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WO2020174660A1 - Gas-liquid separation device and refrigeration cycle device - Google Patents

Gas-liquid separation device and refrigeration cycle device Download PDF

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Publication number
WO2020174660A1
WO2020174660A1 PCT/JP2019/007833 JP2019007833W WO2020174660A1 WO 2020174660 A1 WO2020174660 A1 WO 2020174660A1 JP 2019007833 W JP2019007833 W JP 2019007833W WO 2020174660 A1 WO2020174660 A1 WO 2020174660A1
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WO
WIPO (PCT)
Prior art keywords
gas
liquid
container
swirl vane
separation device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2019/007833
Other languages
French (fr)
Japanese (ja)
Inventor
駿 加藤
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to PCT/JP2019/007833 priority Critical patent/WO2020174660A1/en
Priority to JP2021501496A priority patent/JP7130838B2/en
Publication of WO2020174660A1 publication Critical patent/WO2020174660A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D45/00—Separating dispersed particles from gases or vapours by gravity, inertia, or centrifugal forces
    • B01D45/12—Separating dispersed particles from gases or vapours by gravity, inertia, or centrifugal forces by centrifugal forces
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04C—APPARATUS USING FREE VORTEX FLOW, e.g. CYCLONES
    • B04C3/00—Apparatus in which the axial direction of the vortex flow following a screw-thread type line remains unchanged ; Devices in which one of the two discharge ducts returns centrally through the vortex chamber, a reverse-flow vortex being prevented by bulkheads in the central discharge duct
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant

