WO2021166126A1 - Air-conditioning device - Google Patents

Air-conditioning device Download PDF

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Publication number
WO2021166126A1
WO2021166126A1 PCT/JP2020/006558 JP2020006558W WO2021166126A1 WO 2021166126 A1 WO2021166126 A1 WO 2021166126A1 JP 2020006558 W JP2020006558 W JP 2020006558W WO 2021166126 A1 WO2021166126 A1 WO 2021166126A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
pipe
decompression device
air conditioner
compressor
Prior art date
Application number
PCT/JP2020/006558
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French (fr)
Japanese (ja)
Inventor
尚平 石村
宗史 池田
渡辺　和也
和也 本田
直史 竹中
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2020/006558 priority Critical patent/WO2021166126A1/en
Priority to JP2020536830A priority patent/JPWO2021166126A1/ja
Publication of WO2021166126A1 publication Critical patent/WO2021166126A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled

Definitions

  • This disclosure relates to an air conditioner.
  • HFC refrigerants are widely used in air conditioners.
  • an HFC refrigerant leaks, it stays in the atmosphere for a long period of time without being decomposed due to its chemical stability, and has a problem of exhibiting a greenhouse effect. Therefore, from the viewpoint of protecting the global environment, it is desirable to use a refrigerant having a small value of global warming potential, which decomposes relatively quickly even if it is released into the atmosphere, in the air conditioner.
  • the global warming potential is called GWP (Global Warming Potential) and is a value indicating the degree of the greenhouse effect based on the greenhouse effect of carbon dioxide.
  • an HC refrigerant such as R290 (propane) having a low GWP is considered as one of the alternative candidates.
  • R290 propane
  • the HC refrigerant has a small gas density, there is a problem that the pressure loss increases due to the increase in the flow velocity of the refrigerant in the gas phase state, which causes a decrease in performance.
  • Patent Document 1 in a refrigeration cycle in which a compressor, a condenser, an expansion valve, and an evaporator are sequentially connected by a refrigerant pipe, a space between the condenser and the expansion valve and a space between the evaporator and the compressor are provided.
  • An air conditioner provided with a communicating bypass circuit is disclosed. A part of the liquid refrigerant flowing out of the condenser flows into the bypass circuit.
  • the bypass circuit is provided with a pressure control valve having a function of opening and closing the circuit and an expansion function, and a double pipe as a refrigerant heat exchanger.
  • the low-temperature low-pressure refrigerant that has flowed into the bypass circuit and has been decompressed by the pressure control valve exchanges heat with the high-temperature high-pressure refrigerant that has flowed out of the condenser by the refrigerant heat exchanger, heats and boils, and is then sent to the suction side of the compressor. It is mixed with the refrigerant flowing out of the evaporator and sucked into the compressor.
  • the present disclosure has been made to solve the above problems. Even if a refrigerant having a low gas density such as an HC refrigerant is used, the flow velocity of the refrigerant in the gas phase state can be reduced and the pressure loss is increased. It is an object of the present invention to provide an air conditioner capable of simplifying a refrigerant circuit capable of suppressing the above-mentioned problems and reducing the cost.
  • a compressor, a condenser, a decompression device, and an evaporator are connected in order by a refrigerant pipe, and a main circuit in which a refrigerant circulates, and the condenser and the decompression device are used.
  • It has a bypass pipe that branches from the refrigerant pipe between them and is connected to the refrigerant pipe between the evaporator and the compressor, and the bypass pipe reduces the pressure of the refrigerant flowing through the bypass pipe and at the same time.
  • a thin tube for heat exchange is provided between the refrigerant flowing through the bypass pipe and the liquid refrigerant flowing through the refrigerant pipe in the portion between the condenser and the decompression device.
  • the thin tube reduces the pressure of the refrigerant flowing through the bypass pipe and exchanges heat between the refrigerant and the liquid refrigerant flowing through the refrigerant pipe of the main circuit to produce a low-temperature low-pressure gas refrigerant. Since it is configured to be sent to the refrigerant pipe on the suction side of the compression chamber, even if a refrigerant having a low gas density such as HC refrigerant is used, the refrigerant flow velocity in the vapor phase state can be reduced and an increase in pressure loss can be suppressed. Since this air conditioner has a configuration in which decompression and heat exchange are performed only with a thin tube, the refrigerant circuit can be simplified and the cost can be reduced.
  • FIG. 5 is a refrigerant circuit diagram of the air conditioner according to the first embodiment, which is effective during cooling operation. It is explanatory drawing which showed schematicly the thin tube of the air conditioner which concerns on Embodiment 1 of this embodiment.
  • FIG. 5 is a ph diagram of an air conditioner according to the first embodiment.
  • FIG. 5 is a refrigerant circuit diagram of the air conditioner according to the first embodiment, which is effective during a heating operation.
  • FIG. 5 is a refrigerant circuit diagram of the air conditioner according to the second embodiment, which is effective during cooling operation.
  • FIG. 5 is a refrigerant circuit diagram of the air conditioner according to the second embodiment, which is effective during a heating operation.
  • FIG. 1 is an air conditioner according to the first embodiment, and is a refrigerant circuit diagram effective during cooling operation.
  • FIG. 2 is an explanatory view schematically showing a thin tube of the air conditioner according to the first embodiment.
  • the air conditioner 100 includes an outdoor unit 200 and an indoor unit 300. Then, in the air conditioner 100, the compressor 1, the flow path switching device 2, the outdoor heat exchanger 3, the decompression device 4, and the indoor heat exchanger 5 are sequentially connected by the refrigerant pipe 10a, and the main circuit in which the refrigerant circulates. Has 10.
  • the compressor 1, the flow path switching device 2, the outdoor heat exchanger 3, and the decompression device 4 are provided in the outdoor unit 200.
  • the indoor heat exchanger 5 is provided in the indoor unit 300.
  • the air conditioner 100 is controlled by the control unit 6.
  • the control unit 6 is composed of an arithmetic unit such as a microcomputer or a CPU, and software executed on the arithmetic unit.
  • the control unit 6 may be configured by hardware such as a circuit device that realizes the function.
  • the compressor 1 compresses the sucked refrigerant and discharges it in a high temperature and high pressure state.
  • the compressor 1 is a positive displacement compressor having a configuration in which the operating capacity can be changed and is driven by a motor controlled by an inverter.
  • the flow path switching device 2 is a four-way valve as an example, and has a function of switching the flow path of the refrigerant.
  • the flow path switching device 2 connects the refrigerant discharge side of the compressor 1 and the gas side of the outdoor heat exchanger 3 during the cooling operation, and also connects the refrigerant suction side of the compressor 1 and the gas side of the indoor heat exchanger 5.
  • the refrigerant flow path is switched so as to connect with.
  • the flow path switching device 2 connects the refrigerant discharge side of the compressor 1 and the gas side of the indoor heat exchanger 5 during the heating operation, and also connects the refrigerant suction side of the compressor 1 and the outdoor heat exchanger 3. Switch the refrigerant flow path so as to connect to the gas side.
  • the flow path switching device 2 may be configured by combining, for example, a two-way valve or a three-way valve.
  • the outdoor heat exchanger 3 functions as a condenser during the cooling operation, and exchanges heat between the refrigerant discharged from the compressor 1 and the air. Further, the outdoor heat exchanger 3 functions as an evaporator during the heating operation, and causes heat exchange between the refrigerant flowing out from the decompression device 4 and the air. The outdoor heat exchanger 3 sucks in outdoor air by an outdoor blower and discharges the air that has exchanged heat with the refrigerant to the outside.
  • the decompression device 4 decompresses and expands the refrigerant flowing in the refrigerant circuit, and is composed of an electronic expansion valve whose opening degree is variably controlled as an example.
  • the indoor heat exchanger 5 functions as an evaporator during the cooling operation, and causes heat exchange between the refrigerant flowing out from the decompression device 4 and the air. Further, the indoor heat exchanger 5 functions as a condenser during the heating operation, and causes heat exchange between the refrigerant discharged from the compressor 1 and the air. The indoor heat exchanger 5 sucks indoor air by an indoor blower and supplies the air that has exchanged heat with the refrigerant into the room.
  • a Freon refrigerant or an HFO refrigerant is used as the refrigerant.
  • the fluorocarbon refrigerant include R32 refrigerants such as HFC-based refrigerants, R125 and R134a, and mixed refrigerants such as R410A, R407c and R404A.
  • the HFO refrigerant include HFO-1234yf, HFO-1234ze (E), and HFO-1234ze (Z).
  • a steam compression type heat pump such as a CO 2 refrigerant, an HC refrigerant (for example, propane, isobutane refrigerant), an ammonia refrigerant, and a mixed refrigerant of the above-mentioned refrigerant such as a mixed refrigerant of R32 and HFO-1234yf.
  • a CO 2 refrigerant for example, propane, isobutane refrigerant
  • an ammonia refrigerant such as a mixed refrigerant of R32 and HFO-1234yf.
  • a mixed refrigerant of the above-mentioned refrigerant such as a mixed refrigerant of R32 and HFO-1234yf.
  • the refrigerant used for is used.
  • the air conditioner 100 is a bypass pipe that branches from the refrigerant pipe 10a between the outdoor heat exchanger 3 and the decompression device 4 and is connected to the refrigerant pipe 10a between the indoor heat exchanger 5 and the compressor 1.
  • Has 11 In the bypass pipe 11, the refrigerant flowing through the bypass pipe 11 is depressurized, and the refrigerant flowing through the bypass pipe 11 and the liquid refrigerant flowing through the refrigerant pipe 10a in the portion between the outdoor heat exchanger 3 and the decompression device 4 are provided.
  • a thin tube 7 for exchanging heat between them is provided.
  • the bypass pipe 11 is provided with an on-off valve 8 for opening and closing the bypass pipe 11.
  • a capillary tube for example, a capillary tube is used.
  • the pipe diameter of the thin pipe 7 is smaller than the pipe diameter of the refrigerant pipe 10a constituting the main circuit 10.
