JP5014367B2 - Gas-liquid separator and refrigeration cycle equipment equipped with it - Google Patents

Description

  The present invention relates to a gas-liquid separator and a refrigeration cycle apparatus such as an air conditioner equipped with the gas-liquid separator.

Refrigerant separated by a gas-liquid separator in a refrigeration cycle in which a compressor, a four-way valve, an outdoor heat exchanger, a first expansion valve, a gas-liquid separator, a second expansion valve, and an indoor heat exchanger are sequentially connected by piping. An invention for returning steam to a suction pipe of a compressor is known (for example, see Patent Document 1).
The gas-liquid separator described in FIG. 2 of Patent Document 1 includes a first container to which a first pipe is connected and a second container to which a second pipe is connected. The upper part of the two containers is provided with a pipe for communicating the refrigerant vapor, and the lower part of the first container and the lower part of the second container are provided with a pipe for communicating the refrigerant liquid so as to communicate the refrigerant vapor. A gas outlet pipe for allowing the refrigerant vapor to flow out is provided at the center of the pipe. Here, the gas-liquid two-phase refrigerant flows into the gas-liquid separator from the first pipe during the cooling operation and from the second pipe during the heating operation. Thus, during cooling operation, even if the liquid level of the refrigerant liquid undulates or bubbles in the first container into which the gas-liquid two-phase refrigerant that has passed through the first pipe flows, The liquid level of the refrigerant liquid is suppressed from undulating and bubbling so that the refrigerant liquid flows out of the second pipe and the refrigerant vapor flows out of the gas outlet pipe. In addition, during the heating operation, even if the liquid level of the refrigerant liquid undulates or bubbles in the second container into which the gas-liquid two-phase refrigerant that has passed through the second pipe flows, the refrigerant in the first container The liquid level of the liquid is suppressed from undulating and bubbling so that the refrigerant liquid flows out of the first pipe and the refrigerant vapor flows out of the gas outlet pipe.

Japanese Patent Laying-Open No. 2008-75894 (FIG. 1, FIG. 2, etc.)

In the gas-liquid separator shown in Patent Document 1, when the gas-liquid two-phase refrigerant flows into the first container during the cooling operation, the first container generates undulations and bubbles. However, since the droplets scattered in the first container flow out from the gas outlet pipe together with the refrigerant vapor, there is a problem that the gas-liquid separation efficiency is lowered.
Further, in the first container and the second container, the gas-liquid two-phase refrigerant flow rate is decreased to perform gas-liquid separation, or bubble-shaped refrigerant vapor is generated from the bubbled gas-liquid two-phase refrigerant. In order to perform gas-liquid separation by floating, it is necessary to make the diameter of each container considerably larger than the diameter of the inflow pipe, and there is a problem that the gas-liquid separator becomes large.
The present invention addresses the above-described problems, and provides a compact gas-liquid separator having high gas-liquid separation efficiency and an object of providing a refrigeration cycle apparatus equipped with such a gas-liquid separator. And

The gas-liquid separator of the present invention has a first flow path and a second flow path, and an upper end portion in the vertical direction of the first flow path and an upper end portion in the vertical direction of the second flow path. Are connected at the upper connecting portion, and a lower end portion in the vertical direction of the first flow path and a lower end portion in the vertical direction of the second flow path are connected at the lower connecting portion, and the first flow path A loop-shaped flow path is formed by the second flow path, the upper connecting portion, and the lower connecting portion,
A first inflow / outflow channel through which fluid flows in or out is connected in the middle of the first channel, a second outflow / inflow channel through which fluid flows out or inflow is connected in the middle of the second channel, and the loop The gas-phase fluid outflow channel is connected to the top of the channel,
At least one of a side surface facing the connection opening with the first inflow / outflow channel in the first channel or a side surface facing the connection opening with the second inflow / outflow channel in the second channel. On one side, a protruding portion of the channel having a shape protruding from the inside to the outside is provided.

  According to the present invention, a small gas-liquid separator having high gas-liquid separation efficiency can be obtained. In addition, the coefficient of performance can be improved by the refrigeration cycle apparatus of the present invention.

It is a block diagram of the refrigerating-cycle apparatus carrying the gas-liquid separator by Embodiment 1 of this invention. It is a figure which shows the structure at the time of the structure of the gas-liquid separator shown in FIG. 1, and air_conditionaing | cooling operation. It is a figure which shows the structure at the time of the structure of the gas-liquid separator shown in FIG. 1, and heating operation. It is a figure which shows the change of the pressure and enthalpy of the refrigerating cycle at the time of air_conditionaing | cooling operation of the refrigerating cycle apparatus of FIG. It is a block diagram of the conventional refrigeration cycle apparatus which does not mount a gas-liquid separator. It is a figure which shows the change of the pressure and enthalpy of the refrigerating cycle at the time of heating operation of the refrigerating cycle apparatus of FIG. It is a block diagram which shows the 1st modification of the refrigerating-cycle apparatus carrying the gas-liquid separator by Embodiment 1 of this invention. It is a block diagram which shows the 2nd modification of the refrigerating-cycle apparatus carrying the gas-liquid separator by Embodiment 1 of this invention. It is a block diagram which shows the 3rd modification of the refrigerating-cycle apparatus carrying the gas-liquid separator by Embodiment 1 of this invention. It is a block diagram which shows the 4th modification of the refrigerating-cycle apparatus carrying the gas-liquid separator by Embodiment 1 of this invention. It is a block diagram which shows the 5th modification of the refrigerating-cycle apparatus carrying the gas-liquid separator by Embodiment 1 of this invention. It is a figure which shows the modification of the gas-liquid separator by Embodiment 1 of this invention. It is a figure which shows the modification of the gas-liquid separator by Embodiment 1 of this invention. It is a figure which shows the gas-liquid separator by Embodiment 2 of this invention. It is a figure which shows the modification of the gas-liquid separator by Embodiment 2 of this invention. It is a figure which shows the gas-liquid separator by Embodiment 3 of this invention. It is a figure which shows the modification of the gas-liquid separator by Embodiment 3 of this invention. It is a figure which shows the gas-liquid separator by Embodiment 4 of this invention. It is a figure which shows the upper 2 branch material of the gas-liquid separator by Embodiment 4 of this invention. It is a figure which shows the lower connection material of the gas-liquid separator by Embodiment 4 of this invention. It is a figure which shows the modification of the gas-liquid separator by Embodiment 4 of this invention. It is a figure which shows the gas-liquid separator by Embodiment 5 of this invention. It is a figure which shows the gas-liquid separator by Embodiment 6 of this invention. It is a figure which shows the gas-liquid separator by Embodiment 7 of this invention. It is a figure which shows the modification of the gas-liquid separator by Embodiment 1 to 7 of this invention.

