Patent Publication Number: US-2023133342-A1

Title: Heat exchanger

Description:
FIELD 
     The disclosed technology relates to a heat exchanger. 
     BACKGROUND 
     In general, a heat exchanger used for an air conditioner has a structure in which both ends of a plurality of flat heat transfer tubes having channels are connected to one of associated headers and the other of associated headers and performs branching a flow of a refrigerant from the one header to each of the flat heat transfer tubes. For example, a technology for circulating a refrigerant in an interior portion of the header and uniformly distributing the refrigerant to the plurality of flat heat transfer tubes that are connected to the header has been proposed (see Patent Literature 1). 
     CITATION LIST 
     Patent Literature 
     
         
         Patent Literature 1: Japanese Laid-open Patent Publication No. 2015-127618 
       
    
     SUMMARY 
     Technical Problem 
     However, in the interior of each of the flat heat transfer tubes, a heat exchange amount is different between channels disposed on an upwind side and a downwind side. As a result, a state of the refrigerant is not uniform among the plurality of channels included in the respective flat heat transfer tubes, and thus, performance of heat exchange may sometimes be decreased. 
     The disclosed technology has been conceived in light of the circumstances described above and an object thereof is to provide a heat exchanger capable of performing branching a flow of a refrigerant in consideration of a difference of a heat exchange amount between the channels disposed on the upwind side and the downwind side with respect to each of the flat heat transfer tubes. 
     Solution to Problem 
     According to an aspect of an embodiment, a heat exchanger includes a plurality of flat heat transfer tubes that are laminated at intervals, and a header that has a hollow shape and to which end portions of the plurality of flat heat transfer tubes are connected, wherein the header includes an inflow plate that divides an interior portion of the header into an inflow portion in which a refrigerant flows in and a circulation portion that is located on an upper side of the inflow portion and to which the end portions of the plurality of flat heat transfer tubes are connected, and a first partition member that divides the circulation portion into an ascending path that is located on an inner side that is a side to which the end portions of the plurality of flat heat transfer tubes are connected and a descending path that is located on an outer side disposed on an opposite side of the inner side, that forms an upper communication path that communicates the ascending path and the descending path on an upper side of an interior portion of the circulation portion, and that forms a lower communication path that communicates the ascending path and the descending path on a lower side of the interior portion of the circulation portion, and the inflow plate includes at least one first ejection hole that ejects, on the ascending path side and a downwind side, a refrigerant from the inflow portion to the ascending path. 
     Advantageous Effects of Invention 
     The heat exchanger according to the present disclosure is able to perform branching a flow of a refrigerant in consideration of a difference of a heat exchange amount between the channels disposed on the upwind side and the downwind side with respect to each of the flat heat transfer tubes. 
    
    
     
       BRIEF DESCRIPTION OF DRAWINGS 
         FIG.  1    is a diagram illustrating a configuration of an air conditioner in which heat exchangers according to a first embodiment are applied. 
         FIG.  2 A  is a plan view of the heat exchanger. 
         FIG.  2 B  is a front view of the heat exchanger. 
         FIG.  3    is a perspective view of a header of the heat exchanger according to the first embodiment. 
         FIG.  4    is a diagram illustrating an inflow plate having two ejection holes. 
         FIG.  5    is a cross-sectional view illustrating the header and a part of a plurality of flat heat transfer tubes viewed from an upwind side. 
         FIG.  6    is a cross-sectional view illustrating the header viewed from the plurality of flat heat transfer tubes side. 
         FIG.  7    is a perspective view of a header included in a heat exchanger according to a second embodiment. 
         FIG.  8    is a cross-sectional view of the header included in the heat exchanger according to the second embodiment viewed from an upwind direction. 
         FIG.  9 A  is a cross-sectional view taken along a line a-a illustrated in  FIG.  8   . 
         FIG.  9 B  is a cross-sectional view taken along the line a-a illustrated in  FIG.  8   . 
         FIG.  10    is a cross-sectional view of the header viewed from the plurality of flat heat transfer tube side. 
         FIG.  11    is a diagram for explaining a comparative example of the header illustrated in  FIG.  10   . 
     
    
    
     DESCRIPTION OF EMBODIMENTS 
     Preferred embodiments of a rotor and an electric motor disclosed in the present invention will be described in detail below with reference to the accompanying drawings. In addition, components that are the same as those in the embodiments are assigned the same reference numerals. 