  • the thin tube 7 is provided so as to be wound around the outer periphery of the refrigerant pipe 10a, and heat exchange is performed between the gas-liquid two-phase refrigerant flowing through the thin tube 7 and the liquid refrigerant flowing through the refrigerant pipe 10a.
  • the capillary tube 7 is not limited to the capillary tube, and may be another member.
  • the on-off valve 8 is, for example, an electronic valve and is controlled by the control unit 6.
  • the on-off valve 8 is controlled to open and close according to, for example, the magnitude of the frequency of the compressor 1.
  • the on-off valve 8 may be opened only when the required frequency of the compressor 1 is high and the flow rate of the refrigerant flowing through the refrigerant pipe 10a is large.
  • the on-off valve 8 does not necessarily have to be provided and may be omitted.
  • FIG. 3 is a ph diagram of the air conditioner according to the first embodiment.
  • the points (a) to (e) shown in FIG. 3 indicate the state of the refrigerant at the points (a) to (e) shown in FIG.
  • the state of the refrigerant flowing through the main circuit 10 will be described.
  • the low-temperature low-pressure gas refrigerant is compressed by the compressor 1 and discharged as a high-temperature high-pressure gas refrigerant.
  • the refrigerant compression process of the compressor 1 is compressed so as to be heated by the amount of the adiabatic efficiency of the compressor 1 as compared with the case where the adiabatic compression is performed by the isentropic wire. It is represented by the line shown in (a).
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 passes through the flow path switching device 2 and flows into the outdoor heat exchanger 3.
  • the refrigerant that has flowed into the outdoor heat exchanger 3 is cooled while heating the outdoor air, and becomes a medium-temperature, high-pressure liquid refrigerant.
  • the change in the refrigerant in the outdoor heat exchanger 3 is represented by a slightly inclined straight line shown from the point (a) to the point (b) in FIG.
  • the medium-temperature and high-pressure liquid refrigerant flowing out of the outdoor heat exchanger 3 becomes a low-temperature and high-pressure liquid refrigerant by exchanging heat with the low-temperature gas-liquid two-phase refrigerant flowing through the thin tube 7.
  • the change in the refrigerant at this time changes from the point (b) to the point (c).
  • the low-temperature, high-pressure liquid refrigerant that has exchanged heat with the thin tube 7 flows into the decompression device 4, where it is squeezed to expand and depressurize, resulting in a low-temperature, low-pressure, gas-liquid two-phase state.
  • the change of the refrigerant in the decompression device 4 is performed under a constant enthalpy, and is represented by a vertical line shown by points (c) to (d) in FIG.
  • the refrigerant flowing into the indoor heat exchanger 5 is heated while cooling the indoor air, and becomes a low-temperature low-pressure gas refrigerant.
  • the change in the refrigerant in the indoor heat exchanger 5 is represented by a slightly inclined straight line shown from the point (d) to the point (e) in FIG. 3 in consideration of the pressure loss.
  • the low-temperature low-pressure gas refrigerant flowing out of the indoor heat exchanger 5 passes through the flow path switching device 2, then merges with the low-temperature low-pressure gas refrigerant flowing in from the bypass pipe 11, flows into the compressor 1, and is compressed. NS.
  • a part of the medium-temperature and high-pressure liquid refrigerant that has flowed out of the outdoor heat exchanger 3 is branched into the bypass pipe 11, passes through the on-off valve 8, and flows into the thin pipe 7.
  • the refrigerant flowing through the thin tube 7 becomes low in temperature as the pressure gradually decreases, and evaporates by exchanging heat with the medium-temperature liquid refrigerant flowing in the refrigerant pipe 10a of the main circuit 10 to become a low-temperature low-pressure gas refrigerant.
  • the change in the refrigerant at this time changes from the point (b) to the point (e) in FIG.
  • the low-temperature low-pressure gas refrigerant flowing through the bypass pipe 11 merges with the low-temperature low-pressure gas refrigerant flowing out of the indoor heat exchanger 5 and flows into the compressor 1.
  • FIG. 4 is a refrigerant circuit diagram of the air conditioner according to the first embodiment, which is effective during the heating operation.
  • the indoor heat exchanger 5 functions as a condenser and the outdoor heat exchanger 3 functions as an evaporator during the heating operation. Therefore, the bypass pipe 11 of the air conditioner 100 shown in FIG. 4 branches from the refrigerant pipe 10a between the indoor heat exchanger 5 and the decompression device 4, and the refrigerant between the outdoor heat exchanger 3 and the compressor 1 It is provided so as to be connected to the pipe 10a.
  • the thin pipe 7 provided in the bypass pipe 11 decompresses the refrigerant flowing through the bypass pipe 11, and also flows the refrigerant flowing through the bypass pipe 11 and the refrigerant pipe 10a in the portion between the indoor heat exchanger 5 and the decompression device 4. Heat exchange is performed between the liquid refrigerant and the liquid refrigerant.
  • a part of the medium-temperature and high-pressure liquid refrigerant that has flowed out of the indoor heat exchanger 5 is branched into the bypass pipe 11, passes through the on-off valve 8, and flows into the thin pipe 7.
  • the refrigerant flowing through the thin tube 7 becomes low in temperature as the pressure gradually decreases, and evaporates by exchanging heat with the medium-temperature liquid refrigerant flowing in the refrigerant pipe 10a of the main circuit 10 to become a low-temperature low-pressure gas refrigerant.
  • the refrigerant state during the heating operation of the air conditioner 100 is shown in the ph diagram shown in FIG. 3, and the points (a) to (e) shown in FIG. 4 are the points (a) shown in FIG. ) To the state of the refrigerant at the point (e).
  • the compressor 1 for compressing the refrigerant, the condenser (3 or 5), the decompression device 4, and the evaporator (3 or 5) are included.
  • the main circuit 10 is connected by pipes in order and the refrigerant circulates, and the refrigerant pipe 10a between the condenser (3 or 5) and the decompression device 4 branches to the evaporator (3 or 5) and the compressor 1. It has a bypass pipe 11 connected to the refrigerant pipe 10a between them.
  • the refrigerant flowing through the bypass pipe 11 is depressurized, and the refrigerant flowing through the bypass pipe 11 and the liquid refrigerant flowing through the refrigerant pipe 10a in the portion between the condenser (3 or 5) and the decompression device 4 are used.
  • a thin tube 7 for exchanging heat between the two is provided.
  • the thin tube 7 reduces the pressure of the refrigerant flowing through the bypass pipe 11 and between the refrigerant and the liquid refrigerant flowing through the refrigerant pipe 10a of the main circuit 10. Since heat is exchanged and low-temperature low-pressure gas refrigerant is sent to the refrigerant pipe 10a on the suction side of the compressor 1, even if a refrigerant having a low gas density such as HC refrigerant is used, the refrigerant flow velocity in the vapor phase state is reduced. It is possible to suppress an increase in pressure loss. Since the air conditioner 100 has a configuration in which decompression and heat exchange are performed only by the thin tube 7, the refrigerant circuit can be simplified and the cost can be reduced.
  • the thin tube 7 is provided so as to be wound around the outer periphery of the refrigerant pipe 10a, and is provided between the refrigerant flowing through the bypass pipe 11 and the liquid refrigerant flowing through the refrigerant pipe 10a between the condenser (3 or 5) and the decompression device 4. It is a configuration that exchanges heat. Therefore, the air conditioner 100 according to the first embodiment can effectively simplify the refrigerant circuit.
  • the bypass pipe 11 is provided with an on-off valve 8 for opening and closing the bypass pipe 11.
  • the on-off valve 8 is controlled to open and close according to the magnitude of the frequency of the compressor 1. Therefore, the air conditioner 100 according to the first embodiment opens the bypass pipe 11 when, for example, the required frequency of the compressor 1 is high and the flow rate of the refrigerant flowing through the refrigerant pipe 10a is large, and the required compressor 1 is used.
  • the bypass pipe 11 can be closed, and the operation efficiency can be improved.
  • FIG. 5 is a refrigerant circuit diagram of the air conditioner according to the second embodiment, which is effective during the cooling operation.
  • FIG. 6 is a refrigerant circuit diagram of the air conditioner according to the second embodiment, which is effective during the heating operation.
  • the same components as those of the air conditioner described in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted as appropriate.
  • the main circuit 10 of the air conditioner 101 according to the second embodiment includes a compressor 1, a flow path switching device 2, an outdoor heat exchanger 3, a first decompression device 40, a second decompression device 41, and an indoor heat exchanger 5.
  • the first decompression device 40 and the second decompression device 41 decompress and expand the refrigerant flowing in the refrigerant circuit, and are composed of an electronic expansion valve whose opening degree is variably controlled as an example.
  • the first decompression device 40 is controlled so as to be fully opened during the cooling operation.
  • the bypass pipe 11 has a configuration that branches from the refrigerant pipe 10a between the first decompression device 40 and the second decompression device 41 and is connected to the refrigerant pipe 10a between the indoor heat exchanger 5 and the compressor 1. ..
  • the refrigerant flowing through the bypass pipe 11 is depressurized, and the refrigerant flowing through the bypass pipe 11 and the liquid refrigerant flowing through the refrigerant pipe 10a in the portion between the outdoor heat exchanger 3 and the second decompression device 41 are used.
  • a thin tube 7 for exchanging heat between the two is provided.
  • the bypass pipe 11 is provided with an on-off valve 8 for opening and closing the bypass pipe 11.
  • a capillary tube for example, a capillary tube is used.
  • the pipe diameter of the thin pipe 7 is smaller than the pipe diameter of the refrigerant pipe 10a constituting the main circuit 10.
  • the thin tube 7 is provided so as to be wound around the outer periphery of the refrigerant pipe 10a, and heat exchange is performed between the gas-liquid two-phase refrigerant flowing through the thin tube 7 and the liquid refrigerant flowing through the refrigerant pipe 10a.
  • the capillary tube 7 is not limited to the capillary tube, and may be another member.
  • the on-off valve 8 is, for example, an electronic valve and is controlled by the control unit 6.
