JP7130838B2 - Gas-liquid separator and refrigeration cycle equipment - Google Patents

Description

The present invention relates to a gas-liquid separation device and a refrigeration cycle device.

2. Description of the Related Art Conventionally, in a compressor used as a drive source for a general air conditioner, refrigeration system, etc., oil lubricating the inside of the compressor is discharged out of the compressor together with the compressed high-pressure refrigerant gas. As a result, the sliding parts of the compressor may be seized due to the lack of oil. 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, gaseous refrigerant and liquid oil are separated. That is, a gas-liquid two-phase flow in which gas and liquid are mixed is separated into gas and liquid.

A gas-liquid separation device that separates a gas-liquid two-phase flow into a gas and a liquid is used not only in an oil separator but also in various devices. For example, Japanese Utility Model Laid-Open No. 6-34721 (Patent Document 1) describes a recovery device for separating and recovering paint mist contained in an air flow. In this recovery device, a helical air flow path is formed by a barrier plate around an axis extending laterally inside a cylindrical hollow body. The airflow containing the paint mist that has flowed into the cavity from the inlet of the cavity is separated into the airflow and the paint mist when passing through the spiral air flow path. The airflow passes through the filter and exits through the cavity outlet, and the paint mist exits through the cavity drain.

Japanese Utility Model Laid-Open No. 6-34721

In the recovery device described in the above-mentioned publication, since the air flow path is spirally formed by the barrier plate around the horizontally extending axis, the paint mist separated from the air flow is swirled up from the bottom to the top in the cavity. be done. Therefore, the separated paint mist is caught in the air flow again, and the separation efficiency is lowered.

SUMMARY OF THE INVENTION An object of the present invention is to provide a gas-liquid separator capable of improving the separation efficiency between gas and liquid.

The gas-liquid separator of the present invention separates a gas-liquid two-phase fluid into gas and 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 and surrounding a vertically extending central axis. The inflow pipe has an inflow port for inflowing the gas-liquid two-phase fluid 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. A swirl vane is positioned within the container. The inlet of the inlet pipe is arranged above the swirl vane. A 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. A swirl vane includes a shaft and a plurality of helical plates. The shaft is eccentric with respect to the center of the swirl vane when viewed along the central axis. A plurality of spiral plates extends spirally along the axis. Each of the plurality of helical plates extends from the axis 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 along the central axis.

In the gas-liquid separator of the present invention, a plurality of spiral plates spirally extending along the axis of the swirl vane generate a swirling flow in the gas-liquid two-phase fluid. The swirl force of this swirl flow separates the liquid from the gas-liquid two-phase fluid and suppresses the separated liquid from being swirled up. Thereby, the separation efficiency between the gas and the liquid can be improved. Furthermore, since the lower end of the shaft 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 remaining on the shaft is suppressed from entering the gas discharge port. Thereby, the separation efficiency between the gas and the liquid can be improved.

1 is a refrigerant circuit diagram of a refrigeration cycle device including a gas-liquid separation device according to Embodiment 1 of the present invention; FIG. BRIEF DESCRIPTION OF THE DRAWINGS It is sectional drawing which shows the gas-liquid separation apparatus which concerns on Embodiment 1 of this invention. 1 is a perspective view showing a configuration in which a swirl vane of a gas-liquid separation device according to Embodiment 1 of the present invention is arranged inside a container; FIG. 1 is a perspective view showing a swirl vane of the gas-liquid separation device according to Embodiment 1 of the present invention; FIG. FIG. 2 is a perspective view showing the shaft of the swirl vane and a plurality of spiral plates of the gas-liquid separation device according to Embodiment 1 of the present invention; FIG. 2 is a top view showing the shaft of the swirl vane and a plurality of spiral plates of the gas-liquid separation device according to Embodiment 1 of the present invention; 1 is a conceptual diagram of a swirl vane of a gas-liquid separation device according to Embodiment 1 of the present invention; FIG. FIG. 3 is a cross-sectional view for explaining how gas and liquid are separated in the gas-liquid separation device according to Embodiment 1 of the present invention; It is a cross-sectional view showing a gas-liquid separation device of a comparative example. FIG. 11 is a perspective view showing a flow path of a container of a gas-liquid separation device of a comparative example; FIG. 2 is a perspective view showing a flow path of the container of the gas-liquid separation device according to Embodiment 1 of the present invention; FIG. 10 is a perspective view showing a configuration in which the swirl vanes of Modification 1 of the gas-liquid separation device according to Embodiment 1 of the present invention are arranged in a container; FIG. 5 is a perspective view showing a swirl vane of Modification 1 of the gas-liquid separation device according to Embodiment 1 of the present invention; FIG. 5 is a perspective view showing the shaft of the swirl vane and the plurality of spiral plates of Modification 1 of the gas-liquid separation device according to Embodiment 1 of the present invention; FIG. 5 is a top view showing the shaft of the swirl vane and the plurality of spiral plates of Modification 1 of the gas-liquid separation device according to Embodiment 1 of the present invention; FIG. 5 is a cross-sectional view showing Modification 2 of the gas-liquid separation device according to Embodiment 1 of the present invention. FIG. 8 is a perspective view showing a configuration in which a swirl vane of a gas-liquid separation device according to Embodiment 2 of the present invention is arranged inside a container; FIG. 7 is a perspective view showing a swirl vane of the gas-liquid separation device according to Embodiment 2 of the present invention; FIG. 11 is a perspective view showing a configuration in which a swirl vane of a modification of the gas-liquid separation device according to Embodiment 2 of the present invention is arranged inside a container; FIG. 8 is a perspective view showing a swirl vane of a modified example of the gas-liquid separation device according to Embodiment 2 of the present invention;

