20の配管径を上流側よりも細くすることで、第3バイパス開閉弁23を通過する冷媒を膨張させる。なお、第3バイパス開閉弁23の構成は、これに限定されない。例えば、第3バイパス開閉弁23として、開度が可変に制御される電子膨張弁を用いても良い。また、二方弁とキャピラリーチューブとを直列に接続しても良い。つまり、バイパス回路20における冷媒の流れを開閉でき、通過する冷媒を膨張(減圧)させる構成であれば、任意の構成を用いることができる。
なお、第3バイパス開閉弁23は、本発明における「第2膨張弁」に相当する。
冷房運転時、及び暖房運転において、第3バイパス開閉弁23は閉状態である。
この状態で、上記実施の形態1と同様の動作により、冷房運転、暖房運転が行われる。第3バイパス開閉弁23は閉状態のため、バイパス回路20に冷媒が流入することはない。
なお、蒸発器から湿りガス冷媒(二相冷媒)が流出された場合、アキュムレータ10によって、ガス冷媒と液相冷媒とに分離され、ガス冷媒が圧縮機3へ吸入される。
次に、ポンプダウン運転について説明する。
ポンプダウン運転時において、四方弁4は冷房側(実線で示す状態)に切り換えられる。また、第2開閉弁12、第3バイパス開閉弁23は開状態である。第1開閉弁11は、閉状態である。更に、制御装置40は、膨張弁7の開度を全開にする。また、制御装置40は、熱源側送風機91及び利用側送風機61を運転させる。
なお、本実施の形態2では、熱源側送風機91を停止又は送風量を低下させ、熱源側熱交換器9の熱交換量を少なくしても良い。
バイパス回路20へ流入した高圧液冷媒(状態c)は、第3バイパス開閉弁23を通過する際に膨張(減圧)され、低圧の二相冷媒(状態d)となる。この低圧の二相冷媒は、バイパス回路20からアキュムレータ10へ流入し、ガス冷媒(状態a)と液冷媒(状態e)とに分離される。アキュムレータ10内のガス冷媒は、圧縮機3へ吸入される。一方、液冷媒はアキュムレータ10内に貯留される。
利用側熱交換器6、液配管8、及びガス配管5内の冷媒は、圧縮機3の運転によって吸引され、アキュムレータ10へ流入し、ガス冷媒と液冷媒とに分離され、液冷媒がアキュムレータ10に貯留される。
このため、上記実施の形態1の効果に加えて以下の効果がある。即ち、アキュムレータ10に貯留される冷媒は、膨張(減圧)された低圧の液冷媒(図4のTACC参照)である。このため、高圧の冷媒(図4のTC参照)を貯留する場合と比較して、冷媒の温度が低くなり、冷媒密度を大きくすることができる。よって、ポンプダウン運転において冷媒を貯留する冷媒貯留手段(アキュムレータ10)の容量をより小さくすることができる。
なお、上記の説明では、バイパス回路20は、膨張弁7と第1開閉弁11との間の配管を分岐し、圧縮機3の吸入側の配管に接続する場合を説明したが、熱源側熱交換器9と膨張弁7との間の配管を分岐しても良い。このような構成においても、上記と同様の動作を行うことで同様の効果を得ることができる。
本実施の形態3では実施の形態2との相違点を中心に説明し、実施の形態2と同一の構成には同一の符号を付して説明を省略する。
図5に示すように、実施の形態3に係る空気調和装置100は、上記実施の形態2の構成に加え、気液分離器32を更に備えている。
気液分離器32は、膨張弁7と第1開閉弁11との間の配管に設けられている。気液分離器32は、流入した冷媒を、ガス冷媒と液相冷媒とに分離する。
バイパス回路20は、気液分離器32のガス側の接続口と圧縮機3の吸入側の配管とを接続する。
図6は、実施の形態3に係る空気調和装置100の冷房運転時のp-h線図である。図6の横軸は冷媒の比エンタルピを示し、縦軸は圧力を示す。また、図6内の点a~点fは、図5に示す位置における冷媒状態を示す。
なお、図示の都合上、図6の状態eと状態aとに圧力差を生じさせるように図示しているが、実際には、冷媒流路における圧力損失による低下程度である。
この状態で圧縮機3が起動されると、低圧のガス冷媒(状態a)が圧縮機3で圧縮され高温高圧のガス冷媒(状態b)となって吐出される。圧縮機3から吐出された高圧高温のガス冷媒は、四方弁4を介して熱源側熱交換器9に流入し、室外空気との熱交換により放熱することで高圧液冷媒(状態c)となり流出する。熱源側熱交換器9から流出した高圧液冷媒は、膨張弁7に流入し、低圧の二相冷媒(状態d)となる。
