JPWO2017221401A1 - Heat exchanger and refrigeration cycle apparatus provided with refrigerant branching distributor - Google Patents

Abstract

  The refrigeration cycle apparatus (1) is provided with a branch distribution unit (11) for branching a two-phase refrigerant of a liquid refrigerant and a gas refrigerant into refrigerants having different liquid ratios. The branch distributor (11) includes a pipe (41) including a bent pipe (33), a branch pipe (31), a pipe (43), and a pipe (44). The refrigerant that has flowed through the pipe (41) flows through the bent pipe (33) and the branch pipe (31), and is distributed to a refrigerant having a high liquid ratio and a refrigerant having a low liquid ratio. The refrigerant having a high liquid ratio flows through the pipe (47) and is sent to the heat exchanger (7a) having a large air volume. The refrigerant having a low liquid ratio flows through the pipe (48) and is sent to the heat exchanger (7b) having a small air volume.

Description

  The present invention relates to a refrigerant branching distributor, a heat exchanger including the refrigerant, and a refrigeration cycle apparatus, and more particularly, a refrigerant branching distributor capable of branching a two-phase refrigerant of a liquid refrigerant and a gas refrigerant into refrigerants having different liquid ratios. And a heat exchanger including the refrigerant branching distributor and a refrigeration cycle apparatus including the heat exchanger.

  In recent years, in a heat pump device or a car air conditioner as an air conditioner (refrigeration cycle device), in order to improve heat exchange efficiency and to reduce the charging amount of refrigerant, The flattening of heat transfer tubes is being promoted. By reducing the diameter of the heat transfer tube, the pressure loss in the flow path increases. In order to reduce the pressure loss, many heat exchangers with an increased number of refrigerant paths have been commercialized.

  In general, when a heat exchanger is used to lower the temperature of air, the heat exchanger functions as an evaporator. The refrigerant flows into the heat exchanger as the evaporator in a gas-liquid two-phase flow state in which a gas refrigerant and a liquid refrigerant are mixed. The density of the gas refrigerant and the liquid refrigerant differ by several tens of times.

  Of the two-phase refrigerant flowing into the heat exchanger, the liquid refrigerant mainly absorbs the heat of the air and evaporates to become a gas refrigerant. Thereby, a gas refrigerant (single phase) is sent out from the heat exchanger. The air passing through the heat exchanger becomes cold due to the loss of latent heat (heat of evaporation) when the liquid refrigerant undergoes a phase change.

  In the heat exchanger, there are a portion where the amount of air flowing through the heat exchanger is large and a portion where the air volume is small. Corresponding heat exchange is performed between the portion of the heat exchanger with a large air volume and the portion of the heat exchanger with a small air volume, and the heat exchanger portion with a larger air volume performs heat exchange more efficiently.

  There is a density difference between the density of the gas refrigerant and the density of the liquid refrigerant, and the liquid refrigerant having a higher density is likely to flow into a lower path in the heat exchanger. For this reason, more liquid refrigerant may flow through the heat exchanger where the air volume is small. In such a case, the liquid refrigerant remains without being completely evaporated, and the refrigerant is sent out from the heat exchanger in a two-phase state of the liquid refrigerant and the gas refrigerant. As a result, there exists a problem that the heat exchange rate in a heat exchanger will fall.

  In order to solve such problems, various improvement proposals have been proposed. For example, in patent document 1, the proposal regarding the path | route of a heat exchanger is made | formed. In patent document 2, the proposal regarding the refrigerant distributor which divides a refrigerant | coolant is made | formed.

Japanese Patent Laying-Open No. 2015-87074 JP 2014-25660 A

  Conventionally, when a heat exchanger is used as an evaporator, it is required to efficiently exchange heat between air and the like in a two-phase refrigerant consisting of a liquid refrigerant and a gas refrigerant.

  The present invention has been made as part of such development, and one object is to provide a refrigerant branch distributor that efficiently exchanges heat between two-phase refrigerants, and another object is to It is providing the heat exchanger provided with such a refrigerant | coolant branch distributor, and the other objective is to provide the refrigerating-cycle apparatus provided with such a heat exchanger.

  The refrigerant distributor according to the present invention includes a first flow path, a second flow path, a third flow path, and a branch portion. The branch portion is connected to the first flow path, is connected to the second flow path and the third flow path, and the refrigerant including the liquid refrigerant and the gas refrigerant flowing in from the first flow path is supplied to the second flow path. And the third flow path. The ratio of the liquid refrigerant in the weight ratio between the liquid refrigerant and the gas refrigerant is defined as the liquid ratio. The first liquid ratio of the first refrigerant branched into the second flow path is higher than the second liquid ratio of the second refrigerant branched into the third flow path.

  The heat exchanger which concerns on this invention is a heat exchanger provided with the said refrigerant | coolant branch distributor, and is provided with the 1st heat exchanger and the 2nd heat exchanger. In the first heat exchanger, heat is exchanged between the refrigerant and the first fluid. In the second heat exchanger, heat exchange is performed between the refrigerant and the second fluid. The amount of the first fluid is greater than the amount of the second fluid. The second flow path is connected to the first heat exchanger. The third flow path is connected to the second heat exchanger.

  The refrigeration cycle apparatus according to the present invention is a refrigeration cycle apparatus provided with the heat exchanger.

  According to the refrigerant branching and distributing device according to the present invention, the first refrigerant having a high liquid ratio is positively sent to the second flow path, and the second refrigerant third flow path having a low liquid ratio is positively sent to efficiently. Heat exchange can be performed.

  According to the heat exchanger according to the present invention, the second flow path of the refrigerant branching distributor is connected to the first heat exchanger, and the third flow path is connected to the second heat exchanger. Thereby, in a 2nd heat exchanger, heat exchange is performed between the 2nd refrigerant | coolant and 2nd fluid with a low liquid ratio. In the first heat exchanger, heat exchange is performed between the first refrigerant having a high liquid ratio and the first fluid larger than the amount of the second fluid. As a result, the second refrigerant having a high liquid ratio can be efficiently heat-exchanged.

  According to the refrigeration cycle apparatus according to the present invention, the heat exchange of the refrigerant can be efficiently performed by providing the heat exchanger.