Embodiment 1 FIG.
FIG. 1 shows the configuration of an injectable refrigeration cycle apparatus using a gas-liquid separator according to Embodiment 1 of the present invention. The main refrigeration cycle circuit (main refrigerant circuit) of the refrigeration cycle apparatus includes an injectable compressor 1, a four-way valve 2 that changes the direction of flowing refrigerant and switches between cooling operation and heating operation, a first heat exchanger 3 on the heat source side, The electric expansion valve 4 as the first pressure reducer, the gas-liquid separator 5, the electric expansion valve 6 as the second pressure reducer, and the second heat exchanger 7 on the use side are sequentially connected by piping. An injection circuit is connected from the gas-liquid separator 5 to the injection port 10 of the compressor 1 via the flow rate adjustment valve 8.

  Further, here, the pipe connecting the first heat exchanger 3 and the gas-liquid separator 5 is the first refrigerant pipe 35, and the pipe connecting the second heat exchanger 7 and the gas-liquid separator 5 is the second refrigerant pipe. 36, a pipe connecting the injection port 10 and the gas-liquid separator 5 is referred to as a bypass pipe 9.

2 and 3 show the structure of the gas-liquid separator 5. The gas-liquid separator 5 includes a first vertical pipe 11 as a first flow path, a second vertical pipe 12 as a second flow path, an upper pipe 13 as an upper connection section, and a lower pipe 14 as an upper connection section. Thus, the loop-shaped pipe 30 is formed. A first inflow / outflow as a first inflow / outflow channel is orthogonal to the first vertical pipe 11 at a position that internally divides the uppermost point and the lowermost point of the loop-shaped pipe 30 into a ratio of H1: H2 in the height direction. A pipe 15 is provided, and a second inflow / outflow pipe 17 is provided as a second inflow / outflow channel so as to be orthogonal to the second vertical pipe 12. A first protrusion 18 having a protruding flow path shape is formed on the side surface of the first vertical pipe 11 facing the first inflow / outflow pipe 15, and the second vertical length facing the second inflow / outflow pipe 17. A second projecting portion 33 having a projecting channel shape is formed on the side surface of the pipe 12.
Further, a steam outflow pipe 16 serving as an outflow passage for the gas phase fluid is provided in the middle of the upper pipe 13 positioned at the uppermost point of the loop-shaped pipe 30.
In the refrigeration cycle circuit of FIG. 1, the first inflow / outflow piping 15 is connected to the first refrigerant piping 35, the second inflow / outflow piping 17 is connected to the second refrigerant piping 36, and the vapor outflow piping 16 is connected to the bypass piping 9.
In addition, the protrusion part should just be formed in the vertical piping in which the inflow / outflow piping in which a gas-liquid two-phase refrigerant | coolant flows in is provided, Therefore, it necessarily has both the 1st protrusion part 18 and the 2nd protrusion part 33. You don't have to.
Further, the ratio of H1: H2 is not particularly limited, but can be, for example, about 2: 1 to 3: 1.

  2 also shows the flow direction of the refrigerant during the cooling operation of the refrigeration cycle apparatus of FIG. 1, FIG. 3 also shows the flow direction of the refrigerant during the heating operation, the solid line arrow indicates the flow of the refrigerant liquid 21, and the dotted line arrow indicates the refrigerant vapor. 20 flows are shown.

Next, an operation when the refrigeration cycle apparatus of FIG. 1 performs a cooling operation will be described. In FIG. 1, the direction in which the refrigerant flows during the cooling operation is indicated by a black arrow. FIG. 4 shows a diagram of the pressure P-enthalpy h during the cooling operation of the refrigeration cycle apparatus of FIG. 1, and the alphabets A to K in FIG. 4 correspond to the respective points of the alphabet shown in FIG. Correspond.
The high-temperature and high-pressure refrigerant vapor compressed by the compressor 1 reaches the first heat exchanger 3 serving as a condenser via the four-way valve 2 (point E). The high-temperature and high-pressure refrigerant vapor is condensed by the first heat exchanger 3 to become a refrigerant liquid (point B), and is reduced to an intermediate pressure between the suction pressure and the discharge pressure of the compressor 1 by the first pressure reducer 4. (Point F) Becomes a gas-liquid two-phase refrigerant and enters the gas-liquid separator 5 from the first refrigerant pipe 35 through the first inflow / outflow pipe 15.

As shown in FIG. 2, the gas-liquid two-phase refrigerant 19 that has flowed into the first vertical pipe 11 via the first inflow / outflow pipe 15 crosses the first vertical pipe 11 and enters the first protrusion 18. Then collide. At this time, the refrigerant liquid 21a having a high density in the inflowing gas-liquid two-phase state receives an inertial force and accumulates in the first projecting portion 18, and conversely, the refrigerant vapor 20a having a low density has a first protrusion. The refrigerant liquid 21 a is separated without entering the portion 18. Thereby, the gas-liquid two-phase refrigerant that has flowed into the first vertical pipe 11 via the first inflow / outflow pipe 15 is effectively gas-liquid separated by the first protrusion 18, and the refrigerant in the first protrusion 18. Swelling and foaming of the liquid are suppressed.
Thereafter, the refrigerant liquid 21a receives gravity and becomes the refrigerant liquid 21b. The refrigerant liquid 21a accumulates from the lower part of the first vertical pipe 11 to the lower pipe 14, the lower part of the second vertical pipe 12, and the second projecting portion 33. Will come out through.

