JP2019207033A - Heat exchanger and refrigeration cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a heat exchanger capable of reducing variations in the supply amount of a liquid-phase refrigerant distributed from a refrigerant circulation part to a plurality of heat transfer tubes. SOLUTION: The heat exchanger is provided with an upright tubular refrigerant circulation portion, which is laterally branched from the refrigerant circulation portion, arranged at intervals in the height direction of the refrigerant circulation portion, and has a refrigerant circulation portion. A plurality of heat transfer tubes having an open end that is open to the inside of the section; and an inlet tube that is connected to the refrigerant circulation unit and guides the refrigerant containing the liquid phase refrigerant to the refrigerant circulation unit. The inlet tube has a refrigerant outlet opening inside the refrigerant circulating portion from a direction facing the opening end of the heat transfer tube below the intermediate portion along the height direction of the refrigerant circulating portion, and inside the refrigerant circulating portion. And a barrier provided so as to face the refrigerant outlet of the inlet pipe. [Selection diagram] Fig. 3

Description

  Embodiments described herein relate generally to a parallel flow type heat exchanger and a refrigeration cycle apparatus including the heat exchanger.

  For example, a parallel flow type heat exchanger used in an air conditioner mainly includes a pair of headers standing upright apart from each other, and a plurality of flat heat transfer tubes horizontally extending between the headers. It is prepared as an element. The heat transfer tubes are arranged at intervals in the height direction of the header, and the adjacent heat transfer tubes are thermally connected via heat dissipation fins.

  When this type of heat exchanger is used as an evaporator, a connecting pipe connected to the lower part of one header functions as an inlet pipe, and a gas-liquid two-phase refrigerant that is a refrigerant containing a liquid-phase refrigerant passes through the inlet pipe. It flows into the inside of one header.

  The gas-liquid two-phase refrigerant that has flowed into the header is distributed to the plurality of heat transfer tubes, and the liquid-phase refrigerant contained in the gas-liquid two-phase refrigerant is air in the process of flowing the gas-liquid two-phase refrigerant along the heat transfer tubes. Vaporizes by heat exchange.

Japanese Utility Model Publication No. 4-108191

  By the way, in the process in which the gas-liquid two-phase refrigerant flows into the one header from the inlet pipe, most of the liquid-phase refrigerant concentrates on the lower part of the header due to the weight, and the gas-phase refrigerant moves from the lower part to the upper part of the header The phenomenon of flowing occurs.

  In other words, the liquid phase refrigerant is excessively supplied to the heat transfer tubes connected to the lower portion of the header, and the supply amount of the liquid phase refrigerant distributed to the heat transfer tubes decreases as it proceeds to the upper portion of the header. For this reason, especially in a heat transfer tube in which the supply amount of the liquid-phase refrigerant is extremely insufficient, it is inevitable that a dry-out phenomenon occurs in the process of heat exchange with air and the heat exchange performance is lowered.

  An object of the present invention is to obtain a heat exchanger that can reduce variations in the supply amount of liquid-phase refrigerant distributed from a refrigerant circulation section to a plurality of heat transfer tubes when a heat exchanger is used as an evaporator.

According to the embodiment, the heat exchanger is erected from the upright tubular refrigerant circulation part, and is branched laterally from the refrigerant circulation part, and is arranged at an interval in the height direction of the refrigerant circulation part. And a plurality of heat transfer tubes having an open end opened inside the refrigerant circulation part, and an inlet pipe connected to the refrigerant circulation part and guiding a refrigerant containing a liquid phase refrigerant to the refrigerant circulation part. Yes.
The inlet pipe has a refrigerant outlet that is opened to the inside of the refrigerant circulation part from a direction facing the opening end of the heat transfer pipe below the intermediate part along the height direction of the refrigerant circulation part. It is characterized by having a barrier provided inside the refrigerant circulation part so as to face the refrigerant outlet of the inlet pipe.

It is a circuit diagram showing roughly the composition of the refrigerating cycle device concerning a 1st embodiment. It is a front view of the parallel flow type heat exchanger concerning a 1st embodiment. In 1st Embodiment, it is sectional drawing which shows the relative positional relationship of an inlet tube, a barrier, and a heat exchanger tube. It is sectional drawing which follows the F4-F4 line | wire of FIG. It is sectional drawing which follows the F5-F5 line | wire of FIG. In 1st Embodiment, it is sectional drawing which shows roughly the flow of the liquid-phase refrigerant | coolant which flowed into the refrigerant | coolant distribution part from the inlet pipe. It is sectional drawing which shows the modification 1 of 1st Embodiment. It is sectional drawing which shows the modification 2 of 1st Embodiment. It is sectional drawing which shows the modification 3 of 1st Embodiment. In 2nd Embodiment, it is sectional drawing which shows the relative positional relationship of an inlet tube, a barrier, and a heat exchanger tube. It is a front view of the parallel flow type heat exchanger which concerns on 3rd Embodiment. In 3rd Embodiment, it is sectional drawing which shows the relative positional relationship of a 1st turn part, an inlet tube, a barrier, and a heat exchanger tube. In 3rd Embodiment, it is sectional drawing which shows the relative positional relationship of a 2nd turn part, an inlet tube, a barrier, and a heat exchanger tube.

[First embodiment]
Hereinafter, the first embodiment will be described with reference to FIGS. 1 to 6.

  FIG. 1 is a refrigeration cycle circuit diagram of the air conditioner 1. The air conditioner 1 is an example of a refrigeration cycle apparatus, and includes a hermetic compressor 2, a four-way valve 3, an outdoor heat exchanger 4 that is a heat source side heat exchanger, an expansion device 5, and a room that is a utilization side heat exchanger. The heat exchanger 6 is provided as a main element. The plurality of elements constituting the air conditioner 1 are connected in series via a circulation circuit 7 in which the refrigerant circulates.

  Specifically, the discharge side of the hermetic compressor 2 is connected to the first port 3 a of the four-way valve 3. The second port 3 b of the four-way valve 3 is connected to the outdoor heat exchanger 4. The outdoor heat exchanger 4 is connected to the indoor heat exchanger 6 via an expansion device 5. The indoor heat exchanger 6 is connected to the third port 3 c of the four-way valve 3. The fourth port 3 d of the four-way valve 3 is connected to the suction side of the hermetic compressor 2 via the accumulator 8. The outdoor heat exchanger 4 and the indoor heat exchanger 6 have blowers 4a and 6a, respectively.