It is a figure which shows the structure of the refrigerating-cycle apparatus which has an outdoor unit provided with the refrigerant distributor which concerns on Embodiment 1. FIG. In the embodiment, it is a perspective view which shows an outdoor unit. In the same embodiment, it is a perspective view which shows an example of the relationship between the air volume sent into an outdoor heat exchanger, and a heat exchanger. In the embodiment, it is a figure which shows an example of the routing structure of the heat exchanger tube in a part of outdoor heat exchanger, and an example of the connection relation of a part of outdoor heat exchanger and a branch distribution part. In the embodiment, it is a figure which shows an example of the connection relation of an outdoor heat exchanger and a branch distribution part. In the same embodiment, it is a fragmentary figure which shows the branch distribution part arrange | positioned at the outdoor unit. FIG. 7 is a cross-sectional view showing an example of a distribution of refrigerant in a pipe taken along a cross-sectional line VII-VII shown in FIG. 6 in the same embodiment. FIG. 10 is a partial view showing a refrigerant distributor including a branch distribution unit arranged in an outdoor unit according to the second embodiment. FIG. 9 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line IX-IX shown in FIG. 8 in the same embodiment. FIG. 9 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe at the cross-sectional line XX shown in FIG. 8 in the same embodiment. FIG. 9 is a cross-sectional view showing an example of the distribution of refrigerant in the pipe taken along a cross-sectional line XI-XI shown in FIG. 8 in the same embodiment. FIG. 9 is a cross-sectional view showing an example of a distribution of refrigerant in a pipe taken along a cross-sectional line XII-XII shown in FIG. 8 in the same embodiment. In the same embodiment, it is a fragmentary figure which shows the branch distribution part arrange | positioned at the outdoor unit based on a modification. FIG. 14 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XIV-XIV shown in FIG. 13 in the same embodiment. FIG. 14 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XV-XV shown in FIG. 13 in the same embodiment. FIG. 14 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XVI-XVI shown in FIG. 13 in the same embodiment. FIG. 14 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XVII-XVII shown in FIG. 13 in the same embodiment. It is a fragmentary figure which shows the branch distribution part arrange | positioned at the outdoor unit based on Embodiment 3. FIG. FIG. 19 is a cross-sectional view taken along a cross-sectional line XIX-XIX shown in FIG. 18, of the orifice according to the first example used for the branch distribution unit in the same embodiment. FIG. 19 is a cross-sectional view taken along a cross-sectional line XIX-XIX shown in FIG. 18, of an orifice according to a second example used for the branch distribution unit in the same embodiment. FIG. 19 is a cross-sectional view taken along a cross-sectional line XIX-XIX shown in FIG. 18, of an orifice according to a third example used for the branch distribution unit in the same embodiment. In the embodiment, it is sectional drawing which shows an example of distribution of the refrigerant | coolant in piping in sectional line XXII-XXII shown in FIG. In the embodiment, it is sectional drawing which shows an example of distribution of the refrigerant | coolant in piping in sectional line XXIII-XXIII shown in FIG. FIG. 19 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XXIV-XXIV shown in FIG. 18 in the same embodiment. FIG. 10 is a partial view showing a refrigerant distributor including a branch distribution unit arranged in an outdoor unit according to a fourth embodiment. FIG. 26 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XXVI-XXVI shown in FIG. 25 in the same embodiment. In the embodiment, it is sectional drawing which shows an example of distribution of the refrigerant | coolant in piping in sectional line XXVII-XXVII shown in FIG. In the embodiment, it is sectional drawing which shows an example of distribution of the refrigerant | coolant in piping in sectional line XXVIII-XXVIII shown in FIG. FIG. 26 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XXIX-XXIX shown in FIG. 25 in the same embodiment. FIG. 26 is a cross-sectional view showing an example of a distribution of refrigerant in a pipe taken along a cross-sectional line XXX-XXX shown in FIG. 25 in the same embodiment. FIG. 26 is a cross-sectional view showing an example of a refrigerant distribution in a pipe taken along a cross-sectional line XXXI-XXXI shown in FIG. 25 in the embodiment. FIG. 26 is a cross-sectional view showing an example of a refrigerant distribution in a pipe taken along a cross-sectional line XXXII-XXXII shown in FIG. 25 in the same embodiment. In the same embodiment, it is a fragmentary figure which shows the branch distribution part arrange | positioned at the outdoor unit based on a modification. FIG. 34 is a cross-sectional view showing an example of a distribution of refrigerant in the pipe taken along a cross-sectional line XXXIV-XXXIV shown in FIG. 33 in the same embodiment. FIG. 34 is a cross-sectional view showing an example of a distribution of refrigerant in the pipe taken along a cross-sectional line XXXV-XXXV shown in FIG. 33 in the same embodiment. FIG. 34 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XXXVI-XXXVI shown in FIG. 33 in the same embodiment. FIG. 34 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XXXVII-XXXVII shown in FIG. 33 in the same embodiment. In the embodiment, it is sectional drawing which shows an example of distribution of the refrigerant | coolant in piping in sectional line XXXVIII-XXXVIII shown in FIG. FIG. 34 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XXXIX-XXXIX shown in FIG. 33 in the same embodiment. FIG. 34 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XL-XL shown in FIG. 33 in the same embodiment. It is a fragmentary figure which shows the branch distribution part arrange | positioned at the outdoor unit based on Embodiment 5. FIG. In the embodiment, it is sectional drawing which shows an example of distribution of the refrigerant | coolant in piping in sectional line XLII-XLII shown in FIG. In the embodiment, it is sectional drawing which shows an example of distribution of the refrigerant | coolant in piping in sectional line XLIII-XLIII shown in FIG. In the embodiment, it is sectional drawing which shows an example of distribution of the refrigerant | coolant in piping in sectional line XLIV-XLIV shown in FIG. In the embodiment, it is sectional drawing which shows an example of distribution of the refrigerant | coolant in piping in sectional line XLV-XLV shown in FIG. In the embodiment, it is sectional drawing which shows an example of distribution of the refrigerant | coolant in piping in sectional line XLVI-XLVI shown in FIG. In the embodiment, it is sectional drawing which shows an example of distribution of the refrigerant | coolant in piping in sectional line XLVII-XLVII shown in FIG. In the embodiment, it is sectional drawing which shows an example of distribution of the refrigerant | coolant in piping in sectional line XLVIII-XLVIII shown in FIG.

Embodiment 1 FIG.
A refrigeration cycle apparatus including the refrigerant distributor according to Embodiment 1 will be described. First, the configuration of the refrigeration cycle apparatus will be described. Here, a building multi-air conditioner is taken as an example of the refrigeration cycle apparatus.

  As shown in FIG. 1, in the building multi-air conditioner as the refrigeration cycle apparatus 1, a plurality of indoor heat exchangers 15 a, 15 b, 15 c, 15 d (15) are connected to one outdoor heat exchanger 7. . In addition to the outdoor heat exchanger 7 and the indoor heat exchanger 15, the refrigeration cycle apparatus 1 includes a compressor 3, four-way valves 5a and 5b, indoor fans 19a, 19b, 19c and 19d, expansion valves 13a, 13b and 13c, 13d, expansion valves 9a and 9b, refrigerant distributors 21a and 21b, an outdoor fan 17 and an accumulator 23.