     First Embodiment 
     Air Conditioner 
       FIG.  1    is a diagram illustrating a configuration of an air conditioner  1  in which a heat exchanger  4  and a heat exchanger  5  according to a first embodiment are applied. As illustrated in  FIG.  1   , the air conditioner  1  includes an indoor unit  2  and an outdoor unit  3 . The indoor unit  2  is provided with the heat exchanger  4  for an indoor use, whereas the outdoor unit  3  is provided with, in addition to the heat exchanger  5  for an outdoor use, a compressor  6 , an expansion valve  7 , and a four-way valve  8 . 
     At the time of a heating operation, a high-temperature high-pressure gas refrigerant discharged from the compressor  6  included in the outdoor unit  3  flows into the heat exchanger  4  that functions as a condenser via the four-way valve  8 . At the time of the heating operation, the refrigerant flows in the direction indicated by the black arrow illustrated in  FIG.  1   . In the heat exchanger  4 , the refrigerant that has been subjected to heat exchange with external air is liquefied. The liquefied high pressure refrigerant is decompressed after passing through the expansion valve  7  and flows, as a low-temperature low-pressure gas-liquid two-phase refrigerant, into the heat exchanger  5  that functions as an evaporator. In the heat exchanger  5 , the refrigerant that has been subjected to heat exchange with the external air is gasified. The gasified low pressure refrigerant is taken into the compressor  6  via the four-way valve  8 . 
     At the time of a cooling operation, a high-temperature high-pressure gas refrigerant discharged from the compressor  6  included in the outdoor unit  3  flows into the heat exchanger  5  that functions as a condenser via the four-way valve  8 . At the time of the cooling operation, the refrigerant flows in the direction indicated by the white arrow illustrated in  FIG.  1   . In the heat exchanger  5 , the refrigerant that has been subjected to heat exchange with external air is liquefied. The liquefied high pressure refrigerant is decompressed by passing through the expansion valve  7  and flows, as a low-temperature low-pressure gas-liquid two-phase refrigerant, into the heat exchanger  4  that functions as an evaporator. In the heat exchanger  4 , the refrigerant that has been subjected to heat exchange with the external air is gasified. The gasified low pressure refrigerant is taken into the compressor  6  via the four-way valve  8 . 
     Heat Exchanger 
     The heat exchanger according to the first embodiment is applicable to both of the heat exchanger  4  and the heat exchanger  5 . In a description below, to give specific details, a description will be made with the assumption that the heat exchanger according to the first embodiment is applied to the heat exchanger  5  that functions as an evaporator at the time of the heating operation. 
       FIG.  2 A  is a plan view of the heat exchanger  5 , and  FIG.  2 B  is a front view of the heat exchanger  5 . The heat exchanger  5  includes a plurality of flat heat transfer tubes  11 , a header  12 , a header  13 , and fins  14 . 
     The low-temperature low-pressure gas-liquid two-phase refrigerant that is decompressed by passing through the expansion valve  7  is supplied to the header  12  by a pipe  15  and flows into each of the flat heat transfer tubes  11  by being branched off. At the time of flowing in the flat heat transfer tube  11 , the gas-liquid two-phase refrigerant that has been subjected to heat exchange with the air via the fins  14  is gasified and flows out to the header  13 , and the refrigerant that has been joined at the header  13  is taken into the compressor  6  via a pipe  16  and the four-way valve  8 . In the following, a specific configuration of the plurality of flat heat transfer tubes  11 , the header  12 , the header  13 , and the fins  14  will be described. 
     The plurality of flat heat transfer tubes  11  are conducting tubes that are formed in a flat shape in cross section and that have a plurality of channels that are disposed along a direction in which the flat heat transfer tubes extend and that are used to allow a refrigerant to flow into the interior portion of the flat heat transfer tubes  11 . The plurality of flat heat transfer tubes  11  are laminated at intervals along a vertical direction of each of the header  12  and the header  13  such that the flat heat transfer tubes  11  face with each other in the width direction. An end of each of the plurality of flat heat transfer tubes  11  is connected to the header  12 , whereas the other end of each of the plurality of flat heat transfer tubes  11  is connected to the header  13 . 