  • the on-off valve 8 is controlled to open and close according to, for example, the magnitude of the frequency of the compressor 1.
  • the on-off valve 8 may be opened only when the required frequency of the compressor 1 is high and the flow rate of the refrigerant flowing through the refrigerant pipe 10a is large.
  • the on-off valve 8 does not necessarily have to be provided and may be omitted.
  • the points (a) to (e) shown in FIG. 3 indicate the state of the refrigerant at the points (a) to (e) shown in FIG.
  • the low-temperature low-pressure gas refrigerant is compressed by the compressor 1 and discharged as a high-temperature high-pressure gas refrigerant.
  • the refrigerant compression process of the compressor 1 is compressed so as to be heated by the amount of the adiabatic efficiency of the compressor 1 as compared with the case where the adiabatic compression is performed by the isentropic wire. It is represented by the line shown in (a).
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 passes through the flow path switching device 2 and flows into the outdoor heat exchanger 3.
  • the refrigerant that has flowed into the outdoor heat exchanger 3 is cooled while heating the outdoor air, and becomes a medium-temperature, high-pressure liquid refrigerant.
  • the change in the refrigerant in the outdoor heat exchanger 3 is represented by a slightly inclined straight line shown from the point (a) to the point (b) in FIG.
  • the medium-temperature and high-pressure liquid refrigerant flowing out of the outdoor heat exchanger 3 passes through the fully opened first decompression device 40 and exchanges heat with the low-temperature gas-liquid two-phase refrigerant flowing through the thin tube 7, so that the low-temperature and high-pressure liquid refrigerant flows. It becomes.
  • the change in the refrigerant at this time changes from the point (b) to the point (c).
  • the low-temperature and high-pressure liquid refrigerant that has exchanged heat with the thin tube 7 flows into the second decompression device 41, where it is squeezed to expand and depressurize, resulting in a low-temperature and low-pressure gas-liquid two-phase state.
  • the change of the refrigerant in the second decompression device 41 is performed under a constant enthalpy, and is represented by a vertical line shown by points (c) to (d) in FIG.
  • the refrigerant flowing into the indoor heat exchanger 5 is heated while cooling the indoor air, and becomes a low-temperature low-pressure gas refrigerant.
  • the change in the refrigerant in the indoor heat exchanger 5 is represented by a slightly inclined straight line shown from the point (d) to the point (e) in FIG. 3 in consideration of the pressure loss.
  • the low-temperature low-pressure gas refrigerant flowing out of the indoor heat exchanger 5 passes through the flow path switching device 2, then merges with the low-temperature low-pressure gas refrigerant flowing in from the bypass pipe 11, flows into the compressor 1, and is compressed. NS.
  • a part of the medium-temperature and high-pressure liquid refrigerant that has flowed out of the outdoor heat exchanger 3 is branched into the bypass pipe 11, passes through the on-off valve 8, and flows into the thin pipe 7.
  • the refrigerant flowing through the thin tube 7 becomes low in temperature as the pressure gradually decreases, and evaporates by exchanging heat with the medium-temperature liquid refrigerant flowing in the refrigerant pipe 10a of the main circuit 10 to become a low-temperature low-pressure gas refrigerant.
  • the change in the refrigerant at this time changes from the point (b) to the point (e) in FIG.
  • the low-temperature low-pressure gas refrigerant flowing through the bypass pipe 11 merges with the low-temperature low-pressure gas refrigerant flowing out of the indoor heat exchanger 5 and flows into the compressor 1.
  • the flow of the refrigerant is opposite to that in the cooling operation in the heating operation, so that the second decompression device 41 is fully opened.
  • the refrigerant is depressurized by the first decompression device 40.
  • the thin pipe 7 provided in the bypass pipe 11 decompresses the refrigerant flowing through the bypass pipe 11, and the refrigerant pipe 10a in the portion between the refrigerant flowing through the bypass pipe 11 and the indoor heat exchanger 5 and the first decompression device 40. Heat exchange is performed between the liquid refrigerant flowing through the pipe and the liquid refrigerant flowing through the pipe.
  • the refrigerant state during the heating operation of the air conditioner 101 according to the second embodiment is shown by the ph diagram shown in FIG. 3, and points (a) to (e) shown in FIG. 6 are shown.
  • the state of the refrigerant at the points (a) to (e) shown in FIG. 3 is shown.
  • a bypass circuit is provided during both the cooling operation and the heating operation. Can be enabled.
  • the air conditioner 100 and 101 have been described above based on the embodiment, the air conditioner 100 and 101 are not limited to the configuration of the above-described embodiment.
  • the air conditioners 100 and 101 are not limited to the above-mentioned components, and may include other components.
  • the embodiment in which one indoor unit 300 is connected to one outdoor unit 200 has been described, but the present invention is not limited to this.
  • a plurality of indoor units 300 may be connected to one outdoor unit 200.
  • the air conditioners 100 and 101 include a range of design changes and application variations normally performed by those skilled in the art, as long as they do not deviate from the technical idea thereof.

Abstract

In the present invention, an air-conditioning device has: a main circuit in which a compressor, a condenser, a decompression device, and an evaporator are connected in the stated order by refrigerant piping, a refrigerant circulating in the main circuit; and bypass piping that branches from the refrigerant piping between the condenser and the decompression device and that is connected to the refrigerant piping between the evaporator and the compressor. The bypass piping is provided with a thin pipe in which refrigerant flowing through the bypass piping is decompressed, and in which heat is exchanged between the refrigerant flowing through the bypass piping and a liquid refrigerant flowing through the refrigerant piping in the portion between the condenser and the decompression device.

Description

空気調和装置Air conditioner
　本開示は、空気調和装置に関するものである。 This disclosure relates to an air conditioner.
　現在、空気調和装置では、例えばＨＦＣ冷媒が広く使用されている。ＨＦＣ冷媒は、漏洩すると、その化学的安定性から長期間大気中に分解されずに滞留し、温室効果を発揮するという問題がある。そのため、空気調和装置では、地球環境を守る観点から、万が一大気中に放出されても比較的早く分解されるような地球温暖化係数の値が小さい冷媒を使用することが望ましい。地球温暖化係数は、ＧＷＰ（Ｇｌｏｂａｌ　Ｗａｒｍｉｎｇ　Ｐｏｔｅｎｔｉａｌ）と称され、二酸化炭素の温室効果を基準にした温室効果の度合いを示す値である。そこで、ＧＷＰの低いＲ２９０（プロパン）などのＨＣ冷媒が、代替候補の一つに考えられている。しかし、ＨＣ冷媒は、気体密度が小さいため、気相状態の冷媒流速が増大することで圧力損失が増大し、性能の低下を引き起こす問題がある。 Currently, for example, HFC refrigerants are widely used in air conditioners. When an HFC refrigerant leaks, it stays in the atmosphere for a long period of time without being decomposed due to its chemical stability, and has a problem of exhibiting a greenhouse effect. Therefore, from the viewpoint of protecting the global environment, it is desirable to use a refrigerant having a small value of global warming potential, which decomposes relatively quickly even if it is released into the atmosphere, in the air conditioner. The global warming potential is called GWP (Global Warming Potential) and is a value indicating the degree of the greenhouse effect based on the greenhouse effect of carbon dioxide. Therefore, an HC refrigerant such as R290 (propane) having a low GWP is considered as one of the alternative candidates. However, since the HC refrigerant has a small gas density, there is a problem that the pressure loss increases due to the increase in the flow velocity of the refrigerant in the gas phase state, which causes a decrease in performance.
　そこで、例えば特許文献１には、圧縮機、凝縮器、膨張弁及び蒸発器を順次に冷媒配管で接続した冷凍サイクルに、凝縮器と膨張弁との間及び蒸発器と圧縮器との間を連絡するバイパス回路を設けた空気調和装置が開示されている。バイパス回路には、凝縮器から流出した液冷媒の一部が流入する。バイパス回路には、同回路を開閉する機能及び膨張機能を有する圧力制御弁と、冷媒熱交換器として二重管が設けられている。バイパス回路に流入し、圧力制御弁で減圧された低温低圧冷媒は、冷媒熱交換器により凝縮器から流出した高温高圧冷媒と熱交換して加熱沸騰した後、圧縮機に吸入側に送られ、蒸発器から流出した冷媒と混合して圧縮機に吸入される。 Therefore, for example, in Patent Document 1, in a refrigeration cycle in which a compressor, a condenser, an expansion valve, and an evaporator are sequentially connected by a refrigerant pipe, a space between the condenser and the expansion valve and a space between the evaporator and the compressor are provided. An air conditioner provided with a communicating bypass circuit is disclosed. A part of the liquid refrigerant flowing out of the condenser flows into the bypass circuit. The bypass circuit is provided with a pressure control valve having a function of opening and closing the circuit and an expansion function, and a double pipe as a refrigerant heat exchanger. The low-temperature low-pressure refrigerant that has flowed into the bypass circuit and has been decompressed by the pressure control valve exchanges heat with the high-temperature high-pressure refrigerant that has flowed out of the condenser by the refrigerant heat exchanger, heats and boils, and is then sent to the suction side of the compressor. It is mixed with the refrigerant flowing out of the evaporator and sucked into the compressor.
特開昭５４－１２９５４６号公報JP-A-54-129546
　しかしながら、例えば特許文献１の空気調和装置は、液冷媒の減圧に圧力制御弁が用いられ、冷媒熱交換器として二重管が用いられる。そのため、この空気調和装置では、圧力制御弁と冷媒熱交換器を追加することで、冷媒回路が複雑化し、高コスト化するおそれがある。 However, for example, in the air conditioner of Patent Document 1, a pressure control valve is used for depressurizing the liquid refrigerant, and a double pipe is used as the refrigerant heat exchanger. Therefore, in this air conditioner, the addition of the pressure control valve and the refrigerant heat exchanger may complicate the refrigerant circuit and increase the cost.