Definitions

  • the present invention relates to a gas-liquid separation device and a refrigeration cycle device.
  • an oil separator is used to separate the oil from the oil-containing refrigerant discharged from the compressor and return the oil to the compressor.
  • the gaseous refrigerant and the liquid oil are separated. That is, the gas-liquid two-phase flow in which gas and liquid are mixed is separated into gas and liquid.
  • Patent Document 1 Japanese Utility Model Laid-Open No. 6-34721 (Patent Document 1) describes a recovery device that separates and recovers the paint mist contained in the airflow from the airflow.
  • this recovery device an air flow path is spirally formed by a weir plate around an axis extending in the left and right inside a cylindrical hollow body.
  • the air flow containing the paint mist flowing from the entrance of the hollow body into the hollow body is separated into the air flow and the paint mist when passing through the spiral air flow path.
  • the airflow passes through the filter and is discharged from the outlet of the hollow body, and the paint mist is discharged from the drain port of the hollow body.
  • the weir plate spirally forms the air flow path around the horizontally extending axis, the paint mist separated from the air flow is wound up from the bottom to the top in the hollow body. To be Therefore, the separated paint mist is re-engaged in the air flow, so that the separation efficiency is reduced.
  • the present invention has been made in view of the above problems, and an object thereof is to provide a gas-liquid separation device that can improve the separation efficiency of gas and liquid.
  • the gas-liquid separation device of the present invention separates a gas-liquid two-phase fluid into a gas and a liquid.
  • the gas-liquid separation device includes a container, an inflow pipe, a liquid discharge pipe, a gas discharge pipe, and a swirl vane.
  • the container has an inner wall surface extending along a vertically extending central axis and surrounding the central axis.
  • the inflow pipe has an inflow port for allowing a gas-liquid two-phase fluid to flow into the container.
  • the liquid discharge pipe has a liquid discharge port for discharging the liquid separated from the gas-liquid two-phase fluid from the container.
  • the gas discharge pipe has a gas discharge port for discharging the gas separated from the gas-liquid two-phase fluid from the container.
  • the swirl vane is arranged in the container.
  • the inflow port of the inflow pipe is arranged above the swirl vane.
  • the liquid discharge port of the liquid discharge pipe is arranged below the swirl vane.
  • the gas discharge port of the gas discharge pipe is arranged below the swirl vane and above the liquid discharge port.
  • the swirl vane includes a shaft and a plurality of spiral plates.
  • the shaft is eccentric with respect to the center of the swirl vane when viewed from the direction along the central axis.
  • the plurality of spiral plates extend spirally along the axis. Each of the plurality of spiral plates extends from the shaft toward the inner wall surface of the container.
  • the lower end of the shaft is arranged so as to be displaced from the gas discharge port when viewed from the direction along the central axis.
  • a swirling flow is generated in a gas-liquid two-phase fluid by a plurality of spiral plates spirally extending along the axis of the swirling blade.
  • the swirling force of the swirling flow separates the liquid from the gas-liquid two-phase fluid and suppresses the winding of the separated liquid.
  • the separation efficiency of gas and liquid can be improved.
  • the lower end of the axis of the swirl vane is arranged so as to be displaced from the gas discharge port when viewed from the direction along the central axis of the container, the liquid retained on the shaft is prevented from entering the gas discharge port. Thereby, the separation efficiency of gas and liquid can be improved.
  • FIG. 3 is a perspective view showing a configuration in which swirl vanes of the gas-liquid separation device according to Embodiment 1 of the present invention are arranged in a container. It is a perspective view which shows the turning blade of the gas-liquid separation device which concerns on Embodiment 1 of this invention.
  • FIG. 3 is a perspective view showing a shaft of a swirl vane and a plurality of spiral plates of the gas-liquid separator according to the first embodiment of the present invention.
  • FIG. 3 is a cross-sectional view for explaining how gas and liquid are separated in the gas-liquid separator according to Embodiment 1 of the present invention. It is sectional drawing which shows the gas-liquid separator of a comparative example. It is a perspective view which shows the flow path of the container of the gas-liquid separator of a comparative example.
  • FIG. 6 is a perspective view showing a shaft of a swirl vane and a plurality of spiral plates of a modified example 1 of the gas-liquid separation device according to the first embodiment of the present invention.
  • FIG. 6 is a top view showing a shaft of a swirl vane and a plurality of spiral plates of a first modification of the gas-liquid separator according to the first embodiment of the present invention. It is sectional drawing which shows the modification 2 of the gas-liquid separator which concerns on Embodiment 1 of this invention. It is a perspective view which shows the structure by which the turning blade of the gas-liquid separator which concerns on Embodiment 2 of this invention was arrange
  • FIG. 1 is a refrigerant circuit diagram of a refrigeration cycle device 100 according to this embodiment.
  • Refrigeration cycle device 100 in the present embodiment is, for example, an air conditioner.
  • An oil separator will be described as an example of the gas-liquid separator 10.
  • the refrigeration cycle apparatus 100 in the present embodiment includes a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, a flow rate adjusting valve 4, an indoor heat exchanger 5, and an air
  • a liquid separator (oil separator) 10 is mainly provided.
  • the compressor 1, the four-way valve 2, the outdoor heat exchanger 3, the flow rate adjusting valve 4, the indoor heat exchanger 5, and the gas-liquid separation device 10 are connected by piping. In this way, the refrigerant circuit of the refrigeration cycle device 100 is configured.
  • a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, a flow rate adjusting valve 4, and a gas-liquid separation device 10 are arranged in the outdoor unit 100a.
  • the indoor heat exchanger 5 is arranged in the indoor unit 100b.
  • the outdoor unit 100a and the indoor unit 100b are connected by extension pipes 6a and 6b.
  • the compressor 1 is configured to compress the drawn refrigerant and discharge it.
  • the compressor 1 is configured to compress the refrigerant flowing into the outdoor heat exchanger 3 or the indoor heat exchanger 5.
  • the compressor 1 may be a constant speed compressor having a constant compression capacity, or may be an inverter compressor having a variable compression capacity. This inverter compressor is configured so that the rotation speed can be variably controlled.
  • the four-way valve 2 is configured to switch the flow of refrigerant. Specifically, the four-way valve 2 is configured to switch the flow of the refrigerant to the outdoor heat exchanger 3 or the indoor heat exchanger 5 depending on the heating operation and the cooling operation.
  • the outdoor heat exchanger 3 is connected to the four-way valve 2 and the flow rate adjusting valve 4.
  • the outdoor heat exchanger 3 serves as a condenser that condenses the refrigerant compressed by the compressor 1 during the cooling operation.
  • the outdoor heat exchanger 3 also serves as an evaporator that evaporates the refrigerant whose pressure is reduced by the flow rate adjusting valve 4 during the heating operation.
  • the outdoor heat exchanger 3 is for exchanging heat between the refrigerant and air.
  • the outdoor heat exchanger 3 includes, for example, a pipe (heat transfer pipe) through which a refrigerant flows inside, and fins attached to the outside of the pipe.
  • the flow rate adjusting valve 4 is connected to the outdoor heat exchanger 3 and the indoor heat exchanger 5.
  • the flow rate adjusting valve 4 serves as a throttle device that reduces the pressure of the refrigerant condensed by the outdoor heat exchanger 3 during the cooling operation.
  • the flow rate adjusting valve 4 serves as a throttle device that depressurizes the refrigerant condensed by the indoor heat exchanger 5 during the heating operation.
  • the flow rate adjusting valve 4 is, for example, a capillary tube, an electronic expansion valve, or the like.
  • the indoor heat exchanger 5 is connected to the four-way valve 2 and the flow rate adjusting valve 4.
  • the indoor heat exchanger 5 serves as an evaporator that evaporates the refrigerant decompressed by the flow rate adjusting valve 4 during the cooling operation.
  • the indoor heat exchanger 5 also serves as a condenser that condenses the refrigerant compressed by the compressor 1 during the heating operation.
  • the indoor heat exchanger 5 is for exchanging heat between the refrigerant and air.
  • the indoor heat exchanger 5 includes, for example, a pipe (heat transfer pipe) through which a refrigerant flows inside, and fins attached to the outside of the pipe.
  • the gas-liquid separation device 10 is connected to the downstream side of the discharge pipe of the compressor 1.
  • the gas-liquid separation device 10 is configured to separate a gas-liquid two-phase fluid into a gas and a liquid.
  • the oil separator as the gas-liquid separator 10 is configured to separate oil from the oil-containing refrigerant discharged from the compressor 1.
  • the oil separator as the gas-liquid separator 10 is connected to the upstream side of the suction pipe of the compressor 1 so as to return the oil separated from the oil-containing refrigerant to the compressor 1.
  • FIG. 2 is a sectional view schematically showing the configuration of the gas-liquid separation device 10 according to the present embodiment.
  • the gas-liquid separation device 10 according to the present embodiment has a container 11, an inflow pipe 12, a liquid discharge pipe 13, a gas discharge pipe 14, and a swirl vane 15. There is.
  • the gas-liquid separation device 10 according to the present embodiment uses a separation method using a swirling downward flow.
  • the gas-liquid separation device 10 according to the present embodiment has an inflow part 10a, a separation part 10b, an approach section 10c1, a transition part 10c2, and a liquid collection part (oil collection part) 10d. ..
  • the inflow part 10a is a part where the gas-liquid two-phase fluid flows into the gas-liquid separation device 10.
  • the inflow part 10 a is configured by the inflow pipe 12.
  • the separation part 10b is a part that separates a gas-liquid two-phase fluid into a gas and a liquid.
  • the separation part 10b is composed of the upper part of the container 11 and the swirl vane 15.
  • the run-up section 10c1 is a section between the gas discharge pipe 14 and the swirl vane 15.
  • the run-up section 10c1 is provided in the transition section 10c2.
  • the transition portion 10c2 is a portion where the separated gas is discharged from the gas discharge pipe 14.
  • the transition portion 10c2 is configured by the central portion of the container 11 and the upper portion of the gas exhaust pipe 14.
  • the liquid collecting portion (oil collecting portion) 10d is a portion that collects the separated liquid.
  • the liquid collecting portion (oil collecting portion) 10d is configured by the lower portion of the container 11 and the central portion of the gas discharge pipe 14.
  • the liquid discharge pipe 13 is connected to the liquid collecting section (oil collecting section) 10d.
  • the container 11 extends along a vertically extending central axis CL.
  • the central axis CL of the container 11 extends in the vertical direction.
  • the container 11 has an internal space.
  • the container 11 has an inner wall surface IS surrounding the central axis CL.
  • the inner wall surface IS of the container 11 is configured such that a cross section orthogonal to the central axis CL has a circular shape.
  • the container 11 is configured such that the separation portion 10b and the transition portion 10c2 have the same diameter (inner diameter and outer diameter), and the diameter of the liquid collection portion (oil collection portion) 10d is larger than that of the transition portion 10c2. Is configured.
  • the inflow pipe 12 is connected to the discharge side of the compressor 1 shown in FIG.
  • the inflow pipe 12 is connected to the upper end of the container 11.
  • the inflow pipe 12 is arranged coaxially with the central axis CL of the container 11.
  • the inflow pipe 12 penetrates the ceiling of the container 11.
  • the inflow pipe 12 is configured to allow the gas-liquid two-phase fluid to flow into the container 11.
  • the inflow pipe 12 has an inflow port 12 a through which a gas-liquid two-phase fluid is introduced into the container 11.
  • the inflow pipe 12 is configured to allow the oil-containing refrigerant to flow into the container 11.
  • the inflow port 12 a of the inflow pipe 12 is arranged above the swirl vane 15.
  • the liquid discharge pipe 13 is connected to the oil return pipe 20 shown in FIG.
  • the liquid discharge pipe 13 is connected to the lower end of the container 11.
  • the liquid discharge pipe 13 is arranged at a position different from the central axis CL of the container 11.
  • the liquid discharge pipe 13 penetrates the bottom of the container 11.
  • the liquid discharge pipe 13 is configured to discharge the liquid separated from the gas-liquid two-phase fluid from the container 11.
  • the liquid discharge pipe 13 has a liquid discharge port 13 a for discharging the liquid separated from the gas-liquid two-phase fluid from the container 11.
  • the liquid discharge pipe 13 is configured to discharge the oil separated from the oil-containing refrigerant from the container 11.
  • the liquid discharge port 13 a of the liquid discharge pipe 13 is arranged below the swirl vane 15.
  • the gas exhaust pipe 14 is connected to the four-way valve 2 shown in FIG.
  • the gas exhaust pipe 14 is connected to the lower side of the container 11.
  • the gas discharge pipe 14 is arranged coaxially with the central axis CL of the container 11.
  • the gas discharge pipe 14 penetrates the bottom of the container 11.
  • the gas discharge pipe 14 has a gas discharge port 14 a for discharging the gas separated from the gas-liquid two-phase fluid from the container 11.
  • the gas discharge pipe 14 is configured to discharge the refrigerant, in which the oil is separated from the oil-containing refrigerant, from the container 11.
  • the gas discharge port 14a is arranged so as to overlap the central axis CL.
  • the gas discharge port 14a of the gas discharge pipe 14 is arranged below the swirl vane 15 and above the liquid discharge port 13a. That is, the gas discharge port 14a of the gas discharge pipe 14 is arranged between the swirl vane 15 and the liquid discharge port 13a in the vertical direction.
  • the gas discharge port 14 a is provided at the tip of the gas discharge pipe 14 arranged in the container 11.
  • the gas discharge port 14 a is arranged directly below the swirl vane 15.
  • the gas discharge port 14a is arranged in the up-down direction with the swirl vane 15 leaving a run-up section 10c1.
  • the gas discharge pipe 14 has an outer diameter smaller than the inner diameter of the container 11.
  • the swirl vanes 15 are configured to swirl the gas-liquid two-phase fluid while flowing from the upper side to the lower side.
  • the swirl vanes 15 are configured to generate a swirl flow.
  • the swirl vanes 15 are configured to flow the liquid separated from the gas-liquid two-phase fluid by the swirling force of the swirling flow from above to below while circulating along the inner wall surface IS.
  • the swirl vanes 15 are arranged in the container 11.
  • the swirl vane 15 is arranged on the upper side inside the container 11.
  • the swirl vane 15 is arranged directly below the inflow port 12 a of the inflow pipe 12.
  • FIG. 3 is a perspective view schematically showing a configuration in which the swirl vane 15 is arranged inside the container 11. Note that, for convenience of description, in FIG. 3, portions above and below the swirl vane 15 of the container 11 are not shown.
  • the swirl vane 15 has a shaft 15a and a plurality of spiral plates 15b.
  • the shaft 15a is configured such that a plurality of spiral plates 15b cross each other via the shaft 15a.
  • the lower end of the shaft 15a is arranged so as to be displaced from the gas discharge port 14a when viewed from the direction along the central axis CL. That is, the lower end of the shaft 15a is arranged so as not to overlap the gas discharge port 14a when viewed from the direction along the central axis CL.
  • FIG. 4 is a perspective view schematically showing the structure of the swirl vane 15.
  • each of the plurality of spiral plates 15b is connected to the shaft 15a.
  • the plurality of spiral plates 15b are connected to the shaft 15a so as to intersect each other.
  • Each of the plurality of spiral plates 15b is configured to generate a swirling force on the gas-liquid two-phase fluid.
  • Each of the plurality of spiral plates 15b extends spirally along the axis 15a.
  • Each of the plurality of spiral plates 15b extends from the shaft 15a toward the inner wall surface IS of the container 11.
  • Each of the plurality of spiral plates 15b has a linear shape when viewed from the direction along the central axis CL.
  • the swirl vane 15 has six spiral plates 15b. The number of spiral plates 15b of the swirl vane 15 is not limited to six.
  • FIG. 5 is a perspective view schematically showing the configuration of the shaft 15a of the swirl vane 15 and the plurality of spiral plates 15b.
  • FIG. 6 is a top view schematically showing the configuration of the shaft 15a of the swirl blade 15 and the plurality of spiral plates 15b. In FIGS. 5 and 6, a portion hidden behind the shaft 15a and the plurality of spiral plates 15b and not visible is indicated by a broken line.
  • the shaft 15a is configured to be eccentric with respect to the center CP of the swirl vane 15 when viewed from the direction along the central axis CL.
  • the center CP of the swirl vane 15 is located at the center of the swirl vane 15 when the swirl vane 15 is viewed from the upper side to the lower side.
  • the center CP of the swirl vane 15 is located on the central axis CL of the container 11.
  • the shaft 15a is configured to spirally extend along the central axis CL.
  • the outer peripheral ends of the plurality of spiral plates 15b are in contact with the inner wall surface IS of the container 11. Therefore, when the swirl vanes 15 are viewed from the upper side to the lower side along the central axis CL, there is no gap between the outer peripheral ends of the plurality of spiral plates 15b and the inner wall surface IS of the container 11.
  • Each of the plurality of spiral plates 15b is configured to be twisted at an angle equal to or greater than an angle obtained by dividing 360 degrees by the number of the plurality of spiral plates 15b. That is, when the swirl vanes 15 are viewed from the upper side to the lower side along the central axis CL, each of the plurality of spiral plates 15b has an angle of 360 degrees or more divided by the number of the plurality of spiral plates 15b. It is designed to twist. When the swirl vane 15 is viewed from the upper side to the lower side along the central axis CL, the swirl vane 15 is configured so that the other end cannot be seen from one end.
  • the shaft 15a is configured to be twisted spirally at a rotation angle of 180 degrees about the central axis CL.
  • Each of the plurality of spiral plates 15b is configured to be spirally twisted at a rotation angle of 180 degrees about the central axis CL.
  • the angles of the spiral plates 15b adjacent to each other facing each other via the shaft 15a are acute angles.
  • the plurality of spiral plates 15b are arranged in line symmetry with the two spiral plates 15b aligned in a straight line passing through the center CP of the swirl blade 15 as the axis of symmetry.
  • the container 11 has a first flow passage F1, a second flow passage F2, a third flow passage F3, a fourth flow passage F4, a fifth flow passage F5 and a sixth flow passage F6.
  • the first flow passage F1, the second flow passage F2, the third flow passage F3, the fourth flow passage F4, the fifth flow passage F5, and the sixth flow passage F6 are separated by each of the plurality of spiral plates 15b. ..
  • the first flow passage F1, the second flow passage F2, the third flow passage F3, the fourth flow passage F4, the fifth flow passage F5, and the sixth flow passage F6 rotate counterclockwise about the shaft 15a of the swirl vane 15. They are arranged side by side.
  • the respective flow passages are arranged in line symmetry with the two spiral plates 15b arranged in a straight line passing through the center CP of the swirl vane 15 as the axis of symmetry. That is, the first flow passage F1 and the sixth flow passage F6 are arranged in line symmetry, the second flow passage F2 and the fifth flow passage F5 are arranged in line symmetry, and the third flow passage F3 is arranged.
  • the fourth flow path F4 is arranged in line symmetry.
  • the first channel F1 has a larger channel area than the second channel F2.
  • the second flow passage F2 has a flow passage area larger than that of the third flow passage F3.
  • the sixth flow passage F6 has a larger flow passage area than the fifth flow passage F5.
  • the fifth flow passage F5 has a flow passage area larger than that of the fourth flow passage F4.
  • the first flow passage F1 has the same flow passage area as the sixth flow passage F6.
  • the second flow passage F2 has the same flow passage area as the fifth flow passage F5.
  • the third flow passage F3 has the same flow passage area as the fourth flow passage F4.
  • This flow channel area is the area of each flow channel when viewed from the direction along the central axis CL, and is the area of each flow channel in the cross section orthogonal to the central axis CL.
  • FIG. 7 is a conceptual diagram of the swirl vane 15 according to the present embodiment.
  • the swirl vane 15 has a shape drawn by the cross-sectional shape 101 and the locus 102 when the cross-sectional shape 101 passes through the spiral locus 102.
  • the main intersection 103 inside the cross-sectional shape 101 is eccentric with respect to the center of the locus 102.
  • the main intersection 103 is a portion where the shaft 15a and the plurality of spiral plates 15b intersect in the cross-sectional shape 101.
  • the center of the locus 102 is the center of the x axis, the y axis, and the z axis in FIG. 7.
  • the x-axis corresponds to the front-back direction of the swirl blade 15, the y-axis corresponds to the left-right direction of the swirl blade 15, and the z-axis corresponds to the up-down direction of the swirl blade 15.
  • the cross-sectional shape 101 orthogonal to the central axis CL of the swirl vane 15 becomes similar when the cross-sectional shape 101 in any cross section is rotated about the central axis CL. That is, the cross-sectional shape 101 orthogonal to the central axis CL of the swirl vane 15 has a similar shape in any cross section.
  • the solid line arrow indicates the refrigerant flow during the cooling operation
  • the broken line arrow in the figure indicates the refrigerant flow during the heating operation.
  • the refrigeration cycle device 100 of the present embodiment can selectively perform the cooling operation and the heating operation.
  • the refrigerant circulates through the refrigerant circuit in the order of the compressor 1, the gas-liquid separator (oil separator) 10, the four-way valve 2, the outdoor heat exchanger 3, the flow rate adjusting valve 4, and the indoor heat exchanger 5.
  • the outdoor heat exchanger 3 functions as a condenser
  • the indoor heat exchanger 5 functions as an evaporator.
  • the refrigerant circulates through the refrigerant circuit in the order of the compressor 1, the gas-liquid separator 10, the four-way valve 2, the indoor heat exchanger 5, the flow rate adjusting valve 4, and the outdoor heat exchanger 3.
  • the indoor heat exchanger 5 functions as a condenser
  • the outdoor heat exchanger 3 functions as an evaporator.
  • the high-temperature and high-pressure gas-state refrigerant is discharged from the compressor 1.
  • This refrigerant contains oil that lubricates the inside of the compressor. That is, this refrigerant is an oil-containing refrigerant.
  • the high-temperature and high-pressure gas-state oil-containing refrigerant discharged from the compressor 1 flows into the gas-liquid separation device 10.
  • the gas-liquid separator 10 separates oil from the oil-containing refrigerant.
  • the refrigerant from which oil has been separated by the gas-liquid separation device 10 flows into the outdoor heat exchanger 3 via the four-way valve 2. In the outdoor heat exchanger 3, heat exchange is performed between the gas refrigerant that has flowed in and the outdoor air.
  • the high-temperature and high-pressure gas refrigerant is condensed into a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant sent from the outdoor heat exchanger 3 becomes a two-phase refrigerant of low-pressure gas refrigerant and liquid refrigerant by the flow rate adjusting valve 4.
  • the two-phase refrigerant flows into the indoor heat exchanger 5.
  • heat exchange is performed between the two-phase refrigerant that has flowed in and the indoor air.
  • the two-phase refrigerant becomes a low-pressure gas refrigerant by evaporating the liquid refrigerant. This heat exchange cools the room.
  • the low-pressure gas refrigerant sent from the indoor heat exchanger 5 flows into the compressor 1 through the four-way valve 2, is compressed into a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 1 again. Hereinafter, this cycle is repeated.
  • the high-temperature high-pressure gas-state oil-containing refrigerant is discharged from the compressor 1.
  • the high-temperature and high-pressure gas-state oil-containing refrigerant discharged from the compressor 1 flows into the gas-liquid separation device 10.
  • the gas-liquid separator 10 separates oil from the oil-containing refrigerant.
  • the refrigerant from which the oil has been separated by the gas-liquid separator 10 flows into the indoor heat exchanger 5 via the four-way valve 2.
  • the indoor heat exchanger 5 heat exchange is performed between the flowing refrigerant and the indoor air.
  • the high-temperature and high-pressure gas refrigerant is condensed into a high-pressure liquid refrigerant. This heat exchange warms the room.
  • the high-pressure liquid refrigerant sent out from the indoor heat exchanger 5 becomes a two-phase refrigerant of low-pressure gas refrigerant and liquid refrigerant by the flow rate adjusting valve 4.
  • the two-phase state refrigerant flows into the outdoor heat exchanger 3.
  • heat exchange is performed between the two-phase refrigerant that has flowed in and the outdoor air.
  • the two-phase refrigerant becomes a low-pressure gas refrigerant by evaporating the liquid refrigerant.
  • the low-pressure gas refrigerant sent from the outdoor heat exchanger 3 flows into the compressor 1 via the four-way valve 2, is compressed into a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 1 again. Hereinafter, this cycle is repeated.
  • FIG. 8 is a cross-sectional view for explaining how gas (refrigerant) and liquid (oil) are separated in the gas-liquid separator 10 according to the present embodiment.
  • the flow of the oil-containing refrigerant is shown by a white arrow
  • the flow of the refrigerant is shown by a solid line arrow
  • the oil flow is shown by a broken line arrow.
  • the oil-containing refrigerant discharged from the compressor 1 is separated by the gas-liquid separator 10 into refrigerant and oil.
  • the oil-containing refrigerant contains a refrigerant and oil (refrigerating machine oil) sealed in the compressor 1.
  • the refrigerant separated from the oil-containing refrigerant by the gas-liquid separator 10 is discharged to the four-way valve 2.
  • the oil separated from the oil-containing refrigerant by the gas-liquid separation device 10 is discharged to the suction side of the compressor 1 through the oil return pipe 20.
  • the oil-containing refrigerant when a high flow rate of the oil-containing refrigerant flows into the gas-liquid separator 10 from the inflow pipe 12, the oil-containing refrigerant is separated from the oil-containing refrigerant by the swirling flow generated by the plurality of spiral plates 15 b of the swirl vanes 15.
  • the oil separates.
  • the oil separated from the oil-containing refrigerant becomes a liquid film by colliding with the inner wall surface IS of the container 11, and flows to the bottom of the container 11 along the inner wall surface IS of the container 11 due to gravity and swirling flow. In this way, the oil is collected by the oil collecting section 10d.
  • the collected oil is discharged from the liquid discharge pipe 13.
  • the oil discharged from the liquid discharge pipe 13 is returned to the suction side of the compressor 1 through the oil return pipe 20.
  • the refrigerant from which the oil has been separated is discharged from the gas discharge pipe 14.
  • the refrigerant discharged from the gas discharge pipe 14 flows into the four-way valve 2.
  • FIG. 9 is a sectional view schematically showing the configuration of the gas-liquid separation device 10 of the comparative example.
  • the structure of the swirl vane 15 is different from that of the swirl vane 15 according to the present embodiment.
  • the shaft 15a of the swirl vane 15 of the comparative example extends vertically in a straight line.
  • the shaft 15a of the swirl vane 15 of the comparative example is located on the central axis CL.
  • the liquid separated by the swirling flow stays on the shaft 15a between the spiral plates 15b adjacent to each other due to the surface tension. This liquid drops by gravity and enters the gas outlet 14a. As a result, the separation efficiency between the gas and the liquid decreases.
  • FIG. 10 is a perspective view schematically showing the flow path of the container 11 of the gas-liquid separation device 10 of the comparative example.
  • FIG. 11 is a perspective view schematically showing the flow path of the gas-liquid separation device 10 according to this embodiment. Note that, for convenience of description, in FIGS. 10 and 11, the portions above and below the swirl vanes 15 of the container 11 are not shown.
  • the first flow passage F1 to the sixth flow passage F6 have the same flow passage area.
  • the pressure may pulsate as the flow velocity of the gas-liquid two-phase fluid flowing into the gas-liquid separation device 10 increases or decreases.
  • the pressure may pulsate by opening and closing the valve of the compressor 1.
  • the flow passage areas are the first flow passage F1, the second flow passage F2, and the third flow passage. It becomes smaller in the order of F3.
  • the flow passage area increases in the order of the fourth flow passage F4, the fifth flow passage F5, and the sixth flow passage F6. Therefore, the main flow of the swirling flow is fixed in the wide area of the flow path. That is, the claim of the swirling flow is fixed to the first flow path F1 and the sixth flow path F6. Therefore, the direction in which the liquid flies can be determined. This makes it possible to improve the separation efficiency between the gas and the liquid by more efficiently applying the centrifugal force to the liquid.
  • a swirling flow is generated in the gas-liquid two-phase fluid by the plurality of spiral plates 15b spirally extending along the shaft 15a of the swirling blade 15.
  • the swirling force of the swirling flow separates the liquid from the gas-liquid two-phase fluid and suppresses the winding of the separated liquid. That is, the liquid separated by the swirling flow flows as a liquid film after colliding with the inner wall surface IS of the container 11, and thus re-scattering is suppressed. Further, the separated liquid flows downward along the central axis CL, and the swirling flow swirls around the central axis CL. For this reason, it is possible to prevent the separated liquid from being rolled up from below.
  • the separation efficiency of gas and liquid can be improved. Further, since the lower end of the shaft 15a of the swirl vane 15 is arranged so as to be displaced from the gas discharge port 14a when viewed from the direction along the central axis CL of the container 11, the liquid retained on the shaft 15a is discharged to the gas discharge port 14a. The entry is suppressed. That is, the liquid retained on the shaft 15a between the spiral plates 15b adjacent to each other due to the surface tension of the liquid is prevented from entering the gas discharge port 14a by falling due to gravity. Thereby, the separation efficiency of gas and liquid can be improved.
  • the shaft 15a of the swirl vane 15 is configured to be eccentric with respect to the center CP of the swirl vane 15 when viewed from the direction along the central axis CL. Therefore, the lower end of the shaft 15a is arranged so as to deviate from the gas discharge port 14a when viewed from the direction along the central axis CL of the container 11 while maintaining the size in the circumferential direction of the swirl vane 15 around the central axis CL. be able to.
  • the inflow port 12a of the inflow pipe 12 is arranged above the swirl vane 15.
  • the liquid discharge port 13 a of the liquid discharge pipe 13 is arranged below the swirl vane 15.
  • the gas discharge port 14a of the gas discharge pipe 14 is arranged below the swirl vane 15 and above the liquid discharge port 13a. This makes it possible to realize a separation method using a swirling downward flow.
  • the gas discharge port 14a of the gas discharge pipe 14 is arranged below the swirl vane 15 and above the liquid discharge port 13a. Therefore, it is possible to prevent the liquid separated by the swirl vanes 15 from flowing into the gas discharge pipe 14.
  • the conventional cyclone separator vertically collides the gas-liquid two-phase fluid with the inner wall surface of the container. That is, the gas-liquid two-phase fluid collides with the inner wall surface in the horizontal direction orthogonal to the vertical direction.
  • the conventional cyclone separator when the separation distance between the inner wall surface of the container and the gas discharge pipe is short, the separated liquid is re-scattered and sucked together with the gas, so that the separation efficiency between the gas and the liquid is increased. descend. Therefore, it is difficult to downsize the conventional cyclone separator.
  • a separation method using a swirling downward flow is used. Therefore, the separation distance between the inflow pipe 12 and the gas exhaust pipe 14 can be secured in the vertical direction. Therefore, the gas-liquid separation device 10 according to the present embodiment can be easily downsized as compared with the conventional cyclone separator.
  • the efficiency of oil return to the compressor 1 can be improved by improving the oil separation efficiency. Therefore, it is possible to prevent the seizure of the sliding portion of the compressor 1 due to the oil shortage. Further, it is possible to suppress the oil discharged from the compressor 1 from staying in the outdoor heat exchanger 3 and the indoor heat exchanger 5. Therefore, it is possible to suppress a decrease in the coefficient of performance (COP: Coefficient Of Performance) of the refrigeration cycle apparatus 100.
  • COP Coefficient Of Performance
  • the gas outlet 14a is arranged so as to overlap the central axis CL. Therefore, it becomes easy to dispose the lower end of the shaft 15a so as to deviate from the gas discharge port 14a when viewed from the direction along the central axis CL.
  • the outer peripheral ends of the plurality of spiral plates 15b are in contact with the inner wall surface IS of the container 11. Therefore, the gas-liquid two-phase fluid does not flow through the gap between the outer peripheral end of each of the plurality of spiral plates 15b and the inner wall surface IS of the container 11. Thereby, the separation efficiency of gas and liquid can be improved.
  • the first flow passage F1 has a larger flow passage area than the second flow passage F2. Therefore, the main flow of the swirling flow is fixed to the first flow passage F1 which is a large flow passage area. This makes it possible to improve the separation efficiency between the gas and the liquid by more efficiently applying the centrifugal force to the liquid.
  • the modified example of the gas-liquid separation device 10 according to the present embodiment has the same configuration, operation, and effect as those of the gas-liquid separation device 10 according to the present embodiment described above, unless otherwise specified. Therefore, the same components as those of the gas-liquid separation device 10 according to the present embodiment described above are designated by the same reference numerals, and description thereof will not be repeated.
  • FIG. 12 is a perspective view schematically showing a configuration in which the swirl vanes 15 in the modified example 1 of the gas-liquid separation device 10 according to the present embodiment are arranged in the container 11. Note that, for convenience of description, in FIG. 12, portions above and below the swirl vane 15 of the container 11 are not shown.
  • FIG. 13 is a perspective view schematically showing the configuration of the swirl vanes 15 in the first modification of the gas-liquid separator 10 according to this embodiment.
  • FIG. 14 is a perspective view schematically showing the configurations of the shaft 15a of the swirl vane 15 and the plurality of spiral plates 15b in the first modification of the gas-liquid separation device 10 according to the present embodiment.
  • FIG. 15 is a top view schematically showing the configurations of the shaft 15a of the swirl vane 15 and the plurality of spiral plates 15b in the first modification of the gas-liquid separator 10 according to the present embodiment.
  • a part hidden behind the shaft 15a and the plurality of spiral plates 15b and not visible is indicated by a broken line.
  • the configuration of the swirl vanes 15 is different from that of the gas-liquid separator 10 according to the above embodiment.
  • the shaft 15a is configured to be spirally twisted at a rotation angle of 360 degrees about the central axis CL.
  • Each of the plurality of spiral plates 15b is configured to be spirally twisted at a rotation angle of 360 degrees about the central axis CL.
  • FIG. 16 is a sectional view schematically showing the configuration of Modification 2 of the gas-liquid separation device 10 according to the present embodiment.
  • the second modification of the gas-liquid separation device 10 according to the present embodiment is different in the configuration of the container 11 from the gas-liquid separation device 10 according to the above-described embodiment.
  • the container 11 has a uniform diameter (inner diameter and outer diameter) along the central axis CL.
  • Embodiment 2 of the present invention will be described with reference to FIGS. 17 and 18.
  • the second embodiment of the present invention has the same configuration, operation, and effect as those of the first embodiment of the present invention described above, unless otherwise specified. Therefore, the same components as those in the first embodiment of the present invention described above are designated by the same reference numerals and the description thereof will not be repeated.
  • FIG. 17 is a perspective view schematically showing a configuration in which the swirl vane 15 according to the present embodiment is arranged in the container 11. Note that, for convenience of description, in FIG. 17, portions above and below the swirl vane 15 of the container 11 are not shown.
  • FIG. 18 is a perspective view schematically showing the configuration of swirl vane 15 according to the present embodiment.
  • each of the plurality of spiral plates 15b is configured in an arc shape when viewed from the direction along the central axis CL.
  • the cross-sectional shape of the swirl vane 15 orthogonal to the central axis CL is similar in any cross section. Therefore, each of the plurality of spiral plates 15b has an arc shape in any cross section orthogonal to the central axis CL.
  • Each of the plurality of spiral plates 15b is curved so that the center thereof protrudes counterclockwise around the shaft 15a.
  • each of the plurality of spiral plates 15b is formed in an arc shape when viewed from the direction along the central axis CL. Therefore, the surface areas of the plurality of spiral plates 15b are increased as compared with the case where each of the plurality of spiral plates 15b is configured in a straight line when viewed from the direction along the central axis CL. As a result, a fine liquid (mist) can be captured at the entrance of the swirl vane 15. Further, since the surface areas of the plurality of spiral plates 15b are increased, atomization of the liquid accumulated at the main intersection 103 (FIG. 7) which is a narrow portion at the outlet of the swirl vane 15 can be suppressed. This makes it possible to increase the size of the liquid particles, which facilitates the separation of the liquid by the swirling flow. Therefore, the separation efficiency of gas and liquid can be improved.
  • the modified example of the gas-liquid separation device 10 according to the present embodiment has the same configuration, operation, and effect as those of the gas-liquid separation device 10 according to the present embodiment described above, unless otherwise specified. Therefore, the same components as those of the gas-liquid separation device 10 according to the present embodiment described above are designated by the same reference numerals, and description thereof will not be repeated.
  • FIG. 19 is a perspective view schematically showing a configuration in which the swirl vane 15 according to the present embodiment is arranged in the container 11. Note that, for convenience of description, in FIG. 19, portions above and below the swirl vane 15 of the container 11 are not shown.
  • FIG. 20 is a perspective view schematically showing the configuration of swirl vane 15 according to the present embodiment.
  • the modified example of the gas-liquid separator 10 according to the present embodiment is different from the gas-liquid separator 10 according to the above-described embodiment in the configuration of the swirl vanes 15. ing.
  • the shaft 15a is configured to be twisted spirally at a rotation angle of 360 degrees about the central axis CL.
  • Each of the plurality of spiral plates 15b is configured to be spirally twisted at a rotation angle of 360 degrees about the central axis CL.
  • an oil separator has been described as an example of the gas-liquid separator 10, but the gas-liquid separator 10 is not limited to an oil separator, and may be a water separator, for example.
  • the gas-liquid separation device 10 and the refrigeration cycle device 100 according to each of the above embodiments can be combined as appropriate.