     The refrigerant that is branched off from the header  12  to each of the flat heat transfer tubes  11  flows through the channel located in the interior portion of each of the flat heat transfer tubes  11  and flows out to the header  13 . The refrigerant flowing through the channel located in the interior portion of each of the flat heat transfer tubes  11  performs heat exchange with external air that passes through the space between the plurality of flat heat transfer tubes  11 . In a description below, a flow of the external air on the upstream side is referred to as upwind, whereas on the downstream side is referred to as downwind. 
     Furthermore, in  FIG.  2 B  or the like, a case in which the number of the flat heat transfer tubes  11  is nine is illustrated. However, this is only an example and the number of the flat heat transfer tubes  11  is not limited to nine. 
     The header  12  is a refrigerant channel having a tubular shape (for example, a cylindrical shape). The interior portion of the header  12  is formed to have a hollow shape such that a refrigerant is branched off and flows into the plurality of flat heat transfer tubes  11 . The end portion of each of the plurality of flat heat transfer tubes  11  is connected to the pipe  15  at the header  12 . The refrigerant flowing into the header  12  via the pipe  15  is branched off and flows into each of the flat heat transfer tubes  11  in the header  12 . 
       FIG.  3    is a perspective view of the header  12  included in the heat exchanger  5  according to the first embodiment. As illustrated in  FIG.  3   , the header  12  includes an inflow plate  120  and a first partition member  121 . Furthermore, in a description below, in the header  12 , the side on which the end portion of each of the plurality of flat heat transfer tubes  11  is connected is referred to as an inner side, whereas the side that is an opposite side of the inner side and to which the end portion of each of the plurality of flat heat transfer tubes  11  is not connected is referred to as an outer side. In addition, in  FIG.  3   , the arrow indicates a flowing direction of the external air and an illustration of the fins  14  is omitted. 
     The inflow plate  120  divides the interior portion of the header  12  into an inflow portion  12 F and a circulation portion  12 S that is located on the upper side of the inflow portion  12 F. The pipe  15  is connected to the inflow portion  12 F. The end portions of the plurality of flat heat transfer tubes  11  are connected to the circulation portion  12 S. 
     The first partition member  121  is provided in the interior portion of the header  12  along the longitudinal direction (i.e., in a laminating direction of the flat heat transfer tubes  11 ) of the header  12  that has a tubular shape. The first partition member  121  divides the circulation portion S into an ascending path  12 Su that is located on the inner side and a descending path  12 Sd that is located on the outer side. 
     Furthermore, the cross-sectional area of each of the ascending path  12 Su and the descending path  12 Sd is able to be designed in advance in accordance with the state or the type of the flowing refrigerant. These items may be appropriately set in accordance with the performance needed for the heat exchanger  5 . 
     Furthermore, the first partition member  121  is provided at a distance from each of the upper surface and the bottom surface of the header  12 . The first partition member  121  forms an upper communication path  12 St that communicates the ascending path  12 Su and the descending path  12 Sd on the upper side of the interior portion of the circulation portion  12 S. Furthermore, the first partition member  121  forms a lower communication path  12 Sb that communicates the ascending path  12 Su and the descending path  12 Sd on the lower side of the interior portion of the circulation portion S. 
     Here, the upper end of the first partition member  121  is located above the uppermost flat heat transfer tube  11  out of the plurality of flat heat transfer tubes  11 . The lower end of the first partition member  121  is located below the lowermost flat heat transfer tube  11  out of the plurality of flat heat transfer tubes  11 . 
     The inflow plate  120  includes, on the ascending path  12 Su side and the downwind side, at least one first ejection hole (orifice)  121 H 1  that ejects a refrigerant from the inflow portion  12 F to the ascending path  12 Su. Furthermore, the first ejection hole  121 H 1  is located, when viewed from the top, between the first partition member  121  and the end portions of the plurality of flat heat transfer tubes  11 . In this way, the first ejection hole  121 H 1  is disposed at a position that does not overlap with the end portion of the plurality of flat heat transfer tubes  11 , so that it is possible to suppress deceleration of the refrigerant ejected from the first ejection hole  121 H 1  to the circulation portion  12 S by the plurality of flat heat transfer tubes  11 . 
     Furthermore, in  FIG.  3   , a case in which a single piece of the first ejection hole  121 H 1  is formed in the inflow plate  120  has been illustrated. In contrast, a plurality of the first ejection holes  121 H 1  may be formed in the inflow plate  120 . Furthermore, the number of or the size (cross-sectional area) of the first ejection hole  121 H 1  may be designed in advance in accordance with the state or the type of a flowing refrigerant. These items may be appropriately set in accordance with the performance needed for the heat exchanger  5 . 