Since the refrigerant liquid 21b accumulates in the lower part of the first vertical pipe 11, the flow resistance when the refrigerant vapor 20a separated by the first protrusion 18 tries to pass through the lower part of the first vertical pipe 11 increases. The refrigerant vapor 20 a goes to the upper part of the first vertical pipe 11 and flows out from the vapor outflow pipe 16 through the upper pipe 13. In addition, when the refrigerant | coolant vapor | steam 20a raises the 1st vertical pipe 11, the refrigerant | coolant vapor | steam 20a pulls up the refrigerant | coolant liquid 21c which is a part of refrigerant | coolant liquid 21a, Therefore The refrigerant | coolant liquid 21c comes to raise the 1st vertical pipe | tube. . At this time, by increasing a distance H1 from the center of the first inflow / outflow pipe 15 to the uppermost point of the loop-shaped pipe 30, the refrigerant liquid 21c is dropped by gravity, and the refrigerant liquid 21c is discharged from the vapor outflow pipe 16 into the refrigerant. It does not flow out with the steam 20a. Even when the refrigerant liquid 21c reaches the upper pipe 13, since the density of the refrigerant liquid 21c is large, the refrigerant liquid 21c passes through the bottom of the upper pipe 13 and becomes the refrigerant liquid 21d. The gravity falls through the two vertical pipes 12 and flows out from the second inflow / outflow pipe 17.
Further, when the refrigerant liquid 21a separated by the first protrusion 18 drops by gravity, the refrigerant vapor 20b, which is a part of the refrigerant vapor 20a, may be entrained. It passes through the pipe 14 and flows out from the steam outflow pipe 16 via the second vertical pipe 12.
As described above, by using the gas-liquid separator 5, the gas-liquid two-phase refrigerant can be separated with high gas-liquid separation efficiency.

After the gas-liquid separator 5 performs gas-liquid separation, the refrigerant liquid 15 (point G) passing through the second refrigerant pipe 36 from the second inflow / outflow pipe 17 is reduced from the intermediate pressure to the low pressure by the second pressure reducer 6. Then, the refrigerant becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant and reaches the second heat exchanger 7 serving as an evaporator (H point). Thereafter, the low-temperature low-pressure gas-liquid two-phase refrigerant is evaporated by the second heat exchanger 7 to become refrigerant vapor (point D), returns to the compressor 1 through the four-way valve 2, and is compressed by the compressor 1 to an intermediate pressure. (I point).
On the other hand, the refrigerant vapor 20d (point K) that has passed through the bypass pipe 9 from the vapor outlet pipe 16 is adjusted in flow rate by the flow rate adjusting valve 8, and is injected from the injection port 10 into the compressor 1 at intermediate pressure. (Refer to point J). Further, the mixed refrigerant vapor having intermediate pressure is compressed to the discharge pressure by the compressor 1 and repeats the same operation again.

  FIG. 5 shows a configuration of a conventional refrigeration cycle apparatus not equipped with a gas-liquid separator. In FIG. 5, the direction in which the refrigerant flows during the cooling operation is indicated by black arrows, and the alphabets A ′ to D ′ correspond to the alphabets in FIG. 4. In the refrigeration cycle apparatus of FIG. 5, the high-temperature and high-pressure refrigerant vapor compressed by the compressor 1 reaches the first heat exchanger 3 serving as a condenser via the four-way valve 2 (point A ′). The liquid refrigerant condensed by the first heat exchanger 3 (point B ′) is decompressed to a low pressure by the first decompressor 4 and reaches the second heat exchanger 7 serving as an evaporator (point C ′). The low-temperature and low-pressure refrigerant vapor evaporated by the second heat exchanger 7 (point D ′) returns to the compressor 1 through the four-way valve 2, is compressed to the discharge pressure by the compressor 1, and repeats the same operation again.

  As shown in FIG. 4, in the two-stage compression cycle using the gas-liquid separator 5, the difference in enthalpy (h 4 −h 3) at the inlet / outlet of the compressor 1 is that in a normal refrigeration cycle apparatus that does not use the gas-liquid separator 5. Since it becomes smaller than the enthalpy difference (h5−h3) at the inlet / outlet of the compressor 1, the input of the compressor 1 can be reduced. In addition, this makes it possible to increase the coefficient of performance of the cooling represented by the ratio between the electric input including the input of the compressor 1 and the cooling capacity. Furthermore, in the two-stage compression cycle using the gas-liquid separator 5, the discharge temperature of the compressor 1 can be reduced as compared with the normal refrigeration cycle, so that the compressor 1 is highly reliable and has a long life. can do.

Next, an operation when the refrigeration cycle apparatus of FIG. 1 performs a heating operation will be described. In FIG. 1, the direction in which the refrigerant flows during the heating operation is indicated by white arrows. FIG. 6 shows a diagram of the pressure P-enthalpy h during the heating operation, and alphabets A to K in FIG. 6 correspond to each point of the alphabet shown in FIG.
In the heating operation, the four-way valve 2 is switched, and the high-temperature and high-pressure refrigerant vapor compressed by the compressor 1 reaches the second heat exchanger 7 serving as a condenser via the four-way valve 2 (point D). The high-temperature and high-pressure refrigerant vapor is condensed by the second heat exchanger 7 to become a liquid refrigerant (point H), and is reduced to an intermediate pressure between the suction pressure and the discharge pressure of the compressor 1 by the second pressure reducer 6. (Point G) Becomes a gas-liquid two-phase refrigerant and enters the gas-liquid separator 5 from the second refrigerant pipe 36 through the second inflow / outflow pipe 17.

As shown in FIG. 3, the gas-liquid separator 5 has a line-symmetric shape with respect to the central axis of the steam outflow pipe 16, and thus the gas-liquid two-phase refrigerant 19 that has flowed into the gas-liquid separator 5. Is separated with high gas-liquid separation efficiency in the same manner as the cooling operation, and the refrigerant vapor flows out of the gas-liquid separator 5 through the vapor outflow pipe 16 and the refrigerant liquid through the first inflow / outflow pipe 15. It becomes like this.
The refrigerant liquid 15 (point F) that has passed through the first refrigerant pipe 35 from the first inflow / outflow pipe 15 is depressurized from the intermediate pressure to the low pressure by the first pressure reducer 4, and is a low-temperature low-pressure gas-liquid two-phase refrigerant. Thus, the first heat exchanger 3 serving as an evaporator is reached (point B). Thereafter, the low-temperature low-pressure gas-liquid two-phase refrigerant is evaporated by the first heat exchanger 3 to become refrigerant vapor (point E), returns to the compressor 1 through the four-way valve 2, and is compressed by the compressor 1 to an intermediate pressure. (I point).
On the other hand, the refrigerant vapor 20d (point K) that has passed through the bypass pipe 9 from the vapor outlet pipe 16 is adjusted in flow rate by the flow rate adjusting valve 8, and is injected from the injection port 10 into the compressor 1 at intermediate pressure. (Refer to point J). Further, the mixed refrigerant vapor having intermediate pressure is compressed to the discharge pressure by the compressor 1 and repeats the same operation again.