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Abstract

A gas-liquid separation device (10) comprises: a container (11); an inflow pipe (12); a liquid discharge pipe (13); a gas discharge pipe (14); and a swirl vane (15). The swirl vane (15) includes a shaft (15a) and a plurality of spiral plates (15b). The shaft (15a) is eccentric with respect to the center of the swirl vane (15) when viewed from a direction along a central axis. The plurality of spiral plates (15b) spirally extend along the shaft (15a). Each of the plurality of spiral plates (15b) extends from the shaft (15a) toward an inner wall surface (IS) of the container (11). The lower end of the shaft (15a) is arranged so as to be displaced from a gas discharge port (14a) when viewed from the direction along the central axis.

Description

気液分離装置および冷凍サイクル装置Gas-liquid separation device and refrigeration cycle device

　本発明は、気液分離装置および冷凍サイクル装置に関するものである。 The present invention relates to a gas-liquid separation device and a refrigeration cycle device.

　従来、一般的な空気調和装置、冷凍装置等の駆動源として使用される圧縮機では、圧縮された高圧冷媒ガスとともに圧縮機内部を潤滑する油が圧縮機外へ排出される。この結果、油切れにより圧縮機の摺動部に焼付きが生じることがある。そこで、圧縮機から吐出された油含有冷媒から油を分離して圧縮機へ返油するために、油分離器が用いられる。この油分離器では、気体状の冷媒と液体状の油とが分離される。つまり、気体と液体とが混在する気液二相流が気体と液体とに分離される。 Conventionally, in a compressor used as a drive source for a general air conditioner, refrigerating device, etc., oil that lubricates the inside of the compressor is discharged to the outside of the compressor together with the compressed high pressure refrigerant gas. As a result, seizure may occur in the sliding portion of the compressor due to oil shortage. Therefore, an oil separator is used to separate the oil from the oil-containing refrigerant discharged from the compressor and return the oil to the compressor. In this oil separator, the gaseous refrigerant and the liquid oil are separated. That is, the gas-liquid two-phase flow in which gas and liquid are mixed is separated into gas and liquid.

　気液二相流を気体と液体とに分離する気液分離装置は、油分離器に限らず、様々な装置に用いられている。たとえば、実開平６－３４７２１号公報（特許文献１）には、空気流に含まれた塗料ミストを空気流から分離して回収する回収装置が記載されている。この回収装置では、筒状の空洞体の内部で左右に延びる軸を中心に堰板によって螺旋状に空気流路が構成されている。空洞体の入り口から空洞体内に流れ込んだ塗料ミストを含む空気流は、螺旋状の空気流路を通過する際に、空気流と塗料ミストとに分離される。空気流はフィルターを通過して空洞体の出口から排出され、塗料ミストは空洞体のドレン口から排出される。 　The gas-liquid separator that separates the gas-liquid two-phase flow into gas and liquid is used not only in oil separators but also in various other devices. For example, Japanese Utility Model Laid-Open No. 6-34721 (Patent Document 1) describes a recovery device that separates and recovers the paint mist contained in the airflow from the airflow. In this recovery device, an air flow path is spirally formed by a weir plate around an axis extending in the left and right inside a cylindrical hollow body. The air flow containing the paint mist flowing from the entrance of the hollow body into the hollow body is separated into the air flow and the paint mist when passing through the spiral air flow path. The airflow passes through the filter and is discharged from the outlet of the hollow body, and the paint mist is discharged from the drain port of the hollow body.

実開平６－３４７２１号公報Japanese Utility Model Publication No. 6-34721

　上記公報に記載された回収装置では、水平に延びる軸を中心に堰板によって螺旋状に空気流路が構成されているため、空気流から分離された塗料ミストが空洞体内において下から上に巻き上げられる。したがって、分離された塗料ミストが再び空気流に巻き込まれるため、分離効率が低下する。 In the recovery device described in the above publication, since the weir plate spirally forms the air flow path around the horizontally extending axis, the paint mist separated from the air flow is wound up from the bottom to the top in the hollow body. To be Therefore, the separated paint mist is re-engaged in the air flow, so that the separation efficiency is reduced.

　本発明は上記課題に鑑みてなされたものであり、その目的は気体と液体との分離効率を向上させることができる気液分離装置を提供することである。 The present invention has been made in view of the above problems, and an object thereof is to provide a gas-liquid separation device that can improve the separation efficiency of gas and liquid.

　本発明の気液分離装置は、気液二相流体を気体と液体とに分離するものである。気液分離装置は、容器と、流入管と、液体排出管と、気体排出管と、旋回羽根とを備えている。容器は、上下に延びる中心軸に沿って延在し、かつ中心軸を取り囲む内壁面を有する。流入管は、容器内に気液二相流体を流入させる流入口を有する。液体排出管は、気液二相流体から分離された液体を容器から排出する液体排出口を有する。気体排出管は、気液二相流体から分離された気体を容器から排出する気体排出口を有する。旋回羽根は、容器内に配置されている。流入管の流入口は、旋回羽根の上方に配置されている。液体排出管の液体排出口は、旋回羽根の下方に配置されている。気体排出管の気体排出口は、旋回羽根の下方であり、かつ液体排出口よりも上方に配置されている。旋回羽根は、軸および複数の螺旋状板を含んでいる。軸は中心軸に沿う方向から見て旋回羽根の中心に対して偏心する。複数の螺旋状板は、軸に沿って螺旋状に延在する。複数の螺旋状板の各々は、軸から容器の内壁面に向けて延在している。軸の下端は、中心軸に沿う方向から見て気体排出口からずれるように配置されている。 The gas-liquid separation device of the present invention separates a gas-liquid two-phase fluid into a gas and a liquid. The gas-liquid separation device includes a container, an inflow pipe, a liquid discharge pipe, a gas discharge pipe, and a swirl vane. The container has an inner wall surface extending along a vertically extending central axis and surrounding the central axis. The inflow pipe has an inflow port for allowing a gas-liquid two-phase fluid to flow into the container. The liquid discharge pipe has a liquid discharge port for discharging the liquid separated from the gas-liquid two-phase fluid from the container. The gas discharge pipe has a gas discharge port for discharging the gas separated from the gas-liquid two-phase fluid from the container. The swirl vane is arranged in the container. The inflow port of the inflow pipe is arranged above the swirl vane. The liquid discharge port of the liquid discharge pipe is arranged below the swirl vane. The gas discharge port of the gas discharge pipe is arranged below the swirl vane and above the liquid discharge port. The swirl vane includes a shaft and a plurality of spiral plates. The shaft is eccentric with respect to the center of the swirl vane when viewed from the direction along the central axis. The plurality of spiral plates extend spirally along the axis. Each of the plurality of spiral plates extends from the shaft toward the inner wall surface of the container. The lower end of the shaft is arranged so as to be displaced from the gas discharge port when viewed from the direction along the central axis.

　本発明の気液分離器は、旋回羽根の軸に沿って螺旋状に延在する複数の螺旋状板により気液二相流体に旋回流が発生する。この旋回流の旋回力により、気液二相流体から液体が分離されるとともに、分離された液体の巻き上げが抑制される。これにより、気体と液体との分離効率を向上させることができる。さらに、旋回羽根の軸の下端は、容器の中心軸に沿う方向から見て気体排出口からずれるように配置されているため、軸に留まった液体が気体排出口に入ることが抑制される。これにより、気体と液体との分離効率を向上させることができる。 In the gas-liquid separator of the present invention, a swirling flow is generated in a gas-liquid two-phase fluid by a plurality of spiral plates spirally extending along the axis of the swirling blade. The swirling force of the swirling flow separates the liquid from the gas-liquid two-phase fluid and suppresses the winding of the separated liquid. Thereby, the separation efficiency of gas and liquid can be improved. Furthermore, since the lower end of the axis of the swirl vane is arranged so as to be displaced from the gas discharge port when viewed from the direction along the central axis of the container, the liquid retained on the shaft is prevented from entering the gas discharge port. Thereby, the separation efficiency of gas and liquid can be improved.