  Further, in the refrigeration cycle apparatus 1, the branch distribution unit 11 is provided between the refrigerant distributors 21 a and 21 b and the expansion valve 13. The branch distribution unit 11 will be described later. In addition, the expansion valves 9a and 9b provided between the branch distribution unit 11 and the refrigerant distributors 21a and 21b are not essential, and are provided as necessary.

  Next, heating operation will be described as the operation of the building multi-air conditioner. By driving the compressor 3, high-temperature and high-pressure gaseous refrigerant is discharged from the compressor 3. The discharged high-temperature and high-pressure gas refrigerant (single phase) passes through the four-way valves 5a and 5b and flows into each of the plurality of indoor heat exchangers 15a, 15b, 15c and 15d.

  Air is sent into each of the indoor heat exchangers 15a to 15d by indoor fans 19a, 19b, 19c, and 19d. In each of the indoor heat exchangers 15a to 15d, heat exchange is performed between the fed air and the flowing gas refrigerant, and the high-temperature and high-pressure gas refrigerant is condensed to a high-pressure liquid refrigerant (single phase). Become. By this heat exchange, each room in which the indoor heat exchangers 15a to 15d are arranged is heated.

  Next, the high-pressure liquid refrigerant sent out from the indoor heat exchangers 15a to 15d passes through the expansion valves 13a, 13b, 13c, and 13d, so that it becomes a two-phase refrigerant of low-pressure gas refrigerant and liquid refrigerant. Become.

  The refrigerant in the two-phase state flows into the outdoor unit 25. The refrigerant in the two-phase state that has flowed into the outdoor unit 25 is branched into two in the branch distribution unit 11. Of the two branched refrigerants, one refrigerant (refrigerant A) flows through the piping 47 through the expansion valve 9a and the refrigerant distributor 21a and into the outdoor heat exchanger 7a. Of the two branched refrigerants, the other refrigerant (refrigerant B) flows through the expansion valve 9b and the refrigerant distributor 21b through the pipe 48 and into the outdoor heat exchanger 7b.

  In the outdoor heat exchangers 7a and 7b, heat exchange is performed between the air sent by the outdoor fan 17 and the flowing refrigerant (refrigerant A and refrigerant B), and the liquid refrigerant of the two-phase refrigerant is Evaporates into a low-pressure gas refrigerant (single phase). The low-pressure gas refrigerant sent out from the outdoor unit 25 flows into the compressor 3 through the four-way valves 5a and 5b and the accumulator 23. The low-pressure gas refrigerant that has flowed into the compressor 3 is compressed to become a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 3 again. Thereafter, this cycle is repeated.

  Next, the cooling operation will be described. The high-temperature and high-pressure gas refrigerant compressed by the compressor 3 passes through the four-way valves 5a and 5b and flows into the outdoor heat exchangers 7a and 7b. In the outdoor heat exchangers 7a and 7b, heat exchange is performed between the air sent by the outdoor fan 17 and the gas refrigerant flowing in, and the high-temperature and high-pressure gas refrigerant is condensed to a low-temperature and high-pressure liquid refrigerant (simple Phase).

  The low-temperature and high-pressure liquid refrigerant becomes a low-temperature and low-pressure liquid refrigerant by passing through the expansion valves 13a to 13d and the like. The low-temperature and low-pressure liquid refrigerant flows into each of the plurality of indoor heat exchangers 15a to 15d. In the indoor heat exchangers 15a to 15d, heat exchange is performed between the air sent by the indoor fans 19a to 19d and the flowing liquid refrigerant, and the low-temperature and low-pressure liquid refrigerant evaporates to form a low-pressure gas refrigerant ( Single phase). By this heat exchange, each of the rooms where the indoor heat exchangers 15a to 15d are arranged is cooled.

  The low-pressure gas refrigerant sent out from the indoor heat exchangers 15a to 15d flows into the compressor 3 through the four-way valves 5a and 5b and the accumulator 23. The low-pressure gas refrigerant flowing into the compressor is compressed to become a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor again. Thereafter, this cycle is repeated.

  In the refrigeration cycle apparatus 1 described above, the outdoor heat exchanger 7 of the outdoor unit 25 functions as an evaporator in the heating operation and functions as a condenser in the cooling operation. As an outdoor unit of a building multi air conditioner, there is an outdoor unit having a top flow type fan. As shown in FIG. 2, in the top-flow type outdoor unit 25, the outdoor fan 17 is attached to the upper surface portion of the housing 26.

  Of the four side surfaces of the housing, three side surfaces (three sides) are provided with air intakes 27 for taking in air. As shown in FIG. 3, the outdoor heat exchanger 7 is disposed in the casing 26. The outdoor heat exchanger 7 is disposed so as to face three air intake ports (side surfaces of the housing). In addition, in the casing 26, a branching / distributing unit 11, a compressor (not shown), and the like are arranged.

  In the outdoor unit 25 described above, the outdoor fan 17 is attached to the upper surface portion of the housing 26. Therefore, in the outdoor heat exchanger 7, the air pressure loss decreases as the distance from the outdoor fan 17 decreases, and the air pressure loss increases as the distance from the outdoor fan 17 increases. That is, the pressure loss gradually increases from the upper part to the lower part of the outdoor heat exchanger 7, the air volume passing through the outdoor heat exchanger 7a is relatively large, and the air volume passing through the outdoor heat exchanger 7b. Is relatively small (see arrows in FIG. 3).

  An example of the connection relationship between the outdoor heat exchanger 7a and the piping is shown in FIG. As shown in FIG. 4, the outdoor heat exchanger 7a is composed of, for example, three rows of outdoor heat exchangers 7aa, 7ab, and 7ac. A heat transfer tube (not shown) is attached to each of the three rows of outdoor heat exchangers 7aa, 7ab, 7ac. The plurality of pipes 47 branched from the refrigerant distributor 21a are connected to the corresponding heat transfer tubes of the outdoor heat exchanger 7a in the first row.

  One refrigerant path passes from the heat transfer tube of the outdoor heat exchanger 7aa in the first row to the heat transfer tube of the outdoor heat exchanger 7ab in the second row and the heat transfer tube of the outdoor heat exchanger 7ac in the third row. It is connected to. As shown in FIGS. 1 and 3, a plurality of pipes 48 branched from the refrigerant distributor 21b are also connected to the outdoor heat exchanger 7b disposed below the outdoor heat exchanger 7a (see FIG. 5). ).