　本開示は、上記のような課題を解決するためになされたもので、例えばＨＣ冷媒のように気体密度が小さい冷媒を使用しても、気相状態の冷媒流速を低減でき、圧力損失の増大を抑制できる冷媒回路を、簡素化させて低コスト化を図ることができる空気調和装置を提供することを目的とする。 The present disclosure has been made to solve the above problems. Even if a refrigerant having a low gas density such as an HC refrigerant is used, the flow velocity of the refrigerant in the gas phase state can be reduced and the pressure loss is increased. It is an object of the present invention to provide an air conditioner capable of simplifying a refrigerant circuit capable of suppressing the above-mentioned problems and reducing the cost.
　本開示に係る空気調和装置は、圧縮機と、凝縮器と、減圧装置と、蒸発器と、が順に冷媒配管で接続され、冷媒が循環する主回路と、前記凝縮器と前記減圧装置との間の冷媒配管から分岐し、前記蒸発器と前記圧縮機との間の冷媒配管に接続されるバイパス配管と、を有し、前記バイパス配管には、該バイパス配管を流れる冷媒を減圧させると共に、前記バイパス配管を流れる冷媒と、前記凝縮器と前記減圧装置との間の部分における冷媒配管を流れる液冷媒と、の間で熱交換を行う細管が設けられているものである。 In the air conditioner according to the present disclosure, a compressor, a condenser, a decompression device, and an evaporator are connected in order by a refrigerant pipe, and a main circuit in which a refrigerant circulates, and the condenser and the decompression device are used. It has a bypass pipe that branches from the refrigerant pipe between them and is connected to the refrigerant pipe between the evaporator and the compressor, and the bypass pipe reduces the pressure of the refrigerant flowing through the bypass pipe and at the same time. A thin tube for heat exchange is provided between the refrigerant flowing through the bypass pipe and the liquid refrigerant flowing through the refrigerant pipe in the portion between the condenser and the decompression device.
　本開示の空気調和装置によれば、細管によって、バイパス配管を流れる冷媒を減圧させると共に、該冷媒と主回路の冷媒配管を流れる液冷媒との間で熱交換を行い、低温低圧のガス冷媒を圧縮室の吸入側の冷媒配管に送る構成なので、ＨＣ冷媒のように気体密度が小さい冷媒を使用しても、気相状態の冷媒流速を低減でき、圧力損失の増大を抑制できる。そして、この空気調和装置は、細管のみで減圧と熱交換とを行う構成なので、冷媒回路を簡素化させることができ、低コスト化を図ることができる。 According to the air conditioner of the present disclosure, the thin tube reduces the pressure of the refrigerant flowing through the bypass pipe and exchanges heat between the refrigerant and the liquid refrigerant flowing through the refrigerant pipe of the main circuit to produce a low-temperature low-pressure gas refrigerant. Since it is configured to be sent to the refrigerant pipe on the suction side of the compression chamber, even if a refrigerant having a low gas density such as HC refrigerant is used, the refrigerant flow velocity in the vapor phase state can be reduced and an increase in pressure loss can be suppressed. Since this air conditioner has a configuration in which decompression and heat exchange are performed only with a thin tube, the refrigerant circuit can be simplified and the cost can be reduced.
本実施の形態１に係る空気調和装置であって、冷房運転時に有効な冷媒回路図である。FIG. 5 is a refrigerant circuit diagram of the air conditioner according to the first embodiment, which is effective during cooling operation. 本実施の形態１に係る空気調和装置の細管を概略的に示した説明図である。It is explanatory drawing which showed schematicly the thin tube of the air conditioner which concerns on Embodiment 1 of this embodiment. 本実施の形態１に係る空気調和装置のｐ－ｈ線図である。FIG. 5 is a ph diagram of an air conditioner according to the first embodiment. 本実施の形態１に係る空気調和装置であって、暖房運転時に有効な冷媒回路図である。FIG. 5 is a refrigerant circuit diagram of the air conditioner according to the first embodiment, which is effective during a heating operation. 本実施の形態２に係る空気調和装置であって、冷房運転時に有効な冷媒回路図である。FIG. 5 is a refrigerant circuit diagram of the air conditioner according to the second embodiment, which is effective during cooling operation. 本実施の形態２に係る空気調和装置であって、暖房運転時に有効な冷媒回路図である。FIG. 5 is a refrigerant circuit diagram of the air conditioner according to the second embodiment, which is effective during a heating operation.
　以下、図面を参照して、本開示の実施の形態について説明する。なお、各図中、同一又は相当する部分には、同一符号を付して、その説明を適宜省略又は簡略化する。また、各図に記載の構成について、その形状、大きさ、及び配置等は、適宜変更することができる。 Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. In each figure, the same or corresponding parts are designated by the same reference numerals, and the description thereof will be omitted or simplified as appropriate. In addition, the shape, size, arrangement, etc. of the configurations shown in each figure can be changed as appropriate.
　実施の形態１．
　先ず、図１～図３に基づいて、本実施の形態１に係る空気調和装置１００の冷房運転時に有効な構成を説明する。図１は、本実施の形態１に係る空気調和装置であって、冷房運転時に有効な冷媒回路図である。図２は、本実施の形態１に係る空気調和装置の細管を概略的に示した説明図である。 Embodiment 1.
First, based on FIGS. 1 to 3, a configuration effective during the cooling operation of the air conditioner 100 according to the first embodiment will be described. FIG. 1 is an air conditioner according to the first embodiment, and is a refrigerant circuit diagram effective during cooling operation. FIG. 2 is an explanatory view schematically showing a thin tube of the air conditioner according to the first embodiment.
　本実施の形態１に係る空気調和装置１００は、図１に示すように、室外機２００と、室内機３００と、を備えている。そして、空気調和装置１００は、圧縮機１、流路切替装置２、室外熱交換器３、減圧装置４及び室内熱交換器５が、冷媒配管１０ａにより順次に接続され、冷媒が循環する主回路１０を有している。圧縮機１、流路切替装置２、室外熱交換器３及び減圧装置４は、室外機２００に設けられている。室内熱交換器５は、室内機３００に設けられている。この空気調和装置１００は、制御部６によって制御される。制御部６は、例えばマイコン又はＣＰＵのような演算装置と、その上で実行されるソフトウェアとにより構成される。なお、制御部６は、その機能を実現する回路デバイスのようなハードウェアで構成してもよい。 As shown in FIG. 1, the air conditioner 100 according to the first embodiment includes an outdoor unit 200 and an indoor unit 300. Then, in the air conditioner 100, the compressor 1, the flow path switching device 2, the outdoor heat exchanger 3, the decompression device 4, and the indoor heat exchanger 5 are sequentially connected by the refrigerant pipe 10a, and the main circuit in which the refrigerant circulates. Has 10. The compressor 1, the flow path switching device 2, the outdoor heat exchanger 3, and the decompression device 4 are provided in the outdoor unit 200. The indoor heat exchanger 5 is provided in the indoor unit 300. The air conditioner 100 is controlled by the control unit 6. The control unit 6 is composed of an arithmetic unit such as a microcomputer or a CPU, and software executed on the arithmetic unit. The control unit 6 may be configured by hardware such as a circuit device that realizes the function.
　圧縮機１は、吸入した冷媒を圧縮し、高温高圧の状態にして吐出するものである。圧縮機１は、一例として、運転容量を可変させることが可能とした構成であり、インバータにより制御されるモータによって駆動される容積式圧縮機である。 The compressor 1 compresses the sucked refrigerant and discharges it in a high temperature and high pressure state. As an example, the compressor 1 is a positive displacement compressor having a configuration in which the operating capacity can be changed and is driven by a motor controlled by an inverter.
　流路切替装置２は、一例として四方弁であり、冷媒の流路を切り換える機能を有するものである。流路切替装置２は、冷房運転時において、圧縮機１の冷媒吐出側と室外熱交換器３のガス側とを接続するとともに、圧縮機１の冷媒吸入側と室内熱交換器５のガス側とを接続するように冷媒流路を切り換える。一方、流路切替装置２は、暖房運転時において、圧縮機１の冷媒吐出側と室内熱交換器５のガス側とを接続するとともに、圧縮機１の冷媒吸入側と室外熱交換器３のガス側とを接続するように冷媒流路を切り換える。なお、流路切替装置２は、例えば二方弁又は三方弁を組み合わせて構成してもよい。 The flow path switching device 2 is a four-way valve as an example, and has a function of switching the flow path of the refrigerant. The flow path switching device 2 connects the refrigerant discharge side of the compressor 1 and the gas side of the outdoor heat exchanger 3 during the cooling operation, and also connects the refrigerant suction side of the compressor 1 and the gas side of the indoor heat exchanger 5. The refrigerant flow path is switched so as to connect with. On the other hand, the flow path switching device 2 connects the refrigerant discharge side of the compressor 1 and the gas side of the indoor heat exchanger 5 during the heating operation, and also connects the refrigerant suction side of the compressor 1 and the outdoor heat exchanger 3. Switch the refrigerant flow path so as to connect to the gas side. The flow path switching device 2 may be configured by combining, for example, a two-way valve or a three-way valve.
　室外熱交換器３は、冷房運転時には凝縮器として機能し、圧縮機１から吐出された冷媒と空気との間で熱交換を行わせるものである。また、室外熱交換器３は、暖房運転時には蒸発器として機能し、減圧装置４から流出した冷媒と空気との間で熱交換を行わせるものである。室外熱交換器３は、室外送風機によって室外空気を吸い込み、冷媒との間で熱交換した空気を室外に排出する。 The outdoor heat exchanger 3 functions as a condenser during the cooling operation, and exchanges heat between the refrigerant discharged from the compressor 1 and the air. Further, the outdoor heat exchanger 3 functions as an evaporator during the heating operation, and causes heat exchange between the refrigerant flowing out from the decompression device 4 and the air. The outdoor heat exchanger 3 sucks in outdoor air by an outdoor blower and discharges the air that has exchanged heat with the refrigerant to the outside.
　減圧装置４は、冷媒回路内を流れる冷媒を減圧して膨張させるものであり、一例として開度が可変に制御される電子膨張弁で構成される。 The decompression device 4 decompresses and expands the refrigerant flowing in the refrigerant circuit, and is composed of an electronic expansion valve whose opening degree is variably controlled as an example.