本発明の実施の形態１に係る気液分離装置を備えた冷凍サイクル装置の冷媒回路図である。It is a refrigerant circuit diagram of the refrigerating cycle device provided with the gas-liquid separation device concerning Embodiment 1 of the present invention. 本発明の実施の形態１に係る気液分離装置を示す断面図である。It is sectional drawing which shows the gas-liquid separator which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る気液分離装置の旋回羽根が容器内に配置された構成を示す斜視図である。FIG. 3 is a perspective view showing a configuration in which swirl vanes of the gas-liquid separation device according to Embodiment 1 of the present invention are arranged in a container. 本発明の実施の形態１に係る気液分離装置の旋回羽根を示す斜視図である。It is a perspective view which shows the turning blade of the gas-liquid separation device which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る気液分離装置の旋回羽根の軸および複数の螺旋状板を示す斜視図である。FIG. 3 is a perspective view showing a shaft of a swirl vane and a plurality of spiral plates of the gas-liquid separator according to the first embodiment of the present invention. 本発明の実施の形態１に係る気液分離装置の旋回羽根の軸および複数の螺旋状板を示す上面図である。It is a top view which shows the axis|shaft of the swirl|blade of the gas-liquid separator which concerns on Embodiment 1 of this invention, and several spiral plates. 本発明の実施の形態１に係る気液分離装置の旋回羽根の概念図である。It is a conceptual diagram of the turning blade of the gas-liquid separation device which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る気液分離装置内での気体と液体とが分離される様子を説明するための断面図である。FIG. 3 is a cross-sectional view for explaining how gas and liquid are separated in the gas-liquid separator according to Embodiment 1 of the present invention. 比較例の気液分離装置を示す断面図である。It is sectional drawing which shows the gas-liquid separator of a comparative example. 比較例の気液分離装置の容器の流路を示す斜視図である。It is a perspective view which shows the flow path of the container of the gas-liquid separator of a comparative example. 本発明の実施の形態１に係る気液分離装置の容器の流路を示す斜視図である。It is a perspective view which shows the flow path of the container of the gas-liquid separator which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る気液分離装置の変形例１の旋回羽根が容器内に配置された構成を示す斜視図である。It is a perspective view which shows the structure which the turning blade of the modification 1 of the gas-liquid separator which concerns on Embodiment 1 of this invention arrange|positions in a container. 本発明の実施の形態１に係る気液分離装置の変形例１の旋回羽根を示す斜視図である。It is a perspective view which shows the turning blade of the modification 1 of the gas-liquid separator which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る気液分離装置の変形例１の旋回羽根の軸および複数の螺旋状板を示す斜視図である。FIG. 6 is a perspective view showing a shaft of a swirl vane and a plurality of spiral plates of a modified example 1 of the gas-liquid separation device according to the first embodiment of the present invention. 本発明の実施の形態１に係る気液分離装置の変形例１の旋回羽根の軸および複数の螺旋状板を示す上面図である。FIG. 6 is a top view showing a shaft of a swirl vane and a plurality of spiral plates of a first modification of the gas-liquid separator according to the first embodiment of the present invention. 本発明の実施の形態１に係る気液分離装置の変形例２を示す断面図である。It is sectional drawing which shows the modification 2 of the gas-liquid separator which concerns on Embodiment 1 of this invention. 本発明の実施の形態２に係る気液分離装置の旋回羽根が容器内に配置された構成を示す斜視図である。It is a perspective view which shows the structure by which the turning blade of the gas-liquid separator which concerns on Embodiment 2 of this invention was arrange|positioned in the container. 本発明の実施の形態２に係る気液分離装置の旋回羽根を示す斜視図である。It is a perspective view which shows the turning blade of the gas-liquid separator which concerns on Embodiment 2 of this invention. 本発明の実施の形態２に係る気液分離装置の変形例の旋回羽根が容器内に配置された構成を示す斜視図である。It is a perspective view which shows the structure which the turning blade of the modification of the gas-liquid separator which concerns on Embodiment 2 of this invention arrange|positions in a container. 本発明の実施の形態２に係る気液分離装置の変形例の旋回羽根を示す斜視図である。It is a perspective view which shows the turning blade of the modification of the gas-liquid separator which concerns on Embodiment 2 of this invention.

　以下、本発明の実施の形態を図面に基づいて説明する。なお、以下においては、同一または相当する部材および部位に同一の符号を付し、重複する説明は繰り返さない。 Embodiments of the present invention will be described below with reference to the drawings. In the following, the same or corresponding members and parts will be designated by the same reference numerals, and overlapping description will not be repeated.

　実施の形態１．
　まず、図１を参照して、本発明の実施の形態１に係る冷凍サイクル装置１００の構成について説明する。図１は、本実施の形態に係る冷凍サイクル装置１００の冷媒回路図である。本実施の形態における冷凍サイクル装置１００は、たとえば空気調和装置などである。また、気液分離装置１０の一例として油分離器について説明する。 Embodiment 1.
First, the configuration of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention will be described with reference to FIG. FIG. 1 is a refrigerant circuit diagram of a refrigeration cycle device 100 according to this embodiment. Refrigeration cycle device 100 in the present embodiment is, for example, an air conditioner. An oil separator will be described as an example of the gas-liquid separator 10.

　図１に示されるように、本実施の形態における冷凍サイクル装置１００は、圧縮機１と、四方弁２と、室外熱交換器３と、流量調整弁４と、室内熱交換器５と、気液分離装置（油分離器）１０とを主に備えている。圧縮機１、四方弁２、室外熱交換器３、流量調整弁４、室内熱交換器５および気液分離装置１０は配管によって繋がっている。このようにして冷凍サイクル装置１００の冷媒回路が構成されている。室外機ユニット１００ａ内に、圧縮機１と、四方弁２と、室外熱交換器３と、流量調整弁４と、気液分離装置１０とが配置されている。室内機ユニット１００ｂ内に、室内熱交換器５が配置されている。室外機ユニット１００ａと、室内機ユニット１００ｂとは延長配管６ａ，６ｂで接続されている。 As shown in FIG. 1, the refrigeration cycle apparatus 100 in the present embodiment includes a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, a flow rate adjusting valve 4, an indoor heat exchanger 5, and an air A liquid separator (oil separator) 10 is mainly provided. The compressor 1, the four-way valve 2, the outdoor heat exchanger 3, the flow rate adjusting valve 4, the indoor heat exchanger 5, and the gas-liquid separation device 10 are connected by piping. In this way, the refrigerant circuit of the refrigeration cycle device 100 is configured. A compressor 1, a four-way valve 2, an outdoor heat exchanger 3, a flow rate adjusting valve 4, and a gas-liquid separation device 10 are arranged in the outdoor unit 100a. The indoor heat exchanger 5 is arranged in the indoor unit 100b. The outdoor unit 100a and the indoor unit 100b are connected by extension pipes 6a and 6b.

　圧縮機１は、吸入した冷媒を圧縮して吐出するように構成されている。圧縮機１は、室外熱交換器３または室内熱交換器５に流入する冷媒を圧縮するように構成されている。圧縮機１は、圧縮容量が一定の一定速圧縮機であってもよく、また圧縮容量が可変のインバーター圧縮機であってもよい。このインバーター圧縮機は、回転数を可変に制御可能に構成されている。 The compressor 1 is configured to compress the drawn refrigerant and discharge it. The compressor 1 is configured to compress the refrigerant flowing into the outdoor heat exchanger 3 or the indoor heat exchanger 5. The compressor 1 may be a constant speed compressor having a constant compression capacity, or may be an inverter compressor having a variable compression capacity. This inverter compressor is configured so that the rotation speed can be variably controlled.

　四方弁２は、冷媒の流れを切り替えるように構成されている。具体的には、四方弁２は、暖房運転時と冷房運転時とによって、室外熱交換器３または室内熱交換器５への冷媒の流れを切り替えるように構成されている。 The four-way valve 2 is configured to switch the flow of refrigerant. Specifically, the four-way valve 2 is configured to switch the flow of the refrigerant to the outdoor heat exchanger 3 or the indoor heat exchanger 5 depending on the heating operation and the cooling operation.

　室外熱交換器３は、四方弁２と、流量調整弁４とに接続されている。室外熱交換器３は、冷房運転時、圧縮機１により圧縮された冷媒を凝縮する凝縮器となる。また、室外熱交換器３は、暖房運転時、流量調整弁４により減圧された冷媒を蒸発させる蒸発器となる。室外熱交換器３は冷媒と空気との熱交換を行うためのものである。室外熱交換器３は、たとえば冷媒が内側を流れるパイプ（伝熱管）と、パイプの外側に取り付けられたフィンとを備えている。 The outdoor heat exchanger 3 is connected to the four-way valve 2 and the flow rate adjusting valve 4. The outdoor heat exchanger 3 serves as a condenser that condenses the refrigerant compressed by the compressor 1 during the cooling operation. The outdoor heat exchanger 3 also serves as an evaporator that evaporates the refrigerant whose pressure is reduced by the flow rate adjusting valve 4 during the heating operation. The outdoor heat exchanger 3 is for exchanging heat between the refrigerant and air. The outdoor heat exchanger 3 includes, for example, a pipe (heat transfer pipe) through which a refrigerant flows inside, and fins attached to the outside of the pipe.

　流量調整弁４は、室外熱交換器３と、室内熱交換器５とに接続されている。流量調整弁４は、冷房運転時、室外熱交換器３により凝縮された冷媒を減圧する絞り装置となる。また、流量調整弁４は、暖房運転時、室内熱交換器５により凝縮された冷媒を減圧する絞り装置となる。流量調整弁４は、たとえば、キャピラリーチューブ、電子膨張弁等である。 The flow rate adjusting valve 4 is connected to the outdoor heat exchanger 3 and the indoor heat exchanger 5. The flow rate adjusting valve 4 serves as a throttle device that reduces the pressure of the refrigerant condensed by the outdoor heat exchanger 3 during the cooling operation. The flow rate adjusting valve 4 serves as a throttle device that depressurizes the refrigerant condensed by the indoor heat exchanger 5 during the heating operation. The flow rate adjusting valve 4 is, for example, a capillary tube, an electronic expansion valve, or the like.

　室内熱交換器５は、四方弁２と、流量調整弁４とに接続されている。室内熱交換器５は、冷房運転時、流量調整弁４により減圧された冷媒を蒸発させる蒸発器となる。また、室内熱交換器５は、暖房運転時、圧縮機１により圧縮された冷媒を凝縮する凝縮器となる。室内熱交換器５は冷媒と空気との熱交換を行うためのものである。室内熱交換器５、たとえば冷媒が内側を流れるパイプ（伝熱管）と、パイプの外側に取り付けられたフィンとを備えている。 The indoor heat exchanger 5 is connected to the four-way valve 2 and the flow rate adjusting valve 4. The indoor heat exchanger 5 serves as an evaporator that evaporates the refrigerant decompressed by the flow rate adjusting valve 4 during the cooling operation. The indoor heat exchanger 5 also serves as a condenser that condenses the refrigerant compressed by the compressor 1 during the heating operation. The indoor heat exchanger 5 is for exchanging heat between the refrigerant and air. The indoor heat exchanger 5 includes, for example, a pipe (heat transfer pipe) through which a refrigerant flows inside, and fins attached to the outside of the pipe.

　気液分離装置１０は、圧縮機１の吐出管の下流側に接続されている。気液分離装置１０は、気液二相流体を気体と液体とに分離するように構成されている。本実施の形態では、気液分離装置１０としての油分離器は、圧縮機１から吐出された油含有冷媒から油を分離するように構成されている。また、気液分離装置１０としての油分離器は、油含有冷媒から分離された油を圧縮機１に返すように、圧縮機１の吸入管の上流側に接続されている。 The gas-liquid separation device 10 is connected to the downstream side of the discharge pipe of the compressor 1. The gas-liquid separation device 10 is configured to separate a gas-liquid two-phase fluid into a gas and a liquid. In the present embodiment, the oil separator as the gas-liquid separator 10 is configured to separate oil from the oil-containing refrigerant discharged from the compressor 1. The oil separator as the gas-liquid separator 10 is connected to the upstream side of the suction pipe of the compressor 1 so as to return the oil separated from the oil-containing refrigerant to the compressor 1.

　続いて、図２～図７を参照して、本実施の形態に係る気液分離装置１０の構成について詳しく説明する。 Subsequently, the configuration of the gas-liquid separation device 10 according to the present embodiment will be described in detail with reference to FIGS. 2 to 7.

　図２は、本実施の形態に係る気液分離装置１０の構成を概略的に示す断面図である。図２に示されるように、本実施の形態に係る気液分離装置１０は、容器１１と、流入管１２と、液体排出管１３と、気体排出管１４と、旋回羽根１５とを有している。本実施の形態に係る気液分離装置１０では、旋回下降流による分離方式が用いられている。また、本実施の形態に係る気液分離装置１０は、流入部１０ａと、分離部１０ｂと、助走区間１０ｃ１と、遷移部１０ｃ２と、集液部（集油部）１０ｄとを有している。 FIG. 2 is a sectional view schematically showing the configuration of the gas-liquid separation device 10 according to the present embodiment. As shown in FIG. 2, the gas-liquid separation device 10 according to the present embodiment has a container 11, an inflow pipe 12, a liquid discharge pipe 13, a gas discharge pipe 14, and a swirl vane 15. There is. The gas-liquid separation device 10 according to the present embodiment uses a separation method using a swirling downward flow. Further, the gas-liquid separation device 10 according to the present embodiment has an inflow part 10a, a separation part 10b, an approach section 10c1, a transition part 10c2, and a liquid collection part (oil collection part) 10d. ..

　流入部１０ａは、気液分離装置１０に気液二相流体が流入する部分である。流入部１０ａは、流入管１２によって構成されている。分離部１０ｂは、気液二相流体を気体と液体とに分離する部分である。分離部１０ｂは、容器１１の上部および旋回羽根１５により構成されている。助走区間１０ｃ１は、気体排出管１４と旋回羽根１５との間の区間である。助走区間１０ｃ１は、遷移部１０ｃ２に設けられている。遷移部１０ｃ２は、分離され気体が気体排出管１４から排出される部分である。遷移部１０ｃ２は、容器１１の中央部および気体排出管１４の上部により構成されている。集液部（集油部）１０ｄは、分離された液体を集める部分である。集液部（集油部）１０ｄは、容器１１の下部および気体排出管１４の中央部により構成されている。集液部（集油部）１０ｄに液体排出管１３が接続されている。 The inflow part 10a is a part where the gas-liquid two-phase fluid flows into the gas-liquid separation device 10. The inflow part 10 a is configured by the inflow pipe 12. The separation part 10b is a part that separates a gas-liquid two-phase fluid into a gas and a liquid. The separation part 10b is composed of the upper part of the container 11 and the swirl vane 15. The run-up section 10c1 is a section between the gas discharge pipe 14 and the swirl vane 15. The run-up section 10c1 is provided in the transition section 10c2. The transition portion 10c2 is a portion where the separated gas is discharged from the gas discharge pipe 14. The transition portion 10c2 is configured by the central portion of the container 11 and the upper portion of the gas exhaust pipe 14. The liquid collecting portion (oil collecting portion) 10d is a portion that collects the separated liquid. The liquid collecting portion (oil collecting portion) 10d is configured by the lower portion of the container 11 and the central portion of the gas discharge pipe 14. The liquid discharge pipe 13 is connected to the liquid collecting section (oil collecting section) 10d.

　容器１１は、上下に延びる中心軸ＣＬに沿って延在している。容器１１の中心軸ＣＬは、上下方向に延びている。容器１１は、内部空間を有している。容器１１は、中心軸ＣＬを取り囲む内壁面ＩＳを有する。容器１１の内壁面ＩＳは、中心軸ＣＬに直交する断面が円形状となるように構成されている。容器１１は、分離部１０ｂと遷移部１０ｃ２との径（内径および外径）が等しくなるように構成されており、遷移部１０ｃ２よりも集液部（集油部）１０ｄの径が大きくなるように構成されている。 The container 11 extends along a vertically extending central axis CL. The central axis CL of the container 11 extends in the vertical direction. The container 11 has an internal space. The container 11 has an inner wall surface IS surrounding the central axis CL. The inner wall surface IS of the container 11 is configured such that a cross section orthogonal to the central axis CL has a circular shape. The container 11 is configured such that the separation portion 10b and the transition portion 10c2 have the same diameter (inner diameter and outer diameter), and the diameter of the liquid collection portion (oil collection portion) 10d is larger than that of the transition portion 10c2. Is configured.