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following description, the same or corresponding members and portions are denoted by the same reference numerals, and redundant description will not be repeated.

Embodiment 1.
First, referring to FIG. 1, the configuration of a refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention will be described. 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. Also, an oil separator will be described as an example of the gas-liquid separation device 10 .

As shown in FIG. 1, a refrigeration cycle apparatus 100 according to the present embodiment includes a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, a flow control valve 4, an indoor heat exchanger 5, a A liquid separator (oil separator) 10 is mainly provided. Compressor 1, four-way valve 2, outdoor heat exchanger 3, flow control valve 4, indoor heat exchanger 5 and gas-liquid separator 10 are connected by piping. Thus, 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 control valve 4, and a gas-liquid separator 10 are arranged in the outdoor unit 100a. An 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 and discharge the sucked refrigerant. The compressor 1 is configured to compress refrigerant flowing into the outdoor heat exchanger 3 or the indoor heat exchanger 5 . The compressor 1 may be a constant speed compressor with a constant compression capacity, or an inverter compressor with a variable compression capacity. This inverter compressor is configured so that the number of revolutions 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 refrigerant flow to the outdoor heat exchanger 3 or the indoor heat exchanger 5 depending on whether the air conditioner is in heating operation or in cooling operation.

The outdoor heat exchanger 3 is connected to the four-way valve 2 and the flow control valve 4 . The outdoor heat exchanger 3 functions as a condenser that condenses the refrigerant compressed by the compressor 1 during cooling operation. Also, the outdoor heat exchanger 3 functions as an evaporator that evaporates the refrigerant depressurized by the flow rate control valve 4 during heating operation. The outdoor heat exchanger 3 is for heat exchange between refrigerant and air. The outdoor heat exchanger 3 includes, for example, a pipe (heat transfer pipe) through which a refrigerant flows, and fins attached to the outside of the pipe.

The flow control valve 4 is connected to the outdoor heat exchanger 3 and the indoor heat exchanger 5 . The flow control valve 4 serves as a throttle device that decompresses the refrigerant condensed by the outdoor heat exchanger 3 during cooling operation. In addition, the flow control valve 4 serves as a throttle device that reduces the pressure of the refrigerant condensed by the indoor heat exchanger 5 during heating operation. The flow control 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 control valve 4 . The indoor heat exchanger 5 functions as an evaporator that evaporates the refrigerant depressurized by the flow rate control valve 4 during cooling operation. Also, the indoor heat exchanger 5 functions as a condenser that condenses the refrigerant compressed by the compressor 1 during heating operation. The indoor heat exchanger 5 is for heat exchange between refrigerant and air. It has an indoor heat exchanger 5, for example, a pipe (heat transfer pipe) in which a refrigerant flows, and fins attached to the outside of the pipe.

