JP7327213B2 - Heat exchanger - Google Patents

Description

The present invention relates to heat exchangers.

2. Description of the Related Art Conventionally, there is known a heat exchanger having a structure in which both ends of a flat heat transfer tube having a plurality of flow paths are inserted and connected to left and right headers, respectively, and refrigerant is split from one of the headers to the flat heat transfer tube. In an air conditioner using such a heat exchanger, when heat is exchanged between the refrigerant and the outside air, a large heat load is applied to the refrigerant in the flow path on the windward side. Techniques have been proposed for circulating a larger amount of refrigerant in a flow path located on the windward side than in a flow path located on the leeward side (see Patent Documents 1 and 2, for example).

JP 2006-266521 A Japanese Patent Application Laid-Open No. 2018-100800

In the technique described above, the inside of the header is divided into a windward space and a leeward space, and the refrigerant flows from the windward space to the leeward space. FIG. 10 is a cross-sectional view of the header 60 of Patent Document 1, in which (a) shows a case where the refrigerant flow rate is small and (b) shows a case where the flow rate is large. A wall 61 is provided in the header 60 and extends from the side opposite to the side to which the flat heat transfer tubes 63 are connected. ing. When the flow rate of the refrigerant is small, as shown in FIG. 10(a), most of the liquid-phase refrigerant in the refrigerant flowing into the windward space 62a from the pipe 50 does not reach the wall 61 (the leeward space 62b ), and flows into the windward flow path 63 a of the flat heat transfer tube 63 . On the other hand, when the flow rate of the refrigerant is large, as shown in FIG. 62 b and flows into the leeward flow path 63 b of the flat heat transfer tube 63 . In this case, the amount of liquid-phase refrigerant with a large amount of heat exchange flowing into the flow path of the flat heat transfer tubes on the leeward side with a small heat load increases, and the amount of heat flowing into the flow path on the upwind side of the flat heat transfer tubes with a large heat load increases. In some cases, the amount of gas-phase refrigerant with a small exchange amount becomes large, and the target heat exchange capacity of the heat exchanger cannot be obtained.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a heat exchanger capable of obtaining a target heat exchange capacity regardless of the flow rate of refrigerant.

In order to solve the above-described problems and achieve the object, a heat exchanger according to the present invention includes a plurality of flat heat transfer tubes stacked so that wide surfaces face each other, and end portions of the plurality of flat heat transfer tubes. and a tubular header for branching the refrigerant flow to the plurality of flat heat transfer tubes, wherein the header has a tubular main body that is arranged in the stacking direction of the plurality of flat heat transfer tubes , the space on the upper side and the space on the lower side. A first partition member that partitions the space on the upper side into a refrigerant inflow portion , and a refrigerant circulation return path on the side to which the plurality of flat heat transfer tubes are connected, and the plurality of flat heat transfer tubes are connected. a third partition member that divides the outward circulation path of the refrigerant into an outward circulation path on the opposite side; above the third partition member, a windward inlet for flowing refrigerant into the windward space, and a leeward flow for flowing refrigerant into the leeward space. An inlet is provided, and the opening area of the windward inlet is larger than the opening area of the leeward inlet. A windward circulation port and a leeward circulation port for circulating the refrigerant from the windward space and the leeward space are provided below the third partition member.

According to the present invention, the target heat exchange capacity can be obtained regardless of the flow rate of the refrigerant.

FIG. 1 is a diagram illustrating the configuration of an air conditioner to which a heat exchanger according to Embodiment 1 of the present invention is applied. 2A and 2B are diagrams illustrating the heat exchanger according to Embodiment 1 of the present invention, in which FIG. 2A is a plan view of the heat exchanger and FIG. 2B is a front view of the heat exchanger. FIG. 3 is a perspective view of the header of the heat exchanger according to Embodiment 1 of the present invention. 4 is a horizontal cross-sectional view of the header of FIG. 3; FIG. 5 is a vertical cross-sectional view of the header of FIG. 3. FIG. FIG. 6 is a perspective view of a header of a heat exchanger according to Embodiment 2 of the present invention. FIG. 7 is a horizontal sectional view of a header of a heat exchanger according to Embodiment 2 of the present invention. FIG. 8 is a perspective view of a header of a heat exchanger according to Embodiment 3 of the present invention. FIG. 9 is a horizontal sectional view of a header of a heat exchanger according to Embodiment 3 of the present invention. 10A and 10B are cross-sectional views of the conventional header when the flow rate of the coolant is low, and FIG. 10B when the flow rate is high.