　流入管１２は、図１に示される圧縮機１の吐出側に接続されている。流入管１２は、容器１１の上端に接続されている。流入管１２は、容器１１の中心軸ＣＬと同軸上に配置されている。流入管１２は、容器１１の天井部を貫通している。流入管１２は、容器１１内に気液二相流体を流入させるように構成されている。流入管１２は、容器１１内に気液二相流体を流入させる流入口１２ａを有している。本実施の形態では、流入管１２は、容器１１内に油含有冷媒を流入させるように構成されている。流入管１２の流入口１２ａは旋回羽根１５の上方に配置されている。 The inflow pipe 12 is connected to the discharge side of the compressor 1 shown in FIG. The inflow pipe 12 is connected to the upper end of the container 11. The inflow pipe 12 is arranged coaxially with the central axis CL of the container 11. The inflow pipe 12 penetrates the ceiling of the container 11. The inflow pipe 12 is configured to allow the gas-liquid two-phase fluid to flow into the container 11. The inflow pipe 12 has an inflow port 12 a through which a gas-liquid two-phase fluid is introduced into the container 11. In the present embodiment, the inflow pipe 12 is configured to allow the oil-containing refrigerant to flow into the container 11. The inflow port 12 a of the inflow pipe 12 is arranged above the swirl vane 15.

　液体排出管１３は、図１に示される油戻し管２０に接続されている。液体排出管１３は、容器１１の下端に接続されている。液体排出管１３は容器１１の中心軸ＣＬと異なる位置に配置されている。液体排出管１３は、容器１１の底部を貫通している。液体排出管１３は、気液二相流体から分離された液体を容器１１から排出するように構成されている。液体排出管１３は、気液二相流体から分離された液体を容器１１から排出する液体排出口１３ａを有している。本実施の形態では、液体排出管１３は、油含有冷媒から分離された油を容器１１から排出するように構成されている。液体排出管１３の液体排出口１３ａは旋回羽根１５の下方に配置されている。 The liquid discharge pipe 13 is connected to the oil return pipe 20 shown in FIG. The liquid discharge pipe 13 is connected to the lower end of the container 11. The liquid discharge pipe 13 is arranged at a position different from the central axis CL of the container 11. The liquid discharge pipe 13 penetrates the bottom of the container 11. The liquid discharge pipe 13 is configured to discharge the liquid separated from the gas-liquid two-phase fluid from the container 11. The liquid discharge pipe 13 has a liquid discharge port 13 a for discharging the liquid separated from the gas-liquid two-phase fluid from the container 11. In the present embodiment, the liquid discharge pipe 13 is configured to discharge the oil separated from the oil-containing refrigerant from the container 11. The liquid discharge port 13 a of the liquid discharge pipe 13 is arranged below the swirl vane 15.

　気体排出管１４は、図１に示される四方弁２に接続されている。気体排出管１４は、容器１１の下側に接続されている。気体排出管１４は、容器１１の中心軸ＣＬと同軸上に配置されている。気体排出管１４は、容器１１の底部を貫通している。気体排出管１４は、気液二相流体から分離された気体を容器１１から排出する気体排出口１４ａを有している。本実施の形態では、気体排出管１４は、油含有冷媒から油が分離された冷媒を容器１１から排出するように構成されている。気体排出口１４ａは、中心軸ＣＬに重なるように配置されている。 The gas exhaust pipe 14 is connected to the four-way valve 2 shown in FIG. The gas exhaust pipe 14 is connected to the lower side of the container 11. The gas discharge pipe 14 is arranged coaxially with the central axis CL of the container 11. The gas discharge pipe 14 penetrates the bottom of the container 11. The gas discharge pipe 14 has a gas discharge port 14 a for discharging the gas separated from the gas-liquid two-phase fluid from the container 11. In the present embodiment, the gas discharge pipe 14 is configured to discharge the refrigerant, in which the oil is separated from the oil-containing refrigerant, from the container 11. The gas discharge port 14a is arranged so as to overlap the central axis CL.

　気体排出管１４の気体排出口１４ａは、旋回羽根１５の下方であり、かつ液体排出口１３ａよりも上方に配置されている。つまり、気体排出管１４の気体排出口１４ａは、上下方向において旋回羽根１５と液体排出口１３ａとの間に配置されている。気体排出口１４ａは、容器１１内に配置された気体排出管１４の先端に設けられている。気体排出口１４ａは、旋回羽根１５の真下に配置されている。気体排出口１４ａは、上下方向において旋回羽根１５との間に助走区間１０ｃ１をあけて配置されている。気体排出管１４は、容器１１の内径よりも小さい外径を有している。 The gas discharge port 14a of the gas discharge pipe 14 is arranged below the swirl vane 15 and above the liquid discharge port 13a. That is, the gas discharge port 14a of the gas discharge pipe 14 is arranged between the swirl vane 15 and the liquid discharge port 13a in the vertical direction. The gas discharge port 14 a is provided at the tip of the gas discharge pipe 14 arranged in the container 11. The gas discharge port 14 a is arranged directly below the swirl vane 15. The gas discharge port 14a is arranged in the up-down direction with the swirl vane 15 leaving a run-up section 10c1. The gas discharge pipe 14 has an outer diameter smaller than the inner diameter of the container 11.

　旋回羽根１５は、気液二相流体を旋回させながら上方から下方へ流すように構成されている。旋回羽根１５は、旋回流を発生させるように構成されている。旋回羽根１５は、旋回流の旋回力によって気液二相流体から分離された液体を内壁面ＩＳに沿って周回させながら上方から下方へ流すように構成されている。旋回羽根１５は、容器１１内に配置されている。旋回羽根１５は、容器１１内部の上側に配置されている。旋回羽根１５は、流入管１２の流入口１２ａの真下に配置されている。 The swirl vanes 15 are configured to swirl the gas-liquid two-phase fluid while flowing from the upper side to the lower side. The swirl vanes 15 are configured to generate a swirl flow. The swirl vanes 15 are configured to flow the liquid separated from the gas-liquid two-phase fluid by the swirling force of the swirling flow from above to below while circulating along the inner wall surface IS. The swirl vanes 15 are arranged in the container 11. The swirl vane 15 is arranged on the upper side inside the container 11. The swirl vane 15 is arranged directly below the inflow port 12 a of the inflow pipe 12.

　図３は、旋回羽根１５が容器１１内に配置された構成を概略的に示す斜視図である。なお、説明の便宜のため、図３では、容器１１の旋回羽根１５よりも上側および下側の部分は記載されていない。 FIG. 3 is a perspective view schematically showing a configuration in which the swirl vane 15 is arranged inside the container 11. Note that, for convenience of description, in FIG. 3, portions above and below the swirl vane 15 of the container 11 are not shown.

　図２および図３に示されるように、旋回羽根１５は、軸１５ａと、複数の螺旋状板１５ｂとを有している。軸１５ａは、複数の螺旋状板１５ｂが軸１５ａを介して交差するように構成されている。軸１５ａの下端は、中心軸ＣＬに沿う方向から見て気体排出口１４ａからずれるように配置されている。つまり、軸１５ａの下端は、中心軸ＣＬに沿う方向から見て気体排出口１４ａと重ならないように配置されている。 As shown in FIGS. 2 and 3, the swirl vane 15 has a shaft 15a and a plurality of spiral plates 15b. The shaft 15a is configured such that a plurality of spiral plates 15b cross each other via the shaft 15a. The lower end of the shaft 15a is arranged so as to be displaced from the gas discharge port 14a when viewed from the direction along the central axis CL. That is, the lower end of the shaft 15a is arranged so as not to overlap the gas discharge port 14a when viewed from the direction along the central axis CL.

　図４は、旋回羽根１５の構成を概略的に示す斜視図である。図３および図４に示されるように、複数の螺旋状板１５ｂの各々は、軸１５ａに接続されている。複数の螺旋状板１５ｂは、互いに交差するように軸１５ａに接続されている。複数の螺旋状板１５ｂの各々は、気液二相流体に対し旋回力を発生させるように構成されている。複数の螺旋状板１５ｂの各々は、軸１５ａに沿って螺旋状に延在している。複数の螺旋状板１５ｂの各々は、軸１５ａから容器１１の内壁面ＩＳに向けて延在している。複数の螺旋状板１５ｂの各々は、中心軸ＣＬに沿う方向から見て直線状に構成されている。本実施の形態では、旋回羽根１５は、６枚の螺旋状板１５ｂを有している。なお、旋回羽根１５の螺旋状板１５ｂの枚数は、６枚に限定されない。 FIG. 4 is a perspective view schematically showing the structure of the swirl vane 15. As shown in FIGS. 3 and 4, each of the plurality of spiral plates 15b is connected to the shaft 15a. The plurality of spiral plates 15b are connected to the shaft 15a so as to intersect each other. Each of the plurality of spiral plates 15b is configured to generate a swirling force on the gas-liquid two-phase fluid. Each of the plurality of spiral plates 15b extends spirally along the axis 15a. Each of the plurality of spiral plates 15b extends from the shaft 15a toward the inner wall surface IS of the container 11. Each of the plurality of spiral plates 15b has a linear shape when viewed from the direction along the central axis CL. In the present embodiment, the swirl vane 15 has six spiral plates 15b. The number of spiral plates 15b of the swirl vane 15 is not limited to six.

　図５は、旋回羽根１５の軸１５ａおよび複数の螺旋状板１５ｂの構成を概略的に示す斜視図である。図６は、旋回羽根１５の軸１５ａおよび複数の螺旋状板１５ｂの構成を概略的に示す上面図である。図５および図６では、軸１５ａおよび複数の螺旋状板１５ｂの後ろに隠れて見えない部分が破線で示されている。 FIG. 5 is a perspective view schematically showing the configuration of the shaft 15a of the swirl vane 15 and the plurality of spiral plates 15b. FIG. 6 is a top view schematically showing the configuration of the shaft 15a of the swirl blade 15 and the plurality of spiral plates 15b. In FIGS. 5 and 6, a portion hidden behind the shaft 15a and the plurality of spiral plates 15b and not visible is indicated by a broken line.

　図５および図６に示されるように、軸１５ａは、中心軸ＣＬに沿う方向から見て旋回羽根１５の中心ＣＰに対して偏心するように構成されている。旋回羽根１５の中心ＣＰは、上方から下方に向けて旋回羽根１５を見たときに旋回羽根１５の図心に位置している。本実施の形態では、旋回羽根１５の中心ＣＰは、容器１１の中心軸ＣＬに位置している。軸１５ａは、中心軸ＣＬに沿って螺旋状に延在するように構成されている。 As shown in FIGS. 5 and 6, the shaft 15a is configured to be eccentric with respect to the center CP of the swirl vane 15 when viewed from the direction along the central axis CL. The center CP of the swirl vane 15 is located at the center of the swirl vane 15 when the swirl vane 15 is viewed from the upper side to the lower side. In the present embodiment, the center CP of the swirl vane 15 is located on the central axis CL of the container 11. The shaft 15a is configured to spirally extend along the central axis CL.

　複数の螺旋状板１５ｂの各々の外周端は、容器１１の内壁面ＩＳに接している。したがて、中心軸ＣＬに沿って上方から下方に向けて旋回羽根１５を見たときに、複数の螺旋状板１５ｂの外周端と容器１１の内壁面ＩＳとの間に隙間がない。 The outer peripheral ends of the plurality of spiral plates 15b are in contact with the inner wall surface IS of the container 11. Therefore, when the swirl vanes 15 are viewed from the upper side to the lower side along the central axis CL, there is no gap between the outer peripheral ends of the plurality of spiral plates 15b and the inner wall surface IS of the container 11.

　複数の螺旋状板１５ｂの各々は、３６０度を複数の螺旋状板１５ｂの枚数で除した角度以上でねじれるように構成されている。つまり、中心軸ＣＬに沿って上方から下方に向けて旋回羽根１５を見たときに、複数の螺旋状板１５ｂの各々は、３６０度を複数の螺旋状板１５ｂの枚数で除した角度以上にねじれるように構成されている。中心軸ＣＬに沿って上方から下方に向けて旋回羽根１５を見たときに、旋回羽根１５は一端部から他端部が見えないように構成されている。 Each of the plurality of spiral plates 15b is configured to be twisted at an angle equal to or greater than an angle obtained by dividing 360 degrees by the number of the plurality of spiral plates 15b. That is, when the swirl vanes 15 are viewed from the upper side to the lower side along the central axis CL, each of the plurality of spiral plates 15b has an angle of 360 degrees or more divided by the number of the plurality of spiral plates 15b. It is designed to twist. When the swirl vane 15 is viewed from the upper side to the lower side along the central axis CL, the swirl vane 15 is configured so that the other end cannot be seen from one end.

　本実施の形態では、軸１５ａは、中心軸ＣＬを中心として１８０度の回転角度で螺旋状にねじれるように構成されている。複数の螺旋状板１５ｂの各々は、中心軸ＣＬを中心として１８０度の回転角度で螺旋状にねじれるように構成されている。 In the present embodiment, the shaft 15a is configured to be twisted spirally at a rotation angle of 180 degrees about the central axis CL. Each of the plurality of spiral plates 15b is configured to be spirally twisted at a rotation angle of 180 degrees about the central axis CL.

　中心軸ＣＬに沿う方向から見て、互いに隣り合う螺旋状板１５ｂ同士の軸１５ａを介して向かい合う角度は鋭角となる。中心軸ＣＬに沿う方向から見て、複数の螺旋状板１５ｂは、旋回羽根１５の中心ＣＰを通って一直線上に並ぶ２つの螺旋状板１５ｂを対称軸として、線対称に配置されている。 When viewed from the direction along the central axis CL, the angles of the spiral plates 15b adjacent to each other facing each other via the shaft 15a are acute angles. When viewed from the direction along the central axis CL, the plurality of spiral plates 15b are arranged in line symmetry with the two spiral plates 15b aligned in a straight line passing through the center CP of the swirl blade 15 as the axis of symmetry.

　容器１１は、第１流路Ｆ１、第２流路Ｆ２、第３流路Ｆ３、第４流路Ｆ４、第５流路Ｆ５および第６流路Ｆ６を有している。第１流路Ｆ１、第２流路Ｆ２、第３流路Ｆ３、第４流路Ｆ４、第５流路Ｆ５および第６流路Ｆ６は、複数の螺旋状板１５ｂの各々によって区切られている。第１流路Ｆ１、第２流路Ｆ２、第３流路Ｆ３、第４流路Ｆ４、第５流路Ｆ５および第６流路Ｆ６は、旋回羽根１５の軸１５ａを中心として反時計回りに順に並んで配置されている。各流路は、旋回羽根１５の中心ＣＰを通って一直線上に並ぶ２つの螺旋状板１５ｂを対称軸として線対称に配置されている。つまり、第１流路Ｆ１と第６流路Ｆ６とが線対称に配置されており、第２流路Ｆ２と第５流路Ｆ５とが線対称に配置されており、第３流路Ｆ３と第４流路Ｆ４とが線対称に配置されている。 The container 11 has a first flow passage F1, a second flow passage F2, a third flow passage F3, a fourth flow passage F4, a fifth flow passage F5 and a sixth flow passage F6. The first flow passage F1, the second flow passage F2, the third flow passage F3, the fourth flow passage F4, the fifth flow passage F5, and the sixth flow passage F6 are separated by each of the plurality of spiral plates 15b. .. The first flow passage F1, the second flow passage F2, the third flow passage F3, the fourth flow passage F4, the fifth flow passage F5, and the sixth flow passage F6 rotate counterclockwise about the shaft 15a of the swirl vane 15. They are arranged side by side. The respective flow passages are arranged in line symmetry with the two spiral plates 15b arranged in a straight line passing through the center CP of the swirl vane 15 as the axis of symmetry. That is, the first flow passage F1 and the sixth flow passage F6 are arranged in line symmetry, the second flow passage F2 and the fifth flow passage F5 are arranged in line symmetry, and the third flow passage F3 is arranged. The fourth flow path F4 is arranged in line symmetry.