一方、気液分離器32によって分離された液冷媒(状態e)は、液配管8を通過して室内機2へ流入し、利用側熱交換器6で室内空気と熱交換して蒸発し、低圧ガス冷媒となって流出する。利用側熱交換器6を流出した低圧ガス冷媒は、ガス配管5を通過して室外機1へ流入し、四方弁4、アキュムレータ10を介して、圧縮機3へ戻る。
暖房運転において、第3バイパス開閉弁23は閉状態である。
この状態で、上記実施の形態2と同様の動作により、暖房運転が行われる。第3バイパス開閉弁23は閉状態のため、バイパス回路20に冷媒が流入することはない。
ポンプダウン運転時において、第3バイパス開閉弁23は開状態である。
この状態で、上記実施の形態2と同様の動作により、ポンプダウン運転が行われる。
このため、上記実施の形態1、2の効果に加えて以下の効果がある。即ち、冷房運転時において、気液分離器32で分離したガス冷媒をバイパス回路20へ流入させるので、蒸発器として作用する利用側熱交換器6に流入する冷媒の乾き度が低下し、冷媒の圧力損失を低減することができる。また、熱交換への寄与が小さいガス冷媒をバイパスすることで、冷凍性能を向上することができる。よって、冷房運転時における省エネルギー性を向上することができる。
なお、上記の説明では、実施の形態2の構成に加え、気液分離器32を備える構成を説明したが、実施の形態1の構成に加えて気液分離器32を備える構成としても良い。このような構成においても、冷房運転時に、第1バイパス開閉弁21及び第2バイパス開閉弁22を開状態にすることで、気液分離器32によって分離された低圧のガス冷媒を、容器30を通過させて、圧縮機3の吸入側へ合流させることができる。このような構成においても、同様の効果を得ることができる。
本実施の形態4では実施の形態2との相違点を中心に説明し、実施の形態2と同一の構成には同一の符号を付して説明を省略する。
図7に示すように、実施の形態4に係る空気調和装置100は、上記実施の形態2の構成に加え、気液分離器32を更に備えている。
気液分離器32は、熱源側熱交換器9と膨張弁7との間の配管に設けられている。気液分離器32は、流入した冷媒を、ガス冷媒と液相冷媒とに分離する。
バイパス回路20は、気液分離器32のガス側の接続口と圧縮機3の吸入側の配管とを接続する。
冷房運転において、第3バイパス開閉弁23は閉状態である。
この状態で、上記実施の形態2と同様の動作により、冷房運転が行われる。第3バイパス開閉弁23は閉状態のため、バイパス回路20に冷媒が流入することはない。
図8は、実施の形態4に係る空気調和装置100の暖房運転時のp-h線図である。図8の横軸は冷媒の比エンタルピを示し、縦軸は圧力を示す。また、図8内の点a~点fは、図7に示す位置における冷媒状態を示す。
なお、図示の都合上、図8の状態cと状態aとに圧力差を生じさせるように図示しているが、実際には、冷媒流路における圧力損失による低下程度である。
この状態で圧縮機3が起動されると、低圧のガス冷媒(状態a)が圧縮機3で圧縮され高温高圧のガス冷媒(状態b)となって吐出される。圧縮機3から吐出された高圧高温のガス冷媒は、四方弁4及びガス配管5を介して室内機2の利用側熱交換器6に流入し、室内空気との熱交換により放熱することで高圧液冷媒(状態e)となり流出する。利用側熱交換器6から流出した高圧液冷媒は、液配管8を通過して膨張弁7に流入し、低圧の二相冷媒(状態d)となる。
一方、気液分離器32によって分離された液冷媒(状態c)は、熱源側熱交換器9に流入し、室外空気との熱交換により蒸発することで低圧ガス冷媒(状態f)となって流出する。熱源側熱交換器9を流出した低圧ガス冷媒は、四方弁4を介して、圧縮機3へ戻る。
ポンプダウン運転時において、第3バイパス開閉弁23は開状態である。
この状態で、上記実施の形態2と同様の動作により、ポンプダウン運転が行われる。