The gas-liquid separation device 10 is connected downstream of the discharge pipe of the compressor 1 . The gas-liquid separator 10 is configured to separate a gas-liquid two-phase fluid into gas and liquid. In the present embodiment, the oil separator as the gas-liquid separation device 10 is configured to separate oil from the oil-containing refrigerant discharged from the compressor 1 . An oil separator as the gas-liquid separation device 10 is connected upstream of the suction pipe of the compressor 1 so as to return the oil separated from the oil-containing refrigerant to the compressor 1 .

Next, 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. FIG.

FIG. 2 is a cross-sectional view schematically showing the configuration of the gas-liquid separation device 10 according to this 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 In the gas-liquid separation device 10 according to the present embodiment, a separation method using a swirling downward flow is used. Further, the gas-liquid separation device 10 according to the present embodiment has an inflow portion 10a, a separation portion 10b, a run-up section 10c1, a transition portion 10c2, and a liquid collecting portion (oil collecting portion) 10d. .

The inflow part 10 a is a part into which the gas-liquid two-phase fluid flows into the gas-liquid separation device 10 . The inflow portion 10 a is configured by an inflow pipe 12 . The separation part 10b is a part that separates the gas-liquid two-phase fluid into gas and liquid. The separating section 10b is composed of the upper portion of the container 11 and the swirl vanes 15. As shown in FIG. The approach section 10c1 is a section between the gas discharge pipe 14 and the swirl vane 15. As shown in FIG. The approach section 10c1 is provided in the transition section 10c2. The transition portion 10 c 2 is a portion where the separated gas is discharged from the gas discharge pipe 14 . The transition portion 10 c 2 is composed of the central portion of the container 11 and the upper portion of the gas discharge pipe 14 . The liquid collecting portion (oil collecting portion) 10d is a portion that collects the separated liquid. A liquid collecting portion (oil collecting portion) 10 d is constituted by the lower portion of the container 11 and the central portion of the gas discharge pipe 14 . A liquid discharge pipe 13 is connected to the liquid collecting portion (oil collecting portion) 10d.

The container 11 extends along a vertically extending central axis CL. A central axis CL of the container 11 extends vertically. 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 the cross section orthogonal to the central axis CL is circular. The container 11 is configured so 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 collecting portion (oil collecting portion) 10d is larger than that of the transition portion 10c2. is configured to

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 the gas-liquid two-phase fluid flows into the container 11 . In this 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 .

Liquid discharge pipe 13 is connected to oil return pipe 20 shown in FIG. A 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 . A liquid discharge pipe 13 passes through 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 this embodiment, the liquid discharge pipe 13 is configured to discharge the oil separated from the oil-containing refrigerant from the container 11 . A 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. Gas discharge pipe 14 is connected to the lower side of container 11 . The gas discharge pipe 14 is arranged coaxially with the central axis CL of the container 11 . Gas exhaust pipe 14 penetrates the bottom of 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 from the container 11 the refrigerant in which the oil is separated from the oil-containing refrigerant. The gas discharge port 14a is arranged so as to overlap with the central axis CL.

A 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 inside the container 11 . The gas discharge port 14 a is arranged directly below the swirl vane 15 . The gas discharge port 14a is arranged with an approach section 10c1 between it and the swirl vane 15 in the vertical direction. The gas discharge pipe 14 has an outer diameter smaller than the inner diameter of the container 11 .

The swirl vane 15 is configured to swirl the gas-liquid two-phase fluid so that it flows downward from above. The swirl vane 15 is configured to generate a swirl flow. The swirl vane 15 is configured to cause the liquid separated from the gas-liquid two-phase fluid by the swirl force of the swirl flow to flow downward from above while circulating along the inner wall surface IS. The swirl vane 15 is arranged inside 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. As shown in FIG. For convenience of explanation, FIG. 3 does not show portions of the container 11 above and below the swirl vane 15 .

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 intersect 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 configuration of the swirl vane 15. As shown in FIG. As shown in FIGS. 3 and 4, each of the multiple spiral plates 15b is connected to the shaft 15a. A plurality of spiral plates 15b are connected to the shaft 15a so as to cross each other. Each of the multiple spiral plates 15b is configured to generate a swirling force on the gas-liquid two-phase fluid. Each of the multiple spiral plates 15b spirally extends along the axis 15a. Each of the multiple 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 is linear when viewed from the direction along the central axis CL. In this embodiment, the swirl vane 15 has six spiral plates 15b. Note that 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 vane 15 and the plurality of spiral plates 15b. In FIGS. 5 and 6, portions hidden behind the shaft 15a and the plurality of helical plates 15b are indicated by dashed lines.