　室内熱交換器５は、冷房運転時には蒸発器として機能し、減圧装置４から流出した冷媒と空気との間で熱交換を行わせるものである。また、室内熱交換器５は、暖房運転時には凝縮器として機能し、圧縮機１から吐出された冷媒と空気との間で熱交換を行わせるものである。室内熱交換器５は、室内送風機によって室内空気を吸い込み、冷媒との間で熱交換した空気を室内に供給する。 The indoor heat exchanger 5 functions as an evaporator during the cooling operation, and causes heat exchange between the refrigerant flowing out from the decompression device 4 and the air. Further, the indoor heat exchanger 5 functions as a condenser during the heating operation, and causes heat exchange between the refrigerant discharged from the compressor 1 and the air. The indoor heat exchanger 5 sucks indoor air by an indoor blower and supplies the air that has exchanged heat with the refrigerant into the room.
　冷媒としては、フロン冷媒又はＨＦＯ冷媒が用いられる。フロン冷媒としては、例えば、ＨＦＣ系冷媒のＲ３２冷媒、Ｒ１２５、Ｒ１３４ａなど、又は、これらの混合冷媒のＲ４１０Ａ、Ｒ４０７ｃ、Ｒ４０４Ａなどがある。また、ＨＦＯ冷媒としては、例えば、ＨＦＯ－１２３４ｙｆ、ＨＦＯ－１２３４ｚｅ（Ｅ）、ＨＦＯ－１２３４ｚｅ（Ｚ）などがある。また、その他の冷媒としては、ＣＯ２冷媒、ＨＣ冷媒（例えばプロパン、イソブタン冷媒）、アンモニア冷媒、Ｒ３２とＨＦＯー１２３４ｙｆとの混合冷媒のように前記の冷媒の混合冷媒など、蒸気圧縮式のヒートポンプに用いられる冷媒が用いられる。 As the refrigerant, a Freon refrigerant or an HFO refrigerant is used. Examples of the fluorocarbon refrigerant include R32 refrigerants such as HFC-based refrigerants, R125 and R134a, and mixed refrigerants such as R410A, R407c and R404A. Examples of the HFO refrigerant include HFO-1234yf, HFO-1234ze (E), and HFO-1234ze (Z). Further, as other refrigerants , a steam compression type heat pump such as a CO 2 refrigerant, an HC refrigerant (for example, propane, isobutane refrigerant), an ammonia refrigerant, and a mixed refrigerant of the above-mentioned refrigerant such as a mixed refrigerant of R32 and HFO-1234yf. The refrigerant used for is used.
　また、空気調和装置１００は、室外熱交換器３と減圧装置４との間の冷媒配管１０ａから分岐し、室内熱交換器５と圧縮機１との間の冷媒配管１０ａに接続されるバイパス配管１１を有している。バイパス配管１１には、バイパス配管１１を流れる冷媒を減圧させると共に、バイパス配管１１を流れる冷媒と、室外熱交換器３と減圧装置４との間の部分における冷媒配管１０ａを流れる液冷媒と、の間で熱交換を行う細管７が設けられている。また、バイパス配管１１には、バイパス配管１１を開閉させる開閉弁８が設けられている。 Further, the air conditioner 100 is a bypass pipe that branches from the refrigerant pipe 10a between the outdoor heat exchanger 3 and the decompression device 4 and is connected to the refrigerant pipe 10a between the indoor heat exchanger 5 and the compressor 1. Has 11. In the bypass pipe 11, the refrigerant flowing through the bypass pipe 11 is depressurized, and the refrigerant flowing through the bypass pipe 11 and the liquid refrigerant flowing through the refrigerant pipe 10a in the portion between the outdoor heat exchanger 3 and the decompression device 4 are provided. A thin tube 7 for exchanging heat between them is provided. Further, the bypass pipe 11 is provided with an on-off valve 8 for opening and closing the bypass pipe 11.
　細管７は、例えばキャピラリーチューブが使用される。細管７の管径は、主回路１０を構成する冷媒配管１０ａの管径よりも小さい。細管７は、図２に示すように、冷媒配管１０ａの外周に巻き付けて設けられ、細管７を流れる気液二相冷媒と冷媒配管１０ａを流れる液冷媒との間で熱交換を行う。なお、細管７は、キャピラリーチューブに限定されず、他の部材でもよい。 For the capillary tube 7, for example, a capillary tube is used. The pipe diameter of the thin pipe 7 is smaller than the pipe diameter of the refrigerant pipe 10a constituting the main circuit 10. As shown in FIG. 2, the thin tube 7 is provided so as to be wound around the outer periphery of the refrigerant pipe 10a, and heat exchange is performed between the gas-liquid two-phase refrigerant flowing through the thin tube 7 and the liquid refrigerant flowing through the refrigerant pipe 10a. The capillary tube 7 is not limited to the capillary tube, and may be another member.
　開閉弁８は、例えば電子弁とされ、制御部６によって制御される。開閉弁８は、例えば圧縮機１の周波数の大きさに応じて開閉が制御される。主回路１０の冷媒配管１０ａを流れる冷媒流量が小さいときには、圧力損失が付き難く、冷媒をバイパスさせる効果が小さい。そのため、開閉弁８は、要求される圧縮機１の周波数が大きく、冷媒配管１０ａを流れる冷媒流量が大きい場合にのみ開いてもよい。但し、開閉弁８は、必ずしも設ける必要はなく、省略してもよい。 The on-off valve 8 is, for example, an electronic valve and is controlled by the control unit 6. The on-off valve 8 is controlled to open and close according to, for example, the magnitude of the frequency of the compressor 1. When the flow rate of the refrigerant flowing through the refrigerant pipe 10a of the main circuit 10 is small, pressure loss is unlikely to occur and the effect of bypassing the refrigerant is small. Therefore, the on-off valve 8 may be opened only when the required frequency of the compressor 1 is high and the flow rate of the refrigerant flowing through the refrigerant pipe 10a is large. However, the on-off valve 8 does not necessarily have to be provided and may be omitted.
　図３は、本実施の形態１に係る空気調和装置のｐ－ｈ線図である。図３に示す点（ａ）～点（ｅ）は、図１に示す点（ａ）～点（ｅ）での冷媒の状態を示している。先ず、主回路１０を流れる冷媒の状態について説明する。圧縮機１の運転を開始すると、低温低圧のガス冷媒が圧縮機１によって圧縮され、高温高圧のガス冷媒となって吐出される。この圧縮機１の冷媒圧縮過程は、圧縮機１の断熱効率の分だけ、等エントロピ線で断熱圧縮される場合と比較して加熱されるように圧縮され、図３の点（ｅ）から点（ａ）に示す線で表される。 FIG. 3 is a ph diagram of the air conditioner according to the first embodiment. The points (a) to (e) shown in FIG. 3 indicate the state of the refrigerant at the points (a) to (e) shown in FIG. First, the state of the refrigerant flowing through the main circuit 10 will be described. When the operation of the compressor 1 is started, the low-temperature low-pressure gas refrigerant is compressed by the compressor 1 and discharged as a high-temperature high-pressure gas refrigerant. The refrigerant compression process of the compressor 1 is compressed so as to be heated by the amount of the adiabatic efficiency of the compressor 1 as compared with the case where the adiabatic compression is performed by the isentropic wire. It is represented by the line shown in (a).
　圧縮機１から吐出された高温高圧のガス冷媒は、流路切替装置２を通過して室外熱交換器３に流入する。室外熱交換器３に流入した冷媒は、室外空気を加熱しながら冷却され、中温高圧の液冷媒となる。室外熱交換器３での冷媒変化は、圧力損失を考慮すると、図３の点（ａ）から点（ｂ）に示すやや傾いた水平に近い直線で表される。 The high-temperature and high-pressure gas refrigerant discharged from the compressor 1 passes through the flow path switching device 2 and flows into the outdoor heat exchanger 3. The refrigerant that has flowed into the outdoor heat exchanger 3 is cooled while heating the outdoor air, and becomes a medium-temperature, high-pressure liquid refrigerant. Considering the pressure loss, the change in the refrigerant in the outdoor heat exchanger 3 is represented by a slightly inclined straight line shown from the point (a) to the point (b) in FIG.
　室外熱交換器３から流出した中温高圧の液冷媒は、細管７を流れる低温の気液二相冷媒と熱交換することで低温高圧の液冷媒となる。このときの冷媒変化は点（ｂ）から点（ｃ）となる。細管７と熱交換した低温高圧の液冷媒は、減圧装置４に流入し、ここで絞られて膨張及び減圧し、低温低圧の気液二相状態になる。この減圧装置４での冷媒の変化は、エンタルピーが一定のもとで行われ、図３の点（ｃ）から点（ｄ）に示す垂直線で表される。 The medium-temperature and high-pressure liquid refrigerant flowing out of the outdoor heat exchanger 3 becomes a low-temperature and high-pressure liquid refrigerant by exchanging heat with the low-temperature gas-liquid two-phase refrigerant flowing through the thin tube 7. The change in the refrigerant at this time changes from the point (b) to the point (c). The low-temperature, high-pressure liquid refrigerant that has exchanged heat with the thin tube 7 flows into the decompression device 4, where it is squeezed to expand and depressurize, resulting in a low-temperature, low-pressure, gas-liquid two-phase state. The change of the refrigerant in the decompression device 4 is performed under a constant enthalpy, and is represented by a vertical line shown by points (c) to (d) in FIG.