　第１流路Ｆ１は、第２流路Ｆ２よりも大きな流路面積を有している。第２流路Ｆ２は、第３流路Ｆ３よりも大きな流路面積を有している。第６流路Ｆ６は、第５流路Ｆ５よりも大きな流路面積を有している。第５流路Ｆ５は、第４流路Ｆ４よりも大きな流路面積を有している。第１流路Ｆ１は、第６流路Ｆ６と同じ流路面積を有している。第２流路Ｆ２は、第５流路Ｆ５と同じ流路面積を有している。第３流路Ｆ３は、第４流路Ｆ４と同じ流路面積を有している。この流路面積は、中心軸ＣＬに沿う方向から見たときの各流路の面積であり、中心軸ＣＬに直交する断面における各流路の面積である。 The first channel F1 has a larger channel area than the second channel F2. The second flow passage F2 has a flow passage area larger than that of the third flow passage F3. The sixth flow passage F6 has a larger flow passage area than the fifth flow passage F5. The fifth flow passage F5 has a flow passage area larger than that of the fourth flow passage F4. The first flow passage F1 has the same flow passage area as the sixth flow passage F6. The second flow passage F2 has the same flow passage area as the fifth flow passage F5. The third flow passage F3 has the same flow passage area as the fourth flow passage F4. This flow channel area is the area of each flow channel when viewed from the direction along the central axis CL, and is the area of each flow channel in the cross section orthogonal to the central axis CL.

　図７は、本実施の形態に係る旋回羽根１５の概念図である。図５に示されるように、旋回羽根１５は、断面形状１０１が螺旋状の軌跡１０２を通過したときに断面形状１０１と軌跡１０２とによって描かれた形状で構成されている。断面形状１０１の内部の主交差部１０３は、軌跡１０２の中心に対して偏心している。主交差部１０３は、断面形状１０１において軸１５ａと複数の螺旋状板１５ｂとが交差する部分である。軌跡１０２の中心は、図７中ｘ軸、ｙ軸、ｚ軸の中心である。このｘ軸は旋回羽根１５の前後方向に対応し、このｙ軸は旋回羽根１５の左右方向に対応し、このｚ軸は旋回羽根１５の上下方向に対応する。 FIG. 7 is a conceptual diagram of the swirl vane 15 according to the present embodiment. As shown in FIG. 5, the swirl vane 15 has a shape drawn by the cross-sectional shape 101 and the locus 102 when the cross-sectional shape 101 passes through the spiral locus 102. The main intersection 103 inside the cross-sectional shape 101 is eccentric with respect to the center of the locus 102. The main intersection 103 is a portion where the shaft 15a and the plurality of spiral plates 15b intersect in the cross-sectional shape 101. The center of the locus 102 is the center of the x axis, the y axis, and the z axis in FIG. 7. The x-axis corresponds to the front-back direction of the swirl blade 15, the y-axis corresponds to the left-right direction of the swirl blade 15, and the z-axis corresponds to the up-down direction of the swirl blade 15.

　図５および図７に示されるように、旋回羽根１５の中心軸ＣＬに直交する断面形状１０１は、いずれの断面における断面形状１０１も中心軸ＣＬを中心に回転したときに相似となる。つまり、旋回羽根１５の中心軸ＣＬに直交する断面形状１０１は、いずれの断面においても、相似形状となる。 As shown in FIGS. 5 and 7, the cross-sectional shape 101 orthogonal to the central axis CL of the swirl vane 15 becomes similar when the cross-sectional shape 101 in any cross section is rotated about the central axis CL. That is, the cross-sectional shape 101 orthogonal to the central axis CL of the swirl vane 15 has a similar shape in any cross section.

　次に、再び図１を参照して、本実施の形態における冷凍サイクル装置１００の動作について説明する。図中実線矢印により冷房運転時の冷媒流れが示され、図中破線矢印により暖房運転時の冷媒流れが示されている。 Next, the operation of the refrigeration cycle apparatus 100 according to the present embodiment will be described with reference to FIG. 1 again. In the figure, the solid line arrow indicates the refrigerant flow during the cooling operation, and the broken line arrow in the figure indicates the refrigerant flow during the heating operation.

　本実施の形態の冷凍サイクル装置１００は、冷房運転と暖房運転とを選択的に行うことが可能である。冷房運転においては、圧縮機１、気液分離装置（油分離器）１０、四方弁２、室外熱交換器３、流量調整弁４、室内熱交換器５の順に冷媒が冷媒回路を循環する。冷房運転においては、室外熱交換器３は凝縮器として機能し、室内熱交換器５は蒸発器として機能する。暖房運転においては、圧縮機１、気液分離装置１０、四方弁２、室内熱交換器５、流量調整弁４、室外熱交換器３の順に冷媒が冷媒回路を循環する。暖房運転においては、室内熱交換器５は凝縮器として機能し、室外熱交換器３は蒸発器として機能する。 The refrigeration cycle device 100 of the present embodiment can selectively perform the cooling operation and the heating operation. In the cooling operation, the refrigerant circulates through the refrigerant circuit in the order of the compressor 1, the gas-liquid separator (oil separator) 10, the four-way valve 2, the outdoor heat exchanger 3, the flow rate adjusting valve 4, and the indoor heat exchanger 5. In the cooling operation, the outdoor heat exchanger 3 functions as a condenser, and the indoor heat exchanger 5 functions as an evaporator. In the heating operation, the refrigerant circulates through the refrigerant circuit in the order of the compressor 1, the gas-liquid separator 10, the four-way valve 2, the indoor heat exchanger 5, the flow rate adjusting valve 4, and the outdoor heat exchanger 3. In the heating operation, the indoor heat exchanger 5 functions as a condenser, and the outdoor heat exchanger 3 functions as an evaporator.

　さらに、冷房運転について詳しく説明する。圧縮機１が駆動することによって、圧縮機１から高温高圧のガス状態の冷媒が吐出される。この冷媒には圧縮機内部を潤滑する油が含有されている。つまり、この冷媒は油含有冷媒である。圧縮機１から吐出された高温高圧のガス状態の油含有冷媒は、気液分離装置１０に流れ込む。気液分離装置１０で油含有冷媒から油が分離される。気液分離装置１０で油が分離された冷媒は、四方弁２を介して室外熱交換器３に流れ込む。室外熱交換器３では、流れ込んだガス冷媒と、室外の空気との間で熱交換が行われる。これにより、高温高圧のガス冷媒は、凝縮して高圧の液冷媒になる。 Furthermore, the cooling operation will be explained in detail. By driving the compressor 1, the high-temperature and high-pressure gas-state refrigerant is discharged from the compressor 1. This refrigerant contains oil that lubricates the inside of the compressor. That is, this refrigerant is an oil-containing refrigerant. The high-temperature and high-pressure gas-state oil-containing refrigerant discharged from the compressor 1 flows into the gas-liquid separation device 10. The gas-liquid separator 10 separates oil from the oil-containing refrigerant. The refrigerant from which oil has been separated by the gas-liquid separation device 10 flows into the outdoor heat exchanger 3 via the four-way valve 2. In the outdoor heat exchanger 3, heat exchange is performed between the gas refrigerant that has flowed in and the outdoor air. As a result, the high-temperature and high-pressure gas refrigerant is condensed into a high-pressure liquid refrigerant.

　室外熱交換器３から送り出された高圧の液冷媒は、流量調整弁４によって、低圧のガス冷媒と液冷媒との二相状態の冷媒になる。二相状態の冷媒は、室内熱交換器５に流れ込む。室内熱交換器５では、流れ込んだ二相状態の冷媒と、室内の空気との間で熱交換が行われる。これにより、二相状態の冷媒は、液冷媒が蒸発して低圧のガス冷媒になる。この熱交換によって、室内が冷やされる。室内熱交換器５から送り出された低圧のガス冷媒は、四方弁２を介して圧縮機１に流れ込み、圧縮されて高温高圧のガス冷媒となって、再び圧縮機１から吐出される。以下、このサイクルが繰り返される。 The high-pressure liquid refrigerant sent from the outdoor heat exchanger 3 becomes a two-phase refrigerant of low-pressure gas refrigerant and liquid refrigerant by the flow rate adjusting valve 4. The two-phase refrigerant flows into the indoor heat exchanger 5. In the indoor heat exchanger 5, heat exchange is performed between the two-phase refrigerant that has flowed in and the indoor air. As a result, the two-phase refrigerant becomes a low-pressure gas refrigerant by evaporating the liquid refrigerant. This heat exchange cools the room. The low-pressure gas refrigerant sent from the indoor heat exchanger 5 flows into the compressor 1 through the four-way valve 2, is compressed into a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 1 again. Hereinafter, this cycle is repeated.

　また、暖房運転について詳しく説明する。冷房運転と同様に圧縮機１が駆動することによって、圧縮機１から高温高圧のガス状態の油含有冷媒が吐出される。圧縮機１から吐出された高温高圧のガス状態の油含有冷媒は、気液分離装置１０に流れ込む。気液分離装置１０で油含有冷媒から油が分離される。気液分離装置１０で油が分離された冷媒は、四方弁２を経由して室内熱交換器５に流れ込む。室内熱交換器５では、流れ込んだ冷媒と、室内の空気との間で熱交換が行われる。これにより、高温高圧のガス冷媒は、凝縮して高圧の液冷媒になる。この熱交換によって、室内が暖められる。 Also, explain heating operation in detail. By driving the compressor 1 in the same manner as in the cooling operation, the high-temperature high-pressure gas-state oil-containing refrigerant is discharged from the compressor 1. The high-temperature and high-pressure gas-state oil-containing refrigerant discharged from the compressor 1 flows into the gas-liquid separation device 10. The gas-liquid separator 10 separates oil from the oil-containing refrigerant. The refrigerant from which the oil has been separated by the gas-liquid separator 10 flows into the indoor heat exchanger 5 via the four-way valve 2. In the indoor heat exchanger 5, heat exchange is performed between the flowing refrigerant and the indoor air. As a result, the high-temperature and high-pressure gas refrigerant is condensed into a high-pressure liquid refrigerant. This heat exchange warms the room.

　室内熱交換器５から送り出された高圧の液冷媒は、流量調整弁４によって、低圧のガス冷媒と液冷媒との二相状態の冷媒になる。二相状態の冷媒は、室外熱交換器３に流れ込む。室外熱交換器３では、流れ込んだ二相状態の冷媒と、室外の空気との間で熱交換が行われる。これにより、二相状態の冷媒は、液冷媒が蒸発して低圧のガス冷媒になる。室外熱交換器３から送り出された低圧のガス冷媒は、四方弁２を介して圧縮機１に流れ込み、圧縮されて高温高圧のガス冷媒となって、再び圧縮機１から吐出される。以下、このサイクルが繰り返される。 The high-pressure liquid refrigerant sent out from the indoor heat exchanger 5 becomes a two-phase refrigerant of low-pressure gas refrigerant and liquid refrigerant by the flow rate adjusting valve 4. The two-phase state refrigerant flows into the outdoor heat exchanger 3. In the outdoor heat exchanger 3, heat exchange is performed between the two-phase refrigerant that has flowed in and the outdoor air. As a result, the two-phase refrigerant becomes a low-pressure gas refrigerant by evaporating the liquid refrigerant. The low-pressure gas refrigerant sent from the outdoor heat exchanger 3 flows into the compressor 1 via the four-way valve 2, is compressed into a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 1 again. Hereinafter, this cycle is repeated.

　続いて、図１および図８を参照して、本実施の形態に係る気液分離装置（油分離器）１０の動作について説明する。図８は、本実施の形態に係る気液分離装置１０内での気体（冷媒）と液体（油）とが分離される様子を説明するための断面図である。図８では、油含有冷媒の流れは白抜き矢印で示され、冷媒の流れは実線矢印で示され、油の流れは破線矢印で示されている。 Next, the operation of the gas-liquid separator (oil separator) 10 according to the present embodiment will be described with reference to FIGS. 1 and 8. FIG. 8 is a cross-sectional view for explaining how gas (refrigerant) and liquid (oil) are separated in the gas-liquid separator 10 according to the present embodiment. In FIG. 8, the flow of the oil-containing refrigerant is shown by a white arrow, the flow of the refrigerant is shown by a solid line arrow, and the oil flow is shown by a broken line arrow.

　図１に示されるように、冷凍サイクル装置１００の冷媒回路において、圧縮機１から吐出された油含有冷媒は、気液分離装置１０により冷媒と油とに分離される。油含有冷媒は、冷媒と、圧縮機１内に封入される油（冷凍機油）とを含んでいる。気液分離装置１０により油含有冷媒から分離された冷媒は、四方弁２へ排出される。他方、気液分離装置１０により油含有冷媒から分離された油は、油戻し管２０を通って圧縮機１の吸入側へ排出される。 As shown in FIG. 1, in the refrigerant circuit of the refrigeration cycle apparatus 100, the oil-containing refrigerant discharged from the compressor 1 is separated by the gas-liquid separator 10 into refrigerant and oil. The oil-containing refrigerant contains a refrigerant and oil (refrigerating machine oil) sealed in the compressor 1. The refrigerant separated from the oil-containing refrigerant by the gas-liquid separator 10 is discharged to the four-way valve 2. On the other hand, the oil separated from the oil-containing refrigerant by the gas-liquid separation device 10 is discharged to the suction side of the compressor 1 through the oil return pipe 20.

　図８に示されるように、気液分離装置１０内に流入管１２から高流量の油含有冷媒が流入すると、旋回羽根１５の複数の螺旋状板１５ｂによって発生した旋回流によって、油含有冷媒から油が分離される。油含有冷媒から分離された油は、容器１１の内壁面ＩＳへ衝突することで液膜となり、重力と旋回流とによって容器１１の内壁面ＩＳに沿って容器１１の底部へ流れる。このようにして、集油部１０ｄで油が集油される。集油された油は液体排出管１３から排出される。液体排出管１３から排出された油は、油戻し管２０を通って圧縮機１の吸入側に返される。他方、油が分離された冷媒は、気体排出管１４から排出される。気体排出管１４から排出された冷媒は四方弁２に流れ込む。 As shown in FIG. 8, when a high flow rate of the oil-containing refrigerant flows into the gas-liquid separator 10 from the inflow pipe 12, the oil-containing refrigerant is separated from the oil-containing refrigerant by the swirling flow generated by the plurality of spiral plates 15 b of the swirl vanes 15. The oil separates. The oil separated from the oil-containing refrigerant becomes a liquid film by colliding with the inner wall surface IS of the container 11, and flows to the bottom of the container 11 along the inner wall surface IS of the container 11 due to gravity and swirling flow. In this way, the oil is collected by the oil collecting section 10d. The collected oil is discharged from the liquid discharge pipe 13. The oil discharged from the liquid discharge pipe 13 is returned to the suction side of the compressor 1 through the oil return pipe 20. On the other hand, the refrigerant from which the oil has been separated is discharged from the gas discharge pipe 14. The refrigerant discharged from the gas discharge pipe 14 flows into the four-way valve 2.

　また、気液分離装置１０内に流入管１２から低流量の油含有冷媒が流入すると、旋回羽根１５を通過後、表面張力によって狭小部となる主交差部１０３（図７）の位置に油が集まる。その後、旋回流によって油の一部は内壁面ＩＳへ誘導され、油の他の一部は重量の影響により落下し、液体排出管１３から排出される。高流量の油含有冷媒が流入した場合と同様に、ガス冷媒は、気体排出管１４から排出される。 Further, when a low flow rate of the oil-containing refrigerant flows into the gas-liquid separation device 10 from the inflow pipe 12, the oil flows to the position of the main intersection 103 (FIG. 7) which becomes a narrow portion due to surface tension after passing the swirl vanes 15. get together. Then, part of the oil is guided to the inner wall surface IS by the swirling flow, and the other part of the oil falls due to the influence of the weight and is discharged from the liquid discharge pipe 13. The gas refrigerant is discharged from the gas discharge pipe 14 as in the case where a high flow rate of the oil-containing refrigerant has flowed in.