  Also in the refrigeration cycle apparatus shown in FIG. 5 that does not include a gas-liquid separator, the direction in which the refrigerant flows during heating operation is indicated by white arrows, and the alphabets A ′ to D ′ in FIG. Correspond to alphabets A ′ to D ′. In the refrigeration cycle of FIG. 5, the high-temperature and high-pressure refrigerant vapor compressed by the compressor 1 reaches the second heat exchanger 7 serving as a condenser via the four-way valve 2 (point D ′). The liquid refrigerant condensed by the second heat exchanger 7 (C ′ point) is decompressed to a low pressure by the first decompressor 4 and reaches the first heat exchanger 3 serving as an evaporator (B ′ point). The low-temperature and low-pressure refrigerant vapor evaporated by the first heat exchanger 3 (point A ′) returns to the compressor 1 through the four-way valve 2, is compressed to the discharge pressure by the compressor 1, and repeats the same operation again.

  As shown in FIG. 6, in the two-stage compression cycle using the gas-liquid separator 5, the difference in enthalpy (h4−h3) at the inlet / outlet of the compressor 1 is that in a normal refrigeration cycle apparatus that does not use the gas-liquid separator 5. Since it becomes smaller than the enthalpy difference (h5−h3) at the inlet / outlet of the compressor 1, the input of the compressor 1 can be reduced. Thereby, the coefficient of performance of heating represented by the ratio of the electric input including the input of the compressor 1 and the heating capacity can be increased. Furthermore, in the two-stage compression cycle using the gas-liquid separator 5, the discharge temperature of the compressor 1 can be reduced as compared with the normal refrigeration cycle, so that the compressor 1 is highly reliable and has a long life. can do.

As described above, the gas-liquid separator 5 can achieve high gas-liquid separation efficiency even when the direction of the refrigerant flowing through the refrigeration cycle circuit is changed between the cooling operation and the heating operation.
Moreover, since the gas-liquid separator 5 is comprised by piping which does not have a container, cost can be reduced significantly and size reduction and thickness reduction can be implement | achieved. Thereby, the whole refrigerating-cycle apparatus carrying the gas-liquid separator 5 can also be reduced in size. Furthermore, since the gas-liquid separator 5 is constituted by a pipe having no container, an increase in the amount of refrigerant due to the gas-liquid separator 5 being mounted can be suppressed.
In addition, the two-stage compression cycle equipped with the gas-liquid separator 5 can reduce the compressor input both during the cooling operation and during the heating operation, as compared with a normal refrigeration cycle. In addition, the coefficient of performance for cooling and heating can be increased. Furthermore, since the discharge temperature of the compressor 1 can be reduced compared to the normal refrigeration cycle during both the cooling operation and the heating operation, high reliability and long life of the compressor 1 can be realized. it can.

  Here, the example in which the gas-liquid separator 5 shown in the first embodiment is used when the refrigerant flow directions are different between the cooling operation and the heating operation has been described. It can also be applied to time only cases. That is, even when the gas-liquid separator 5 is used in a refrigeration cycle apparatus in which a gas-liquid two-phase refrigerant flows only from either the first inflow / outflow piping 15 or the second inflow / outflow piping 17, it is high. It has gas-liquid separation efficiency and can improve the coefficient of performance of cooling or heating.

  In addition, the refrigerating cycle which mounts the gas-liquid separator 5 does not need to be a two-stage compression cycle, and may be mounted in a one-stage compression cycle. For example, FIG. 7 shows a configuration diagram of a refrigeration cycle apparatus when the gas-liquid separator 5 is mounted in a single-stage compression cycle and a cooling operation is performed. At this time, in the one-stage compression cycle, since the compressor 1 does not include the injection port 10 as in the two-stage compression cycle of FIG. 1, the bypass pipe 9 is connected to the suction side of the compressor 1. Moreover, since it is not necessary to set an intermediate pressure, the second pressure reducer 6 is not necessary. In this case, only the refrigerant liquid 21 separated by the gas-liquid separator 5 flows to the second heat exchanger 7. Therefore, the pressure loss of the refrigerant passing through the second heat exchanger 7 is reduced as compared with the refrigeration cycle apparatus shown in FIG. 5 in which the gas-liquid two-phase refrigerant flows through the second heat exchanger 7. Thereby, since the suction pressure of the compressor 1 rises and the input of the compressor 1 falls, the coefficient of performance of cooling can be increased.

  FIG. 8 shows a configuration diagram of the refrigeration cycle apparatus when the gas-liquid separator 5 is mounted in a single compression cycle and heating operation is performed. Similarly to FIG. 7, in the one-stage compression cycle, the injection port 10 as in the two-stage compression cycle of FIG. 1 is not provided in the compressor 1, and therefore the bypass pipe 9 is connected to the suction side of the compressor 1. Moreover, since there is no need to set an intermediate pressure, the first pressure reducer 4 is not necessary. In this case, only the refrigerant liquid 21 separated by the gas-liquid separator 5 flows to the first heat exchanger 3. For this reason, the pressure loss of the refrigerant passing through the first heat exchanger 3 is reduced as compared with the normal cycle in which the gas-liquid two-phase refrigerant flows through the first heat exchanger 3. Thereby, since the suction pressure of the compressor 1 rises and the input of the compressor 1 falls, the coefficient of performance of heating can be increased.

  FIG. 9 shows a configuration diagram of a refrigeration cycle apparatus in which the gas-liquid separator 5 is mounted in a single-stage compression cycle to perform cooling operation and heating operation. By reducing the pressure loss in the second pressure reducer 6 in the cooling operation and reducing the pressure loss in the first pressure reducer 4 in the heating operation, both of the circuits in FIGS. 7 and 8 can be realized. Thereby, in the cooling operation and the heating operation, the suction pressure of the compressor 1 is increased and the input of the compressor 1 is decreased, so that the coefficient of performance of the cooling and heating can be increased.