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments for carrying out the present invention (hereinafter referred to as "embodiments") will be described with reference to the accompanying drawings. The same numbers are assigned to the same configurations throughout the description of the embodiments.

[Embodiment 1]
(air conditioner)
FIG. 1 is a diagram illustrating the configuration of an air conditioner 1 to which a heat exchanger 4 and a heat exchanger 5 according to Embodiment 1 of the present invention are applied. As shown in FIG. 1 , the air conditioner 1 includes an indoor unit 2 and an outdoor unit 3 . The indoor unit 2 is provided with an indoor heat exchanger 4 , and the outdoor unit 3 is provided with a compressor 6 , an expansion valve 7 and a four-way valve 8 in addition to the outdoor heat exchanger 5 .

During heating operation, high-temperature, high-pressure gas refrigerant discharged from the compressor 6 of the outdoor unit 3 flows through the four-way valve 8 into the heat exchanger 4 functioning as a condenser. During heating operation, the refrigerant flows in the direction indicated by the black arrow in FIG. In the heat exchanger 4, the refrigerant that has exchanged heat with the outside air is liquefied. The liquefied high-pressure refrigerant passes through the expansion valve 7, is decompressed, and flows into the heat exchanger 5 functioning as an evaporator as a low-temperature, low-pressure gas-liquid two-phase refrigerant. In the heat exchanger 5, the refrigerant that has exchanged heat with the outside air is gasified. The gasified low-pressure refrigerant is sucked into the compressor 6 via the four-way valve 8 .

During cooling operation, high-temperature and high-pressure gas refrigerant discharged from the compressor 6 of the outdoor unit 3 flows through the four-way valve 8 into the heat exchanger 5 functioning as a condenser. During cooling operation, the refrigerant flows in the direction indicated by the white arrow in FIG. In the heat exchanger 5, the refrigerant that has exchanged heat with the outside air is liquefied. The liquefied high-pressure refrigerant passes through the expansion valve 7, is decompressed, and flows into the heat exchanger 4 functioning as an evaporator as a low-temperature, low-pressure gas-liquid two-phase refrigerant. In the heat exchanger 4, the refrigerant that has exchanged heat with the outside air is gasified. The gasified low-pressure refrigerant is sucked into the compressor 6 via the four-way valve 8 .

(Heat exchanger)
The heat exchanger according to Embodiment 1 of the present invention can be applied to both the heat exchanger 4 and the heat exchanger 5. However, it is assumed that the heat exchanger 5 functions as an evaporator during heating operation. explain. 2A and 2B are diagrams for explaining the heat exchanger 5 according to Embodiment 1 of the present invention, where (a) is a plan view of the heat exchanger 4 and (b) is a front view of the heat exchanger 5. .

The heat exchanger 5 includes a plurality of flat heat transfer tubes 11 through which a refrigerant flows, a tubular header 12 to which end portions of the plurality of flat heat transfer tubes 11 are connected, and a plurality of flat heat transfer tubes 11 to distribute the refrigerant to the flat heat transfer tubes 11 . It includes a tubular header 13 to which the other ends of the heat tubes 11 are connected and which joins the refrigerant flowing out from the flat heat transfer tubes 11 , and a plurality of flat plate-shaped fins 14 joined to the flat heat transfer tubes 11 . The flat heat transfer tube 11 extends in a direction perpendicular to the direction in which the external air circulates, as indicated by the arrow in FIG. 2(a), and has a flat cross section. The inside of the flat heat transfer tube 11 has a plurality of flow paths extending in the same direction as the direction in which the flat heat transfer tube extends. In this embodiment, the direction in which the outside air circulates is the width direction of the flat heat transfer tubes 11, and the direction in which the flat heat transfer tubes 11 extend, which is perpendicular to the direction in which the outside air circulates, is the length direction of the flat heat transfer tubes 11. and As shown in FIG. 2B, the flat heat transfer tubes 11 are stacked vertically so that the flat surfaces (wide surfaces) of the side surfaces face each other, and the left and right ends are connected to the headers 12 and 13. It is A plurality of fins 14 are arranged between the headers 12 and 13 so as to be perpendicular to the flat heat transfer tubes 11 . The low-temperature, low-pressure gas-liquid two-phase refrigerant decompressed by passing through the expansion valve 7 is supplied to the header 12 through the pipe 15 and branched to the flat heat transfer tubes 11 . When flowing through the flat heat transfer tubes 11, the gas-liquid two-phase refrigerant that has exchanged heat with the air through the fins 14 is gasified and flows out to the header 13. It is sucked into the compressor through