  When the air conditioner 1 operates in the cooling mode, the four-way valve 3 is switched so that the first port 3a communicates with the second port 3b and the third port 3c communicates with the fourth port 3d. When the operation of the air conditioner 1 is started in the cooling mode, the high-temperature and high-pressure gas-phase refrigerant is discharged from the hermetic compressor 2 to the circulation circuit 7. The high-temperature and high-pressure gas-phase refrigerant is guided to the outdoor heat exchanger 4 that functions as a condenser via the four-way valve 3.

  The gas-phase refrigerant guided to the outdoor heat exchanger 4 is condensed by heat exchange with the air blown from the blower 4a, and changes to a high-pressure liquid-phase refrigerant. The high-pressure liquid-phase refrigerant is reduced in pressure in the process of passing through the expansion device 5 and is changed to a gas-liquid two-phase refrigerant that is a refrigerant containing a low-pressure liquid-phase refrigerant. The gas-liquid two-phase refrigerant is guided to the indoor heat exchanger 6 functioning as an evaporator, and exchanges heat with air blown from the blower 6a in the process of passing through the indoor heat exchanger 6.

  As a result, the gas-liquid two-phase refrigerant takes heat from the air and evaporates, and changes to a low-temperature / low-pressure gas-phase refrigerant. The air passing through the indoor heat exchanger 6 is cooled by the latent heat of vaporization of the liquid refrigerant, and is sent to a place to be air-conditioned (cooled) as cold air.

  The low-temperature and low-pressure gas-phase refrigerant that has passed through the indoor heat exchanger 6 is guided to the accumulator 8 via the four-way valve 3. If liquid refrigerant that could not evaporate is mixed in the refrigerant, the accumulator 8 separates it into liquid phase refrigerant and gas phase refrigerant. The low-temperature and low-pressure gas-phase refrigerant separated from the liquid-phase refrigerant is sucked into the hermetic compressor 2 from the accumulator 8. The gas-phase refrigerant sucked into the hermetic compressor 2 is compressed again into a high-temperature / high-pressure gas-phase refrigerant and discharged to the circulation circuit 7.

  On the other hand, when the air conditioner 1 operates in the heating mode, the four-way valve 3 is switched so that the first port 3a communicates with the third port 3c and the second port 3b communicates with the fourth port 3d. When the operation of the air conditioner 1 is started in the heating mode, the high-temperature and high-pressure gas-phase refrigerant discharged from the hermetic compressor 2 is guided to the indoor heat exchanger 6 via the four-way valve 3 and blower Heat exchange with the air sent from 6a. That is, the indoor heat exchanger 6 functions as a condenser.

  As a result, the gas-phase refrigerant passing through the indoor heat exchanger 6 is condensed by exchanging heat with air, and changes to a high-pressure liquid-phase refrigerant. The air passing through the indoor heat exchanger 6 is heated by heat exchange with the gas-phase refrigerant, and is sent to a place to be air-conditioned (heated) as warm air.

  The high-pressure liquid-phase refrigerant that has passed through the indoor heat exchanger 6 is reduced in pressure in the process of passing through the expansion device 5 and changes to a low-pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant is guided to the outdoor heat exchanger 4 functioning as an evaporator, and evaporates by exchanging heat with the air sent from the blower 4a, thereby changing to a low-temperature / low-pressure gas-phase refrigerant. The low-temperature and low-pressure gas-phase refrigerant that has passed through the outdoor heat exchanger 4 is guided to the accumulator 8 via the four-way valve 3.

  If liquid refrigerant that could not evaporate is mixed in the refrigerant, the accumulator 8 separates it into liquid phase refrigerant and gas phase refrigerant. The low-temperature and low-pressure gas-phase refrigerant separated from the liquid-phase refrigerant is sucked into the hermetic compressor 2 from the accumulator 8 as in the cooling mode.

  In this embodiment, a parallel flow type heat exchanger 10 as shown in FIG. 2 is used as the outdoor heat exchanger 4 and the indoor heat exchanger 6. Hereinafter, a specific configuration of the parallel flow heat exchanger 10 will be described with reference to FIGS. 2 to 6.

  As shown in FIG. 2, the parallel flow heat exchanger 10 includes a first header 11, a second header 12, a plurality of heat transfer tubes 13, and a plurality of corrugated radiating fins 14 as main elements. .

  The first header 11 and the second header 12 are straight circular tubular elements, respectively, and are erected in the vertical direction. The first header 11 and the second header 12 are arranged in parallel with a space between each other, and their upper and lower ends are closed.

  The inside of the first header 11 constitutes the refrigerant inflow portion 16 when the parallel flow heat exchanger 10 functions as an evaporator. The refrigerant inflow part 16 is an example of a refrigerant circulation part. The inside of the second header 12 constitutes the refrigerant outflow portion 17 when the parallel flow heat exchanger 10 functions as an evaporator.

  The heat transfer tube 13 spans horizontally with a certain gap G in the height direction of the first header 11 and the second header 12 so as to connect the refrigerant inflow portion 16 and the refrigerant outflow portion 17. Has been. In other words, the heat transfer tube 13 is branched laterally from the refrigerant inflow portion 16 and the refrigerant outflow portion 17.

  Furthermore, the heat transfer tube 13 has a flat shape crushed from the height direction of the first header 11 and the second header 12, and the inside of the heat transfer tube 13 includes a plurality of flow paths (not shown). ).

  As shown in FIG. 2, the heat transfer tube 13 has a first opening end 18a and a second opening end 18b. The first opening end 18 a of the heat transfer tube 13 passes through the outer peripheral wall of the first header 11 and is opened inside the refrigerant inflow portion 16. The first opening ends 18a are arranged in a line with a space in the height direction of the first header 11 with respect to the refrigerant inflow portion 16, and are directed in the same direction.

  The second opening end 18 b of the heat transfer tube 13 passes through the outer peripheral wall of the second header 12 and is opened inside the refrigerant outflow portion 17. The second open ends 18b are arranged in a line at intervals in the height direction of the second header 12 with respect to the refrigerant outflow portion 17, and are directed in the same direction.

  The heat radiating fins 14 are arranged in a space between the adjacent heat transfer tubes 13. The radiating fins 14 extend in the longitudinal direction of the heat transfer tube 13 so as to straddle between the first header 11 and the second header 12 and are thermally connected to the heat transfer tube 13 by means of brazing, for example. Has been.