  FIG. 10 shows a configuration diagram of the refrigeration cycle apparatus when the gas-liquid separator 5 and the bridge circuit 31 are mounted in a single-stage compression cycle to perform cooling operation and heating operation. Here, the second pressure reducer 6 becomes unnecessary. In this case, the bridge circuit 31 causes the gas-liquid two-phase refrigerant to flow into the gas-liquid separator 5 through the first inflow / outflow pipe 15 during both the cooling operation and the heating operation, and the separated refrigerant liquid is supplied to the first refrigerant flow. 2 It flows out through the inflow / outflow piping 17. For this reason, since the suction pressure of the compressor 1 is increased and the input of the compressor 1 is decreased in the cooling operation and the heating operation, the coefficient of performance of the cooling and heating can be increased.

  In addition, as the compressor 1, each compressor, such as a reciprocating, a rotary, and a scroll, provided with an injection port 10 can be used. In addition, as shown in FIG. 11, a two-stage compressor 116 is used to form a two-stage compression cycle, and in the middle of the intermediate refrigerant circuit 119 connected from the low-stage compressor 117 to the high-stage compressor 118. The injection port 10 may be provided, and the refrigerant vapor 20d separated by the gas-liquid separator 5 may be injected. In this case, the hole diameter of the injection port 10 can be increased, and an appropriate injection amount can be adjusted, so that the coefficient of performance of cooling and heating is further improved in the two-stage compression cycle by the gas-liquid separator 5. can do.

  Further, the first vertical pipe 11, the upper pipe 13, the second vertical pipe 12, and the lower pipe 14 are formed as an integral pipe, and the first inflow / outflow pipe 15 and the first protrusion 18 are formed in the first vertical pipe 11. Alternatively, the second outflow / inflow pipe 17 and the second protrusion 33 may be formed in the second vertical pipe 12, and the steam outflow pipe 16 may be formed in the upper pipe 13. In this case, the number of parts can be reduced, the number of joints can be reduced, manufacturing costs can be reduced, and manufacturing efficiency can be improved.

In the first embodiment, the upper pipe 13 and the lower pipe 14 are bent. However, as shown in FIG. 12, they may be arranged horizontally.
Moreover, although the steam outflow piping 16 was provided in the middle of the upper piping 13 located in the uppermost point of the loop-shaped piping 30, the steam outflow piping 16 should just be connected to the upper part of the loop-shaped piping 30. FIG.

Moreover, although the flow path shape and structure of the 1st protrusion part 18 are arbitrary, it is preferable to set the flow path cross-sectional area to be equal to or larger than the cross-sectional area of the first inflow / outflow pipe 15. As a result, the gas-liquid two-phase refrigerant 19 that has passed through the first inflow / outflow pipe 15 and blown out from the side surface of the first vertical pipe 11 collides at the first protrusion 18 to be separated from the gas and liquid. Therefore, the gas-liquid separation efficiency of the gas-liquid separator 5 is improved.
Similarly, the flow path shape and structure of the second projecting portion 33 are arbitrary, but by setting the cross-sectional area to be equal to or greater than the cross-sectional area of the second inflow / outflow pipe 17, the second inflow / outflow pipe 17 is passed. Then, the gas-liquid two-phase refrigerant 19 blown out from the side surface of the second vertical pipe 12 collides with the one end at the second projecting portion 33 and is gas-liquid separated. Separation efficiency is improved.

Moreover, it is preferable to set the flow path protrusion length of the first protrusion 18 to be equal to or larger than the diameter of the flow path cross section of the second protrusion perpendicular to the traveling direction of the fluid passing through the first inflow / outflow pipe 15. This makes it easier to hold the refrigerant liquid 21 a in the first protrusion 18, and the impact caused by the collision of the gas-liquid two-phase refrigerant 15 flowing in from the first inflow / outflow pipe 15 is interfered. Gas-liquid separation is improved, and the gas-liquid separation efficiency of the gas-liquid separator 5 is improved.
Similarly, it is preferable to set the channel protrusion length of the second protrusion 33 to be equal to or larger than the diameter of the channel cross section of the second protrusion 33 that is orthogonal to the traveling direction of the fluid passing through the second inflow / outflow pipe 17. . Thereby, it becomes easy to hold the refrigerant liquid 21a in the second projecting portion 33, the impact caused by the collision of the refrigerant 15 in the gas-liquid two-phase state flowing in from the second inflow / outflow pipe 17 is interfered, and the second projecting portion 33 Gas-liquid separation is improved, and the gas-liquid separation efficiency of the gas-liquid separator 5 is improved.
In addition, when the channel cross-sectional shape of each protrusion part 18 and 33 is not a circle | round | yen, it can be set as the diameter d using the equivalent diameter by (1) Formula.
d = 4 × A / l (1)
Here, A is the flow path cross-sectional area of each protrusion 18, 33, and l indicates the circumferential length of the flow path cross section of each protrusion 18, 33.

In addition, as shown in FIG. 13, the first liquid projecting portion 18 and the second projecting portion 33 may be provided with a structure 32 having a capillary force to increase the retention of the refrigerant liquid. Thereby, the holding power of the refrigerant liquid 21a in the first protrusion 18 or the second protrusion 33 is improved, and the gas-liquid two-phase refrigerant 19 flowing in from the first inflow / outflow pipe 15 or the second inflow / outflow pipe 17 is improved. The impact force at the time of colliding with the 1st protrusion part 18 or the 2nd protrusion part 33 can be relieve | moderated more. Therefore, the disturbance of the refrigerant liquid is suppressed, and the gas-liquid separation efficiency can be further improved.
In addition, as the structure 32 having a capillary force, a porous body or a mesh may be added, or the protruding portion 18 may be provided with a function of the capillary force structure 32 by adopting an internally grooved tube. Good. When an internally grooved tube is adopted, an additional structure is not necessary as the structure 32 having a capillary force, so that the number of parts can be reduced.