(header)
Next, the header 12 according to Embodiment 1 of the present invention will be described with reference to FIGS. 3 to 5. FIG. In this specification, the side of the header 12 facing the flat heat transfer tubes 11 is referred to as the inside, and the side of the header 12 facing the flat heat transfer tubes 11 is referred to as the outside. The heat exchanger 5 is arranged so that the length direction and width direction of the flat heat transfer tubes 11, that is, the direction parallel to the flat surface of the flat heat transfer tubes 11, is the horizontal direction. Furthermore, the heat exchanger 5 is arranged such that the stacking direction of the flat heat transfer tubes 11, that is, the direction orthogonal to the flat surfaces of the flat heat transfer tubes 11 is the vertical direction. A blower fan (not shown) is provided in the vicinity of the heat exchanger 5 , and blows outside air to the heat exchanger 5 . In FIG. 3, illustration of the fins 14 is omitted.

As shown in FIGS. 3 and 4, the header 12 includes a first partition member 21 that partitions the tubular main body 20 into an upper portion and a lower portion in the stacking direction (vertical direction) of the flat heat transfer tubes 11; It has a second partition member 22 that partitions the upper part of the main body 20 partitioned by one partition member 21 into one space and the other space in the width direction (horizontal direction) of the flat heat transfer tube 11 . The heat exchanger 5 is arranged such that the other space is on the upstream side (windward side) of the external air, and the other space is on the downstream side (leeward side) of the external air. The first partition member 21 is provided over the entire horizontal direction of the body portion 20 , and the second partition member 22 is provided over the entire vertical direction above the first partition member 21 of the body portion 20 . there is As shown in FIGS. 3 and 4, the header 12 has a cylindrical shape, but is not limited to a cylindrical shape, and may have a prismatic shape with a hollow interior.

A space on the lower side of the body portion 20 partitioned by the first partition member 21 is a refrigerant inflow portion 23 into which a low-temperature, low-pressure gas-liquid two-phase refrigerant flows from the expansion valve 7 via the pipe 15 . In the space on the upper side of the main body 20 partitioned by the first partition member 21, one of the spaces on the windward side of the external air partitioned by the second partition member 22 is the windward space 24, The other space on the leeward side is the leeward space 25 .

The first partition member 21 forming the windward side of the first partition member 21, that is, the bottom surface of the windward space 24, is provided with the windward inlet 26, and the leeward side of the first partition member 21, that is, the leeward side. A leeward inlet 27 is provided in the first partition member 21 that forms the bottom surface of the flow path. Refrigerant flows into the windward space 24 from the refrigerant inlet 23 through the windward inlet 26 , and flows into the leeward space 25 from the refrigerant inlet 23 through the leeward inlet 27 .

In Embodiment 1, the opening area of the windward inlet 26 is formed to be larger than the opening area of the leeward inlet 27 . The refrigerant that has flowed into the refrigerant inlet 23 flows into the windward space 24 and the leeward space 25 via the windward inlet 26 and the leeward inlet 27. It is approximately proportional to the opening area of the side inlet 27 . Therefore, by adjusting the opening areas of the windward inlet 26 and the leeward inlet 27, the amounts of refrigerant flowing into the windward space 24 and the leeward space 25 can be easily controlled. In addition, in the first embodiment, regardless of the flow rate of the refrigerant flowing into the refrigerant inflow portion 23 from the pipe 15, the ratio of the flow rate of the refrigerant flowing out from the windward side inlet 26 and the leeward side inlet 27 is appropriately adjusted. can keep.