  The radiating fins 14 are not limited to corrugated fins, and may be, for example, plate-like fins having cutout portions into which flat heat transfer tubes 13 can be inserted.

  As shown in FIGS. 2 to 4, the first connecting pipe 20 is connected to the lower end of the first header 11. The first connection pipe 20 is an element that guides the gas-liquid two-phase refrigerant that has passed through the expansion device 5 to the refrigerant inflow portion 16 when the parallel flow heat exchanger 10 functions as an evaporator, In other words.

  The second connection pipe 21 is connected to the upper end portion of the second header 12. When the parallel flow type heat exchanger 10 functions as an evaporator, the second connecting pipe 21 allows the low-temperature and low-pressure gas-phase refrigerant that has passed through the parallel flow type heat exchanger 10 to pass through the accumulator 8 from the four-way valve 3. Thus, it is an element that leads to the hermetic compressor 2 and can be rephrased as an outlet pipe.

  As shown in FIGS. 3 to 5, the first connecting pipe 20 has a refrigerant outlet 22 opened in the refrigerant inflow portion 16. The diameter D1 of the refrigerant outlet 22 is larger than the inner dimension D2 along the height direction of the first opening end 18a of the heat transfer tube 13, and smaller than the inner dimension D3 along the width direction of the first opening end 18a.

  The refrigerant outlet 22 is opened to the inside of the refrigerant inflow portion 16 from a direction facing the first opening end 18 a of the heat transfer tube 13 below the intermediate portion along the height direction of the first header 11. According to this embodiment, the refrigerant outlet 22 of the first connection pipe 20 is connected to the first opening end 18 a of the heat transfer pipe 13 closest to the bottom 16 a of the refrigerant inflow portion 16 and the other heat transfer pipe 13 on the heat transfer pipe 13. It is located between the first open end 18 a of the heat tube 13. Therefore, the refrigerant outlet 22 is opened inside the refrigerant inflow part 16 between the first opening ends 18 a of the two heat transfer tubes 13 adjacent at the lowermost part of the refrigerant inflow part 16.

  Further, a center line A1 extending horizontally through the center O1 of the refrigerant outlet 22 of the first connection pipe 20 passes through an intermediate point O2 between two adjacent heat transfer pipes 13 at the lowermost part of the refrigerant inflow portion 16. Therefore, it is positioned slightly below the reference line A2 extending horizontally. Therefore, the center O1 of the refrigerant outlet 22 and the intermediate point O2 between the two adjacent heat transfer tubes 13 are shifted by a distance L1 along the height direction of the first header 11.

  As shown in FIGS. 3 to 5, the barrier 23 is provided inside the refrigerant inflow portion 16. The barrier 23 is erected in the vertical direction from the bottom 16 a of the refrigerant inflow portion 16. According to the present embodiment, the barrier 23 is interposed between the first open end 18 a of the heat transfer tube 13 closest to the bottom 16 a of the refrigerant inflow portion 16 and the refrigerant outlet 22 of the first connection tube 20. .

  The upper edge 23a of the barrier 23 extends in a straight line in the horizontal direction. The upper end edge 23a of the barrier 23 is positioned between the inner peripheral lower end of the refrigerant outlet 22 and the inner peripheral upper end of the refrigerant outlet 22 as a preferable example, and extends horizontally through the center O1 of the refrigerant outlet 22. It protrudes upwards. As a result, the barrier 23 has a height dimension H so as to face most of the refrigerant outlet 22 opened in the refrigerant inflow portion 16.

  Further, the barrier 23 has a width dimension W along the radial direction of the first header 11. The width dimension W of the barrier 23 is larger than the diameter D1 of the refrigerant outlet 22. In other words, the barrier 23 is formed wider than the refrigerant outlet 22.

  As best shown in FIG. 4, both side portions along the width direction of the barrier 23 are abutted against the inner peripheral surface of the first header 11. For this reason, the lowermost part of the refrigerant inflow portion 16 is partitioned by the barrier 23 into a first region 25 and a second region 26. The refrigerant outlet 22 of the first connection pipe 20 is opened to the first region 25. The first opening end 18 a of the heat transfer tube 13 positioned at the lowermost portion of the refrigerant inflow portion 16 that is in a positional relationship facing the refrigerant outlet 22 is opened in the second region 26.

  In the first embodiment, when the air conditioner 1 starts operation in the cooling mode, the indoor heat exchanger 6 constituted by the parallel flow heat exchanger 10 functions as an evaporator. For this reason, the low-temperature and low-pressure gas-liquid two-phase refrigerant that has passed through the expansion device 5 flows from the refrigerant outlet 22 of the first connection pipe 20 into the refrigerant inflow portion 16 inside the first header 11.

  Since the gas-liquid two-phase refrigerant is affected by gravity in the process of flowing from the refrigerant outlet 22 into the refrigerant inflow portion 16, the liquid-phase refrigerant contained in the gas-liquid two-phase refrigerant is concentrated at the lower portion of the refrigerant inflow portion 16. The gas phase refrigerant separated from the liquid phase refrigerant rises from the lower part to the upper part of the refrigerant inflow part 16.

  According to the present embodiment, the barrier 23 rising from the bottom 16 a of the refrigerant inflow portion 16 has the first opening end of the heat transfer tube 13 positioned at the lowermost portion of the refrigerant outlet 22 of the first connection tube 20 and the refrigerant inflow portion 16. The upper portion of the barrier 23 faces most of the refrigerant outlet 22.

  For this reason, as indicated by arrows in FIG. 6, most of the main flow of the liquid-phase refrigerant flowing from the refrigerant outlet 22 into the refrigerant inflow portion 16 collides with the barrier 23 and is guided by the barrier 23 to blow in the antigravity direction. Go up.

  Therefore, the liquid-phase refrigerant flowing into the refrigerant inflow portion 16 from the refrigerant outlet 22 can be actively guided toward the upper side of the refrigerant inflow portion 16 against the gravity, and the refrigerant inflow portion 16 away from the refrigerant outlet 22 can be guided. A large amount of liquid refrigerant can be distributed to the first open ends 18a of the plurality of heat transfer tubes 13 located in the middle or upper part.