     Furthermore, the inflow plate  120  may include, on the ascending path  12 Su side and on the upwind side with respect to the first ejection hole  121 H 1 , at least one second ejection hole that ejects a refrigerant from the inflow portion  12 F to the ascending path  12 Su. The second ejection hole is formed to be smaller than the first ejection hole  121 H 1 . In other words, the first ejection hole  121 H 1  is formed to be larger than the second ejection hole. 
       FIG.  4    is a diagram illustrating the inflow plate  120  having a second ejection hole  121 H 2 . As illustrated in  FIG.  4   , the first ejection hole  121 H 1  disposed on the downwind side is formed larger than the second ejection hole  121 H 2  disposed on the upwind side. 
     As illustrated in  FIG.  2 A ,  FIG.  2 B , and  FIG.  3   , the header  13  is a refrigerant channel that has a tubular shape (for example, a cylindrical shape) and that is paired with the header  12 . The header  13  has substantially the same configuration as that of the header  12 . The other end of each of the pipe  16  and the plurality of flat heat transfer tubes  11  is connected to the header  13 . The other end of each of the plurality of flat heat transfer tubes  11  is connected, and the refrigerant that flows out from each of the flat heat transfer tubes  11  joins in the interior of the header  13 . 
     The fins  14  extend in a direction intersecting the plurality of flat heat transfer tubes  11  and is bonded to the plurality of flat heat transfer tubes  11 . The fins  14  are arrayed, along the longitudinal direction of the plurality of flat heat transfer tubes  11 , at a predetermined pitch with a space therebetween through which air passes. 
     Circulation of Refrigerant Performed in Header 
     In the following, circulation of a refrigerant performed in the header will be described. In addition, in a description below, to give specific details, the header  12  is used as an example. 
       FIG.  5    and  FIG.  6    are diagrams each illustrating circulation of a refrigerant performed in the header  12 .  FIG.  5    indicates a cross-sectional view of the header  12  and a part of the plurality of flat heat transfer tubes  11  viewed from the upwind side. Furthermore,  FIG.  6    indicates a cross-sectional view of the header  12  viewed from the plurality of flat heat transfer tubes  11  side. In addition, in  FIG.  6   , the dotted area of the circulation portion  12 S schematically indicates a distribution of a liquid refrigerant, whereas the solid white area of the circulation portion  12 S schematically indicates a distribution of a gas refrigerant. Furthermore, in  FIG.  5    and  FIG.  6   , an illustration of the fins  14  is omitted. 
     As illustrated in  FIG.  5   , the refrigerant (gas-liquid two-phase refrigerant) supplied from the pipe  15  to the inflow portion  12 F is ejected to the circulation portion  12 S via the first ejection hole  121 H 1  included in the inflow plate  120 . The first ejection hole  121 H 1  is formed, in the inflow portion  12 F, on the ascending path  12 Su side and the downwind side. Accordingly, as indicated by an arrow A 1  illustrated in  FIG.  6   , the refrigerant ejected from the first ejection hole  121 H 1  to the circulation portion  12 S ascends on the downwind side of the ascending path  12 Su. 
     In other words, the refrigerant ejected from the first ejection hole  121 H 1  to the ascending path  12 Su of the circulation portion  12 S is a gas-liquid two-phase refrigerant that is a combination of a liquid refrigerant and a gas refrigerant; however, the flow velocity of the gas refrigerant is higher than that of the liquid refrigerant. As a result, if the refrigerant is ejected from the first ejection hole  121 H 1  to the downwind side of the ascending path  12 Su and ascends, most of the gas refrigerant vigorously flows, as indicated by the arrow A 1  illustrated in  FIG.  6   , from the first ejection hole  121 H 1  toward an upper part of the downwind side of the ascending path  12 Su. 
     In contrast, as indicated by the arrow A 2  illustrated in  FIG.  6   , the liquid refrigerant flowing at a low flow velocity is pushed out from the downwind side to the upwind side due to an air current of the gas refrigerant ejected from the first ejection hole  121 H 1 . As a result, as illustrated in  FIG.  6   , a large amount of a gas refrigerant that has been blown up and that flows at a high flow velocity is distributed on the downwind side of the ascending path  12 Su, whereas a large amount of a liquid refrigerant that flows at a flow velocity that is lower than that of the gas refrigerant is distributed on the upwind side of the ascending path  12 Su. 