[Embodiment 2]
The header used in the heat exchanger according to Embodiment 2 has a circulation line through which at least part of the refrigerant flowing into the header circulates. Further, as in the first embodiment, the heat exchanger 5 is arranged such that the length direction and the width direction of the flat heat transfer tubes 11, that is, the direction parallel to the flat surface of the flat heat transfer tubes 11 is the horizontal direction. be. Furthermore, the heat exchanger 5 is arranged such that the stacking direction of the flat heat transfer tubes 11, that is, the direction orthogonal to the flat surfaces of the flat heat transfer tubes 11 is the vertical direction. A blower fan (not shown) is provided in the vicinity of the heat exchanger 5 , and blows outside air to the heat exchanger 5 . FIG. 6 is a perspective view of the header 12A of the heat exchanger according to Embodiment 2 of the present invention. 7A is a horizontal sectional view of the middle portion, (b) is a horizontal sectional view of the upper portion, and (c) is a horizontal sectional view of the lower portion of the header 12A of the heat exchanger according to Embodiment 2 of the present invention. is. 6, illustration of the flat heat transfer tubes 11 connected to the header 12A is omitted.

In addition to the first partition member 21 and the second partition member 22A, the header 12A includes a third partition partitioning the upper portion of the main body 20 partitioned by the first partition member 21 in the longitudinal direction of the flat heat transfer tubes 11 . It further has a partition member 30 of The header 12</b>A has a refrigerant inflow portion 23 into which a low-temperature, low-pressure gas-liquid two-phase refrigerant flows from the expansion valve 7 via the pipe 15 . In addition, in the space on the upper side where the main body portion 20 is partitioned by the first partition member 21, the third partition member 30 separates the inner space (flat heat transfer tube 11 side) and the outer space (flat heat transfer tube 11 side). and the space on the opposite side). Here, the outer space is the outward circulation path 31 . The inner space is partitioned into one space and the other space in the width direction of the flat heat transfer tube 11 by the second partition member 22A. One space partitioned by the second partition member 22A is the windward space 24A, and the other space is the leeward space 25A. The windward space 24A and the leeward space 25A serve as circulation return paths, which will be described later.

An inflow port 32 is provided on the outside of the first partition member 21 , that is, on the first partition member 21 that serves as the bottom surface of the forward circulation path 31 . Refrigerant flows into the outward circulation path 31 from the refrigerant inflow portion 23 via the inlet 32 .

A windward inlet 26A is provided on the windward side of the upper portion of the third partition member 30, and a leeward inlet port 27A is provided on the leeward side of the upper portion of the third partition member 30. A windward circulation port 33 is provided on the windward side of the lower portion of the third partition member 30 , and a leeward side circulation port 34 is provided on the leeward side of the lower portion of the third partition member 30 . The sum of the opening areas of the windward inlet 26A is larger than the sum of the opening areas of the leeward inlet 27A, and the sum of the opening areas of the windward circulation inlet 33 is larger than the sum of the opening areas of the leeward circulation inlet 34. It is By making the opening area of the windward inlet 26A larger than the opening area of the leeward inlet 27A, the amount of refrigerant flowing into the windward space 24A can be increased.

The refrigerant that has flowed from the refrigerant inflow portion 23 into the outward circulation passage 31 through the inflow port 32 rises in the outward circulation passage 31, flows into the windward space 24A from the windward inflow port 26A, and flows downwind from the leeward side inflow port 27A. It flows into the side space 25A. The refrigerant split into the windward space 24A and the leeward space 25A descends and flows out to the plurality of flat heat transfer tubes 11, and part of it circulates in the outward circulation path 31 from the windward circulation port 33 and the leeward circulation port 34. do.