  In addition, the barrier 23 includes a first region 25 where the refrigerant outlet 22 is opened at a lower end portion of the refrigerant inflow portion 16, and a first opening end 18 a of the heat transfer tube 13 positioned at the lowermost portion of the refrigerant inflow portion 16. The second region 26 is partitioned. For this reason, in the lower part of the refrigerant inflow part 16, the flow of the liquid phase refrigerant from the refrigerant outlet 22 toward the first opening end 18 a of the heat transfer tube 13 is blocked by the barrier 23.

  At the same time, a part of the liquid-phase refrigerant blocked by the barrier 23 flows into the second region 26 only when it gets over the upper edge 23a of the barrier 23. Therefore, the barrier 23 prevents the liquid refrigerant from being excessively supplied to the heat transfer tubes 13 that are in a positional relationship facing the refrigerant outlet 22.

  As a result, variation in the supply amount of the liquid phase refrigerant distributed from the refrigerant inflow portion 16 to the plurality of heat transfer tubes 13 is reduced so that the supply amount of the liquid phase refrigerant to the specific heat transfer tube 13 is not extremely short. can do. Therefore, the heat exchange performance of the parallel flow heat exchanger 10 can be enhanced with a simple configuration in which the barrier 23 is added to the refrigerant inflow portion 16.

  In the present embodiment, the refrigerant outlet 22 of the first connection pipe 20 is located inside the refrigerant inflow part 16 between the first open ends 18 a of the two heat transfer pipes 13 adjacent at the lowermost part of the refrigerant inflow part 16. It is open. At the same time, a center line A1 extending horizontally through the center O1 of the refrigerant outlet 22 is a reference line extending horizontally through an intermediate point O2 between two adjacent heat transfer tubes 13 at the lowermost portion of the refrigerant inflow portion 16. It is located slightly below A2.

  Therefore, the refrigerant outlet 22 of the first connecting pipe 20 is located near the lowermost part of the refrigerant inflow portion 16, and the liquid-phase refrigerant flowing from the refrigerant outlet 22 into the refrigerant inflow portion 16 stays at the bottom of the first region 25. Is prevented.

  Furthermore, according to the present embodiment, the upper end edge 23a of the barrier 23 is positioned between the inner peripheral lower end of the refrigerant outlet 22 and the inner peripheral upper end of the refrigerant outlet 22, and horizontally through the center O1 of the refrigerant outlet 22. It protrudes above the extending center line A1. According to this configuration, a part of the liquid-phase refrigerant flowing into the refrigerant inflow portion 16 from the refrigerant outlet 22 flows substantially horizontally toward the second region 26 without being blocked by the barrier 23, and the remaining liquid phase The refrigerant blows up in the antigravity direction along the barrier 23.

  That is, by specifying the position of the upper edge 23a of the barrier 23 with respect to the refrigerant outlet 22, the refrigerant flow along the substantially horizontal direction and the refrigerant flow upward can be formed at the lower end of the refrigerant inflow portion 16. .

  Therefore, the liquid phase refrigerant can be distributed without excess or deficiency over the entire length along the height direction of the first header 11, and the effect of suppressing variations in the supply amount of the liquid phase refrigerant distributed to the plurality of heat transfer tubes 13. Becomes higher.

  In addition, according to this embodiment, since the width dimension W of the barrier 23 is larger than the diameter D1 of the refrigerant outlet 22, the liquid-phase refrigerant flowing from the refrigerant outlet 22 into the refrigerant inflow portion 16 opens into the second region 26. The direct flow into the first opening end 18a of the heat transfer tube 13 can be prevented.

  When the air conditioner 1 starts operation in the heating mode, the outdoor heat exchanger 4 functions as an evaporator. Since the outdoor heat exchanger 4 is configured by the parallel flow heat exchanger 10 having the barrier 23 similarly to the indoor heat exchanger 6, the heat exchange performance of the outdoor heat exchanger 4 in the heating mode is improved. Can do.

[Variation 1 of the first embodiment]
FIG. 7 discloses a first modification of the first embodiment. In the first modification, the upper end edge 23a of the barrier 23 has a curved shape so as to draw an upward arc. The maximum value of the height dimension H of the barrier 23 is defined by the apex of the upper edge 23a. The position of the top of the upper edge 23a with respect to the refrigerant outlet 22 is the same as that of the barrier 23 of the first embodiment.

  According to the first modification, the height dimension H of the barrier 23 is lower than that of the first embodiment at both ends along the width direction of the barrier 23, so the liquid refrigerant blocked by the barrier 23 gets over the barrier 23. It becomes easy. For this reason, the supply amount of the liquid-phase refrigerant supplied to the heat transfer tube 13 in a positional relationship facing the refrigerant outlet 22 slightly increases.

[Modification 2 of the first embodiment]
FIG. 8 discloses a second modification of the first embodiment. In the second modification, the upper end edge 23a of the barrier 23 has a curved shape so as to draw a downward arc. The maximum value of the height dimension H of the barrier 23 is defined by both ends along the width direction of the upper end edge 23a. The positions of both ends of the upper end edge 23a with respect to the refrigerant outlet 22 are the same as those of the barrier 23 of the first embodiment. According to the second modification, the height dimension H of the barrier 23 is set at the central portion along the width direction of the barrier 23. Since it becomes low compared with the first embodiment, the amount of the liquid-phase refrigerant flowing in the horizontal direction without being blocked by the barrier 23 increases. For this reason, the supply amount of the liquid-phase refrigerant supplied to the heat transfer tube 13 in a positional relationship facing the refrigerant outlet 22 slightly increases.

[Modification 3 of the first embodiment]
FIG. 9 discloses a third modification of the first embodiment. In Modification 3, a slit 31 is opened above the barrier 23. The slit 31 extends in the horizontal direction so as to face a part of the refrigerant outlet 22.

  According to Modification 3, since the slit 31 is opened in the barrier 23, the amount of the liquid-phase refrigerant that flows in the horizontal direction without being blocked by the barrier 23 increases. For this reason, the supply amount of the liquid-phase refrigerant supplied to the heat transfer tube 13 in a positional relationship facing the refrigerant outlet 22 slightly increases.

[Second Embodiment]
FIG. 10 discloses a second embodiment. The second embodiment is different from the first embodiment in matters relating to the height dimension H of the barrier 23. Other configurations are the same as those in the first embodiment. Therefore, in the second embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  As shown in FIG. 10, the barrier 23 passes through the refrigerant outlet 22 of the first connection pipe 20, and the second heat transfer pipe 13 from the bottom adjacent to the heat transfer pipe 13 closest to the bottom 16 a of the refrigerant inflow portion 16. It rises above the first opening end 18a.