     In the ascending path  12 Su, the refrigerant exhibiting a phase distribution illustrated in  FIG.  6    is branched off and flows into the plurality of flat heat transfer tubes  11 . When the refrigerant that is branched off and flows into the plurality of flat heat transfer tubes  11  flows through each of the flat heat transfer tubes  11 , the refrigerant that has been subjected to heat exchange with air via the fins  14  is gasified and flows out to the header  13 . 
     In addition, the refrigerant that is not branched off and does not flow into the plurality of flat heat transfer tubes  11  inverts its vertical flow direction in the upper communication path  12 St and flows into the descending path  12 Sd of the circulation portion  12 S. The refrigerant flowing into the descending path  12 Sd descends the descending path  12 Sd of the circulation portion  12 S, inverts its vertical flow direction in the lower communication path  12 Sb, and again flows into the ascending path  12 Su. 
     The refrigerant flowing into the ascending path  12 Su as described above is joined with a refrigerant that is newly ejected from the first ejection hole  121 H 1  to the circulation portion  12 S and repeats the same circulation as described above. 
     As described above, by providing the first ejection hole  121 H 1  on the ascending path  12 Su side of the inflow plate  120  and the downwind side, it is possible to vigorously flow the gas refrigerant to above the ascending path  12 Su. By using the ascending flow on the downwind side of the gas refrigerant, as illustrated in  FIG.  6   , it is possible to change the flow ratio of the gas refrigerant to the liquid refrigerant related in the width direction of each of the plurality of flat heat transfer tubes  11 . Specifically, it is possible to allow a larger amount of the liquid refrigerant, out of the gas-liquid two-phase refrigerants, to branch off and flow through each of the flat heat transfer tubes  11  on the upwind side in which an amount of heat exchanged is large and allow a larger amount of the gas refrigerant to branch off and flow on the downwind side in which an amount of heat exchanged is less than that on the upwind side. Furthermore, in the present embodiment, in this way, an effect in which the ratio of gas refrigerant to the liquid refrigerant related to the plurality of flat heat transfer tubes  11  in the width direction is made to vary is referred to as a bias effect of the refrigerant phase distribution. 
     Furthermore, the bias effect of the refrigerant phase distribution as described above is also applied to the flat heat transfer tubes  11  located on the upper portion of the header  12  because the gas refrigerant is vigorously ejected from the first ejection hole  121 H 1  to an upper part of the ascending path  12 Su. In addition, it is possible to suppress the liquid refrigerant from flowing into the lowermost flat heat transfer tube  11  because the liquid refrigerant is vigorously ejected from the first ejection hole  121 H 1  to an upper part of the ascending path  12 Su together with the gas refrigerant. 
     Furthermore, it is conceivable that a case in which the inflow plate  120  is provided with the second ejection hole  121 H 2  on the upwind side and the first ejection hole  121 H 1  on the downwind side (see  FIG.  4   ). By providing the second ejection hole  121 H 2 , it is possible to push up the liquid refrigerant that is likely to be retained on the upwind side of the upper surface of the inflow plate  120  by using the gas refrigerant that has been ejected from the second ejection hole  121 H 2 , and it is thus possible to suppress a bias of an amount of the refrigerant that is allowed to flow into the plurality of flat heat transfer tubes  11 . In this case, the first ejection hole  121 H 1  disposed on the downwind side is formed to be larger than the first ejection hole  121 H 1  disposed on the upwind side. In general, an amount of the refrigerant flowing from each of the first ejection hole  121 H 1  disposed on the downwind side and the second ejection hole  121 H 2  disposed on the upwind side into the circulation portion  12 S is in proportion to the respective opening areas. Accordingly, it is possible to increase an ejection amount of the refrigerant ejected from the first ejection hole  121 H 1  disposed on the downwind side as compared to an ejection amount of the refrigerant ejected from the second ejection hole  121 H 2  disposed on the upwind side. As a result, even when the inflow plate  120  is provided with the second ejection hole  121 H 2  on the upwind side and the first ejection hole  121 H 1  on the downwind side, it is possible to allow a large amount of the liquid refrigerant out of the gas-liquid two-phase refrigerant to branch off and flow on the upwind side in which an amount of heat exchanged is large and allow a larger amount of gas refrigerant to off and flow on the downwind side in which an amount of heat exchanged is less than that on the upwind side. 