In the header 12A, the third partition member 30 is arranged so that the horizontal cross-sectional area of the forward circulation path 31 is smaller than the sum of the horizontal cross-sectional areas of the windward space 24A and the leeward space 25A. As a result, the flow velocity of the refrigerant flowing through the outward circulation path 31 becomes higher than that of the return circulation path (the windward space 24A and the leeward space 25A), so that the refrigerant is likely to rise. In addition, the horizontal cross-sectional area of the forward circulation path 31 is formed to be larger than the sum of the opening areas of the windward circulation port 33 and the leeward circulation port 34, which will be described later. As a result, it is possible to prevent the refrigerant from backflowing (the windward space 24A and the leeward space 25A serve as an outward path, and the circulation outward path 31 serves as a return path), thereby facilitating the formation of a circulation flow.

Also in Embodiment 2, the sum of the opening areas of the windward inlet 26A is formed to be larger than the sum of the opening areas of the leeward inlet 27A. Refrigerant that has flowed into the outward circulation path 31 from the refrigerant inflow portion 23 flows into the windward space 24A and the leeward space 25A through the windward inlet 26A and the leeward inlet 27A. It is substantially proportional to the opening areas of the inlet 26A and the leeward inlet 27A. Therefore, by adjusting the sum of the opening areas of the windward inlet 26A and the leeward inlet 27A, the amount of refrigerant flowing into the windward space 24A and the leeward space 25A can be easily controlled. Further, in the second embodiment, similarly to the first embodiment, regardless of the flow rate of the refrigerant flowing into the refrigerant inflow portion 23 from the pipe 15, the refrigerant flows out from the windward inlet 26A and the leeward inlet 27A. The flow rate ratio of the refrigerant can be appropriately maintained.

Furthermore, in the second embodiment, the outward circulation path 31 is provided outside the header 12A, and the refrigerant is circulated together with the windward space 24A and the leeward space 25A. It is possible to prevent unevenness in the flow rate of the coolant depending on the arrangement position (position in the stacking direction).

In Embodiment 2, the windward inlet 26A, the leeward inlet 27A, the windward circulation opening 33, and the leeward circulation opening 34 are configured by a plurality of holes, but are not limited to this. However, the windward inlet 26A, the leeward inlet 27A, the windward circulation inlet 33, and the leeward circulation inlet 34 are formed in a gap (slit) formed in the upper or lower portion of the outward circulation path 31, that is, the main body 20 or the first outlet. It may be a gap (slit) provided between the partition member 21 and the third partition member 30 .

[Embodiment 3]
The header used in the heat exchanger according to the third embodiment has a circulation line through which at least part of the refrigerant flowing into the header circulates, as in the second embodiment. Further, as in the first and second embodiments, the heat exchanger 5 is configured such that the length direction and width direction of the flat heat transfer tubes 11, that is, the direction parallel to the flat surface of the flat heat transfer tubes 11 is the horizontal direction. placed. Furthermore, the heat exchanger 5 is arranged such that the stacking direction of the flat heat transfer tubes 11, that is, the direction orthogonal to the flat surfaces of the flat heat transfer tubes 11 is the vertical direction. A blower fan (not shown) is provided in the vicinity of the heat exchanger 5 , and blows outside air to the heat exchanger 5 . FIG. 8 is a perspective view of a header 12B of a heat exchanger according to Embodiment 3 of the present invention. 9 is a horizontal cross-sectional view of an intermediate portion, (b) a horizontal cross-sectional view of an upper portion, and (c) a horizontal cross-sectional view of a lower portion of a header 12B of a heat exchanger according to Embodiment 3 of the present invention. is. 8, illustration of the flat heat transfer tubes 11 connected to the header 12B is omitted.

In the header 12B, a space below the main body 20 partitioned by the first partition member 21 is a refrigerant inflow portion 23 into which a low-temperature, low-pressure gas-liquid two-phase refrigerant flows from the expansion valve 7 via the pipe 15 . In addition, in the space on the upper side of the main body 20 partitioned by the first partition member 21, the second partition member 22 partitions the space on the windward side of the external air and the space on the leeward side. In the windward space, the third partition member 30B separates the inner space (on the side of the flat heat transfer tubes 11) and the outer space (on the side opposite to the side to which the flat heat transfer tubes 11 are connected). Here, the outer space is the forward circulation path 31B. The inner space is the windward space 24B, and the leeward space is the leeward space 25B. The windward space 24B and the leeward space 25B serve as circulation return paths, which will be described later.