  Therefore, in this embodiment, the barrier 23 is interposed between the refrigerant outlet 22 and the first opening ends 18 a of the two heat transfer tubes 13 that are in a positional relationship facing the refrigerant outlet 22. Accordingly, all of the refrigerant outlets 22 are opened in the first region 25, and all of the first opening ends 18a of the two heat transfer tubes 13 in a positional relationship facing the refrigerant outlet 22 are in the second region. 26 is opened.

  The height dimension H of the barrier 23 is desirably set so that the distance L2 from the inner peripheral lower end of the refrigerant outlet 22 to the upper edge 23a of the barrier 23 is twice the diameter D1 of the refrigerant outlet 22.

  According to such a configuration, all of the main flow of the liquid-phase refrigerant flowing from the refrigerant outlet 22 into the refrigerant inflow portion 16 collides with the barrier 23 and is guided by the barrier 23 to blow up in the antigravity direction. Further, all of the flow of the liquid refrigerant from the refrigerant outlet 22 toward the heat transfer pipe 13 in a positional relationship facing the refrigerant outlet 22 is blocked by the barrier 23.

  For this reason, similarly to the first embodiment, the liquid-phase refrigerant flowing into the refrigerant inflow portion 16 from the refrigerant outlet 22 can be actively guided upward of the refrigerant inflow portion 16 against gravity. Therefore, it is possible to reduce variations in the supply amount of the liquid-phase refrigerant distributed from the refrigerant inflow portion 16 to the plurality of heat transfer tubes 13.

[Third embodiment]
The third embodiment is different from the first embodiment in matters relating to the parallel flow heat exchanger 50. Other configurations of the air conditioner 1 are the same as those in the first embodiment. Therefore, in the third embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  As shown in FIG. 11, the parallel flow type heat exchanger 50 includes a first header 51, a second header 52, a plurality of heat transfer tubes 53, and a plurality of corrugated radiating fins 54 as main elements. .

  The first header 51 and the second header 52 are straight circular tubular elements, respectively, and are erected along the vertical direction. The first header 51 and the second header 52 are arranged in parallel with a space between each other, and their upper and lower ends are closed.

  The interior of the first header 51 is partitioned into first to fourth refrigerant circulation portions 56a, 56b, 56c, and 56d by a plurality of partition plates 55. The partition plate 55 is disposed at a distance from each other in the height direction of the first header 51 and constitutes the bottom of the second to fourth refrigerant circulation portions 56b, 56c, and 56d. Therefore, the first to fourth refrigerant circulation portions 56 a, 56 b, 56 c and 56 d are arranged in a line along the height direction of the first header 51.

  The length S4 of the fourth refrigerant circulation part 56d is longer than the length S3 of the third refrigerant circulation part 56c. The length S3 of the third refrigerant circulation part 56c is longer than the length S2 of the second refrigerant circulation part 56b. The length S2 of the second refrigerant circulation part 56b is longer than the length S1 of the first refrigerant circulation part 56a.

  The inside of the second header 52 is partitioned into fifth to eighth refrigerant circulation portions 56e, 56f, 56g, and 56h by a plurality of partition plates 57. The partition plate 57 is disposed at a distance from each other in the height direction of the second header 52, and constitutes the bottom of the sixth to eighth refrigerant circulation portions 56f, 56g, and 56h. Therefore, the fifth to eighth refrigerant circulation portions 56e, 56f, 56g, and 56h are arranged in a line along the height direction of the second header 52.

  The length S8 of the eighth refrigerant circulation part 56h is equal to the length S4 of the fourth refrigerant circulation part 56d. The length S7 of the seventh refrigerant circulation part 56g is equal to the length S3 of the third refrigerant circulation part 56c. The length S6 of the sixth refrigerant circulation part 56f is equal to the length S2 of the second refrigerant circulation part 56b. The length S5 of the fifth refrigerant circulation part 56e is equal to the length S1 of the first refrigerant circulation part 56a.

  The heat transfer tube 53 includes first to fourth refrigerant circulation portions 56a, 56b, 56c, 56d of the first header 51 and fifth to eighth refrigerant circulation portions 56e, 56f, 56g, 56h of the second header 52. The first header 51 and the second header 52 are bridged horizontally with a constant gap G in the height direction. Therefore, the heat transfer tube 53 can be paraphrased as being branched laterally from the first header 51 and the second header 52.

  Furthermore, the heat transfer tube 53 has a flat shape crushed from the height direction of the first header 51 and the second header 52, and the inside of the heat transfer tube 53 includes a plurality of flow paths (not shown). ).

  As shown in FIGS. 12 and 13, the heat transfer tube 53 has a first open end 60a and a second open end 60b. The first opening end 60a passes through the outer peripheral wall of the first header 51 and is opened inside the first to fourth refrigerant circulation portions 56a, 56b, 56c, and 56d. The first open ends 60a are arranged in a line at intervals in the height direction of the first header 51, and are directed in the same direction.

  The second opening end 60b passes through the outer peripheral wall of the second header 52 and is opened inside the fifth to eighth refrigerant circulation portions 56e, 56f, 56g, and 56h. The second open ends 60b are arranged in a line at intervals in the height direction of the second header 52, and are directed in the same direction.

  Therefore, as shown in FIG. 11, the first to fourth refrigerant circulation portions 56 a, 56 b, 56 c and 56 d of the first header 51 are respectively connected to the fifth header 52 via the plurality of heat transfer tubes 14. Or it is connected to the 8th refrigerant | coolant distribution part 56e, 56f, 56g, 56h.

  The plurality of heat transfer pipes 53 connecting between the first refrigerant circulation part 56a and the fifth refrigerant circulation part 56e cooperate with the first refrigerant circulation part 56a and the fifth refrigerant circulation part 56e. The heat exchange area 61a is configured.

  The plurality of heat transfer pipes 53 connecting between the second refrigerant circulation part 56b and the sixth refrigerant circulation part 56f cooperate with the second refrigerant circulation part 56b and the sixth refrigerant circulation part 56f and The heat exchange area 61b is configured.

  The plurality of heat transfer pipes 53 connecting between the third refrigerant circulation part 56c and the seventh refrigerant circulation part 56g cooperate with the third refrigerant circulation part 56c and the seventh refrigerant circulation part 56g. The heat exchange area 61c is configured.