　減圧装置４から流出した低温低圧の気液二相状態の冷媒は、室内熱交換器５に流入する。室内熱交換器５に流入した冷媒は、室内空気を冷却しながら加熱され、低温低圧のガス冷媒となる。室内熱交換器５での冷媒の変化は、圧力損失を考慮すると、図３の点（ｄ）から点（ｅ）に示すやや傾いた水平に近い直線で表される。室内熱交換器５を流出した低温低圧のガス冷媒は、流路切替装置２を通った後、バイパス配管１１から流入する低温低圧のガス冷媒と合流して、圧縮機１に流入し、圧縮される。 The low-temperature low-pressure gas-liquid two-phase refrigerant flowing out of the decompression device 4 flows into the indoor heat exchanger 5. The refrigerant flowing into the indoor heat exchanger 5 is heated while cooling the indoor air, and becomes a low-temperature low-pressure gas refrigerant. The change in the refrigerant in the indoor heat exchanger 5 is represented by a slightly inclined straight line shown from the point (d) to the point (e) in FIG. 3 in consideration of the pressure loss. The low-temperature low-pressure gas refrigerant flowing out of the indoor heat exchanger 5 passes through the flow path switching device 2, then merges with the low-temperature low-pressure gas refrigerant flowing in from the bypass pipe 11, flows into the compressor 1, and is compressed. NS.
　次に、バイパス配管１１を流れる冷媒の状態について説明する。室外熱交換器３を流出した中温高圧の液冷媒の一部は、バイパス配管１１に分岐され、開閉弁８を通過し、細管７に流入する。細管７を流れる冷媒は、徐々に圧力が低下することで低温になり、主回路１０の冷媒配管１０ａを流れる中温の液冷媒と熱交換することで蒸発し、低温低圧のガス冷媒となる。このときの冷媒変化は、図３の点（ｂ）から点（ｅ）となる。そして、バイパス配管１１を流れる低温低圧のガス冷媒は、室内熱交換器５を流出した低温低圧のガス冷媒と合流して、圧縮機１に流入する。 Next, the state of the refrigerant flowing through the bypass pipe 11 will be described. A part of the medium-temperature and high-pressure liquid refrigerant that has flowed out of the outdoor heat exchanger 3 is branched into the bypass pipe 11, passes through the on-off valve 8, and flows into the thin pipe 7. The refrigerant flowing through the thin tube 7 becomes low in temperature as the pressure gradually decreases, and evaporates by exchanging heat with the medium-temperature liquid refrigerant flowing in the refrigerant pipe 10a of the main circuit 10 to become a low-temperature low-pressure gas refrigerant. The change in the refrigerant at this time changes from the point (b) to the point (e) in FIG. Then, the low-temperature low-pressure gas refrigerant flowing through the bypass pipe 11 merges with the low-temperature low-pressure gas refrigerant flowing out of the indoor heat exchanger 5 and flows into the compressor 1.
　次に、図４に基づいて、本実施の形態１に係る空気調和装置１００の暖房運転時に有効な構成を説明する。図４は、本実施の形態１に係る空気調和装置であって、暖房運転時に有効な冷媒回路図である。本実施の形態１に係る空気調和装置１００では、暖房運転時において、室内熱交換器５が凝縮器として機能し、室外熱交換器３が蒸発器として機能する。そのため、図４に示す空気調和装置１００のバイパス配管１１は、室内熱交換器５と減圧装置４との間の冷媒配管１０ａから分岐し、室外熱交換器３と圧縮機１との間の冷媒配管１０ａに接続されるように設けられている。 Next, based on FIG. 4, a configuration effective during the heating operation of the air conditioner 100 according to the first embodiment will be described. FIG. 4 is a refrigerant circuit diagram of the air conditioner according to the first embodiment, which is effective during the heating operation. In the air conditioner 100 according to the first embodiment, the indoor heat exchanger 5 functions as a condenser and the outdoor heat exchanger 3 functions as an evaporator during the heating operation. Therefore, the bypass pipe 11 of the air conditioner 100 shown in FIG. 4 branches from the refrigerant pipe 10a between the indoor heat exchanger 5 and the decompression device 4, and the refrigerant between the outdoor heat exchanger 3 and the compressor 1 It is provided so as to be connected to the pipe 10a.
　バイパス配管１１に設けられた細管７は、バイパス配管１１を流れる冷媒を減圧させると共に、バイパス配管１１を流れる冷媒と、室内熱交換器５と減圧装置４との間の部分における冷媒配管１０ａを流れる液冷媒と、の間で熱交換を行う。 The thin pipe 7 provided in the bypass pipe 11 decompresses the refrigerant flowing through the bypass pipe 11, and also flows the refrigerant flowing through the bypass pipe 11 and the refrigerant pipe 10a in the portion between the indoor heat exchanger 5 and the decompression device 4. Heat exchange is performed between the liquid refrigerant and the liquid refrigerant.
　室内熱交換器５を流出した中温高圧の液冷媒の一部は、バイパス配管１１に分岐され、開閉弁８を通過し、細管７に流入する。細管７を流れる冷媒は、徐々に圧力が低下することで低温になり、主回路１０の冷媒配管１０ａを流れる中温の液冷媒と熱交換することで蒸発し、低温低圧のガス冷媒となる。なお、空気調和装置１００の暖房運転時における冷媒状態は、図３に示すｐ－ｈ線図で示され、図４に示す点（ａ）～点（ｅ）が、図３に示す点（ａ）～点（ｅ）での冷媒の状態を示している。 A part of the medium-temperature and high-pressure liquid refrigerant that has flowed out of the indoor heat exchanger 5 is branched into the bypass pipe 11, passes through the on-off valve 8, and flows into the thin pipe 7. The refrigerant flowing through the thin tube 7 becomes low in temperature as the pressure gradually decreases, and evaporates by exchanging heat with the medium-temperature liquid refrigerant flowing in the refrigerant pipe 10a of the main circuit 10 to become a low-temperature low-pressure gas refrigerant. The refrigerant state during the heating operation of the air conditioner 100 is shown in the ph diagram shown in FIG. 3, and the points (a) to (e) shown in FIG. 4 are the points (a) shown in FIG. ) To the state of the refrigerant at the point (e).
　以上のように、本実施の形態に係る空気調和装置１００は、冷媒を圧縮する圧縮機１と、凝縮器（３又は５）と、減圧装置４と、蒸発器（３又は５）と、が順に配管で接続され、冷媒が循環する主回路１０と、凝縮器（３又は５）と減圧装置４との間の冷媒配管１０ａから分岐し、蒸発器（３又は５）と圧縮機１との間の冷媒配管１０ａに接続されるバイパス配管１１と、を有している。バイパス配管１１には、バイパス配管１１を流れる冷媒を減圧させると共に、バイパス配管１１を流れる冷媒と、凝縮器（３又は５）と減圧装置４との間の部分における冷媒配管１０ａを流れる液冷媒と、の間で熱交換を行う細管７が設けられている。 As described above, in the air conditioner 100 according to the present embodiment, the compressor 1 for compressing the refrigerant, the condenser (3 or 5), the decompression device 4, and the evaporator (3 or 5) are included. The main circuit 10 is connected by pipes in order and the refrigerant circulates, and the refrigerant pipe 10a between the condenser (3 or 5) and the decompression device 4 branches to the evaporator (3 or 5) and the compressor 1. It has a bypass pipe 11 connected to the refrigerant pipe 10a between them. In the bypass pipe 11, the refrigerant flowing through the bypass pipe 11 is depressurized, and the refrigerant flowing through the bypass pipe 11 and the liquid refrigerant flowing through the refrigerant pipe 10a in the portion between the condenser (3 or 5) and the decompression device 4 are used. A thin tube 7 for exchanging heat between the two is provided.
　つまり、本実施の形態１に係る空気調和装置１００によれば、細管７によって、バイパス配管１１を流れる冷媒を減圧させると共に、該冷媒と主回路１０の冷媒配管１０ａを流れる液冷媒との間で熱交換を行い、低温低圧のガス冷媒を圧縮機１の吸入側の冷媒配管１０ａに送る構成なので、ＨＣ冷媒のように気体密度が小さい冷媒を使用しても、気相状態の冷媒流速を低減でき、圧力損失の増大を抑制できる。そして、この空気調和装置１００は、細管７のみで減圧と熱交換とを行う構成なので、冷媒回路を簡素化させることができ、低コスト化を図ることができる。 That is, according to the air conditioner 100 according to the first embodiment, the thin tube 7 reduces the pressure of the refrigerant flowing through the bypass pipe 11 and between the refrigerant and the liquid refrigerant flowing through the refrigerant pipe 10a of the main circuit 10. Since heat is exchanged and low-temperature low-pressure gas refrigerant is sent to the refrigerant pipe 10a on the suction side of the compressor 1, even if a refrigerant having a low gas density such as HC refrigerant is used, the refrigerant flow velocity in the vapor phase state is reduced. It is possible to suppress an increase in pressure loss. Since the air conditioner 100 has a configuration in which decompression and heat exchange are performed only by the thin tube 7, the refrigerant circuit can be simplified and the cost can be reduced.
　細管７は、冷媒配管１０ａの外周に巻き付けて設けられ、バイパス配管１１を流れる冷媒と、凝縮器（３又は５）と減圧装置４との間における冷媒配管１０ａを流れる液冷媒と、の間で熱交換を行う構成である。よって、本実施の形態１に係る空気調和装置１００は、効果的に冷媒回路を簡素化させることができる。 The thin tube 7 is provided so as to be wound around the outer periphery of the refrigerant pipe 10a, and is provided between the refrigerant flowing through the bypass pipe 11 and the liquid refrigerant flowing through the refrigerant pipe 10a between the condenser (3 or 5) and the decompression device 4. It is a configuration that exchanges heat. Therefore, the air conditioner 100 according to the first embodiment can effectively simplify the refrigerant circuit.
　バイパス配管１１には、該バイパス配管１１を開閉させる開閉弁８が設けられている。開閉弁８は、圧縮機１の周波数の大きさに応じて開閉が制御される。よって、本実施の形態１に係る空気調和装置１００は、例えば要求される圧縮機１の周波数が大きく、冷媒配管１０ａを流れる冷媒流量が大きい場合にバイパス配管１１を開き、要求される圧縮機１の周波数が小さく、圧力損失が付き難いときにバイパス配管１１を閉じることができ、運転の効率化を図ることができる。 The bypass pipe 11 is provided with an on-off valve 8 for opening and closing the bypass pipe 11. The on-off valve 8 is controlled to open and close according to the magnitude of the frequency of the compressor 1. Therefore, the air conditioner 100 according to the first embodiment opens the bypass pipe 11 when, for example, the required frequency of the compressor 1 is high and the flow rate of the refrigerant flowing through the refrigerant pipe 10a is large, and the required compressor 1 is used. When the frequency of the bypass pipe 11 is small and pressure loss is unlikely to occur, the bypass pipe 11 can be closed, and the operation efficiency can be improved.