As shown in FIGS. 5 and 6, the shaft 15a is eccentric with respect to the center CP of the swirl vane 15 when viewed along the central axis CL. The center CP of the swirl vane 15 is positioned at the centroid of the swirl vane 15 when the swirl vane 15 is viewed from above. In this embodiment, the center CP of the swirl vane 15 is positioned on the central axis CL of the container 11 . The shaft 15a is configured to spirally extend along the central axis CL.

An outer peripheral end of each of the plurality of spiral plates 15 b is in contact with the inner wall surface IS of the container 11 . Therefore, when the swirl vane 15 is viewed from above 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 360 degrees divided by the number of the plurality of spiral plates 15b. That is, when the swirl vane 15 is viewed from above along the central axis CL, each of the plurality of spiral plates 15b has an angle equal to or larger than 360 degrees divided by the number of the plurality of spiral plates 15b. configured to twist. The swirl vane 15 is configured so that one end and the other end cannot be seen when the swirl vane 15 is viewed from above downward along the central axis CL.

In this embodiment, the shaft 15a is configured to spirally twist at a rotation angle of 180 degrees around the central axis CL. Each of the plurality of helical plates 15b is configured to be helically twisted at a rotation angle of 180 degrees around the central axis CL.

When viewed from the direction along the central axis CL, the angle between the spiral plates 15b adjacent to each other facing each other via the axis 15a is an acute angle. When viewed from the direction along the central axis CL, the plurality of spiral plates 15b are arranged line-symmetrically with the two spiral plates 15b aligned in a straight line passing through the center CP of the swirl vane 15 as an axis of symmetry.

The container 11 has a first flow path F1, a second flow path F2, a third flow path F3, a fourth flow path F4, a fifth flow path F5 and a sixth flow path F6. The first flow path F1, the second flow path F2, the third flow path F3, the fourth flow path F4, the fifth flow path F5 and the sixth flow path F6 are separated by each of the plurality of spiral plates 15b. . The first flow path F1, the second flow path F2, the third flow path F3, the fourth flow path F4, the fifth flow path F5, and the sixth flow path F6 rotate counterclockwise about the axis 15a of the swirl vane 15. They are arranged in order. Each flow path is arranged line-symmetrically with two helical plates 15b aligned on a straight line passing through the center CP of the swirl vane 15 as the axis of symmetry. That is, the first flow path F1 and the sixth flow path F6 are arranged axisymmetrically, the second flow path F2 and the fifth flow path F5 are arranged axisymmetrically, and the third flow path F3 and the 4th flow path F4 is arrange|positioned line-symmetrically.

The first flow path F1 has a flow area larger than that of the second flow path F2. The second flow path F2 has a flow area larger than that of the third flow path F3. The sixth flow path F6 has a larger flow area than the fifth flow path F5. The fifth flow path F5 has a larger flow area than the fourth flow path F4. The first channel F1 has the same channel area as the sixth channel F6. The second flow path F2 has the same flow area as the fifth flow path F5. The third flow path F3 has the same flow area as the fourth flow path F4. The 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 a cross section orthogonal to the central axis CL.

FIG. 7 is a conceptual diagram of the swirl vane 15 according to this embodiment. As shown in FIG. 5, the swirl vane 15 has a shape drawn by the cross-sectional shape 101 and the trajectory 102 when the cross-sectional shape 101 passes through the spiral trajectory 102 . A main intersection 103 inside the cross-sectional shape 101 is eccentric with respect to the center of the locus 102 . A main intersection portion 103 is a portion of the cross-sectional shape 101 where the shaft 15a and the plurality of spiral plates 15b intersect. The center of the trajectory 102 is the center of the x-, y-, and z-axes in FIG. The x-axis corresponds to the longitudinal direction of the swirl vanes 15 , the y-axis corresponds to the lateral direction of the swirl vanes 15 , and the z-axis corresponds to the vertical direction of the swirl vanes 15 .

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 around the central axis CL. That is, the cross-sectional shape 101 perpendicular to the central axis CL of the swirl vane 15 is similar in any cross-section.

Next, with reference to FIG. 1 again, the operation of refrigeration cycle apparatus 100 in the present embodiment will be described. The solid line arrows in the figure indicate the refrigerant flow during the cooling operation, and the broken line arrows in the figure indicate the refrigerant flow during the heating operation.