  The plurality of heat transfer pipes 53 connecting the fourth refrigerant circulation part 56d and the eighth refrigerant circulation part 56h cooperate with the fourth refrigerant circulation part 56d and the eighth refrigerant circulation part 56h to provide a fourth. The heat exchange area 61d is configured.

  Furthermore, the fourth heat exchange region 61d has more heat transfer tubes 53 than the third heat exchange region 61c. The third heat exchange region 61c has more heat transfer tubes 53 than the second heat exchange region 61b. The second heat exchange region 61b has more heat transfer tubes 53 than the first heat exchange region 61a. For this reason, the area and the heat capacity increase in the direction from the first heat exchange region 61a to the fourth heat exchange region 61d.

  The heat radiating fins 54 are arranged in a space between the adjacent heat transfer tubes 53. The radiating fin 54 extends in the longitudinal direction of the heat transfer tube 53 so as to straddle between the first header 51 and the second header 52, and is thermally connected to the heat transfer tube 53 by means of, for example, brazing. Has been.

  As shown in FIG. 11, the first connecting pipe 62 is connected to the lower end of the first header 51. The first connecting pipe 51 is an element for guiding the gas-liquid two-phase refrigerant that has passed through the expansion device 5 to the first refrigerant circulation portion 56a when the parallel flow heat exchanger 50 functions as an evaporator. .

  A second connection pipe 63 is connected to the upper end portion of the first header 51. When the parallel flow heat exchanger 50 functions as an evaporator, the second connection pipe 63 allows the low-temperature and low-pressure gas-phase refrigerant that has passed through the parallel flow heat exchanger 50 to pass through the accumulator 8 from the four-way valve 3. And is an element for leading to the hermetic compressor 2.

  As shown in FIGS. 11 to 13, the parallel flow heat exchanger 50 includes first to third turn portions 65 a, 65 b, and 65 c that reverse the flow direction of the refrigerant. The first turn 65a is an element that connects the downstream end of the first heat exchange region 61a and the upstream end of the second heat exchange region 61b, and includes an outlet pipe 66, an inlet pipe 67, and a U vent 68. It has.

  The outlet pipe 66 has a refrigerant inlet 69 connected to the fifth refrigerant circulation part 56e located at the downstream end of the first heat exchange region 61a. The refrigerant inlet 69 is opened to the upper part of the fifth refrigerant circulation part 56e from the direction facing the second opening end 60b of the heat transfer tube 53.

  The inlet pipe 67 has a refrigerant outlet 70 connected to the sixth refrigerant circulation portion 56f located at the upstream end of the second heat exchange region 61b. The refrigerant outlet 70 has a sixth refrigerant from the direction facing the second opening end 60a of the heat transfer tube 53 below the intermediate portion along the height direction of the sixth refrigerant circulation portion 56f of the second header 52. It opens to the inside of the circulation part 56f.

  According to the present embodiment, the refrigerant outlet 70 of the inlet pipe 67 includes the second open end 60b of the heat transfer pipe 53 closest to the partition plate 57 serving as the bottom of the sixth refrigerant circulation portion 56f, and the top of the heat transfer pipe 53. It is located between the second open end 60 b of the other heat transfer tube 53. Therefore, the refrigerant outlet 70 is opened inside the sixth refrigerant circulation part 56f between the second opening ends 60b of the two heat transfer tubes 53 adjacent at the lowermost part of the sixth refrigerant circulation part 56f. .

  Further, the center line A3 extending horizontally through the center O3 of the refrigerant outlet 70 of the inlet pipe 67 passes through the middle point O4 of the two adjacent heat transfer pipes 53 at the lowermost part of the sixth refrigerant circulation portion 56f. It is located slightly below the reference line A4 extending in the direction. Therefore, the center O3 of the refrigerant outlet 70 and the intermediate point O4 between the two adjacent heat transfer tubes 53 are separated by a distance L3 along the height direction of the second header 52.

  The outlet pipe 66 and the inlet pipe 67 protrude horizontally toward the outer side of the second header 52. The U vent 68 connects between the protruding end of the outlet pipe 66 and the protruding end of the inlet pipe 67.

  As shown in FIG. 12, the barrier 72 is provided inside the sixth refrigerant flow part 56f. The barrier 72 is erected in the vertical direction from the partition plate 57 serving as the bottom of the sixth refrigerant circulation portion 56f. According to the present embodiment, the barrier 72 is interposed between the second open end 60 b of the heat transfer pipe 53 closest to the bottom of the sixth refrigerant circulation portion 56 f and the refrigerant outlet 70 of the inlet pipe 67.

  The upper end edge 72a of the barrier 72 extends in a straight line in the horizontal direction. The upper end edge 72a of the barrier 72 is positioned between the inner peripheral lower end of the refrigerant outlet 70 and the inner peripheral upper end of the refrigerant outlet 70 as a preferred example, and extends horizontally through the center O3 of the refrigerant outlet 70. It protrudes upwards. As a result, the barrier 72 has a height dimension H so as to face most of the refrigerant outlet 70 opened in the sixth refrigerant circulation portion 56f.

  The barrier 72 is formed wider than the diameter D4 of the refrigerant outlet 70. Furthermore, both side portions along the width direction of the barrier 72 are abutted against the inner peripheral surface of the second header 52. For this reason, the lowermost part of the sixth refrigerant circulation part 56 f is partitioned by the barrier 72 into the first region 73 and the second region 74. The refrigerant outlet 70 is opened in the first region 73. The second opening end 60 b of the heat transfer tube 53 positioned at the lowermost portion of the sixth refrigerant circulation portion 56 f that is in a positional relationship facing the refrigerant outlet 70 is opened in the second region 74.

  As shown in FIG. 13, the second turn portion 65b is an element that connects the downstream end of the second heat exchange region 61b and the upstream end of the third heat exchange region 61c, Similar to the turn portion 65a, an outlet pipe 66, an inlet pipe 67, and a U vent 68 are provided.

  The outlet pipe 66 has a refrigerant inlet 69 connected to the second refrigerant circulation part 56b located at the downstream end of the second heat exchange region 61b. The refrigerant inlet 69 is opened to the upper part of the second refrigerant circulation part 56b from the direction facing the first opening end 60a of the heat transfer tube 53.