このため、上記実施の形態1、2の効果に加えて以下の効果がある。即ち、暖房運転時において、気液分離器32で分離したガス冷媒をバイパス回路20へ流入させるので、蒸発器として作用する熱源側熱交換器9に流入する冷媒の乾き度が低下し、冷媒の圧力損失を低減することができる。また、熱交換への寄与が小さいガス冷媒をバイパスすることで、冷凍性能を向上することができる。よって、暖房運転時における省エネルギー性を向上することができる。
なお、上記の説明では、実施の形態2の構成に加え、気液分離器32を備える構成を説明したが、実施の形態1の構成に加えて気液分離器32を備える構成としても良い。このような構成においても、暖房運転時に、第1バイパス開閉弁21及び第2バイパス開閉弁22を開状態にすることで、気液分離器32によって分離された低圧のガス冷媒を、容器30を通過させて、圧縮機3の吸入側へ合流させることができる。このような構成においても、同様の効果を得ることができる。
Claims (5)
- 圧縮機、熱源側熱交換器、膨張弁、及び利用側熱交換器が配管で接続され、冷媒が循環する冷媒回路を備えた空気調和装置であって、
前記膨張弁と前記利用側熱交換器との間の前記配管に設けられた第1開閉弁と、
前記膨張弁と前記第1開閉弁との間の前記配管、又は前記熱源側熱交換器と前記膨張弁との間の前記配管を分岐し、前記圧縮機の吸入側の前記配管に接続するバイパス回路と、
前記バイパス回路を流通した前記冷媒を貯留する冷媒貯留手段と、
を備え、
前記第1開閉弁が閉状態で、前記圧縮機を運転させるポンプダウン運転において、
前記熱源側熱交換器を流出した前記冷媒が前記バイパス回路に流入し、該冷媒が前記冷媒貯留手段に貯留される
空気調和装置。 - 前記バイパス回路の前記冷媒の流入側に設けられた第1バイパス開閉弁と、
前記バイパス回路の前記冷媒の流出側に設けられた第2バイパス開閉弁と、
を更に備え、
前記冷媒貯留手段は、前記冷媒を貯留する容器によって構成され、前記第1バイパス開閉弁と前記第2バイパス開閉弁との間の前記バイパス回路に設けられ、
前記第1バイパス開閉弁が開状態、前記第2バイパス開閉弁が閉状態で前記ポンプダウン運転が実行され、
前記バイパス回路に流入した前記冷媒が前記容器に貯留される
請求項1に記載の空気調和装置。 - 前記バイパス回路に設けられた第2膨張弁を、更に備え、
前記冷媒貯留手段は、前記圧縮機の吸入側に設けられたアキュムレータによって構成され、
前記バイパス回路は、前記アキュムレータの吸入側と前記利用側熱交換器との間の前記配管に接続され、
前記ポンプダウン運転において、
前記バイパス回路へ流入した前記冷媒が前記第2膨張弁で膨張され、該冷媒が前記アキュムレータへ流入し、
前記アキュムレータに流入した前記冷媒が貯留される
請求項1に記載の空気調和装置。 - 前記膨張弁と前記第1開閉弁との間の前記配管に設けられた気液分離器を、更に備え、
前記バイパス回路は、前記気液分離器のガス側と前記圧縮機の吸入側の前記配管とを接続し、
前記熱源側熱交換器が凝縮器として作用し、前記利用側熱交換器が蒸発器として作用する冷房運転において、
前記気液分離器で分離されたガス状態の前記冷媒が、前記バイパス回路に流入する
請求項1~3の何れか一項に記載の空気調和装置。 - 前記熱源側熱交換器と前記膨張弁との間の前記配管に設けられた気液分離器を、更に備え、
前記バイパス回路は、前記気液分離器のガス側と前記圧縮機の吸入側の前記配管とを接続し、
前記熱源側熱交換器が蒸発器として作用し、前記利用側熱交換器が凝縮器として作用する暖房運転において、
前記気液分離器で分離されたガス状態の前記冷媒が、前記バイパス回路に流入する
請求項1~3の何れか一項に記載の空気調和装置。
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CN106062490A (zh) | 2016-10-26 |
KR20160121581A (ko) | 2016-10-19 |
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EP3115714B1 (en) | 2018-11-28 |
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