The refrigeration cycle apparatus 100 of the present embodiment can selectively perform cooling operation and heating operation. In cooling operation, refrigerant circulates through the refrigerant circuit in the order of compressor 1, gas-liquid separator (oil separator) 10, four-way valve 2, outdoor heat exchanger 3, flow control valve 4, and indoor heat exchanger 5. In cooling operation, the outdoor heat exchanger 3 functions as a condenser, and the indoor heat exchanger 5 functions as an evaporator. In 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 control valve 4, and the outdoor heat exchanger 3. In heating operation, the indoor heat exchanger 5 functions as a condenser, and the outdoor heat exchanger 3 functions as an evaporator.

Furthermore, the cooling operation will be explained in detail. When the compressor 1 is driven, a high-temperature, high-pressure gaseous 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, high-pressure gaseous 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 is separated by the gas-liquid separator 10 flows into the outdoor heat exchanger 3 via the four-way valve 2 . In the outdoor heat exchanger 3, heat is exchanged between the flowing gas refrigerant and the outdoor air. As a result, the high-temperature and high-pressure gas refrigerant is condensed into a high-pressure liquid refrigerant.

The high-pressure liquid refrigerant sent out from the outdoor heat exchanger 3 is turned into a two-phase refrigerant of low-pressure gas refrigerant and liquid refrigerant by the flow control valve 4 . The two-phase refrigerant flows into the indoor heat exchanger 5 . In the indoor heat exchanger 5, heat is exchanged between the flowing two-phase refrigerant and indoor air. As a result, the two-phase refrigerant evaporates from the liquid refrigerant and becomes a low-pressure gas refrigerant. This heat exchange cools the room. The low-pressure gas refrigerant sent out from the indoor heat exchanger 5 flows into the compressor 1 via the four-way valve 2, is compressed into high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 1 again. This cycle is then repeated.

Also, the heating operation will be described in detail. By driving the compressor 1 in the same manner as in the cooling operation, the oil-containing refrigerant in a high-temperature, high-pressure gas state is discharged from the compressor 1 . The high-temperature, high-pressure gaseous 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 is 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 is exchanged between the refrigerant that has flowed in 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 heats the room.

The high-pressure liquid refrigerant sent out from the indoor heat exchanger 5 is turned into a two-phase refrigerant of low-pressure gas refrigerant and liquid refrigerant by the flow control valve 4 . The two-phase refrigerant flows into the outdoor heat exchanger 3 . In the outdoor heat exchanger 3, heat is exchanged between the flowing two-phase refrigerant and the outdoor air. As a result, the two-phase refrigerant evaporates from the liquid refrigerant and becomes a low-pressure gas refrigerant. The low-pressure gas refrigerant sent out from the outdoor heat exchanger 3 flows into the compressor 1 via the four-way valve 2, is compressed into high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 1 again. This cycle is then repeated.

Next, operation of the gas-liquid separation device (oil separator) 10 according to the present embodiment will be described with reference to FIGS. 1 and 8. FIG. FIG. 8 is a cross-sectional view for explaining how gas (refrigerant) and liquid (oil) are separated in gas-liquid separation device 10 according to the present embodiment. In FIG. 8, the flow of oil-containing refrigerant is indicated by hollow arrows, the flow of refrigerant is indicated by solid arrows, and the flow of oil is indicated by dashed arrows.

As shown in FIG. 1 , in the refrigerant circuit of the refrigeration cycle device 100 , the oil-containing refrigerant discharged from the compressor 1 is separated into refrigerant and oil by the gas-liquid separation device 10 . The oil-containing refrigerant contains refrigerant and oil (refrigerating machine oil) enclosed in the compressor 1 . The refrigerant separated from the oil-containing refrigerant by the gas-liquid separation device 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 .

As shown in FIG. 8, when a high flow rate of the oil-containing refrigerant flows into the gas-liquid separation device 10 from the inflow pipe 12, the swirling flow generated by the plurality of spiral plates 15b of the swirl vanes 15 causes Oil is separated. The oil separated from the oil-containing refrigerant collides with the inner wall surface IS of the container 11 to form a liquid film, 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. Thus, the oil is collected by the oil collecting portion 10d. The collected oil is discharged from the liquid discharge pipe 13 . 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 .