  The inlet pipe 67 has a refrigerant outlet 70 connected to the third refrigerant circulation portion 56c located at the upstream end of the third heat exchange region 61c. The refrigerant outlet 70 is a third refrigerant from the direction facing the first opening end 60a of the heat transfer tube 53 below the intermediate portion along the height direction of the third refrigerant circulation portion 56c of the first header 51. It opens to the inside of the circulation part 56c.

  According to this embodiment, the refrigerant outlet 70 of the inlet pipe 67 includes the first open end 60a of the heat transfer pipe 53 closest to the partition plate 55 serving as the bottom of the third refrigerant circulation portion 56c, and the top of the heat transfer pipe 53. It is located between the first open end 60a of the other heat transfer tube 53. Therefore, the refrigerant outlet 70 is opened inside the third refrigerant circulation part 56c between the first opening ends 60a of the two heat transfer tubes 53 adjacent at the lowermost part of the third refrigerant circulation part 56c. .

  Further, the center line A5 extending horizontally through the center O5 of the refrigerant outlet 70 of the inlet pipe 67 passes through the intermediate point O6 of the two heat transfer pipes 53 adjacent at the lowermost part of the third refrigerant circulation portion 56c. It is located slightly below the reference line A6 extending in the direction. Therefore, the center O5 of the refrigerant outlet 70 and the intermediate point O6 between the two adjacent heat transfer tubes 53 are separated by a distance L4 along the height direction of the first header 51.

  The outlet pipe 66 and the inlet pipe 67 protrude horizontally toward the outer side of the first header 51. The U vent 68 connects between the protruding end of the outlet pipe 66 and the protruding end of the inlet pipe 67.

  As shown in FIG. 13, the barrier 76 is provided inside the third refrigerant circulation portion 56 c. The barrier 76 is erected in the vertical direction from the partition plate 55 serving as the bottom of the third refrigerant circulation portion 56c. According to the present embodiment, the barrier 76 is interposed between the first open end 60 a of the heat transfer tube 53 closest to the bottom of the third refrigerant circulation portion 56 c and the refrigerant outlet 70 of the inlet pipe 67.

  The upper end edge 76a of the barrier 76 extends in a straight line in the horizontal direction. The upper end edge 76a of the barrier 76 is positioned between the inner peripheral lower end of the refrigerant outlet 70 and the inner peripheral upper end of the refrigerant outlet 70 as a preferred example, and extends horizontally through the center O5 of the refrigerant outlet 70. It protrudes upwards. As a result, the barrier 76 has a height dimension H so as to face most of the refrigerant outlet 70 opened in the third refrigerant circulation portion 56c.

  The barrier 76 is formed wider than the diameter D5 of the refrigerant outlet 70. Furthermore, both side portions along the width direction of the barrier 76 are abutted against the inner peripheral surface of the first header 51. For this reason, the lowermost part of the third refrigerant circulation part 56 c is partitioned into a first region 77 and a second region 78 by the barrier 76. The refrigerant outlet 70 is opened in the first region 77. A first opening end 60 a of the heat transfer tube 53 positioned at the lowermost portion of the third refrigerant circulation portion 56 c that is in a positional relationship facing the refrigerant outlet 70 is opened in the second region 78.

  As shown in FIG. 11, the third turn part 65c is located at the upstream end of the seventh refrigerant circulation part 56g and the fourth heat exchange area 61d located at the downstream end of the third heat exchange area 61c. Eight refrigerant circulation portions 56h are connected to each other, and an outlet pipe 66, an inlet pipe 67, and a U vent 68 are provided in the same manner as the first turn portion 65a.

  Since the positional relationship between the inlet pipe 67 and the two heat transfer pipes 53 adjacent to each other at the lowermost part of the eighth refrigerant circulation part 56h is the same as that of the first turn part 65a, the description thereof is omitted. Further, the barrier 80 is erected in the vertical direction from the partition plate 57 which becomes the bottom of the eighth refrigerant circulation portion 56h. The positional relationship between the barrier 80 and the inlet pipe 67 and the positional relationship between the barrier 80 and the heat transfer pipe 53 closest to the bottom of the eighth refrigerant circulation portion 56h are the same as the contents disclosed in FIG. Is omitted.

  According to the third embodiment, when the parallel flow heat exchanger 50 functions as an evaporator, a low-temperature, low-pressure gas-liquid two-phase refrigerant flows into the first heat exchange region 61a from the first connection pipe 62. The first heat exchange region 61a flows from the left to the right in FIG.

  The gas-liquid two-phase refrigerant that has passed through the first heat exchange region 61a is reversed by 180 ° in the flow direction at the first turn part 65a, and then flows into the second heat exchange region 61b, where the second heat exchange is performed. The region 61b flows from the right to the left in FIG.

  The gas-liquid two-phase refrigerant that has passed through the second heat exchange region 61b is reversed by 180 ° again in the flow direction at the second turn portion 65b, and then flows into the third heat exchange region 61c, where the third heat The exchange area 61c flows from the left to the right in FIG.

  Furthermore, the gas-liquid two-phase refrigerant that has passed through the third heat exchange region 61b is reversed by 180 ° again in the flow direction at the third turn portion 65c, and then flows into the fourth heat exchange region 61d. The heat exchange region 61d flows from the right to the left in FIG.

  For this reason, the gas-liquid two-phase refrigerant that has flowed into the first heat exchange region 61a changes to a gas-phase refrigerant in the process of passing through the first to fourth heat exchange regions 61a, 61b, 61c, 61d, From the connecting pipe 63.

  Since the gas-liquid two-phase refrigerant that has passed through the first heat exchange region 61a flows into the second heat exchange region 61b through the first turn part 65a, the gas-liquid two-phase refrigerant is affected by gravity. The liquid-phase refrigerant contained in the gas-liquid two-phase refrigerant concentrates in the lower part of the sixth refrigerant circulation part 56f. The gas-phase refrigerant separated from the liquid-phase refrigerant rises from the lower part to the upper part of the sixth refrigerant circulation part 56f.

  According to the third embodiment, the barrier 72 rising from the bottom of the sixth refrigerant circulation part 56f is the refrigerant outlet 70 of the inlet pipe 67 and the first of the heat transfer pipes 53 positioned at the lowermost part of the sixth refrigerant circulation part 56f. 2 and the upper end of the barrier wall 72 faces most of the refrigerant outlet 70.