An inflow port 32 is provided on the outside and upstream side of the first partition member 21, that is, on the first partition member 21, which serves as the bottom surface of the forward circulation path 31B. Refrigerant flows from the refrigerant inflow portion 23 through the inflow port 32 into the outward circulation path 31B.

A windward inlet 26B is provided in the upper portion of the third partition member 30B, and a leeward inlet 27B is provided outside the upper portion of the second partition member 22B. A windward circulation port 33B is provided at the lower portion of the third partition member 30B, and a leeward circulation port 34B is provided at the outer side of the lower portion of the second partition member 22B. The sum of the opening areas of the windward inlet 26B is approximately equal to the sum of the opening areas of the leeward inlet 27B, and the sum of the opening areas of the windward circulation inlet 33B is larger than the sum of the opening areas of the leeward circulation inlet 34B. formed.

The refrigerant that has flowed into the outward circulation passage 31B from the refrigerant inflow portion 23 through the inflow port 32 rises in the outward circulation passage 31B, flows into the windward space 24B from the windward inflow port 26B, and flows downwind from the leeward side inflow port 27B. It flows into the side space 25B. The refrigerant split into the windward space 24B and the leeward space 25B descends and flows out into the plurality of flat heat transfer tubes 11, and part of it circulates in the outward circulation path 31B from the windward circulation port 33B and the leeward circulation port 34B. do.

In the header 12B as well, the second partition member 22 and the third partition member are arranged so that the horizontal cross-sectional area of the forward circulation path 31B is smaller than the sum of the horizontal cross-sectional areas of the windward space 24B and the leeward space 25B. 30B is arranged. This makes it easier for the refrigerant to rise in the forward circulation path 31B. In addition, the horizontal cross-sectional area of the forward circulation path 31B is formed to be larger than the sum of the opening areas of the windward circulation port 33B and the leeward circulation port 34B. As a result, it is possible to prevent the refrigerant from backflowing (the windward space 24B and the leeward space 25B are the outward path, and the circulation outward path 31B is the return path), thereby facilitating the formation of the circulation flow.

In Embodiment 3, the distance between the windward inlet 26B and the flat heat transfer tubes 11 in the windward space 24B is shorter than the distance between the leeward inlet 27B and the flat heat transfer tubes 11 in the leeward space 25B. As a result, the pressure loss of the refrigerant is smaller in the windward space 24B than in the leeward space 25B. Since the lower the pressure loss, the lower the density of the refrigerant is, the more the liquid-phase refrigerant is supplied to the flow path of the flat heat transfer tubes 11 in the windward space 24, and the flow separation can be improved.

Furthermore, in the third embodiment, as in the second embodiment, a forward circulation path 31B is provided outside the header 12B, and the coolant is circulated together with the windward space 24B and the leeward space 25B. It is possible to prevent unevenness in the flow rate of the refrigerant due to the height difference in the arrangement of the flat heat transfer tubes 11 .

In the third embodiment, as in the second embodiment, the windward inlet 26B, the leeward inlet 27B, the windward circulation inlet 33B, and the leeward circulation inlet 34B are formed of a plurality of holes. However, it is not limited to this, and the windward inlet 26B, the leeward inlet 27B, the windward circulation outlet 33B, and the leeward circulation inlet 34B are gaps (slits) formed in the upper or lower part of the outward circulation path 31B. That is, it may be a gap (slit) provided between the main body portion 20 or the first partition member 21 and the third partition member 30B or the second partition member 22 .

Although the embodiment of the present invention has been described above, the present invention is not limited to this, and may include various embodiments and the like not described here.