Further, when a low flow rate of oil-containing refrigerant flows into the gas-liquid separation device 10 from the inflow pipe 12, after passing through the swirl vane 15, the oil is trapped at the position of the main intersection portion 103 (FIG. 7) which becomes a narrow portion due to surface tension. get together. After that, part of the oil is guided to the inner wall surface IS by the swirling flow, and the other part of the oil drops due to the influence of its weight and is discharged from the liquid discharge pipe 13 . The gas refrigerant is discharged from the gas discharge pipe 14 in the same manner as when the oil-containing refrigerant flows in at a high flow rate.

Next, the effects of this embodiment will be described in comparison with a comparative example.
A gas-liquid separation device (oil separator) 10 of a comparative example will be described with reference to FIGS. 9 and 10. FIG. FIG. 9 is a cross-sectional view schematically showing the configuration of a gas-liquid separation device 10 of a 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 linearly vertically. The shaft 15a of the swirl vane 15 of the comparative example is positioned on the central axis CL. Therefore, in the swirl vane 15 of the comparative example, the liquid separated by the swirl flow stays on the shaft 15a between the spiral plates 15b adjacent to each other due to surface tension. This liquid falls by gravity and enters the gas outlet 14a. This reduces the separation efficiency between gas and liquid.

FIG. 10 is a perspective view schematically showing the channel 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. For convenience of explanation, FIGS. 10 and 11 do not show portions of the container 11 above and below the swirl vane 15 .

As shown in FIG. 10, in the container 11 of the gas-liquid separation device 10 of the comparative example, the first to sixth flow paths F1 to F6 have the same flow area. The pressure may pulsate due to an increase or decrease in the flow velocity of the gas-liquid two-phase fluid flowing into the gas-liquid separation device 10 . For example, the opening and closing of valves in the compressor 1 may cause pressure pulsations. 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, the swirling occurs according to the timing of the pressure pulsation. The flow path changes as the current becomes stronger. Specifically, the flow paths in which the swirling flow becomes stronger in the order of the first flow path F1 to the sixth flow path F6 change with the passage of time. Therefore, the direction in which the liquid flies is uncertain.

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 channel areas are the first flow channel F1, the second flow channel F2, the third flow channel It becomes smaller in order of F3. Also, the flow path area increases in the order of the fourth flow path F4, the fifth flow path F5, and the sixth flow path F6. Therefore, the main stream of the swirling flow is fixed in the wide area of the flow path. In other words, the swirl flow assertion is fixed to the first flow path F1 and the sixth flow path F6. Therefore, the flying direction of the liquid can be determined. As a result, it is possible to improve the separation efficiency between the gas and the liquid by applying the centrifugal force to the liquid more efficiently.

According to the gas-liquid separation device 10 according to the present embodiment, a plurality of spiral plates 15b spirally extending along the axis 15a of the swirl vane 15 generate a swirling flow in the gas-liquid two-phase fluid. The swirl force of this swirl flow separates the liquid from the gas-liquid two-phase fluid and suppresses the separated liquid from being swirled up. 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, thereby suppressing re-scattering. Also, the separated liquid flows downward along the central axis CL, and the swirling flow swirls around the central axis CL. Therefore, the separated liquid is suppressed from being swirled upward. Therefore, the separation efficiency between gas and liquid can be improved. Furthermore, 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 remaining on the shaft 15a flows into the gas discharge port 14a. restricted from entering. That is, the liquid remaining 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 outlet 14a by dropping due to gravity. Thereby, the separation efficiency between the gas and the liquid can be improved.

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, while maintaining the size of the swirl vane 15 in the circumferential direction around the central axis CL, 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 of the container 11. be able to.

In the gas-liquid separation device 10 according to the present embodiment, the inflow port 12 a of the inflow pipe 12 is arranged above the swirl vane 15 . A 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.

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 suppress the liquid separated by the swirl vane 15 from flowing into the gas discharge pipe 14 .

A conventional cyclonic separator impinges a gas-liquid two-phase fluid perpendicularly against the inner wall surface of a vessel. That is, the gas-liquid two-phase fluid collides with the inner wall surface in the horizontal direction perpendicular to the vertical direction. However, in conventional cyclone separators, when the distance between the inner wall surface of the container and the gas discharge pipe is short, the separated liquid scatters again and is sucked in together with the gas, reducing the gas-liquid separation efficiency. descend. Therefore, it is difficult to reduce the size of conventional cyclone separators. 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 discharge pipe 14 can be secured in the vertical direction. Therefore, the gas-liquid separation device 10 according to the present embodiment can be easily miniaturized as compared with the conventional cyclone separator.