  When the outdoor heat exchanger 7 is caused to function as an evaporator, in order to efficiently evaporate the liquid refrigerant out of the two-phase refrigerant into a gas refrigerant, the outdoor heat exchanger 7a having a larger air volume is sent to the outdoor heat exchanger 7a. It is required to flow. Therefore, as shown in FIG. 5, the branch distribution unit 11 is provided in the outdoor unit 25.

  In the branch distribution unit 11, during the heating operation, the two-phase refrigerant flowing from the indoor heat exchanger 15 is branched into two systems of refrigerant (refrigerant A and refrigerant B). In the weight ratio between the liquid refrigerant and the gas refrigerant, the ratio of the liquid refrigerant is the liquid ratio. The refrigerant A is a refrigerant with a high liquid ratio. The refrigerant B is a refrigerant with a low liquid ratio. In the branch distribution unit 11, the refrigerant is distributed macroscopically into the refrigerant A having a high liquid ratio and the refrigerant B having a low liquid ratio. The refrigerant A is further microscopically distributed by the refrigerant distributor 21a and sent to the outdoor heat exchanger 7a having a large air volume. The refrigerant B is further microscopically distributed by the refrigerant distributor 21b and sent to the outdoor heat exchanger 7b having a small air volume.

  A first example of a specific structure of the branching / distributing unit 11 will be described. As shown in FIG. 6, the branch distributor 11 includes a pipe 41 (first flow path) including a bent pipe 33, a branch pipe 31 (branch section), a pipe 43 (second flow path), and a pipe 44 (third flow). Road). The refrigerant in the two-phase state that has flowed through the pipe 41 flows through the bent pipe 33, thereby causing an uneven distribution of the liquid refrigerant. That is, the amount of liquid refrigerant flowing along the inner wall surface on the outer peripheral side of the bent pipe 33 is larger than the amount of liquid refrigerant flowing along the inner wall surface on the inner peripheral side due to the centrifugal force.

  Thereby, in the pipe 41 immediately after flowing through the bent pipe 33, the refrigerant (refrigerant A) having a high liquid ratio flows in a region corresponding to the outer peripheral side of the bent pipe 33, and corresponds to the inner peripheral side of the bent pipe 33. A refrigerant having a low liquid ratio (refrigerant B) flows in the region. The refrigerant that has flowed through the pipe 41 in this state is distributed to the refrigerant A and the refrigerant B by the branch pipe 31. The distributed refrigerant A flows through the pipe 43, the refrigerant distributor 21a and the pipe 47 and is sent to the outdoor heat exchanger 7a. On the other hand, the refrigerant B flows through the pipe 45, the refrigerant distributor 21b, and the pipe 48 and is sent to the outdoor heat exchanger 7b.

  Thus, in the outdoor unit 25, the refrigerant A having a high liquid ratio flows into the outdoor heat exchanger 7a having a larger air volume, and the refrigerant B having a low liquid ratio flows into the outdoor heat exchanger 7b having a smaller air volume. Thereby, heat exchange between the two-phase refrigerant and the air can be performed efficiently.

  Conventionally, pressure loss is adjusted by changing the length of piping connected to the outdoor heat exchangers 7a and 7b, the inner diameter of the piping, or the like as a method of flowing a refrigerant having a high liquid ratio to the outdoor heat exchanger 7a having a larger air volume. There is a technique. That is, there is a technique for distributing the refrigerant microscopically. However, with this method, as the number of pipes increases, it becomes difficult to adjust the length of the pipes. Moreover, the area | region for routing piping is also needed. Furthermore, the routing of the piping is complicated.

  In contrast to such a method, in the method using the branch distribution unit 11 described above, a refrigerant having a high liquid ratio to the outdoor heat exchanger 7a having a simple structure and a larger air volume is formed by only the bent pipe 33 and the branch pipe 31. Can be sent in.

  Of the pipe 41, the length L of the straight portion from the bent pipe 33 to the branch pipe 31 is a length that flows into the branch pipe 31 with an uneven distribution (see FIG. 7) in which the liquid refrigerant in the pipe 41 is biased. It is necessary to set it. Here, when the inner diameter φ of the bent pipe is D, the length L of the straight portion needs to satisfy the relationship L <10 × D. When the length L of the straight line portion is L ≧ 10 × D, the liquid refrigerant returns to a state in which the liquid refrigerant is distributed almost uniformly and annularly on the inner wall of the pipe 41 from the uneven distribution of the liquid refrigerant. . For this reason, it becomes impossible to send more liquid refrigerant into the outdoor heat exchanger 7a.

  Further, expansion valves 9a and 9b may be provided between the refrigerant distributors 21a and 21b and the branch distributor 11 as shown in FIG. In particular, it is possible to prevent excessive liquid refrigerant from flowing into the pipe 43 by adjusting the opening degree of the expansion valve 9a.

Embodiment 2. FIG.
Here, the 2nd example of the branch distribution part which comprises a refrigerant | coolant branch distributor is demonstrated. As shown in FIG. 8, the branch distribution unit 11 includes a T-shaped branch pipe 35 a (35) (branch portion) similar to the shape of the alphabet “T”. The T-shaped branch pipe 35a is provided with a part extending in one direction (pipe part A) and a part (pipe part B) branching from the pipe part A in a direction substantially perpendicular to the one direction. Yes.

  A pipe 43 (second flow path) including a bent pipe 33 is connected to the pipe portion A. The refrigerant distributor 21a is connected to the pipe 43, and a plurality of pipes 47 are connected to the refrigerant distributor 21a. On the other hand, a pipe 44 (third flow path) is connected to the pipe part B. The refrigerant distributor 21b is connected to the pipe 44, and a plurality of pipes 48 are connected to the refrigerant distributor 21b. The plurality of pipes 47 are connected to the outdoor heat exchanger 7a, and the plurality of pipes 48 are connected to the outdoor heat exchanger 7b (see FIG. 3).

  Since the configuration of the outdoor unit and the configuration of the refrigeration cycle apparatus other than the above are the same as those shown in FIGS. 1 and 3, the description thereof will not be repeated unless necessary.

  In the branch distribution unit 11 described above, when the two-phase refrigerant flowing through the pipe 41 (first flow path) flows into the T-shaped branch pipe 35a, the pipe part A extending in one direction due to inertia. Will cause more liquid refrigerant to flow. As a result, as shown in FIG. 9, the refrigerant (refrigerant A) having a high liquid ratio flows into the pipe 43 connected to the pipe portion A.

  On the other hand, more gas refrigerant flows through the pipe part B branched from the pipe part A. Thereby, as shown in FIG. 10, the refrigerant (refrigerant B) having a low liquid ratio flows into the pipe 44 connected to the pipe portion B.