　実施の形態２．
　次に、本実施の形態２に係る空気調和装置１０１を図５及び図６に基づいて説明する。図５は、本実施の形態２に係る空気調和装置であって、冷房運転時に有効な冷媒回路図である。図６は、本実施の形態２に係る空気調和装置であって、暖房運転時に有効な冷媒回路図である。なお、実施の形態１で説明した空気調和装置と同一の構成要素については、同一の符号を付して、その説明を適宜省略する。 Embodiment 2.
Next, the air conditioner 101 according to the second embodiment will be described with reference to FIGS. 5 and 6. FIG. 5 is a refrigerant circuit diagram of the air conditioner according to the second embodiment, which is effective during the cooling operation. FIG. 6 is a refrigerant circuit diagram of the air conditioner according to the second embodiment, which is effective during the heating operation. The same components as those of the air conditioner described in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted as appropriate.
　先ず、図５に基づいて、本実施の形態２に係る空気調和装置１０１の冷房運転時に有効な構成を説明する。本実施の形態２に係る空気調和装置１０１の主回路１０は、圧縮機１、流路切替装置２、室外熱交換器３、第１減圧装置４０、第２減圧装置４１及び室内熱交換器５が、冷媒配管１０ａにより順次に接続された構成である。第１減圧装置４０及び第２減圧装置４１は、冷媒回路内を流れる冷媒を減圧して膨張させるものであり、一例として開度が可変に制御される電子膨張弁で構成される。第１減圧装置４０は、冷房運転時に全開となるように制御される。 First, based on FIG. 5, a configuration effective during the cooling operation of the air conditioner 101 according to the second embodiment will be described. The main circuit 10 of the air conditioner 101 according to the second embodiment includes a compressor 1, a flow path switching device 2, an outdoor heat exchanger 3, a first decompression device 40, a second decompression device 41, and an indoor heat exchanger 5. Is a configuration in which the refrigerant pipes 10a are sequentially connected to each other. The first decompression device 40 and the second decompression device 41 decompress and expand the refrigerant flowing in the refrigerant circuit, and are composed of an electronic expansion valve whose opening degree is variably controlled as an example. The first decompression device 40 is controlled so as to be fully opened during the cooling operation.
　バイパス配管１１は、第１減圧装置４０と第２減圧装置４１との間の冷媒配管１０ａから分岐し、室内熱交換器５と圧縮機１との間の冷媒配管１０ａに接続された構成である。バイパス配管１１には、バイパス配管１１を流れる冷媒を減圧させると共に、バイパス配管１１を流れる冷媒と、室外熱交換器３と第２減圧装置４１との間の部分における冷媒配管１０ａを流れる液冷媒と、の間で熱交換を行う細管７が設けられている。また、バイパス配管１１には、バイパス配管１１を開閉させる開閉弁８が設けられている。 The bypass pipe 11 has a configuration that branches from the refrigerant pipe 10a between the first decompression device 40 and the second decompression device 41 and is connected to the refrigerant pipe 10a between the indoor heat exchanger 5 and the compressor 1. .. In the bypass pipe 11, the refrigerant flowing through the bypass pipe 11 is depressurized, and the refrigerant flowing through the bypass pipe 11 and the liquid refrigerant flowing through the refrigerant pipe 10a in the portion between the outdoor heat exchanger 3 and the second decompression device 41 are used. A thin tube 7 for exchanging heat between the two is provided. Further, the bypass pipe 11 is provided with an on-off valve 8 for opening and closing the bypass pipe 11.
　細管７は、例えばキャピラリーチューブが使用される。細管７の管径は、主回路１０を構成する冷媒配管１０ａの管径よりも小さい。細管７は、図２に示すように、冷媒配管１０ａの外周に巻き付けて設けられ、細管７を流れる気液二相冷媒と冷媒配管１０ａを流れる液冷媒との間で熱交換を行う。なお、細管７は、キャピラリーチューブに限定されず、他の部材でもよい。 For the capillary tube 7, for example, a capillary tube is used. The pipe diameter of the thin pipe 7 is smaller than the pipe diameter of the refrigerant pipe 10a constituting the main circuit 10. As shown in FIG. 2, the thin tube 7 is provided so as to be wound around the outer periphery of the refrigerant pipe 10a, and heat exchange is performed between the gas-liquid two-phase refrigerant flowing through the thin tube 7 and the liquid refrigerant flowing through the refrigerant pipe 10a. The capillary tube 7 is not limited to the capillary tube, and may be another member.
　開閉弁８は、例えば電子弁とされ、制御部６によって制御される。開閉弁８は、例えば圧縮機１の周波数の大きさに応じて開閉が制御される。主回路１０の冷媒配管１０ａを流れる冷媒流量が小さいときには、圧力損失が付き難く、冷媒をバイパスさせる効果が小さい。そのため、開閉弁８は、要求される圧縮機１の周波数が大きく、冷媒配管１０ａを流れる冷媒流量が大きい場合にのみ開いてもよい。但し、開閉弁８は、必ずしも設ける必要はなく、省略してもよい。 The on-off valve 8 is, for example, an electronic valve and is controlled by the control unit 6. The on-off valve 8 is controlled to open and close according to, for example, the magnitude of the frequency of the compressor 1. When the flow rate of the refrigerant flowing through the refrigerant pipe 10a of the main circuit 10 is small, pressure loss is unlikely to occur and the effect of bypassing the refrigerant is small. Therefore, the on-off valve 8 may be opened only when the required frequency of the compressor 1 is high and the flow rate of the refrigerant flowing through the refrigerant pipe 10a is large. However, the on-off valve 8 does not necessarily have to be provided and may be omitted.
　次に、本実施の形態２に係る空気調和装置１０１の冷房運転時の冷媒の状態を図３に基づいて説明する。図３に示す点（ａ）～点（ｅ）は、図５に示す点（ａ）～点（ｅ）での冷媒の状態を示している。先ず、圧縮機１の運転を開始すると、低温低圧のガス冷媒が圧縮機１によって圧縮され、高温高圧のガス冷媒となって吐出される。この圧縮機１の冷媒圧縮過程は、圧縮機１の断熱効率の分だけ、等エントロピ線で断熱圧縮される場合と比較して加熱されるように圧縮され、図３の点（ｅ）から点（ａ）に示す線で表される。 Next, the state of the refrigerant during the cooling operation of the air conditioner 101 according to the second embodiment will be described with reference to FIG. The points (a) to (e) shown in FIG. 3 indicate the state of the refrigerant at the points (a) to (e) shown in FIG. First, when the operation of the compressor 1 is started, the low-temperature low-pressure gas refrigerant is compressed by the compressor 1 and discharged as a high-temperature high-pressure gas refrigerant. The refrigerant compression process of the compressor 1 is compressed so as to be heated by the amount of the adiabatic efficiency of the compressor 1 as compared with the case where the adiabatic compression is performed by the isentropic wire. It is represented by the line shown in (a).
　圧縮機１から吐出された高温高圧のガス冷媒は、流路切替装置２を通過して室外熱交換器３に流入する。室外熱交換器３に流入した冷媒は、室外空気を加熱しながら冷却され、中温高圧の液冷媒となる。室外熱交換器３での冷媒変化は、圧力損失を考慮すると、図３の点（ａ）から点（ｂ）に示すやや傾いた水平に近い直線で表される。 The high-temperature and high-pressure gas refrigerant discharged from the compressor 1 passes through the flow path switching device 2 and flows into the outdoor heat exchanger 3. The refrigerant that has flowed into the outdoor heat exchanger 3 is cooled while heating the outdoor air, and becomes a medium-temperature, high-pressure liquid refrigerant. Considering the pressure loss, the change in the refrigerant in the outdoor heat exchanger 3 is represented by a slightly inclined straight line shown from the point (a) to the point (b) in FIG.
　室外熱交換器３から流出した中温高圧の液冷媒は、全開にしてある第１減圧装置４０を通過し、細管７を流れる低温の気液二相冷媒と熱交換することで低温高圧の液冷媒となる。このときの冷媒変化は点（ｂ）から点（ｃ）となる。細管７と熱交換した低温高圧の液冷媒は、第２減圧装置４１に流入し、ここで絞られて膨張及び減圧し、低温低圧の気液二相状態になる。この第２減圧装置４１での冷媒の変化は、エンタルピーが一定のもとで行われ、図３の点（ｃ）から点（ｄ）に示す垂直線で表される。 The medium-temperature and high-pressure liquid refrigerant flowing out of the outdoor heat exchanger 3 passes through the fully opened first decompression device 40 and exchanges heat with the low-temperature gas-liquid two-phase refrigerant flowing through the thin tube 7, so that the low-temperature and high-pressure liquid refrigerant flows. It becomes. The change in the refrigerant at this time changes from the point (b) to the point (c). The low-temperature and high-pressure liquid refrigerant that has exchanged heat with the thin tube 7 flows into the second decompression device 41, where it is squeezed to expand and depressurize, resulting in a low-temperature and low-pressure gas-liquid two-phase state. The change of the refrigerant in the second decompression device 41 is performed under a constant enthalpy, and is represented by a vertical line shown by points (c) to (d) in FIG.