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 suppress seizure of the sliding portion of the compressor 1 due to oil shortage. Moreover, it is possible to prevent the oil discharged from the compressor 1 from remaining in the outdoor heat exchanger 3 and the indoor heat exchanger 5 . Therefore, a decrease in the coefficient of performance (COP) of the refrigeration cycle device 100 can be suppressed.

In the gas-liquid separation device 10 according to the present embodiment, the gas discharge port 14a is arranged so as to overlap with 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.

In the gas-liquid separation device 10 according to the present embodiment, the outer peripheral end of each of the plurality of spiral plates 15 b is 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 spiral plates 15 b and the inner wall surface IS of the container 11 . Thereby, the separation efficiency between the gas and the liquid can be improved.

In the gas-liquid separation device 10 according to the present embodiment, the first channel F1 has a larger channel area than the second channel F2. Therefore, the main flow of the swirling flow is fixed to the first flow path F1 as the wide flow path area. As a result, it is possible to improve the separation efficiency between the gas and the liquid by applying the centrifugal force to the liquid more efficiently.

Next, a modified example of the gas-liquid separation device 10 according to the present embodiment will be described. It should be noted that the modified example of the gas-liquid separation device 10 according to the present embodiment has the same configuration, operation and effect as the gas-liquid separation device 10 according to the above-described present embodiment unless otherwise specified. Therefore, the same components as those of the gas-liquid separation device 10 according to the present embodiment are denoted by the same reference numerals, and description thereof will not be repeated.

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. FIG. 12 is a perspective view schematically showing a configuration in which swirl vanes 15 are arranged in container 11 in modification 1 of gas-liquid separation device 10 according to the present embodiment. For convenience of explanation, FIG. 12 does not show portions of the container 11 above and below the swirl vane 15 . FIG. 13 is a perspective view schematically showing the configuration of the swirl vane 15 in Modification 1 of the gas-liquid separation device 10 according to the present embodiment.

FIG. 14 is a perspective view schematically showing the configuration of shaft 15a of swirl vane 15 and a plurality of spiral plates 15b in modification 1 of gas-liquid separation device 10 according to the present embodiment. FIG. 15 is a top view schematically showing the configuration of shaft 15a of swirl vane 15 and a plurality of spiral plates 15b in modification 1 of gas-liquid separation device 10 according to the present embodiment. In FIGS. 14 and 15, portions hidden behind the shaft 15a and the plurality of helical plates 15b are indicated by broken lines.

As shown in FIGS. 12 to 15, the first modification of the gas-liquid separation device 10 according to the present embodiment has a configuration of the swirl vane 15 that is different from that of the gas-liquid separation device 10 according to the present embodiment. different. In Modified Example 1 of the gas-liquid separation device 10 according to the present embodiment, the shaft 15a is configured to spirally twist at a rotation angle of 360 degrees around the central axis CL. Each of the plurality of helical plates 15b is configured to be helically twisted at a rotation angle of 360 degrees around the central axis CL.

Next, Modification 2 of the gas-liquid separation device 10 according to the present embodiment will be described with reference to FIG. 16 . FIG. 16 is a cross-sectional view schematically showing the configuration of Modification 2 of gas-liquid separation device 10 according to the present embodiment.

As shown in FIG. 16, Modification 2 of gas-liquid separation device 10 according to the present embodiment differs in the configuration of container 11 from gas-liquid separation device 10 according to the above-described present embodiment. In Modification 2 of gas-liquid separation device 10 according to the present embodiment, container 11 has a uniform diameter (inner diameter and outer diameter) along central axis CL.

Embodiment 2.
Embodiment 2 of the present invention will be described with reference to FIGS. 17 and 18. FIG. The second embodiment of the present invention has the same configuration, operation and effect as those of the first embodiment of the present invention unless otherwise specified. Therefore, the same reference numerals are given to the same configurations as in the first embodiment of the present invention, 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 this embodiment is arranged inside the container 11. As shown in FIG. For convenience of explanation, FIG. 17 does not show portions of the container 11 above and below the swirl vane 15 . FIG. 18 is a perspective view schematically showing the structure of swirl vane 15 according to the present embodiment.