     As described above, with the heat exchanger  5  according to the first embodiment, it is possible to branch off and flow a refrigerant through each of the flat heat transfer tubes  11  in consideration of a difference of an amount of heat exchanged between the channels that are disposed on the upwind side and the downwind side. 
     Second Embodiment 
     In the following, a heat exchanger according to a second embodiment will be described. 
       FIG.  7    is a perspective view of the header  12  included in the heat exchanger  5  according to the second embodiment.  FIG.  8    is a cross-sectional view of the header  12  included in the heat exchanger  5  according to the second embodiment when viewed from the upwind direction. As illustrated in  FIG.  7    and  FIG.  8   , the heat exchanger  5  according to the second embodiment has a configuration in which, in addition to the heat exchanger  5  according to the first embodiment, a second partition member is further provided in the circulation portion  12 S included in the header  12 . 
     A second partition member  123  divides the circulation portion  12 S included in the header  12  into an upper circulation portion  12 S 1  that is located on the upper side and a lower circulation portion  12 S 2  that is located on the lower side. The second partition member  123  is provided at the center of the circulation portion S or above the center in the laminating direction of, for example, the plurality of flat heat transfer tubes  11  (in the longitudinal direction of the header  12  in  FIG.  7    and  FIG.  8   ). 
     Furthermore, in  FIG.  7    and  FIG.  8   , the number of the flat heat transfer tubes  11  connected to the upper circulation portion  12 S 1  is set to be four, whereas the number of the flat heat transfer tubes  11  connected to the lower circulation portion  12 S 2  is set to be five. However, this is only an example and the number of the flat heat transfer tubes  11  connected to the upper circulation portion  12 S 1  and the lower circulation portion  12 S 2  is not limited to this example. 
       FIG.  9 A  and  FIG.  9 B  are diagrams each illustrating a cross-sectional view taken along a line a-a illustrated in  FIG.  8    and are diagrams that are associated with the front view of the second partition member  123 . As illustrated in  FIG.  9 A , the second partition member  123  includes an opening portion  123 H 1  on the ascending path  12 Su side and the downwind side. The opening portion  123 H 1  ejects a refrigerant from the lower circulation portion  12 S 2  to the upper circulation portion  12 S 1 . Furthermore, the second partition member  123  includes, on the descending path  12 Sd side, at least one opening portion  123 H 2  that ejects a refrigerant from the upper circulation portion  1231  to the lower circulation portion  12 S 2 . 
     Furthermore, the shape of the opening portion  123 H 1  may be a hole shape or a notch shape. In addition, as illustrated in  FIG.  9 B , the opening portion  123 H 1  has a positional relationship so as to be overlapped with at least one of the first ejection holes  121 H 1  viewed from the top. For example, the opening portion  123 H 1  is located above (for example, immediately above) the first ejection hole  121 H 1  included in the inflow plate  120 . Furthermore, the size (an opening area) of the opening portion  123 H 1  is larger than the entire opening area of, for example, at least one of the first ejection holes  121 H 1 . 
     The reason for setting the positional relationship and the size between the opening portion  123 H 1  and the first ejection hole  121 H 1  is as follows. Namely, this is because the portion other than the opening portion  123 H 1  included in the second partition member  123  (i.e., the plate shaped portion) does not act as channel resistance of the refrigerant that has been ejected from the first ejection hole  121 H 1 . 
     Furthermore, a specific number of the opening portions  123 H 1  and the size thereof may be designed in advance in accordance with the state or the type of the flowing refrigerant. These items may be appropriately set in accordance with the performance needed for the heat exchanger  5 . 
     Circulation of Refrigerant Performed in Header 
     In the following, a circulation of a refrigerant performed in a header will be described with reference to  FIG.  8    and  FIG.  10   . 
       FIG.  10    is a cross-sectional view of the header  12  viewed from the plurality of flat heat transfer tubes  11  side. In addition, in also  FIG.  10   , similarly to  FIG.  6   , the dotted area of the circulation portion  12 S schematically indicates a distribution of a liquid refrigerant, whereas the solid white area of the circulation portion  12 S schematically indicates a distribution of a gas refrigerant. Furthermore, in  FIG.  10   , an illustration of the fins  14  is omitted. 