　第２減圧装置４１から流出した低温低圧の気液二相状態の冷媒は、室内熱交換器５に流入する。室内熱交換器５に流入した冷媒は、室内空気を冷却しながら加熱され、低温低圧のガス冷媒となる。室内熱交換器５での冷媒の変化は、圧力損失を考慮すると、図３の点（ｄ）から点（ｅ）に示すやや傾いた水平に近い直線で表される。室内熱交換器５を流出した低温低圧のガス冷媒は、流路切替装置２を通った後、バイパス配管１１から流入する低温低圧のガス冷媒と合流して、圧縮機１に流入し、圧縮される。 The low-temperature low-pressure gas-liquid two-phase refrigerant flowing out of the second decompression device 41 flows into the indoor heat exchanger 5. The refrigerant flowing into the indoor heat exchanger 5 is heated while cooling the indoor air, and becomes a low-temperature low-pressure gas refrigerant. The change in the refrigerant in the indoor heat exchanger 5 is represented by a slightly inclined straight line shown from the point (d) to the point (e) in FIG. 3 in consideration of the pressure loss. The low-temperature low-pressure gas refrigerant flowing out of the indoor heat exchanger 5 passes through the flow path switching device 2, then merges with the low-temperature low-pressure gas refrigerant flowing in from the bypass pipe 11, flows into the compressor 1, and is compressed. NS.
　次に、バイパス配管１１を流れる冷媒の状態について説明する。室外熱交換器３を流出した中温高圧の液冷媒の一部は、バイパス配管１１に分岐され、開閉弁８を通過し、細管７に流入する。細管７を流れる冷媒は、徐々に圧力が低下することで低温になり、主回路１０の冷媒配管１０ａを流れる中温の液冷媒と熱交換することで蒸発し、低温低圧のガス冷媒となる。このときの冷媒変化は、図３の点（ｂ）から点（ｅ）となる。そして、バイパス配管１１を流れる低温低圧のガス冷媒は、室内熱交換器５を流出した低温低圧のガス冷媒と合流して、圧縮機１に流入する。 Next, the state of the refrigerant flowing through the bypass pipe 11 will be described. A part of the medium-temperature and high-pressure liquid refrigerant that has flowed out of the outdoor heat exchanger 3 is branched into the bypass pipe 11, passes through the on-off valve 8, and flows into the thin pipe 7. The refrigerant flowing through the thin tube 7 becomes low in temperature as the pressure gradually decreases, and evaporates by exchanging heat with the medium-temperature liquid refrigerant flowing in the refrigerant pipe 10a of the main circuit 10 to become a low-temperature low-pressure gas refrigerant. The change in the refrigerant at this time changes from the point (b) to the point (e) in FIG. Then, the low-temperature low-pressure gas refrigerant flowing through the bypass pipe 11 merges with the low-temperature low-pressure gas refrigerant flowing out of the indoor heat exchanger 5 and flows into the compressor 1.
　次に、図６に示すように、本実施の形態２に係る空気調和装置１０１は、暖房運転の場合、冷房運転のときとは冷媒の流れが逆となるため、第２減圧装置４１を全開にし、第１減圧装置４０で冷媒を減圧する。バイパス配管１１に設けられた細管７は、バイパス配管１１を流れる冷媒を減圧させると共に、バイパス配管１１を流れる冷媒と、室内熱交換器５と第１減圧装置４０との間の部分における冷媒配管１０ａを流れる液冷媒と、の間で熱交換を行う。なお、本実施の形態２に係る空気調和装置１０１の暖房運転時における冷媒状態は、図３に示すｐ－ｈ線図で示され、図６に示す点（ａ）～点（ｅ）が、図３に示す点（ａ）～点（ｅ）での冷媒の状態を示している。 Next, as shown in FIG. 6, in the air conditioner 101 according to the second embodiment, the flow of the refrigerant is opposite to that in the cooling operation in the heating operation, so that the second decompression device 41 is fully opened. Then, the refrigerant is depressurized by the first decompression device 40. The thin pipe 7 provided in the bypass pipe 11 decompresses the refrigerant flowing through the bypass pipe 11, and the refrigerant pipe 10a in the portion between the refrigerant flowing through the bypass pipe 11 and the indoor heat exchanger 5 and the first decompression device 40. Heat exchange is performed between the liquid refrigerant flowing through the pipe and the liquid refrigerant flowing through the pipe. The refrigerant state during the heating operation of the air conditioner 101 according to the second embodiment is shown by the ph diagram shown in FIG. 3, and points (a) to (e) shown in FIG. 6 are shown. The state of the refrigerant at the points (a) to (e) shown in FIG. 3 is shown.
　つまり、本実施の形態２に係る空気調和装置１０１では、第１減圧装置４０の開度および第２減圧装置４１の開度を調整することで、冷房運転時と暖房運転時の両方でバイパス回路を有効にすることができる。 That is, in the air conditioner 101 according to the second embodiment, by adjusting the opening degree of the first decompression device 40 and the opening degree of the second decompression device 41, a bypass circuit is provided during both the cooling operation and the heating operation. Can be enabled.
　以上に、空気調和装置１００及び１０１を実施の形態に基づいて説明したが、空気調和装置１００及び１０１は上述した実施の形態の構成に限定されるものではない。例えば空気調和装置１００及び１０１は、上述した構成要素に限定されるものではなく、他の構成要素を含んでもよい。また、本実施の形態では、１台の室外機２００に、１台の室内機３００を接続した形態を説明したが、この限りではない。１台の室外機２００に、複数台の室内機３００を接続した構成でもよい。要するに、空気調和装置１００及び１０１は、その技術的思想を逸脱しない範囲において、当業者が通常に行う設計変更及び応用のバリエーションの範囲を含むものである。 Although the air conditioner 100 and 101 have been described above based on the embodiment, the air conditioner 100 and 101 are not limited to the configuration of the above-described embodiment. For example, the air conditioners 100 and 101 are not limited to the above-mentioned components, and may include other components. Further, in the present embodiment, the embodiment in which one indoor unit 300 is connected to one outdoor unit 200 has been described, but the present invention is not limited to this. A plurality of indoor units 300 may be connected to one outdoor unit 200. In short, the air conditioners 100 and 101 include a range of design changes and application variations normally performed by those skilled in the art, as long as they do not deviate from the technical idea thereof.
　１　圧縮機、２　流路切替装置、３　室外熱交換器、４　減圧装置、５　室内熱交換器、６　制御部、７　細管、８　開閉弁、１０　主回路、１０ａ　冷媒配管、１１　バイパス配管、４０　第１減圧装置、４１　第２減圧装置、１００、１０１　空気調和装置、２００　室外機、３００　室内機。 1 compressor, 2 flow path switching device, 3 outdoor heat exchanger, 4 decompression device, 5 indoor heat exchanger, 6 control unit, 7 thin tube, 8 on-off valve, 10 main circuit, 10a refrigerant piping, 11 bypass piping, 40 1st decompression device, 41 2nd decompression device, 100, 101 air conditioner, 200 outdoor unit, 300 indoor unit.

Claims (7)

  1. 　圧縮機と、凝縮器と、減圧装置と、蒸発器と、が順に冷媒配管で接続され、冷媒が循環する主回路と、
    　前記凝縮器と前記減圧装置との間の冷媒配管から分岐し、前記蒸発器と前記圧縮機との間の冷媒配管に接続されるバイパス配管と、を有し、
    　前記バイパス配管には、該バイパス配管を流れる冷媒を減圧させると共に、前記バイパス配管を流れる冷媒と、前記凝縮器と前記減圧装置との間の部分における冷媒配管を流れる液冷媒と、の間で熱交換を行う細管が設けられている、空気調和装置。     A main circuit in which a compressor, a condenser, a decompression device, and an evaporator are connected in order by a refrigerant pipe and a refrigerant circulates.
    It has a bypass pipe that branches off from the refrigerant pipe between the condenser and the decompression device and is connected to the refrigerant pipe between the evaporator and the compressor.
    In the bypass pipe, the refrigerant flowing through the bypass pipe is depressurized, and heat is generated between the refrigerant flowing through the bypass pipe and the liquid refrigerant flowing through the refrigerant pipe in the portion between the condenser and the decompression device. An air conditioner provided with a thin tube for replacement.
  2. 　前記細管は、前記冷媒配管の外周に巻き付けて設けられ、前記バイパス配管を流れる冷媒と、前記凝縮器と前記減圧装置との間の部分における前記冷媒配管を流れる液冷媒と、の間で熱交換を行う構成である、請求項１に記載の空気調和装置。 The thin tube is provided so as to be wound around the outer periphery of the refrigerant pipe, and heat exchanges between the refrigerant flowing through the bypass pipe and the liquid refrigerant flowing through the refrigerant pipe at a portion between the condenser and the decompression device. The air conditioner according to claim 1, wherein the air conditioner is configured to perform the above.
  3. 　前記バイパス配管には、該バイパス配管を開閉させる開閉弁が設けられている、請求項１又は２に記載の空気調和装置。 The air conditioner according to claim 1 or 2, wherein the bypass pipe is provided with an on-off valve for opening and closing the bypass pipe.
  4. 　前記開閉弁は、前記圧縮機の周波数の大きさに応じて開閉が制御される、請求項３に記載の空気調和装置。 The air conditioner according to claim 3, wherein the on-off valve is controlled to open and close according to the magnitude of the frequency of the compressor.
  5. 　前記減圧装置は、前記凝縮器と前記蒸発器との間に順に設けられた第１減圧装置と、第２減圧装置とを有し、
    　前記バイパス配管は、前記第１減圧装置と前記第２減圧装置との間の冷媒配管から分岐し、前記蒸発器と前記圧縮機との間の部分における冷媒配管に接続されている、請求項１～４のいずれか一項に記載の空気調和装置。     The decompression device includes a first decompression device and a second decompression device, which are sequentially provided between the condenser and the evaporator.
    The bypass pipe branches from the refrigerant pipe between the first decompression device and the second decompression device, and is connected to the refrigerant pipe in the portion between the evaporator and the compressor. The air conditioner according to any one of 4 to 4.
  6. 　前記第１減圧装置は、冷房運転時に全開となるように制御される、請求項５に記載の空気調和装置。 The air conditioner according to claim 5, wherein the first decompression device is controlled so as to be fully opened during cooling operation.
  7. 　前記第２減圧装置は、暖房運転時に全開となるように制御される、請求項５に記載の空気調和装置。 The air conditioner according to claim 5, wherein the second decompression device is controlled so as to be fully opened during a heating operation.
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