  Further, as a refrigerant used in the refrigeration cycle, carbon dioxide, hydrocarbons, or the like, which are natural refrigerants, may be used in addition to the fluorocarbon refrigerant such as R410A. In addition, global warming potential (GWP) is determined based on internationally recognized knowledge as a numerical value indicating the ratio of carbon dioxide to the extent to which global warming is caused. Tetrafluoropropene which is a refrigerant having a low coefficient may be used.

In general, when carbon dioxide, which is a high-pressure refrigerant, is used, the compression ratio is large, and the volumetric efficiency decreases with leakage during compression. Therefore, by using a two-stage compression refrigeration cycle equipped with a two-stage compressor and equipped with the gas-liquid separator 5 shown in the first embodiment, the compression ratio in each of the low-stage and high-stage compressors can be reduced. Make it smaller. As a result, the volumetric efficiency can be improved, so that the coefficient of performance of the cooling operation and the heating operation can be greatly improved.
In addition, even when flammable hydrocarbons or tetrafluoropropene is used in the first embodiment, the amount of refrigerant charged in the refrigeration cycle circuit can be suppressed, so that combustion at the time of refrigerant leakage can be suppressed. it can.
Further, although the flow rate adjusting valve 8 is provided in the bypass pipe 9, a fixed throttle such as a capillary tube may be used instead of the flow rate adjusting valve 8.
Moreover, although the electric expansion valve is used for the first pressure reducer 4 and the second pressure reducing device 6, a fixed throttle such as a capillary tube may be used instead of the electric expansion valve.

Embodiment 2. FIG.
As shown in FIG. 14, the gas-liquid separator 5 according to the second embodiment includes a first projecting portion 18 and a second projecting portion 33 that are integrated with each other, and the first projecting portion 18 and the second projecting portion 33. Is provided with a partition member 37. Here, the partition member 37 may be formed of, for example, a cylinder, inserted into an integral pipe that forms the first protrusion 18 and the second protrusion 33, and may be fixed by caulking the pipe. In this case, brazing is not necessary, and the manufacturing cost can be reduced.
According to this configuration, the first projecting portion 18 and the second projecting portion 33 are configured by an integral pipe, and the first projecting portion 18 and the second projecting portion 33 are formed by the partition member 37. Formation of the part 18 and the 2nd protrusion part 33 becomes easy.
Moreover, since the 1st protrusion part 18 and the 2nd protrusion part 33 are comprised by integral piping, since it can also serve as a reinforcing material of the loop-shaped piping 30, the intensity | strength of the gas-liquid separator 5 is increased. It is also possible.

In addition, as shown in FIG. 15, the first projecting portion 18 and the second projecting portion 33 are configured by an integral pipe, and without using the partition member 37, the throttle section 34 is provided in the integral pipe for partitioning. The first protrusion 18 and the second protrusion 33 may be formed. At this time, even if there is a slight gap in the throttle 34, only the refrigerant liquid accumulated in the first protrusion 18 or the second protrusion 33 moves through the gap, so that high gas-liquid separation efficiency is achieved. Can be secured. In this case, the partition member 37 becomes unnecessary, and the gas-liquid separator 5 can be further reduced in cost.
As a method of fixing the partition member, a method of caulking the pipe is shown, but the partition member may be brazed to the pipe.

Embodiment 3 FIG.
As shown in FIG. 16, the gas-liquid separator 5 shown in the third embodiment is arranged so that the first inflow / outflow piping 15 intersects with the second vertical piping 12 without joining (three-dimensional intersection), The second inflow / outflow piping 17 is arranged so as to intersect (three-dimensional intersection) without joining the first vertical piping 11. This case also has the same effect as the first embodiment.
Thereby, even when the space restriction is imposed when the gas-liquid separator 5 is installed in the refrigeration cycle circuit, the straight portions L of the first inflow / outflow piping 15 and the second inflow / outflow piping 17 can be lengthened. It becomes possible. Therefore, the run-up section of the refrigerant 19 in the gas-liquid two-phase state passing through the first inflow / outflow piping 15 and the second inflow / outflow piping 17 can be extended, and the flow state is stabilized to disturb the gas-liquid two-phase state. , And the turbulence in the first protrusion 18 and the second protrusion 33 can be further suppressed, and the gas-liquid separation efficiency can be further improved.
Furthermore, as shown in FIG. 17, if the first inflow / outflow piping 15 and the second inflow / outflow piping 17 are bent, the lateral width W of the gas / liquid separator 5 can be further reduced. Compactness can be achieved. The direction in which the first inflow / outflow piping 15 and the second inflow / outflow piping 17 are bent is arbitrary, such as a vertical direction or a horizontal direction.

Embodiment 4 FIG.
As shown in FIG. 18, in the gas-liquid separator 5 shown in the fourth embodiment, the upper pipe 13 is formed by an upper bifurcated material 22 that branches one flow path into two flow paths, and the lower pipe 14 is formed by 2 parts. It is formed by a lower connecting member 23 that connects two flow paths. Here, the first inflow / outflow pipe 15 and the first projecting portion 18 are in a plane including the central axis of the first vertical pipe 11 and the central axis of the second vertical pipe 12 so as not to interfere with the second vertical pipe 12. It is formed to be vertical. Similarly, the second inflow / outflow piping 17 and the second projecting portion 33 are in a plane including the central axis of the first vertical piping 11 and the central axis of the second vertical piping 12 so as not to interfere with the first vertical piping 11. It is formed to be vertical. At this time, as shown in the AA section, the direction of the refrigerant 19 flowing into the first inflow / outflow pipe 15 and the direction of the refrigerant liquid flowing out of the second outflow / inflow pipe 17 are arranged in the same direction. Yes. This case also has the same effect as the first embodiment.