1 Air conditioner 2 Indoor unit 3 Outdoor units 4, 5 Heat exchanger 6 Compressor 7 Expansion valve 8 Four-way valve 11 Flat heat transfer tubes 12, 13 Header 14 Fins 15, 16 Piping 20 Main body 21 First partition member 22 Second 2 partition member 23 refrigerant inlet portions 24, 24A, 24B windward spaces 25, 25A, 25B leeward spaces 26, 26A, 26B windward inlets 27, 27A, 27B leeward inlet 30 third partition member 31, 31B outward circulation path 32 inlets 33, 33B windward circulation ports 34, 34B leeward circulation ports

Claims (5)

a plurality of flat heat transfer tubes stacked so that their wide surfaces face each other;
a tubular header to which the ends of the plurality of flat heat transfer tubes are connected and which distributes the refrigerant to the plurality of flat heat transfer tubes;
The header is
a first partition member that partitions the tubular main body into an upper space and a lower refrigerant inflow portion that are aligned in the stacking direction of the plurality of flat heat transfer tubes;
The space on the upper side is partitioned into a refrigerant circulation return path on the side to which the plurality of flat heat transfer tubes are connected, and a refrigerant circulation outward path on the side opposite to the side to which the plurality of flat heat transfer tubes are connected. 3 partition members;
a second partition member that partitions the return circulation path into one windward space and the other leeward space in the width direction of the plurality of flat heat transfer tubes;
Above the third partition member,
a windward inlet for flowing refrigerant into the windward space;
a leeward inlet for inflowing a refrigerant into the leeward space,
The opening area of the windward inlet is larger than the opening area of the leeward inlet ,
A heat exchanger in which a windward circulation port and a leeward circulation port for circulating refrigerant from the windward space and the leeward space are provided below the third partition member. 2. The heat exchanger according to claim 1, wherein the horizontal cross-sectional area of the outward circulation path is larger than the sum of opening areas of the windward circulation port and the leeward circulation port. The sum of the opening areas of the windward circulation ports is larger than the sum of the opening areas of the leeward circulation ports.
A heat exchanger according to claim 1 or claim 2. a plurality of flat heat transfer tubes stacked so that their wide surfaces face each other;
a tubular header to which the ends of the plurality of flat heat transfer tubes are connected and which distributes the refrigerant to the plurality of flat heat transfer tubes;
The header is
a first partition member that partitions the tubular main body into an upper space and a lower refrigerant inflow portion that are aligned in the stacking direction of the plurality of flat heat transfer tubes;
The space on the upper side is partitioned into a refrigerant circulation return path on the side to which the plurality of flat heat transfer tubes are connected, and a refrigerant circulation outward path on the side opposite to the side to which the plurality of flat heat transfer tubes are connected. 3 partition members;
a second partition member that partitions the return circulation path into one windward space and the other leeward space in the width direction of the plurality of flat heat transfer tubes;
Above the third partition member,
a windward inlet for flowing refrigerant into the windward space;
a leeward inlet for inflowing a refrigerant into the leeward space,
The opening area of the windward inlet is larger than the opening area of the leeward inlet,
A heat exchanger in which a distance between the flat heat transfer tubes in the windward space and the windward inlet is shorter than a distance between the flat heat transfer tubes in the leeward space and the leeward inlet. a plurality of flat heat transfer tubes stacked so that their wide surfaces face each other;
a tubular header to which the ends of the plurality of flat heat transfer tubes are connected and which distributes the refrigerant to the plurality of flat heat transfer tubes;
The header is
a first partition member that partitions the tubular main body into an upper space and a lower refrigerant inflow portion that are aligned in the stacking direction of the plurality of flat heat transfer tubes;
The space on the upper side is partitioned into a refrigerant circulation return path on the side to which the plurality of flat heat transfer tubes are connected, and a refrigerant circulation outward path on the side opposite to the side to which the plurality of flat heat transfer tubes are connected. 3 partition members;
a second partition member that partitions the return circulation path into one windward space and the other leeward space in the width direction of the plurality of flat heat transfer tubes;
Above the third partition member,
a windward inlet for flowing refrigerant into the windward space;
a leeward inlet for inflowing a refrigerant into the leeward space,
The opening area of the windward inlet is larger than the opening area of the leeward inlet,
A heat exchanger in which the longitudinal cross-sectional area of the plurality of flat heat transfer tubes in the forward circulation path is smaller than the sum of the longitudinal cross-sectional areas of the plurality of flat heat transfer tubes in the windward space and the leeward space .

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