　次に、本実施の形態の作用効果について比較例と対比して説明する。
　図９および図１０を参照して、比較例の気液分離装置（油分離器）１０について説明する。図９は、比較例の気液分離装置１０の構成を概略的に示す断面図である。図９に示されるように、比較例の気液分離装置１０では、旋回羽根１５の構成が本実施の形態に係る旋回羽根１５と異なっている。比較例の旋回羽根１５の軸１５ａは、上下に直線状に延在している。比較例の旋回羽根１５の軸１５ａは、中心軸ＣＬ上に位置している。このため、比較例の旋回羽根１５では、旋回流によって分離された液体は、表面張力によって互いに隣り合う螺旋状板１５ｂの間で軸１５ａに留まる。この液体は、重力によって落下して気体排出口１４ａに入る。これにより、気体と液体との分離効率が低下する。 Next, the operation and effect of this embodiment will be described in comparison with a comparative example.
A gas-liquid separator (oil separator) 10 of a comparative example will be described with reference to FIGS. 9 and 10. FIG. 9 is a sectional view schematically showing the configuration of the gas-liquid separation device 10 of the comparative example. As shown in FIG. 9, in the gas-liquid separation device 10 of the comparative example, the structure of the swirl vane 15 is different from that of the swirl vane 15 according to the present embodiment. The shaft 15a of the swirl vane 15 of the comparative example extends vertically in a straight line. The shaft 15a of the swirl vane 15 of the comparative example is located on the central axis CL. Therefore, in the swirl vane 15 of the comparative example, the liquid separated by the swirling flow stays on the shaft 15a between the spiral plates 15b adjacent to each other due to the surface tension. This liquid drops by gravity and enters the gas outlet 14a. As a result, the separation efficiency between the gas and the liquid decreases.

　図１０は、比較例の気液分離装置１０の容器１１の流路を概略的に示す斜視図である。図１１は、本実施の形態に係る気液分離装置１０の流路を概略的に示す斜視図である。なお、説明の便宜のため、図１０および図１１では、容器１１の旋回羽根１５よりも上側および下側の部分は記載されていない。 FIG. 10 is a perspective view schematically showing the flow path of the container 11 of the gas-liquid separation device 10 of the comparative example. FIG. 11 is a perspective view schematically showing the flow path of the gas-liquid separation device 10 according to this embodiment. Note that, for convenience of description, in FIGS. 10 and 11, the portions above and below the swirl vanes 15 of the container 11 are not shown.

　図１０に示されるように、比較例の気液分離装置１０の容器１１では、第１流路Ｆ１～第６流路Ｆ６は、互いに同じ流路面積を有している。気液分離装置１０に流入する気液二相流体の流速が増減することにより圧力が脈動することがある。たとえば、圧縮機１の弁の開閉により圧力が脈動することがある。圧力が脈動する場合、比較例の気液分離装置１０の容器１１では、第１流路Ｆ１～第６流路Ｆ６の流路面積が均一であるため、圧力が脈動するタイミングに応じて、旋回流が強くなる流路が変化する。具体的には、時間の経過に伴って第１流路Ｆ１～第６流路Ｆ６の順に旋回流が強くなる流路が変化する。このため、液体の飛ぶ方向が不確定である。 As shown in FIG. 10, in the container 11 of the gas-liquid separation device 10 of the comparative example, the first flow passage F1 to the sixth flow passage F6 have the same flow passage area. The pressure may pulsate as the flow velocity of the gas-liquid two-phase fluid flowing into the gas-liquid separation device 10 increases or decreases. For example, the pressure may pulsate by opening and closing the valve of the compressor 1. When the pressure pulsates, in the container 11 of the gas-liquid separation device 10 of the comparative example, since the flow passage areas of the first flow passage F1 to the sixth flow passage F6 are uniform, it is swirled in accordance with the timing of the pressure pulsation. The flow path where the flow becomes stronger changes. Specifically, the passage in which the swirling flow becomes stronger changes in the order of the first passage F1 to the sixth passage F6 with the passage of time. Therefore, the direction in which the liquid flies is uncertain.

　これに対して、図１１に示されるように、本実施の形態に係る気液分離装置１０の容器１１では、流路面積は、第１流路Ｆ１、第２流路Ｆ２、第３流路Ｆ３の順に小さくなっている。また、流路面積は、第４流路Ｆ４、第５流路Ｆ５、第６流路Ｆ６の順に大きくなっている。このため、旋回流の主流が流路広大域に固定される。つまり、旋回流の主張が第１流路Ｆ１および第６流路Ｆ６に固定される。このため、液体の飛ぶ方向を確定できる。これにより、液体に対してより効率的に遠心力を付与することで気体と液体との分離効率を向上させることができる。 On the other hand, as shown in FIG. 11, in the container 11 of the gas-liquid separation device 10 according to the present embodiment, the flow passage areas are the first flow passage F1, the second flow passage F2, and the third flow passage. It becomes smaller in the order of F3. In addition, the flow passage area increases in the order of the fourth flow passage F4, the fifth flow passage F5, and the sixth flow passage F6. Therefore, the main flow of the swirling flow is fixed in the wide area of the flow path. That is, the claim of the swirling flow is fixed to the first flow path F1 and the sixth flow path F6. Therefore, the direction in which the liquid flies can be determined. This makes it possible to improve the separation efficiency between the gas and the liquid by more efficiently applying the centrifugal force to the liquid.

　本実施の形態に係る気液分離装置１０によれば、旋回羽根１５の軸１５ａに沿って螺旋状に延在する複数の螺旋状板１５ｂにより気液二相流体に旋回流が発生する。この旋回流の旋回力により、気液二相流体から液体が分離されるとともに、分離された液体の巻き上げが抑制される。つまり、旋回流によって分離された液体は、容器１１の内壁面ＩＳに衝突後に液膜として流動することで再飛散が抑制される。また、分離された液体は中心軸ＣＬに沿って下方に流れ、旋回流は中心軸ＣＬを中心に旋回する。このため、分離された液体の下方から上方への巻き上げが抑制される。したがって、気体と液体との分離効率を向上させることができる。さらに、旋回羽根１５の軸１５ａの下端は、容器１１の中心軸ＣＬに沿う方向から見て気体排出口１４ａからずれるように配置されているため、軸１５ａに留まった液体が気体排出口１４ａに入ることが抑制される。つまり、液体の表面張力によって互いに隣り合う螺旋状板１５ｂの間で軸１５ａに留まった液体が、重力によって落下することにより気体排出口１４ａに入ることが抑制される。これにより、気体と液体との分離効率を向上させることができる。 According to the gas-liquid separation device 10 according to the present embodiment, a swirling flow is generated in the gas-liquid two-phase fluid by the plurality of spiral plates 15b spirally extending along the shaft 15a of the swirling blade 15. The swirling force of the swirling flow separates the liquid from the gas-liquid two-phase fluid and suppresses the winding of the separated liquid. That is, the liquid separated by the swirling flow flows as a liquid film after colliding with the inner wall surface IS of the container 11, and thus re-scattering is suppressed. Further, the separated liquid flows downward along the central axis CL, and the swirling flow swirls around the central axis CL. For this reason, it is possible to prevent the separated liquid from being rolled up from below. Therefore, the separation efficiency of gas and liquid can be improved. Further, since the lower end of the shaft 15a of the swirl vane 15 is arranged so as to be displaced from the gas discharge port 14a when viewed from the direction along the central axis CL of the container 11, the liquid retained on the shaft 15a is discharged to the gas discharge port 14a. The entry is suppressed. That is, the liquid retained on the shaft 15a between the spiral plates 15b adjacent to each other due to the surface tension of the liquid is prevented from entering the gas discharge port 14a by falling due to gravity. Thereby, the separation efficiency of gas and liquid can be improved.

　また、旋回羽根１５の軸１５ａは、中心軸ＣＬに沿う方向から見て旋回羽根１５の中心ＣＰに対して偏心するように構成されている。このため、旋回羽根１５の中心軸ＣＬを中心とした周方向の大きさを維持しながら軸１５ａの下端を容器１１の中心軸ＣＬに沿う方向から見て気体排出口１４ａからずれるように配置することができる。 Further, the shaft 15a of the swirl vane 15 is configured to be eccentric with respect to the center CP of the swirl vane 15 when viewed from the direction along the central axis CL. Therefore, the lower end of the shaft 15a is arranged so as to deviate from the gas discharge port 14a when viewed from the direction along the central axis CL of the container 11 while maintaining the size in the circumferential direction of the swirl vane 15 around the central axis CL. be able to.

　本実施の形態に係る気液分離装置１０では、流入管１２の流入口１２ａは旋回羽根１５の上方に配置されている。また、液体排出管１３の液体排出口１３ａは旋回羽根１５の下方に配置されている。さらに、気体排出管１４の気体排出口１４ａは旋回羽根１５の下方であり、かつ液体排出口１３ａよりも上方に配置されている。これにより、旋回下降流による分離方式を実現することが可能となる。 In the gas-liquid separation device 10 according to the present embodiment, the inflow port 12a of the inflow pipe 12 is arranged above the swirl vane 15. The liquid discharge port 13 a of the liquid discharge pipe 13 is arranged below the swirl vane 15. Further, the gas discharge port 14a of the gas discharge pipe 14 is arranged below the swirl vane 15 and above the liquid discharge port 13a. This makes it possible to realize a separation method using a swirling downward flow.

　また、本実施の形態に係る気液分離装置１０では、気体排出管１４の気体排出口１４ａは旋回羽根１５の下方であり、かつ液体排出口１３ａよりも上方に配置されている。このため、旋回羽根１５で分離された液体が気体排出管１４に流入することを抑制することができる。 Further, in the gas-liquid separation device 10 according to the present embodiment, the gas discharge port 14a of the gas discharge pipe 14 is arranged below the swirl vane 15 and above the liquid discharge port 13a. Therefore, it is possible to prevent the liquid separated by the swirl vanes 15 from flowing into the gas discharge pipe 14.

　従来のサイクロン式分離器は、気液二相流体を容器の内壁面に垂直に衝突させる。つまり、気液二相流体は上下方向に直交する水平方向に内壁面に衝突する。しかしながら、従来のサイクロン式分離器では、容器の内壁面と気体排出管との離間距離が短い場合、分離された液体が再飛散して気体とともに吸引されることで気体と液体との分離効率が低下する。そのため、従来のサイクロン式分離器では小型化は困難である。これに対して、本実施の形態に係る気液分離装置１０では、旋回下降流による分離方式が用いられている。そのため、流入管１２と気体排出管１４との離間距離を上下方向に確保することができる。したがって、本実施の形態に係る気液分離装置１０では、従来のサイクロン式分離器と比較して小型化することが容易となる。 　The conventional cyclone separator vertically collides the gas-liquid two-phase fluid with the inner wall surface of the container. That is, the gas-liquid two-phase fluid collides with the inner wall surface in the horizontal direction orthogonal to the vertical direction. However, in the conventional cyclone separator, when the separation distance between the inner wall surface of the container and the gas discharge pipe is short, the separated liquid is re-scattered and sucked together with the gas, so that the separation efficiency between the gas and the liquid is increased. descend. Therefore, it is difficult to downsize the conventional cyclone separator. On the other hand, in the gas-liquid separation device 10 according to the present embodiment, a separation method using a swirling downward flow is used. Therefore, the separation distance between the inflow pipe 12 and the gas exhaust pipe 14 can be secured in the vertical direction. Therefore, the gas-liquid separation device 10 according to the present embodiment can be easily downsized as compared with the conventional cyclone separator.

　本実施の形態に係る気液分離装置１０としての油分離器では、油の分離効率を向上させることにより、圧縮機１への返油効率を向上させることができる。このため、油切れにより圧縮機１の摺動部に焼付きが生じることを抑制することができる。また、室外熱交換器３および室内熱交換器５に圧縮機１から排出された油が滞留することを抑制することができる。したがって、冷凍サイクル装置１００の成績係数（ＣＯＰ：Coefficient　Of　Performance）の低下を抑制することができる。 In the oil separator as the gas-liquid separation device 10 according to the present embodiment, the efficiency of oil return to the compressor 1 can be improved by improving the oil separation efficiency. Therefore, it is possible to prevent the seizure of the sliding portion of the compressor 1 due to the oil shortage. Further, it is possible to suppress the oil discharged from the compressor 1 from staying in the outdoor heat exchanger 3 and the indoor heat exchanger 5. Therefore, it is possible to suppress a decrease in the coefficient of performance (COP: Coefficient Of Performance) of the refrigeration cycle apparatus 100.

　本実施の形態に係る気液分離装置１０では、気体排出口１４ａは中心軸ＣＬに重なるように配置されている。このため、軸１５ａの下端を中心軸ＣＬに沿う方向から見て気体排出口１４ａからずれるように配置することが容易となる。 In the gas-liquid separation device 10 according to this embodiment, the gas outlet 14a is arranged so as to overlap the central axis CL. Therefore, it becomes easy to dispose the lower end of the shaft 15a so as to deviate from the gas discharge port 14a when viewed from the direction along the central axis CL.

　本実施の形態に係る気液分離装置１０では、複数の螺旋状板１５ｂの各々の外周端は、容器１１の内壁面ＩＳに接している。このため、気液二相流体は、複数の螺旋状板１５ｂの各々の外周端と容器１１の内壁面ＩＳとの間の隙間を流れない。これにより、気体と液体との分離効率を向上させることができる。 In the gas-liquid separation device 10 according to the present embodiment, the outer peripheral ends of the plurality of spiral plates 15b are in contact with the inner wall surface IS of the container 11. Therefore, the gas-liquid two-phase fluid does not flow through the gap between the outer peripheral end of each of the plurality of spiral plates 15b and the inner wall surface IS of the container 11. Thereby, the separation efficiency of gas and liquid can be improved.

　本実施の形態に係る気液分離装置１０では、第１流路Ｆ１は第２流路Ｆ２よりも大きな流路面積を有している。このため、旋回流の主流が流路広大域としての第１流路Ｆ１に固定される。これにより、液体に対してより効率的に遠心力を付与することで気体と液体との分離効率を向上させることができる。 In the gas-liquid separation device 10 according to this embodiment, the first flow passage F1 has a larger flow passage area than the second flow passage F2. Therefore, the main flow of the swirling flow is fixed to the first flow passage F1 which is a large flow passage area. This makes it possible to improve the separation efficiency between the gas and the liquid by more efficiently applying the centrifugal force to the liquid.

　次に、本実施の形態に係る気液分離装置１０の変形例について説明する。なお、本実施の形態に係る気液分離装置１０の変形例は、特に説明しない限り上記の本実施の形態に係る気液分離装置１０と同一の構成、動作および効果を有している。したがって、上記の本実施の形態に係る気液分離装置１０と同一の構成には同一の符号を付し、説明を繰り返さない。 Next, a modified example of the gas-liquid separation device 10 according to the present embodiment will be described. The modified example of the gas-liquid separation device 10 according to the present embodiment has the same configuration, operation, and effect as those of the gas-liquid separation device 10 according to the present embodiment described above, unless otherwise specified. Therefore, the same components as those of the gas-liquid separation device 10 according to the present embodiment described above are designated by the same reference numerals, and description thereof will not be repeated.

　図１２～図１５を参照して、本実施の形態に係る気液分離装置１０の変形例１について説明する。図１２は、本実施の形態に係る気液分離装置１０の変形例１における旋回羽根１５が容器１１内に配置された構成を概略的に示す斜視図である。なお、説明の便宜のため、図１２では、容器１１の旋回羽根１５よりも上側および下側の部分は記載されていない。図１３は、本実施の形態に係る気液分離装置１０の変形例１における旋回羽根１５の構成を概略的に示す斜視図である。 Modification 1 of the gas-liquid separation device 10 according to the present embodiment will be described with reference to FIGS. 12 to 15. FIG. 12 is a perspective view schematically showing a configuration in which the swirl vanes 15 in the modified example 1 of the gas-liquid separation device 10 according to the present embodiment are arranged in the container 11. Note that, for convenience of description, in FIG. 12, portions above and below the swirl vane 15 of the container 11 are not shown. FIG. 13 is a perspective view schematically showing the configuration of the swirl vanes 15 in the first modification of the gas-liquid separator 10 according to this embodiment.