     As illustrated in  FIG.  10   , the refrigerant (gas-liquid two-phase refrigerant) supplied from the pipe  15  to the inflow portion  12 F is ejected to the ascending path  12 Su of the lower circulation portion  12 S 2  via the first ejection hole  121 H 1  included in the inflow plate  120 . The first ejection hole  121 H 1  is formed, in the inflow portion  12 F, on the ascending path  12 Su side and the downwind side. Accordingly, the refrigerant ejected from the first ejection hole  121 H 1  to the ascending path  12 Su of the lower circulation portion  12 S 2  vigorously ascends on the downwind side, as indicated by an arrow A 3  illustrated in  FIG.  10   . The liquid refrigerant flowing at a low flow velocity is pushed out, as indicated by an arrow A 5  illustrated in FIG, from the downwind side to the upwind side.  10  caused by an air current of the gas refrigerant ejected from the first ejection hole  121 H 1 . As a result, in the lower circulation portion  12 S 2 , the bias effect of the refrigerant phase distribution described above is implemented. 
     In the ascending path  12 Su of the lower circulation portion  12 S 2 , the refrigerant in which a large amount of the gas refrigerant is distributed on the downwind side and a large amount of liquid refrigerant is distributed on the upwind side is branched off and flows into the plurality of flat heat transfer tubes  11  that are connected to the lower circulation portion  12 S 2 . When The refrigerant that is branched off and flows into the plurality of flat heat transfer tubes  11  that are connected to the lower circulation portion  12 S 2  flows through each of the flat heat transfer tubes  11 , the refrigerant that has been subjected to heat exchange with air via the fins  14  is gasified and flows out into the header  13 . 
     Furthermore, the refrigerant that is not branched off and does not into the plurality of flat heat transfer tubes  11  is ejected from the opening portion  123 H 1  of the second partition member  123  to the upper circulation portion  12 S 1  of the ascending path  12 Su. A large amount of gas refrigerant is again accelerated by the opening portion  123 H 1  of the second partition member  123  and, as indicated by an arrow A 4  illustrated in  FIG.  10   , vigorously ascends toward an upper part of the upper circulation portion  12 S 1 . The liquid refrigerant flowing at low flow velocity is pushed out, as indicated by an arrow A 5  illustrated in  FIG.  10   , from the downwind side to the upwind side caused by an air current of the gas refrigerant that is re-accelerated and ejected from the opening portion  123 H 1 . As a result, in the upper circulation portion  12 S 1 , the bias effect of the refrigerant phase distribution described above is implemented. 
     In the ascending path  12 Su of the upper circulation portion  12 S 1 , the refrigerant in which a large amount of the gas refrigerant is distributed on the downwind side and a large amount of the liquid refrigerant is distributed on the upwind side is branched off and flows into the plurality of flat heat transfer tubes  11  that are connected to the upper circulation portion  12 S 1 . When the refrigerant that is branched off and flows into the plurality of flat heat transfer tubes  11  that are connected to the upper circulation portion  12 S 1  flows through each of the flat heat transfer tubes  11 , the refrigerant that has been subjected to heat exchange with air via the fins  14  is gasified and flows out into the header  13 . 
     Furthermore, the refrigerant that is not branched off and does not into the plurality of flat heat transfer tubes  11  that are connected to the upper circulation portion  12 S 1  inverts its vertical flow direction in the upper communication path  12 St and flows into the descending path  12 Sd of the circulation portion  12 S. The refrigerant flowing into the descending path  12 Sd descends the descending path  12 Sd of the circulation portion  12 S, inverts its vertical flow direction in the lower communication path  12 Sb, and again flows into the ascending path  12 Su of the lower circulation portion  12 S 2 . 
     The refrigerant flowing into the ascending path  12 Su of the lower circulation portion  12 S 2  as described above is joined with a refrigerant that is newly ejected from the first ejection hole  121 H 1  to the lower circulation portion  12 S 2  and repeats the same circulation as described above. 
     As described above, by providing the first ejection hole  121 H 1  on the ascending path  12 Su side of the inflow plate  120  and the downwind side, a large amount of the gas refrigerant flowing from the lower circulation portion  12 S 2  to the upper circulation portion  12 S 1  is re-accelerated by the opening portion  123 H 1  of the second partition member  123 . As a result, it is possible to further increase a flow ratio of gas refrigerant to liquid refrigerant in the width direction of the plurality of flat heat transfer tubes  11  at an upper part of the circulation portion  12 S as compared to the case in which the second partition member  123  that includes the opening portion  123 H 1  is not provided. In other words, it is also possible to implement a bias effect of the refrigerant phase distribution in the upper circulation portion  12 S 1  without reducing the efficiency as compared to the lower circulation portion  12 S 2 . As a result, it is possible to further efficiently perform branching a flow of the refrigerant in consideration of a difference of an amount heat exchanged between the channels that are disposed on the upwind side and the downwind side with respect to each of the flat heat transfer tubes  11 . 