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 formed in an arc shape when viewed from the direction along the central axis CL. The cross-sectional shape perpendicular to the central axis CL of the swirl vane 15 is similar in any cross-section. Therefore, each of the plurality of spiral plates 15b has an arc shape in any cross section perpendicular to the central axis CL. Each of the plurality of spiral plates 15b is curved so that the center protrudes counterclockwise around the axis 15a.

According to the gas-liquid separation device 10 according to the present embodiment, each of the plurality of spiral plates 15b has an arc shape when viewed from the direction along the central axis CL. Therefore, the surface area of the plurality of spiral plates 15b is increased compared to the case where each of the plurality of spiral plates 15b is linear when viewed from the direction along the central axis CL. As a result, fine liquid (mist) can be captured at the inlet of the swirl vane 15 . Further, since the surface area of the plurality of helical plates 15b is increased, it is possible to suppress atomization of the liquid accumulated in the narrow main intersection 103 (FIG. 7) at the outlet of the swirl vane 15. FIG. This makes it possible to increase the size of the droplets of the liquid, thereby facilitating separation of the liquid by the swirling flow. Therefore, the separation efficiency between gas and liquid can be improved.

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. FIG. It should be noted that the modified example of the gas-liquid separation device 10 according to the present embodiment has the same configuration, operation and effect as the gas-liquid separation device 10 according to the above-described present embodiment unless otherwise specified. Therefore, the same components as those of the gas-liquid separation device 10 according to the present embodiment are denoted 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 this embodiment is arranged inside the container 11. As shown in FIG. For convenience of explanation, FIG. 19 does not show portions of the container 11 above and below the swirl vane 15 . FIG. 20 is a perspective view schematically showing the structure of swirl vane 15 according to the present embodiment.

As shown in FIGS. 19 and 20, the modification of the gas-liquid separation device 10 according to the present embodiment differs in the configuration of the swirl vane 15 from the gas-liquid separation device 10 according to the above-described present embodiment. ing. In the modified example of the gas-liquid separation device 10 according to the present embodiment, the shaft 15a is configured to spirally twist at a rotation angle of 360 degrees around the central axis CL. Each of the plurality of helical plates 15b is configured to be helically twisted at a rotation angle of 360 degrees around the central axis CL.

Although the oil separator has been described as an example of the gas-liquid separation device 10 in each of the above embodiments, the gas-liquid separation device 10 is not limited to the oil separator, and may be, for example, a water separator.

The gas-liquid separation device 10 and the refrigeration cycle device 100 according to each of the above embodiments can be combined as appropriate.

It should be considered that the embodiments disclosed this time are illustrative in all respects and not restrictive. The scope of the present invention is indicated by the scope of the claims rather than the above description, and is intended to include all changes within the scope and meaning equivalent to the scope of the claims.

1 compressor, 2 four-way valve, 3 outdoor heat exchanger, 4 flow control valve, 5 indoor heat exchanger, 10 gas-liquid separator, 11 container, 12 inflow pipe, 12a inflow port, 13 liquid discharge pipe, 13a liquid discharge Outlet 14 Gas discharge pipe 14a Gas discharge port 15 Swirl vane 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 channel, F2 second channel, IS inner wall surface.

Claims (6)

A gas-liquid separation device for separating a gas-liquid two-phase fluid into a gas and a liquid,
a container having an inner wall surface extending along a vertically extending central axis and surrounding the central axis;
an inflow pipe having an inflow port for inflowing 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 within the container;
The inlet 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 viewed from the direction along the central axis and a plurality of helical plates spirally extending along the axis;
each of the plurality of helical plates extends from the axis toward the inner wall surface of the container;
The gas-liquid separation device, wherein the lower end of the shaft is arranged to be displaced from the gas discharge port when viewed from the direction along the central axis. 2. The gas-liquid separator according to claim 1, wherein said gas outlet is arranged so as to overlap said central axis. 3. The gas-liquid separation device according to claim 1, wherein an outer peripheral edge of each of said plurality of spiral plates is in contact with said inner wall surface of said container. the container includes a first channel and a second channel separated 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 channel has a larger channel area than the second channel. The gas-liquid separator according to any one of claims 1 to 4, wherein each of said plurality of helical plates has an arc shape in a cross section perpendicular to said central axis. A refrigeration cycle device comprising the gas-liquid separation device according to any one of claims 1 to 5.

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