  The two-phase refrigerant (refrigerant A) having a high liquid ratio flowing through the pipe 43 flows through the bent pipe 33. At this time, the distribution of the liquid refrigerant contained in the refrigerant A is biased. In other words, as described above, the amount of liquid refrigerant flowing along the inner wall surface on the outer peripheral side of the bent pipe 33 becomes larger than the amount of liquid refrigerant flowing along the inner wall surface on the inner peripheral side due to the centrifugal force.

  Accordingly, as shown in FIG. 11, in the pipe 43 immediately after flowing through the bent pipe 33, the refrigerant (refrigerant AA) having a high liquid ratio flows in the area corresponding to the outer peripheral side, and the area corresponding to the inner peripheral side. In addition, a refrigerant having a low liquid ratio (refrigerant AB) flows.

  The refrigerant (refrigerant AA, refrigerant AB) flowing through the pipe 43 flows into the refrigerant distributor 21a in that state. In the refrigerant distributor 21 a, the refrigerant that has flowed is distributed to the plurality of pipes 47. At this time, as shown in FIG. 12, among the plurality of pipes 47, the refrigerant AA having a high liquid ratio flows into the pipes 47 arranged at positions corresponding to the outer peripheral side of the bent pipes. On the other hand, the refrigerant AB having a low liquid ratio flows into the pipe 47 arranged at a position corresponding to the inner peripheral side of the bent pipe.

  The distributed refrigerant AA and refrigerant AB flow through the pipe 47 and are sent to the outdoor heat exchanger 7a. On the other hand, the refrigerant B flows through the pipe 48 and is sent to the outdoor heat exchanger 7b. Thus, in the outdoor unit 25, the refrigerant A (refrigerant AA, refrigerant AB) having a high liquid ratio flows into the outdoor heat exchanger 7a having a larger air volume, and the refrigerant having a low liquid ratio flows to the outdoor heat exchanger 7b having a smaller air volume. B will flow in.

  In particular, in the outdoor heat exchanger 7a, the refrigerant AA having a high liquid ratio is caused to flow through an upper path having a relatively large air volume in the outdoor heat exchanger 7a, and the refrigerant AB having a low liquid ratio is supplied to the outdoor heat exchanger 7a. In the lower path having a relatively small air volume (see FIG. 5). Thereby, heat exchange with a refrigerant | coolant and air can be performed more efficiently.

(Modification)
Here, a modified example of the T-shaped branch pipe will be described. As shown in FIG. 13, in the T-shaped branch pipe 35b (branch part) according to the modification, two parts (pipe part B, pipe part C) are divided from a part extending in one direction (pipe part A). ) Is provided. A pipe 45 (fourth flow path) is connected to the pipe portion C. The refrigerant distributor 21c is connected to the pipe 45, and a plurality of pipes 49 are connected to the refrigerant distributor 21c. A plurality of piping 49 is connected to outdoor heat exchanger 7b with piping 48, for example.

  In addition, about the structure of T-shaped branch piping 35b etc. other than this, it is the same as that of the structure shown in FIG. 8, and about the structure of an outdoor unit and the structure of a refrigeration cycle apparatus, the structure shown in FIG. 1 and FIG. It is the same. For this reason, the same code | symbol is attached | subjected to the same member and the description will not be repeated unless it is required.

  In the branch distribution section 11 described above, when the two-phase refrigerant that has flowed through the pipe 41 (first flow path) flows into the T-shaped branch pipe 35b, the pipe 43 (second pipe) connected to the pipe portion A. As described above, the liquid refrigerant 51 easily flows into the flow path) due to inertia, and the refrigerant (refrigerant A) having a high liquid ratio flows.

  On the other hand, the liquid refrigerant hardly flows through the pipe part B and the pipe part C branched from the pipe part A, and the refrigerant (refrigerant B) having a low liquid ratio flows. In the pipe part B and the pipe part C, the gas refrigerant easily flows into the pipe part C located on the upstream side of the refrigerant flow, and the refrigerant having a low liquid ratio flows into the pipe part C, and downstream of the refrigerant flow. A refrigerant with a high liquid ratio flows into the piping part B located.

  Thereby, as shown in FIG. 14, the refrigerant (refrigerant BB) having a low liquid ratio flows into the pipe 45 connected to the pipe portion C. As shown in FIG. 15, the refrigerant (refrigerant BA) having a high liquid ratio flows into the pipe 44 (third flow path) connected to the pipe part B.

  The refrigerant (refrigerant BB) flowing through the pipe 45 flows into the refrigerant distributor 21c. In the refrigerant distributor 21 c, the flowing refrigerant is distributed to the plurality of pipes 49. The refrigerant (refrigerant BA) flowing through the pipe 44 flows into the refrigerant distributor 21b. In the refrigerant distributor 21b, the flowing refrigerant is distributed to the plurality of pipes 48.

  As described above, the refrigerant A flowing through the pipe 43 is distributed to the plurality of pipes 47 by the refrigerant distributor 21a. As shown in FIG. 16, in the pipe 43 immediately after flowing through the bent pipe 33, the refrigerant (refrigerant AA) having a high liquid ratio flows in the area corresponding to the outer peripheral side, and the liquid corresponding to the area corresponding to the inner peripheral side. A refrigerant with a low ratio (refrigerant AB) flows.

  As shown in FIG. 17, the refrigerant AA having a high liquid ratio flows into a pipe 47 arranged at a position corresponding to the outer peripheral side of the bent pipe among the plurality of pipes 47. The refrigerant AB having a low liquid ratio flows into the pipe 47 arranged at a position corresponding to the inner peripheral side of the bent pipe. The refrigerant AA and the refrigerant AB flow through the pipe 47 and are sent to the outdoor heat exchanger 7a.

  On the other hand, the distributed refrigerant B (refrigerant BB, refrigerant BA) flows through the pipes 48 and 49 and is sent to the outdoor heat exchanger 7b. Thus, in the outdoor unit 25, the refrigerant A having a high liquid ratio flows into the outdoor heat exchanger 7a having a larger air volume, and the refrigerant B having a low liquid ratio (refrigerant BB, refrigerant BA) is supplied to the outdoor heat exchanger 7b having a smaller air volume. ) Will flow.

  In particular, in the outdoor heat exchanger 7b, the refrigerant BA having a high liquid ratio is caused to flow through the upper path having a relatively large air volume in the outdoor heat exchanger 7b, and the refrigerant BB having a low liquid ratio is supplied to the outdoor heat exchanger 7b. In the lower path having a relatively small air volume (see FIG. 5). Thereby, heat exchange with a refrigerant | coolant and air can be performed more efficiently.