As an example of the upper bifurcated material 22, as shown in FIG. 19, an embossing process may be performed so that the bifurcated portions are adjacent. Moreover, as an example of the lower connecting member 23, as shown in FIG. 20, it can be processed by embossing so that two connecting portions are adjacent to each other. In this case, the first vertical pipe 11 having the first inflow / outflow pipe 15 and the first projecting portion 18 in the two adjacent holes of the upper bifurcated member 22 and the lower connecting member 23, and the second inflow / outflow pipe 17. And the second vertical pipe 12 having the second projecting portion 33 is inserted and brazed, and the steam outflow pipe 16 is inserted into the remaining hole of the upper bifurcated member 22 and brazed, so that the gas-liquid It is possible to form a separator 5. Thereby, manufacture of the gas-liquid separator 5 can be greatly simplified, and cost reduction can be realized.
Further, the lateral width W of the gas-liquid separator 5 can be further reduced, and the gas-liquid separator 5 can be greatly downsized.
Further, since the take-out directions of the first inflow / outflow piping 15 and the second outflow / inflow piping 17 are reversed, the degree of freedom in the bending direction of the first outflow / inflow piping 15 and the second inflow / outflow piping 17 is widened. It becomes easy to install the separator 5 in the refrigeration cycle circuit.
In addition, as shown in FIG. 21, you may comprise so that the direction of the refrigerant | coolant 19 which flows in into the 1st inflow / outflow piping 15 and the direction of the refrigerant | coolant liquid which flows out out of the 2nd inflow / outflow piping 17 may become a reverse direction. In this case, since the first inflow / outflow piping 15 and the second outflow / inflow piping 17 are taken out in the same direction, it is easy to mount the gas-liquid separator 5 in the refrigeration cycle from the same direction.

Embodiment 5 FIG.
In the gas-liquid separator 5 shown in the fifth embodiment, as shown in FIG. 22, the upper pipe 13 is formed by an upper multi-branch material 24 that branches one flow path into three flow paths, and the lower pipe 14 is formed by 3 It is formed of a lower multi-connection material 25 that connects two flow paths. The first vertical pipe 11 having the first inflow / outflow pipe 15 and the first projecting portion 18, the second inflow / outflow pipe 17, and the first The second vertical pipe 12 having the two projecting portions 33 and the third vertical pipe 38 as the third flow path are inserted and brazed, and the steam outflow pipe 16 is inserted into the remaining hole of the upper multi-branch member 24. Is inserted and brazed. At this time, as shown in the AA cross section, the refrigerant 19 flowing into the first inflow / outflow pipe 15 and the refrigerant liquid flowing out of the second outflow / inflow pipe 17 are arranged in opposite directions. Yes.
In this case, the addition of the third vertical pipe 38 increases the cross-sectional area when branched by the upper multi-branch member 24 in addition to the effects shown in the first embodiment, and therefore the refrigerant is pulled by the refrigerant vapor 20a. Thus, the rising refrigerant liquid 21 c is easily separated into gas and liquid by the upper multi-branch material 24. Furthermore, since the cross-sectional area at the time of branching by the lower multi-connecting material 25 is increased by adding the third vertical pipe 38, the refrigerant vapor 20b entrapped in the refrigerant liquid 21b is Gas-liquid separation is facilitated. By providing the third vertical pipe 38 in this way, the gas-liquid separation efficiency can be further improved.

In addition, although the case where one 3rd vertical piping 38 was added was demonstrated here, several 3rd vertical piping 38 was added and the connection hole of the upper multi-branch material 24 and the lower multi-connection material 25 in connection with it. The number may be increased. In this case, since the cross-sectional area when branched by the upper multi-branch material 24 and the cross-sectional area when branched by the lower multi-connection member 25 are further increased, the gas-liquid separation efficiency of the gas-liquid separator 5 is further increased. Can be improved.
The direction of the refrigerant 19 flowing into the first inflow / outflow pipe 15 and the direction of the refrigerant liquid flowing out from the second outflow / inflow pipe 17 may be arranged in the same direction.

Embodiment 6 FIG.
As shown in FIG. 23, the gas-liquid separator 5 shown in the sixth embodiment is arranged on the first plate member 26 and the second plate member 27 with the first vertical pipe 11 as shown in FIG. 2 of the first embodiment. The second vertical pipe 12, the upper pipe 13, the lower pipe 14, the first inflow / outflow pipe 15, the first protrusion 18, the second inflow / outflow pipe 17, the second protrusion 33, and the flow path corresponding to the steam outflow pipe 16. The plate members 26 and 27 are joined and laminated so that the respective channels formed in the first plate member 26 and the second plate member 27 face each other, so that the channel through which the refrigerant passes is formed. Formed.
As a result, the number of equipment constituting the gas-liquid separator 5 can be reduced. Further, since the gas-liquid separator 5 can be formed by joining the first plate member 26 and the second plate member 27 at a time by brazing in the furnace or the like, the manufacture becomes easy.
Here, the method of forming each flow path in the first plate member 26 and the second plate member 27 may be cutting, forging, or casting.
Further, the flow path may be formed in one of the first plate member 26 and the second plate member 27, or in the flow path instead of the two layers of the first plate member 26 and the second plate member 27. You may make it form a flow path by laminating | stacking the several plate member by which the corresponding process was carried out.
In addition, although the gas-liquid separator 5 of Embodiment 1 has been shown as an example in which the flow path is formed by a plate member here, even if it is applied to the gas-liquid separator 5 shown in Embodiments 2 to 5, Similar effects can be obtained.

Embodiment 7 FIG.
As shown in FIG. 24, the gas-liquid separator 5 shown in the seventh embodiment forms a flow path by drilling inside from the end surface of the plate member 29 along the plane direction of the plate member. Furthermore, a blind member 28 is installed in an unnecessary opening in the plate member 29, and the first vertical pipe 11, the second vertical pipe 12, the upper pipe 13, and the lower pipe as shown in FIG. 12 of the first embodiment. 14, the first inflow / outflow pipe 15, the first protrusion 18, the second inflow / outflow pipe 17, the second protrusion 33, and the flow paths corresponding to the steam outflow pipe 16 are formed.
Here, after drilling the plate member 29 from the position indicated by the white arrow in the figure, the blind member 28 is provided at four locations to form a flow path through which the refrigerant passes.
Thereby, since a junction location becomes only the installation part of the blind member 28, the junction location of the gas-liquid separator 5 is reduced significantly, and manufacture becomes easy. Moreover, since it becomes only a drilling process, manufacturing cost can be reduced.

The position where the plate member 29 is drilled and the position where the blind member 28 is installed are arbitrary, as long as the flow path of the gas-liquid separator 5 as shown in the first to seventh embodiments can be formed. When the upper pipe 13 and the lower pipe 14 have a bend, they can be drilled by replacing them with straight lines.
Alternatively, the blind member 28 may be screwed and fixed at a location where the blind member 28 is attached. In this case, welding and brazing of the gas-liquid separator 5 are not necessary, and manufacturing is greatly facilitated, and manufacturing cost can be reduced.