  For this reason, as indicated by arrows in FIG. 12, most of the main flow of the liquid-phase refrigerant flowing from the refrigerant outlet 70 into the sixth refrigerant circulation portion 56f collides with the barrier 72 and is guided by the barrier 72 to be antigravity. Blow up in the direction.

  Therefore, the liquid-phase refrigerant flowing from the refrigerant outlet 70 into the sixth refrigerant circulation part 56f can be actively guided toward the upper side of the sixth refrigerant circulation part 56f against gravity, and separated from the refrigerant outlet 70. In addition, a large amount of liquid refrigerant can be distributed to the second open ends 60b of the plurality of heat transfer tubes 53 located in the middle part or upper part of the sixth refrigerant circulation part 56f.

  Moreover, the flow of the liquid-phase refrigerant from the refrigerant outlet 70 toward the second opening end 60 b of the heat transfer tube 53 is blocked by the barrier 72 at the lower part of the sixth refrigerant circulation portion 56 f. At the same time, a part of the liquid-phase refrigerant blocked by the barrier 72 flows into the second region 74 where the second opening end 60b of the heat transfer tube 53 is opened only when it passes over the upper edge 72a of the barrier 72. The barrier 72 prevents the liquid phase refrigerant from being excessively supplied to the heat transfer tubes 53 that are in a positional relationship facing the refrigerant outlet 70.

  Therefore, variations in the supply amount of the liquid phase refrigerant distributed from the sixth refrigerant circulation portion 56f to the plurality of heat transfer tubes 53 so that the supply amount of the liquid phase refrigerant to the specific heat transfer tube 53 is not extremely short. Can be reduced.

  Such control of the flow of the liquid-phase refrigerant is performed when the gas-liquid two-phase refrigerant flows from the second heat exchange region 61b into the third heat exchange region 61c via the second turn part 65b, and the gas-liquid The same process is performed when the two-phase refrigerant flows from the third heat exchange region 61c into the fourth heat exchange region 61d through the third turn portion 65c.

  As a result, in each of the second to fourth heat exchange regions 61b, 61c, 61d, it becomes possible to distribute the liquid-phase refrigerant to the plurality of heat transfer tubes 53 without excess or deficiency. Heat exchange performance is improved.

  Although several embodiments of the present invention have been described, these embodiments are presented by way of example and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the claims and the equivalents thereof.

  In the first embodiment, the refrigerant outlet of the first connection pipe is located between the first open ends of the two heat transfer pipes located at the lowermost part of the refrigerant inflow portion, but is not limited thereto. It is not something. If the refrigerant outlet is below the intermediate part along the height direction of the refrigerant inflow part, for example, it is positioned between the first open ends of the fourth and fifth heat transfer tubes counting from the bottom of the refrigerant inflow part. May be.

  That is, the position of the refrigerant outlet may be appropriately set according to the height of the refrigerant inflow portion, and the position of the refrigerant outlet is not particularly limited.

  Further, the position of the upper edge of the barrier may be adjusted according to the arrangement interval of the heat transfer tubes or the position of the refrigerant outlet, and the position of the upper edge of the barrier is not particularly limited. At the same time, the barrier need not be erected along the vertical direction, and the barrier may be inclined toward the refrigerant outlet or the first opening end.

  In addition, in the said embodiment, although both the outdoor heat exchanger and the indoor heat exchanger were comprised with the parallel flow type heat exchanger which has a barrier, only one heat exchanger has the parallel flow type heat exchange which has a barrier. You may comprise with a vessel.

  DESCRIPTION OF SYMBOLS 2 ... Compressor (sealed type compressor), 4 ... Heat source side heat exchanger (outdoor heat exchanger), 5 ... Expansion device, 6 ... Usage side heat exchanger (indoor heat exchanger), 7 ... Circulation circuit, 10 , 50 ... parallel flow type heat exchanger, 13, 53 ... heat transfer tubes, 16, 56a, 56b, 56c, 56d, 56e, 56f, 56g, 56h ... refrigerant circulation part (refrigerant inflow part, first to eighth refrigerants) (Circulation part), 17 ... refrigerant outflow part, 18a, 18b, 60a, 60b ... opening end (first opening end, second opening end), 20, 67 ... inlet pipe (first connection pipe), 22, 70: Refrigerant outlet, 23, 72, 76, 78, 80 ... Barrier.

Claims (6)

A standing tubular refrigerant circulation section;
A plurality of heat transfer tubes branched laterally from the refrigerant circulation part and arranged at intervals in the height direction of the refrigerant circulation part and having an open end opened inside the refrigerant circulation part; ,
An inlet pipe that is connected to the refrigerant circulation part and guides the refrigerant containing the liquid phase refrigerant to the refrigerant circulation part,
The inlet pipe has a refrigerant outlet that is opened to the inside of the refrigerant circulation part from a direction facing the opening end of the heat transfer pipe below the intermediate part along the height direction of the refrigerant circulation part.
A heat exchanger having a barrier provided inside the refrigerant circulation part so as to face the refrigerant outlet of the inlet pipe.   The refrigerant outlet of the inlet pipe is opened to the inside of the refrigerant circulation part between the opening ends of the two heat transfer pipes adjacent at the lowermost part in the height direction of the refrigerant circulation part, 2. The heat exchanger according to claim 1, wherein the center of the refrigerant outlet is positioned below an intermediate point between the two heat transfer tubes adjacent in the height direction of the refrigerant circulation portion.   The said barrier stands up from the bottom of the said refrigerant | coolant circulation part, The upper end edge of the said barrier is located between the inner peripheral lower end of the said refrigerant | coolant outlet, and the inner peripheral upper end of the said refrigerant | coolant outlet. Item 3. The heat exchanger according to Item 2.   The barrier includes a first region where the refrigerant outlet is opened inside the refrigerant circulation portion and a second region where the opening end of the heat transfer tube which is in a positional relationship facing the refrigerant outlet is opened. The heat exchanger according to any one of claims 1 to 3, wherein the heat exchanger is partitioned.   The heat exchanger according to claim 1, wherein the barrier is wider than an inner diameter of the refrigerant outlet of the inlet pipe.   The refrigerant circulates and has a circulation circuit to which a compressor, a heat source side heat exchanger, an expansion device, and a use side heat exchanger are connected, and at least one of the heat source side heat exchanger and the use side heat exchanger is A refrigeration cycle apparatus comprising the heat exchanger according to any one of claims 1 to 5.

Images