Embodiment 3 FIG.
Here, the 3rd example of the branch distribution part which comprises a refrigerant | coolant branch distributor is demonstrated. As shown in FIG. 18, the branch distribution unit 11 includes an orifice 39 in the pipe 41 (first flow path) before (upstream side) the T-shaped branch pipe 35 a (35) (branch part). In the orifice 39, an opening through which the refrigerant flows is provided in a shielding part that blocks the flow of the refrigerant. The area of the opening of the orifice 39 (channel cross-sectional area) is narrower than the channel cross-sectional area of the pipe 41.

  A first example of the orifice 39 is shown in FIG. In the orifice 39, a substantially circular opening 39b is concentrically formed in a shielding part 39a that blocks the flow of the refrigerant. A second example of the orifice 39 is shown in FIG. In the orifice 39, a substantially semicircular opening 39b is formed in a shielding part 39a that blocks the flow of the refrigerant. In the orifice 39, the shielding part 39a is disposed at a circumferential position where the pipe 44 (third flow path) is connected to the T-shaped branch pipe 35a.

  A third example of the orifice 39 is shown in FIG. In the orifice 39, a substantially circular opening 39b is formed in a shielding part 39a that blocks the flow of the refrigerant. The substantially circular opening 39b is formed in the shielding part 39a so that the center of the opening 39b deviates from the center of the orifice 39. In the orifice 39, the shielding part 39a is disposed at a circumferential position where the pipe 44 is connected to the T-shaped branch pipe 35a.

  The other configurations of the T-shaped branch pipe 35a and the like are the same as those shown in FIG. 8, and the configurations of the outdoor unit and the refrigeration cycle apparatus are the configurations shown in FIGS. It is the same. For this reason, the same code | symbol is attached | subjected to the same member and the description will not be repeated unless it is required.

  In the branch distribution section 11 described above, the refrigerant in the two-phase state flowing through the pipe 41 is peeled off from the inner wall of the pipe 41 by the shielding section 39a of the orifice 39 before flowing into the T-shaped branch pipe 35a. Moreover, the flow rate of the refrigerant increases as the refrigerant passes through the opening 39b having a narrow channel cross-sectional area. This makes it easier for more liquid refrigerant to flow through the pipe portion A extending in one direction of the T-shaped branch pipe 35a. In particular, when the flow rate of the refrigerant in the two-phase state is small, the amount of liquid refrigerant flowing into the pipe portion A can be increased.

  On the other hand, the liquid refrigerant is peeled off from the inner wall of the pipe 41 in front of the pipe part B branching from the pipe part A, so that the liquid refrigerant is less likely to flow as compared with the case where there is no orifice. Gas refrigerant can easily flow. Thereby, as shown in FIG. 22, the refrigerant (refrigerant B) having a low liquid ratio flows into the pipe 44 connected to the pipe part B.

  In particular, by arranging the shielding portion 39a of the orifice 39 shown in FIG. 20 or FIG. 21 at the circumferential position where the pipe 44 is connected to the T-shaped branch pipe 35a, the amount of liquid refrigerant flowing into the pipe 44 can be reduced. The amount of liquid refrigerant flowing into the pipe 43 (second flow path) can be increased accordingly.

  As described above, the refrigerant having a high liquid ratio that has flowed into the pipe 43 flows through the bent pipe 33, so that a refrigerant having a high liquid ratio (refrigerant AA) and a refrigerant having a low liquid ratio (refrigerant) as shown in FIG. AB). The distributed refrigerant AA and refrigerant AB are further distributed by the refrigerant distributor 21a. As shown in FIG. 24, the distributed refrigerant AA and refrigerant AB flow through the pipe 47 and are sent to the outdoor heat exchanger 7a. On the other hand, the refrigerant B flows through the pipe 48 and is sent to the outdoor heat exchanger 7b. Thus, in the outdoor unit 25, heat exchange between the refrigerant and the air can be performed more efficiently.

Embodiment 4 FIG.
Here, the 4th example of the branch distribution part which comprises a refrigerant | coolant branch distributor is demonstrated. As shown in FIG. 25, the branch distribution unit 11 includes a Y-shaped branch pipe 37a (37) (branch unit) similar to the shape of the alphabet “Y”. In the Y-shaped branch pipe 37a, one pipe is bifurcated. A pipe 43 is connected to one branch pipe portion branched into two branches, and a pipe 44 is connected to the other branch pipe portion. The Y-shaped branch pipe 37a is arranged so that the pipe 43 is located below and the pipe 44 is located above. The pipes 43 and 44 include a bent pipe 33.

  Since the configuration of the outdoor unit and the configuration of the refrigeration cycle apparatus other than the above are the same as those shown in FIGS. 1 and 3, the description thereof will not be repeated unless necessary.

  In the branch distribution unit 11 described above, the two-phase refrigerant (see FIG. 26) that has flowed through the pipe 41 (first flow path) flows into the Y-shaped branch pipe 37a. The refrigerant flowing into the Y-shaped branch pipe 37a is distributed to the pipe 43 (second flow path) and the pipe 44 (third flow path). At this time, as shown in FIG. 27, the liquid refrigerant easily flows into the pipe 43 disposed below due to gravity, and the refrigerant (refrigerant A) having a high liquid ratio flows. On the other hand, as shown in FIG. 28, the liquid refrigerant is difficult to flow into the pipe 44 disposed above, and the refrigerant (refrigerant B) having a low liquid ratio flows.

  The refrigerant flowing through the pipe 43 flows through the bent pipe 33 and is further distributed by the refrigerant distributor 21a. The distributed refrigerant flows through the pipe 47 and is sent to the outdoor heat exchanger 7a. On the other hand, the refrigerant flowing through the pipe 44 flows through the bent pipe 33 and is further distributed by the refrigerant distributor 21b. The distributed refrigerant flows through the pipe 48 and is sent to the outdoor heat exchanger 7b.

  The distribution of the refrigerant in the pipe 43 immediately after flowing through the bent pipe 33 of the pipe 43 is shown in FIG. 29, and the distribution of the refrigerant in the pipe 44 immediately after flowing through the bent pipe 33 of the pipe 44 is shown in FIG. The distribution of the refrigerant in the pipe 47 is shown in FIG. 31, and the distribution of the refrigerant in the pipe 48 is shown in FIG.

  As shown in FIGS. 27 to 32, the refrigerant flowing into the Y-shaped branch pipe 37 a is distributed by the branch distributor 11 into a refrigerant with a high liquid ratio and a refrigerant with a low liquid ratio. A refrigerant with a high liquid ratio flows into the outdoor heat exchanger 7a, and a refrigerant with a low liquid ratio flows into the outdoor heat exchanger 7b.