By the way, in the gas-liquid separator 5 shown in the first to seventh embodiments, the cross-sectional area of each flow path is arbitrary. For example, as shown in FIG. 25, the channel cross-sectional area may be changed for each channel. However, if the gas-liquid separator 5 is formed with a pipe having the same diameter, the types of pipes can be unified, so that parts management becomes easier.
In each of the above embodiments, the gas-liquid separator of the present invention is used in a refrigeration cycle apparatus, and an example of gas-liquid separation of the refrigerant used therein has been described. However, the gas-liquid separator of the present invention is In addition to the refrigerant, it can be applied to gas-liquid separation of various fluids.

  DESCRIPTION OF SYMBOLS 1 Compressor, 2 Four way valve, 3 1st heat exchanger, 1st decompressor, 5 Gas-liquid separator, 6 2nd decompressor, 7 2nd heat exchanger, 8 Flow control valve, 9 Bypass piping, 10 Injection port, 11 First vertical pipe (first flow path), 12 Second vertical pipe (second flow path), 13 Upper pipe (upper connection part), 14 Lower pipe (lower connection part), 15 First Inflow / outflow piping (first inflow / outflow passage), 16 Steam outflow piping (outflow passage for gas phase fluid), 17 Second inflow / outflow piping (second inflow / outflow passage), 18 First protrusion, 19 Gas-liquid two-phase Refrigerant, 20 Refrigerant vapor, 21 Refrigerant liquid, 22 Upper bifurcated material, 23 Lower connection material, 24 Upper multi-branch material, 25 Lower multi-connection material, 26 First plate member, 27 Second plate member, 28 Blind member, 29 Plate member, 30 loop piping, 31 bridge circuit, 32 capillary force structure 33 Second projecting portion, 34 Restriction portion, 35 First refrigerant piping, 36 Second refrigerant piping, 37 Partition member, 38 Third vertical piping (third flow path), 116 Two-stage compressor, 117 Low-stage side Compressor, 118 High stage compressor, 119 Intermediate refrigerant circuit.

Claims (16)

A first flow path and a second flow path;
An upper end portion in the vertical direction of the first flow path and an upper end portion in the vertical direction of the second flow path are connected by an upper connecting portion, and a lower end portion in the vertical direction of the first flow path and the second flow path The lower end of the flow path in the vertical direction is connected by a lower connecting portion, and a loop-shaped flow path is formed by the first flow path, the second flow path, the upper connecting section, and the lower connecting section. Formed,
A first inflow / outflow channel through which fluid flows in or out is connected in the middle of the first channel, a second outflow / inflow channel through which fluid flows out or inflow is connected in the middle of the second channel, and the loop The gas-phase fluid outflow channel is connected to the top of the channel,
At least one of a side surface facing the connection opening with the first inflow / outflow channel in the first channel or a side surface facing the connection opening with the second inflow / outflow channel in the second channel. On the one hand, a gas-liquid separator characterized by being provided with a protruding portion of a channel having a shape protruding from the inside to the outside.   The flow passage cross-sectional area of the protruding portion is equal to or larger than the cross-sectional area of the first inflow / outflow passage or the second inflow / outflow passage having a connection opening on a side surface facing the protrusion. The gas-liquid separator described in 1.   3. The gas-liquid separator according to claim 1, wherein a length of the flow path protrusion of the protrusion is equal to or greater than a diameter of a flow path cross section of the protrusion.   The gas-liquid separator according to any one of claims 1 to 3, wherein the protrusion has a structure having a capillary force.   The gas-liquid separator according to any one of claims 1 to 4, further comprising a third flow path for connecting the upper connecting portion and the lower connecting portion.   The projecting portion includes a first projecting portion provided on a side surface of the first channel facing the connection opening with the first inflow / outflow channel, and the second outflow / inflow channel in the second channel. It has the 2nd projection part provided in both the side opposite to a connection opening, the 1st projection part and the 2nd projection part are formed with an integral member, and the integral member is partitioned and the above-mentioned The gas-liquid separator according to any one of claims 1 to 5, wherein the gas-liquid separator is divided into a first protrusion and the second protrusion.   The at least one set of the second flow path and the first inflow / outflow flow path, or the first flow path and the second inflow / outflow flow path intersects each other without joining. The gas-liquid separator according to any one of claims 1 to 6.   The gas-liquid separator according to any one of claims 1 to 7, wherein each of the flow paths is formed using a pipe.   The said upper connection part is formed of the branch material which a branch part adjoins, and the said lower connection part is formed of the connection material which a connection part adjoins. The gas-liquid separator according to one item.   The first flow path, the second flow path, the upper connection part, the lower connection part, the first inflow / outflow path, the second inflow / outflow path, the outflow path of the gas phase fluid, and the protrusion The gas-liquid separator according to claim 1, wherein the gas-liquid separator is formed by stacking a plurality of plate-like members.   The first flow path, the second flow path, the upper connection part, the lower connection part, the first inflow / outflow path, the second inflow / outflow path, the outflow path of the gas phase fluid, and the protrusion The gas-liquid separator according to claim 1, wherein the gas-liquid separator is formed by an internal hole that is drilled along a plane of a plate-like member.   The gas-liquid separator as described in any one of Claims 1-11 is arrange | positioned at the refrigerating cycle circuit, The refrigerating-cycle apparatus characterized by the above-mentioned.   The refrigeration cycle apparatus according to claim 12, wherein the refrigeration cycle circuit is of a two-stage compression cycle.   The compressor constituting the refrigeration cycle circuit is a two-stage compressor, and the outflow passage of the gas-liquid separator is provided in the middle of a refrigerant circuit connected from a low-stage compressor to a high-stage compressor. The refrigeration cycle apparatus according to claim 13, wherein a gas phase fluid flowing out from the tank is injected.   The refrigerant flowing through the refrigeration cycle circuit is hydrocarbon or tetrafluoropropene, and the refrigeration cycle apparatus according to any one of claims 12 to 14.   The refrigerant that flows through the refrigeration cycle circuit is carbon dioxide, which is a natural refrigerant, and the refrigeration cycle apparatus according to any one of claims 12 to 14.

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