       FIG.  11    is a diagram illustrating a case in which, as a comparative example with the header illustrated in  FIG.  10   , a refrigerant flowing at a low circulation volume (low flow rate) is allowed to flow into the header according to the first embodiment. When the header illustrated in  FIG.  11    is compared to the header illustrated in  FIG.  10   , in the header illustrated in  FIG.  11   , the second partition member  123  including the opening portion  123 H 1  is not present. Furthermore, in  FIG.  11   , an oblique line area of the ascending path  12 Su of the circulation portion  12 S schematically indicates a distribution of the gas-liquid two-phase refrigerant, a dotted area of the circulation portion  12 S schematically indicates a distribution of the liquid refrigerant, and a solid white area of the circulation portion  12 S schematically indicates a distribution of the gas refrigerant. In addition, in  FIG.  11   , an illustration of the fins  14  is omitted. 
     In the header according to the comparative example illustrated in  FIG.  11   , the refrigerant that has been ejected from the first ejection hole  121 H 1  to the ascending path  12 Su of the circulation portion  12 S is a low circulation volume, so that, as indicated by an arrow A 6  illustrated in  FIG.  11   , the refrigerant loses its speed as the refrigerant ascends. As a result, a difference of the flow velocity between the upwind side and the downwind side of the ascending path  12 Su of the circulation portion  12 S is decreased as the refrigerant flows toward the upper portion of the circulation portion  12 S. In an area closer to the first ejection hole  121 H 1  of the ascending path  12 Su of the circulation portion  12 S, as indicated by an arrow A 7  illustrated in  FIG.  11   , it is possible to push out the liquid refrigerant flowing at low flow velocity from the downwind side to the upwind side by the gas refrigerant whose ascent velocity is high. In contrast, if the gas refrigerant loses its speed, the gas refrigerant is not able to push out the liquid refrigerant from the downwind side to the upwind side. Accordingly, as indicated by an arrow A 8  illustrated in  FIG.  11   , a large amount of the gas-liquid two-phase refrigerant consequently flows as the refrigerant flows toward in an upward direction of the ascending path  12 Su of the circulation portion  12 S, so that it is conceivable that the phase distribution between the liquid refrigerant and the gas refrigerant is changed to a state in which no bias is present. 
     In contrast, in the heat exchanger according to the present embodiment, the bias effect of the refrigerant phase distribution acts further efficiently on the flat heat transfer tubes  11  that are located at an upper portion of the upper circulation portion  12 S 1  because the gas refrigerant is re-accelerated by the opening portion  123 H 1  and vigorously ejected to an upper part of the upper circulation portion  12 S 1 . Furthermore, the gas refrigerant is vigorously ejected from the first ejection hole  121 H 1  to an upper part of the upper circulation portion  12 S 1 , so that it is possible to suppress the liquid refrigerant from flowing into the lowermost flat heat transfer tube  11 . 
     As described above, with the heat exchanger  5  according to the first embodiment, it is possible to perform branching a flow of the refrigerant in consideration of a difference of an amount of heat exchanged between the channels that are disposed on the upwind side and the downwind side with respect to each of the flat heat transfer tubes  11 . 
     In the above, the embodiments have been described; however, the disclosed technology is not limited to these and may include various embodiments or the like that are not described here. 
     REFERENCE SIGNS LIST 
     
         
           1  air conditioner 
           2  indoor unit 
           3  outdoor unit 
           4 ,  5  heat exchanger 
           6  compressor 
           7  expansion valve 
           8  four-way valve 
           11  flat heat transfer tube 
           12 ,  13  header 
           14  fin 
           15 ,  16  pipe 
           12 F inflow portion 
           12 S circulation portion 
           12 S 1  upper circulation portion 
           12 S 2  lower circulation portion 
           12 Su ascending path 
           12 Sd descending path 
           12 St upper communication path 
           12 Sb lower communication path 
           120  inflow plate 
           121  first partition member 
           121 H 1  first ejection hole 
           121 H 2  second ejection hole 
           123  second partition member 
           123 H 1  opening portion