　図１４は、本実施の形態に係る気液分離装置１０の変形例１における旋回羽根１５の軸１５ａおよび複数の螺旋状板１５ｂの構成を概略的に示す斜視図である。図１５は、本実施の形態に係る気液分離装置１０の変形例１における旋回羽根１５の軸１５ａおよび複数の螺旋状板１５ｂの構成を概略的に示す上面図である。図１４および図１５では、軸１５ａおよび複数の螺旋状板１５ｂの後ろに隠れて見えない部分が破線で示されている。 FIG. 14 is a perspective view schematically showing the configurations of the shaft 15a of the swirl vane 15 and the plurality of spiral plates 15b in the first modification of the gas-liquid separation device 10 according to the present embodiment. FIG. 15 is a top view schematically showing the configurations of the shaft 15a of the swirl vane 15 and the plurality of spiral plates 15b in the first modification of the gas-liquid separator 10 according to the present embodiment. In FIGS. 14 and 15, a part hidden behind the shaft 15a and the plurality of spiral plates 15b and not visible is indicated by a broken line.

　図１２～図１５に示されるように、本実施の形態に係る気液分離装置１０の変形例１は、上記の本実施の形態に係る気液分離装置１０に比べて旋回羽根１５の構成が異なっている。本実施の形態に係る気液分離装置１０の変形例１では、軸１５ａは、中心軸ＣＬを中心として３６０度の回転角度で螺旋状にねじれるように構成されている。複数の螺旋状板１５ｂの各々は、中心軸ＣＬを中心として３６０度の回転角度で螺旋状にねじれるように構成されている。 As shown in FIGS. 12 to 15, in the first modification of the gas-liquid separator 10 according to the present embodiment, the configuration of the swirl vanes 15 is different from that of the gas-liquid separator 10 according to the above embodiment. Different. In the first modification of the gas-liquid separation device 10 according to the present embodiment, the shaft 15a is configured to be spirally twisted at a rotation angle of 360 degrees about the central axis CL. Each of the plurality of spiral plates 15b is configured to be spirally twisted at a rotation angle of 360 degrees about the central axis CL.

　続いて、図１６を参照して、本実施の形態に係る気液分離装置１０の変形例２について説明する。図１６は、本実施の形態に係る気液分離装置１０の変形例２の構成を概略的に示す断面図である。 Next, with reference to FIG. 16, a second modification of the gas-liquid separation device 10 according to the present embodiment will be described. FIG. 16 is a sectional view schematically showing the configuration of Modification 2 of the gas-liquid separation device 10 according to the present embodiment.

　図１６に示されるように、本実施の形態に係る気液分離装置１０の変形例２は、上記の本実施の形態に係る気液分離装置１０に比べて容器１１の構成が異なっている。本実施の形態に係る気液分離装置１０の変形例２では、容器１１は、中心軸ＣＬに沿って均一な径（内径および外径）を有している。 As shown in FIG. 16, the second modification of the gas-liquid separation device 10 according to the present embodiment is different in the configuration of the container 11 from the gas-liquid separation device 10 according to the above-described embodiment. In the second modification of the gas-liquid separation device 10 according to the present embodiment, the container 11 has a uniform diameter (inner diameter and outer diameter) along the central axis CL.

　実施の形態２．
　図１７および図１８を参照して、本発明の実施の形態２について説明する。なお、本発明の実施の形態２は、特に説明しない限り、上記の本発明の実施の形態１と同一の構成、動作および効果を有している。したがって、上記の本発明の実施の形態１と同一の構成には同一の符号を付し、説明を繰り返さない。 Embodiment 2.
Embodiment 2 of the present invention will be described with reference to FIGS. 17 and 18. The second embodiment of the present invention has the same configuration, operation, and effect as those of the first embodiment of the present invention described above, unless otherwise specified. Therefore, the same components as those in the first embodiment of the present invention described above are designated by the same reference numerals and the description thereof will not be repeated.

　図１７は、本実施の形態に係る旋回羽根１５が容器１１内に配置された構成を概略的に示す斜視図である。なお、説明の便宜のため、図１７では、容器１１の旋回羽根１５よりも上側および下側の部分は記載されていない。図１８は、本実施の形態に係る旋回羽根１５の構成を概略的に示す斜視図である。 FIG. 17 is a perspective view schematically showing a configuration in which the swirl vane 15 according to the present embodiment is arranged in the container 11. Note that, for convenience of description, in FIG. 17, portions above and below the swirl vane 15 of the container 11 are not shown. FIG. 18 is a perspective view schematically showing the configuration of swirl vane 15 according to the present embodiment.

　図１７および図１８に示されるように、本実施の形態に係る旋回羽根１５では、複数の螺旋状板１５ｂの各々は、中心軸ＣＬに沿う方向から見て弧状に構成されている。旋回羽根１５の中心軸ＣＬに直交する断面形状は、いずれの断面においても相似形状となる。このため、複数の螺旋状板１５ｂの各々は、中心軸ＣＬに直交するいずれの断面においても弧状に構成されている。複数の螺旋状板１５ｂの各々は、軸１５ａを中心として反時計回りに中央が突き出すように湾曲している。 As shown in FIGS. 17 and 18, in the swirl vane 15 according to the present embodiment, each of the plurality of spiral plates 15b is configured in an arc shape when viewed from the direction along the central axis CL. The cross-sectional shape of the swirl vane 15 orthogonal to the central axis CL is similar in any cross section. Therefore, each of the plurality of spiral plates 15b has an arc shape in any cross section orthogonal to the central axis CL. Each of the plurality of spiral plates 15b is curved so that the center thereof protrudes counterclockwise around the shaft 15a.

　本実施の形態に係る気液分離装置１０によれば、複数の螺旋状板１５ｂの各々は、中心軸ＣＬに沿う方向から見て弧状に構成されている。このため、複数の螺旋状板１５ｂの各々が中心軸ＣＬに沿う方向から見て直線状に構成されている場合に比べて、複数の螺旋状板１５ｂの表面積が増加する。これにより、旋回羽根１５の入口において、微細な液体（ミスト）を捕捉することができる。また、複数の螺旋状板１５ｂの表面積が増加するため、旋回羽根１５の出口において狭小部である主交差部１０３（図７）に集積した液体の微粒化を抑制することができる。これにより、液体の粒を大きくすることが可能となるため、旋回流によって液体を分離することが容易となる。したがって、気体と液体との分離効率を向上させることができる。 According to the gas-liquid separation device 10 of the present embodiment, each of the plurality of spiral plates 15b is formed in an arc shape when viewed from the direction along the central axis CL. Therefore, the surface areas of the plurality of spiral plates 15b are increased as compared with the case where each of the plurality of spiral plates 15b is configured in a straight line when viewed from the direction along the central axis CL. As a result, a fine liquid (mist) can be captured at the entrance of the swirl vane 15. Further, since the surface areas of the plurality of spiral plates 15b are increased, atomization of the liquid accumulated at the main intersection 103 (FIG. 7) which is a narrow portion at the outlet of the swirl vane 15 can be suppressed. This makes it possible to increase the size of the liquid particles, which facilitates the separation of the liquid by the swirling flow. Therefore, the separation efficiency of gas and liquid can be improved.

　次に、図１９および図２０を参照して、本実施の形態に係る気液分離装置１０の変形例について説明する。なお、本実施の形態に係る気液分離装置１０の変形例は、特に説明しない限り上記の本実施の形態に係る気液分離装置１０と同一の構成、動作および効果を有している。したがって、上記の本実施の形態に係る気液分離装置１０と同一の構成には同一の符号を付し、説明を繰り返さない。 Next, a modification of the gas-liquid separation device 10 according to the present embodiment will be described with reference to FIGS. 19 and 20. The modified example of the gas-liquid separation device 10 according to the present embodiment has the same configuration, operation, and effect as those of the gas-liquid separation device 10 according to the present embodiment described above, unless otherwise specified. Therefore, the same components as those of the gas-liquid separation device 10 according to the present embodiment described above are designated by the same reference numerals, and description thereof will not be repeated.

　図１９は、本実施の形態に係る旋回羽根１５が容器１１内に配置された構成を概略的に示す斜視図である。なお、説明の便宜のため、図１９では、容器１１の旋回羽根１５よりも上側および下側の部分は記載されていない。図２０は、本実施の形態に係る旋回羽根１５の構成を概略的に示す斜視図である。 FIG. 19 is a perspective view schematically showing a configuration in which the swirl vane 15 according to the present embodiment is arranged in the container 11. Note that, for convenience of description, in FIG. 19, portions above and below the swirl vane 15 of the container 11 are not shown. FIG. 20 is a perspective view schematically showing the configuration of swirl vane 15 according to the present embodiment.

　図１９および図２０に示されるように、本実施の形態に係る気液分離装置１０の変形例は、上記の本実施の形態に係る気液分離装置１０に比べて旋回羽根１５の構成が異なっている。本実施の形態に係る気液分離装置１０の変形例では、軸１５ａは、中心軸ＣＬを中心として３６０度の回転角度で螺旋状にねじれるように構成されている。複数の螺旋状板１５ｂの各々は、中心軸ＣＬを中心として３６０度の回転角度で螺旋状にねじれるように構成されている。 As shown in FIG. 19 and FIG. 20, the modified example of the gas-liquid separator 10 according to the present embodiment is different from the gas-liquid separator 10 according to the above-described embodiment in the configuration of the swirl vanes 15. ing. In the modified example of the gas-liquid separation device 10 according to the present embodiment, the shaft 15a is configured to be twisted spirally at a rotation angle of 360 degrees about the central axis CL. Each of the plurality of spiral plates 15b is configured to be spirally twisted at a rotation angle of 360 degrees about the central axis CL.

　上記の各実施の形態では、気液分離装置１０の一例として油分離器について説明したが、気液分離装置１０は油分離器に限定されず、たとえば水分離器であってもよい。 In each of the above embodiments, an oil separator has been described as an example of the gas-liquid separator 10, but the gas-liquid separator 10 is not limited to an oil separator, and may be a water separator, for example.

　上記の各実施の形態に係る気液分離装置１０および冷凍サイクル装置１００は、適宜組み合わせられ得る。 The gas-liquid separation device 10 and the refrigeration cycle device 100 according to each of the above embodiments can be combined as appropriate.

　今回開示された実施の形態はすべての点で例示であって制限的なものではないと考えられるべきである。本発明の範囲は上記した説明ではなくて請求の範囲によって示され、請求の範囲と均等の意味および範囲内でのすべての変更が含まれることが意図される。 The embodiments disclosed this time are to be considered as illustrative in all points and not restrictive. The scope of the present invention is shown not by the above description but by the scope of the claims, and is intended to include meanings equivalent to the scope of the claims and all modifications within the scope.

　１　圧縮機、２　四方弁、３　室外熱交換器、４　流量調整弁、５　室内熱交換器、１０　気液分離装置、１１　容器、１２　流入管、１２ａ　流入口、１３　液体排出管、１３ａ　液体排出口、１４　気体排出管、１４ａ　気体排出口、１５　旋回羽根、１５ａ　軸、１５ｂ　螺旋状板、２０　油戻し管、１００　冷凍サイクル装置、１００ａ　室外機ユニット、１００ｂ　室内機ユニット、１０１　断面形状、１０２　軌跡、１０３　主交差部、ＣＬ　中心軸、ＣＰ　中心、Ｆ１　第１流路、Ｆ２　第２流路、ＩＳ　内壁面。 1 compressor, 2 4-way valve, 3 outdoor heat exchanger, 4 flow control valve, 5 indoor heat exchanger, 10 gas-liquid separator, 11 container, 12 inflow pipe, 12a inlet, 13 liquid discharge pipe, 13a liquid discharge Outlet, 14 gas discharge pipe, 14a gas discharge port, 15 swirl vanes, 15a shaft, 15b spiral plate, 20 oil return pipe, 100 refrigeration cycle device, 100a outdoor unit, 100b indoor unit, 101 cross-sectional shape, 102 trajectory , 103 main intersection, CL central axis, CP center, F1 first flow path, F2 second flow path, IS inner wall surface.

Claims (6)

　気液二相流体を気体と液体とに分離する気液分離装置であって、
　上下に延びる中心軸に沿って延在し、かつ前記中心軸を取り囲む内壁面を有する容器と、
　前記容器内に前記気液二相流体を流入させる流入口を有する流入管と、
　前記気液二相流体から分離された前記液体を前記容器から排出する液体排出口を有する液体排出管と、
　前記気液二相流体から分離された前記気体を前記容器から排出する気体排出口を有する気体排出管と、
　前記容器内に配置された旋回羽根とを備え、
　前記流入管の前記流入口は、前記旋回羽根の上方に配置されており、
　前記液体排出管の前記液体排出口は、前記旋回羽根の下方に配置されており、
　前記気体排出管の前記気体排出口は、前記旋回羽根の下方であり、かつ前記液体排出口よりも上方に配置されており、
　前記旋回羽根は、前記中心軸に沿う方向から見て前記旋回羽根の中心に対して偏心する軸および前記軸に沿って螺旋状に延在する複数の螺旋状板を含み、
　前記複数の螺旋状板の各々は、前記軸から前記容器の前記内壁面に向けて延在しており、
　前記軸の下端は、前記中心軸に沿う前記方向から見て前記気体排出口からずれるように配置されている、気液分離装置。 A gas-liquid separator for separating a gas-liquid two-phase fluid into a gas and a liquid,
A container that extends along a vertically extending central axis and has an inner wall surface that surrounds the central axis,
An inflow pipe having an inflow port for introducing the gas-liquid two-phase fluid into the container;
A liquid discharge pipe having a liquid discharge port for discharging the liquid separated from the gas-liquid two-phase fluid from the container;
A gas discharge pipe having a gas discharge port for discharging the gas separated from the gas-liquid two-phase fluid from the container;
A swirl vane disposed in the container,
The inflow port of the inflow pipe is arranged above the swirl vane,
The liquid discharge port of the liquid discharge pipe is arranged below the swirl vane,
The gas discharge port of the gas discharge pipe is arranged below the swirl vane and above the liquid discharge port,
The swirl vane includes an axis eccentric with respect to the center of the swirl vane when viewed from a direction along the central axis and a plurality of spiral plates spirally extending along the axis,
Each of the plurality of spiral plates extends from the shaft toward the inner wall surface of the container,
The gas-liquid separation device, wherein the lower end of the shaft is arranged so as to be displaced from the gas discharge port when viewed from the direction along the central axis. 　前記気体排出口は、前記中心軸に重なるように配置されている、請求項１に記載の気液分離装置。 The gas-liquid separation device according to claim 1, wherein the gas outlet is arranged so as to overlap the central axis. 　前記複数の螺旋状板の各々の外周端は、前記容器の前記内壁面に接している、請求項１または２に記載の気液分離装置。 The gas-liquid separation device according to claim 1 or 2, wherein an outer peripheral end of each of the plurality of spiral plates is in contact with the inner wall surface of the container. 　前記容器は、前記複数の螺旋状板の各々によって区切られた第１流路と第２流路とを含み、
　前記第１流路は、前記第２流路よりも大きな流路面積を有している、請求項１～３のいずれか１項に記載の気液分離装置。 The container includes a first flow path and a second flow path divided by each of the plurality of spiral plates,
The gas-liquid separation device according to any one of claims 1 to 3, wherein the first flow passage has a flow passage area larger than that of the second flow passage. 　前記複数の螺旋状板の各々は、前記中心軸に沿う前記方向から見て弧状に構成されている、請求項１～４のいずれか１項に記載の気液分離装置。 The gas-liquid separation device according to any one of claims 1 to 4, wherein each of the plurality of spiral plates is formed in an arc shape when viewed from the direction along the central axis. 　請求項１～５のいずれか１項に記載の気液分離装置を備えた、冷凍サイクル装置。 A refrigeration cycle apparatus equipped with the gas-liquid separator according to any one of claims 1 to 5.
PCT/JP2019/007833 2019-02-28 2019-02-28 Gas-liquid separation device and refrigeration cycle device Ceased WO2020174660A1 (en)

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