  Thus, in the outdoor unit 25, the refrigerant A having a high liquid ratio flows into the outdoor heat exchanger 7a having a larger air volume, and the refrigerant B having a low liquid ratio flows into the outdoor heat exchanger 7b having a smaller air volume. As a result, heat exchange between the refrigerant and the air can be performed more efficiently.

(Modification)
Here, a modified example of the Y-shaped branch pipe will be described. As shown in FIG. 33, the Y-shaped branch pipe 37b (37) (branch part) according to the modification has an aspect component (X direction component) with respect to the direction of refrigerant flow (for example, the X direction). And a portion (piping portion B) for branching the refrigerant in a mode having a directional component (-X direction component) opposite to the direction component thereof (piping portion A). (See vector shown in FIG. 33).

  Structurally, the Y-shaped branch pipe 37b has a part extending in one direction (pipe part A) into which the refrigerant flows and a part extending in another direction (pipe part B) intersecting with the one direction. ) And a portion (pipe portion C) extending in a direction opposite to the other direction.

  In the branch distribution section 11 described above, the two-phase refrigerant (see FIG. 34) that has flowed through the pipe 41 (first flow path) flows into the Y-shaped branch pipe 37b. The refrigerant flowing into the Y-shaped branch pipe 37b is distributed to the pipe 43 (second flow path) and the pipe 44 (third flow path). At this time, as shown in FIG. 35, the liquid refrigerant easily flows into the pipe 43 due to the inertial force, and the refrigerant (refrigerant A) having a high liquid ratio flows into the pipe 43. On the other hand, as shown in FIG. 36, the liquid refrigerant hardly flows and the refrigerant (refrigerant B) having a low liquid ratio flows into the pipe 44.

  The refrigerant flowing through the pipe 43 flows through the bent pipe 33 and is further distributed by the refrigerant distributor 21a. The distributed refrigerant flows through the pipe 47 and is sent to the outdoor heat exchanger 7a. On the other hand, the refrigerant flowing through the pipe 44 flows through the bent pipe 33 and is further distributed by the refrigerant distributor 21b. The distributed refrigerant flows through the pipe 48 and is sent to the outdoor heat exchanger 7b.

  The distribution of the refrigerant in the pipe 43 immediately after flowing through the bent pipe 33 of the pipe 43 is shown in FIG. 37, and the distribution of the refrigerant in the pipe 44 immediately after flowing through the bent pipe 33 of the pipe 44 is shown in FIG. The distribution of the refrigerant in the pipe 47 is shown in FIG. 39, and the distribution of the refrigerant in the pipe 48 is shown in FIG.

  In particular, the Y-shaped branch pipe 37b has a portion (pipe portion A) for branching the refrigerant in a manner having a direction component (X direction component) with respect to the direction (X direction) in which the refrigerant flows. Thus, even if the flow rate of the refrigerant is small, the liquid refrigerant can easily flow due to the inertial force, and the refrigerant having a high liquid ratio can be flowed from the pipe portion A to the pipe 43.

  Thereby, in the outdoor unit 25, the refrigerant A having a high liquid ratio flows into the outdoor heat exchanger 7a having a larger air volume, and the refrigerant B having a low liquid ratio flows into the outdoor heat exchanger 7b having a smaller air volume. . As a result, heat exchange between the refrigerant and the air can be performed more efficiently.

Embodiment 5. FIG.
Here, the 5th example of the branch distribution part which comprises a refrigerant | coolant branch distributor is demonstrated. As shown in FIG. 41, the branch distribution unit 11 includes a cylindrical body 36 (branch portion). A pipe 41 (first flow path) is connected to the side surface of the cylindrical body 36. A pipe 43 (second flow path) is connected to the lower surface portion of the cylindrical body 36. A pipe 44 (third flow path) is connected to the upper surface portion of the cylindrical body 36. The pipes 43 and 44 include a bent pipe 33.

  Since the configuration of the outdoor unit and the configuration of the refrigeration cycle apparatus other than the above are the same as those shown in FIGS. 1 and 3, the description thereof will not be repeated unless necessary.

  In the branch distribution unit 11 described above, the two-phase refrigerant (see FIG. 42) that has flowed through the pipe 41 flows into the cylindrical body 36. Of the refrigerant that has flowed in, the high-density liquid refrigerant gathers in the lower part of the cylindrical body 36 due to gravity, and the low-density gas refrigerant gathers in the upper part of the cylindrical body 36.

  The refrigerant containing a large amount of liquid refrigerant collected at the lower part of the cylindrical body 36 flows through the pipe 43 including the bent pipe 33 and is further distributed by the refrigerant distributor 21a. The distributed refrigerant flows through the pipe 47 and is sent to the outdoor heat exchanger 7a. On the other hand, the refrigerant containing a large amount of gas refrigerant collected at the upper part of the cylindrical body 36 flows through the pipe 44 including the bent pipe 33 and is further distributed by the refrigerant distributor 21b. The distributed refrigerant flows through the pipe 48 and is sent to the outdoor heat exchanger 7b.

  The distribution of the refrigerant in the pipe 43 immediately after flowing out of the cylindrical body 36 is shown in FIG. 43, and the distribution of the refrigerant in the pipe 44 immediately after flowing out of the cylindrical body 36 is shown in FIG. The distribution of the refrigerant in the pipe 43 immediately after flowing through the bent pipe 33 of the pipe 43 is shown in FIG. 45, and the distribution of the refrigerant in the pipe 44 immediately after flowing through the bent pipe 33 of the pipe 44 is shown in FIG. The distribution of the refrigerant in the pipe 47 is shown in FIG. 47, and the distribution of the refrigerant in the pipe 48 is shown in FIG.

  As shown in FIGS. 43 to 48, the refrigerant flowing through the pipe 41 is distributed into a refrigerant with a high liquid ratio and a refrigerant with a low liquid ratio by the cylindrical body 36 and the bent pipe 33. A refrigerant with a high liquid ratio flows into the outdoor heat exchanger 7a, and a refrigerant with a low liquid ratio flows into the outdoor heat exchanger 7b.

  Thus, in the outdoor unit 25, the refrigerant A having a high liquid ratio flows into the outdoor heat exchanger 7a having a larger air volume, and the refrigerant B having a low liquid ratio flows into the outdoor heat exchanger 7b having a smaller air volume. Thereby, heat exchange with a refrigerant | coolant and air can be performed more efficiently.

  It should be noted that the branching / distributing units described in the embodiments can be variously combined as necessary. For example, the orifice described in the third embodiment may be applied to the branch / distribution unit of another embodiment. Moreover, although the building multi-air conditioner has been described as an example of the refrigeration cycle apparatus, it can be applied to a refrigeration cycle apparatus such as a heat pump apparatus or a car air conditioner.

  The embodiment disclosed this time is an example, and the present invention is not limited to this. The present invention is defined by the terms of the claims, rather than the scope described above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

  The present invention is effectively used in a refrigeration cycle apparatus including a heat exchanger.

  DESCRIPTION OF SYMBOLS 1 Refrigeration cycle apparatus, 3 Compressor, 5a, 5b Four-way valve, 7, 7a, 7b, 7aa, 7ab, 7ac Outdoor heat exchanger, 9a, 9b Expansion valve, 11 Branch distribution part, 13a, 13b, 13c, 13d Expansion Valve, 15, 15a, 15b, 15c, 15d Indoor heat exchanger, 17 Outdoor fan, 19a, 19b Indoor fan, 21a, 21b Refrigerant distributor, 23 Accumulator, 25 Outdoor unit, 26 Housing, 27 Air intake port, 31 Branch piping, 33 Curved piping, 35, 35a, 35b, 35c T-shaped branch piping, 36 Tubular body, 37, 37a, 37b Y-shaped branch piping, 39 Orifice, 39a Shielding portion, 39b Opening portion, 41, 43 44, 45, 47, 48, 49 Piping, 51 Liquid refrigerant, 53 Gas refrigerant.

The present invention relates to a heat exchanger and a refrigeration cycle apparatus provided with a refrigerant branch distributor, in particular, provided with a refrigerant branch distributor capable of branching the refrigerant in two-phase state of liquid refrigerant and gas refrigerant in the different refrigerants liquid ratio In addition, the present invention relates to a heat exchanger and a refrigeration cycle apparatus including the heat exchanger.

The present invention has been made as part of such development, and one object thereof is to provide a heat exchanger provided with a refrigerant branching distributor that efficiently exchanges heat between two-phase refrigerants . Another object is to provide a refrigeration cycle apparatus equipped with such a heat exchanger.

Thereby, in the pipe 41 immediately after flowing through the bent pipe 33, the refrigerant (refrigerant A) having a high liquid ratio flows in a region corresponding to the outer peripheral side of the bent pipe 33, and corresponds to the inner peripheral side of the bent pipe 33. A refrigerant having a low liquid ratio (refrigerant B) flows in the region. The refrigerant that has flowed through the pipe 41 in this state is distributed to the refrigerant A and the refrigerant B by the branch pipe 31. The distributed refrigerant A flows through the pipe 43, the refrigerant distributor 21a and the pipe 47 and is sent to the outdoor heat exchanger 7a. On the other hand, the refrigerant B flows through the pipe 44 , the refrigerant distributor 21b and the pipe 48 and is sent to the outdoor heat exchanger 7b.

Claims (16)

A first flow path, a second flow path, and a third flow path;
A refrigerant connected to the first flow path, connected to the second flow path and the third flow path, and including liquid refrigerant and gas refrigerant flowing from the first flow path is supplied to the second flow path. A branch part that branches into a path and the third flow path,
When the ratio of the liquid refrigerant in the weight ratio of the liquid refrigerant and the gas refrigerant is a liquid ratio,
The refrigerant branching / distributing device, wherein a first liquid ratio of the first refrigerant branched into the second flow path is higher than a second liquid ratio of the second refrigerant branched into the third flow path. The first flow path includes a curved first bent portion,
The second flow path is connected to a first position corresponding to an outer peripheral side of the first bent portion in the branch portion,
2. The refrigerant branch distributor according to claim 1, wherein the third flow path is connected to a second position of the branch portion corresponding to an inner peripheral side of the first bent portion. The first flow path includes a straight part between the first bent part and the branch part,
The refrigerant branch distributor according to claim 2, wherein the length L of the straight portion is set to L <10 × D, where D is the inner diameter of the first flow path. The branch portion is
A first extending portion extending in a first direction in which the first flow path extends from a portion of the branch portion to which the first flow path is connected;
A second extension part extending from the first extension part in a second direction that intersects the first direction;
The second flow path is connected to the first extension part,
The refrigerant branching distributor according to claim 1, wherein the third flow path is connected to the second extending portion.   The refrigerant branch distributor according to claim 4, wherein the second flow path includes a second bent portion.   The refrigerant branching distributor according to claim 4, wherein an orifice is disposed in the first flow path. The branch portion is
A third extending portion extending from a portion of the branching portion to which the first flow channel is connected, branching and extending in a third direction intersecting a first direction in which the first flow channel extends;
Including at least a fourth extending portion that branches and extends in a fourth direction intersecting the first direction and the third direction from a portion of the branch portion to which the first flow path is connected;
The branch portion is arranged with the third extension portion up and the fourth extension portion down,
The second flow path is connected to the fourth extension part,
The refrigerant branching distributor according to claim 1, wherein the third flow path is connected to the third extending portion.   The refrigerant branch distributor according to claim 7, wherein the second flow path includes a third bent portion.   The refrigerant branch distributor according to claim 7, wherein an orifice is disposed in the first flow path. The branch portion is
A third extending portion extending from a portion of the branching portion to which the first flow channel is connected, branching and extending in a third direction intersecting a first direction in which the first flow channel extends;
Including at least a fourth extending portion extending from a portion of the branching portion to which the first flow path is connected and branching in a fourth direction opposite to the third direction;
The second flow path is connected to the third extension part,
The refrigerant branching distributor according to claim 1, wherein the third flow path is connected to the fourth extending portion.   The refrigerant branching / distributing device according to claim 10, wherein the second flow path includes a fourth bent portion.   The refrigerant branching distributor according to claim 10, wherein an orifice is disposed in the first flow path. The branch portion includes a cylindrical body,
The cylindrical body includes an upper surface portion, a lower surface portion and a side surface portion,
The first flow path is connected to the side surface;
The second flow path is connected to the lower surface portion;
The refrigerant branching distributor according to claim 1, wherein the third flow path is connected to the upper surface portion.   The refrigerant branching distributor according to claim 13, wherein the second flow path includes a fifth bent portion. A heat exchanger comprising the refrigerant branch distributor according to any one of claims 1 to 14,
A first heat exchanger for performing heat exchange between the refrigerant and the first fluid;
A second heat exchanger that exchanges heat between the refrigerant and the second fluid,
The amount of the first fluid is greater than the amount of the second fluid;
The second flow path is connected to the first heat exchanger;
The third flow path is a heat exchanger connected to the second heat exchanger.   A refrigeration cycle apparatus comprising the heat exchanger according to claim 15.

Images