JP7310655B2 - 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. 9 is a cross-sectional view of the inside of the header 60 of Patent Document 1, in which (a) shows a case where the flow rate of the refrigerant 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. 9A, most of the liquid-phase refrigerant among the refrigerant that has flowed 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. 9B, the liquid-phase refrigerant is pushed toward the wall 61 by inertial force, collides with the wall 61, and then flows along the wall 61 into the leeward space. 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 to the plurality of flat heat transfer tubes, the header partitioning the tubular main body into two spaces aligned in the stacking direction of the plurality of flat heat transfer tubes. 1 partition member, and the space on the upper side of the tubular main body partitioned by the first partition member is divided into a circulation return path, which is a space on the side to which the plurality of flat heat transfer tubes are connected, and the plurality of flat heat transfer tubes. a second partition member that divides the space into an outward circulation path, which is a space to which the heat pipe is not connected, and is provided with an upper communication port at an upper portion and a lower communication port at a lower portion, and the tubular body portion is the first partition The space on the upper side partitioned by the member is a refrigerant inflow portion, and the first partition member is provided with a refrigerant inflow port through which the refrigerant flows into the outward circulation path, and communicates with the lower portion of the second partition member. The opening is provided on one side in the width direction of the plurality of flat heat transfer tubes, and the one side is the leeward side in the direction of flow of the external air.

According to the present invention, it is possible to obtain the target heat exchange capacity 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) a horizontal sectional view of the middle portion, (b) a horizontal sectional view of the upper portion, and (c) a horizontal sectional view of the lower portion of the header of FIG. FIG. 5 is a perspective view of a header of a heat exchanger according to Embodiment 2 of the present invention. FIG. 6 shows (a) 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 of a heat exchanger according to Embodiment 2 of the present invention. FIG. 7 is a perspective view of a header of a heat exchanger according to Embodiment 3 of the present invention. FIG. 8 shows (a) 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 of a heat exchanger according to Embodiment 3 of the present invention. 9A and 9B are cross-sectional views of the header of the prior art when the flow rate of the refrigerant is small, and FIG.

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 illustrating the heat exchanger 5 according to Embodiment 1 of the present invention, in which (a) is a plan view of the heat exchanger 5 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 flow direction of the external air, 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. is sucked into the compressor 6 via the

(header)
Next, the header 12 according to Embodiment 1 of the present invention will be described with reference to FIGS. 3 and 4. 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.

3 and 4, in the stacking direction (vertical direction) of the flat heat transfer tubes 11, the header 12 is configured such that the tubular body portion 20 is divided into two spaces, an upper space and a lower space, arranged in the stacking direction. and a second partition member 22 provided in the upper space partitioned by the first partition member 21 . The upper space partitioned by the first partition member 21 has a return circulation path 25 which is a space connected to the flat heat transfer tubes 11 and an outward circulation path 24 separated from the return circulation path 25 by the second partition member 22. The first partition member 21 is provided over the entire body portion 20 in the horizontal direction. The second partition member 22 is provided over the entire vertical direction of the space above the first partition member 21 of the main body 20 . 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 second partition member 22 includes a second partition member airflow surface 22 a that is parallel to the stacking direction and width direction of the flat heat transfer tubes 11 and a second partition member wind surface 22 a that is parallel to the length direction and width direction of the flat heat transfer tubes 11 . There are two partition member leeward surfaces 22b. 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 an internal cavity.

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 . The outward circulation path 24 is used so as to be on the windward side of the main body 20 .

Inside the main body 20 , a coolant inlet 26 is provided on the windward side and outside of the first partition member 21 , that is, on the first partition member 21 that serves as the bottom surface of the outward circulation path 24 . Refrigerant flows into the outward circulation path 24 from the refrigerant inflow portion 23 via the refrigerant inlet 26 .

An upper communication port 27 is provided above the second partition member 22 and on the windward side in the direction of external air flow, i.e., above the second partition member 22a. A lower communication port 28 is provided on the leeward side of the air flow direction, that is, on the lower portion of the leeward surface 22b of the second partition member. The refrigerant that has flowed into the outward circulation path 24 from the refrigerant inlet 26 rises in the outward circulation path 24 and flows into the return circulation path 25 via the upper communication port 27 . The refrigerant that has flowed into the return circulation path 25 descends and is split into a plurality of flat heat transfer tubes 11 connected to the return circulation path 25 , and part of the refrigerant flows into the outward circulation path 24 through the lower communication port 28 . In the header 12, by forming a circulating flow with the forward circulation path 24, the upper communication port 27, the return circulation path 25, and the lower communication port 28, the flat heat transfer tubes 11 connected to the header 12 are arranged at different positions (arranged at the top). It is possible to reduce unevenness in the flow rate of the refrigerant due to the flat heat transfer tubes 11 and the flat heat transfer tubes 11 arranged at the bottom.

The second partition member 22 is arranged so that the horizontal cross-sectional area of the outward circulation path 24 is smaller than the horizontal cross-sectional area of the return circulation path 25 . As a result, the flow velocity of the refrigerant flowing through the forward circulation path 24 increases, so that the refrigerant rises easily. Further, the horizontal cross-sectional area of the forward circulation path 24 is formed to be larger than the sum of the opening areas of the lower communication ports 28, which will be described later. As a result, it is possible to prevent reverse flow of the refrigerant (the return circulation path 25 is the outward path and the outward circulation path 24 is the return path), thereby facilitating the formation of the circulation flow.

In the header 12 , the upper communication port 27 is provided on one side of the flat heat transfer tubes 11 in the width direction (horizontal direction). The heat exchanger 5 is used such that the one side thereof is positioned on the windward side in the direction of flow of the external air. As a result, the distance between the flow path on the windward side of the flat heat transfer tubes 11 connected to the header 12 and the upper communication port 27 is Shorter than 27 distances. The distance between the flow path on the windward side of the flat heat transfer tubes 11 and the upper communication port 27 is shorter than the distance between the flow path on the leeward side and the upper communication port 27, so that the flow path on the windward side of the flat heat transfer tubes 11 has more air flow. Refrigerant can flow in, and more heat can be exchanged on the windward side where the heat load is relatively large.

Further, the header 12 is used so that the lower communication port 28 is positioned on the leeward side in the direction of the flow of the outside air. Since the lower communication port 28 is positioned on the leeward side, the refrigerant flowing on the leeward side of the return circulation path 25 is more likely to be drawn into the lower communication port 28 than the refrigerant flowing on the windward side. This makes it easier for the refrigerant to flow through the flow path located on the windward side of the flat heat transfer tubes 11, and the flow rate of the refrigerant can be increased.

In the first embodiment, the outward circulation path 24 is provided outside the header 12 and on the windward side of the external air flow, and the lower communication port 28 is positioned on the leeward side of the external air flow. It is possible to allow more refrigerant to flow into the flow path on the windward side of the inside.

In Embodiment 1, by positioning the upper communication port 27 on the windward side of the flow of the external air, the distance between the flow path on the windward side of the flat heat transfer tube 11 and the upper communication port 27 is the flow path on the leeward side. and the upper communication port 27 , more refrigerant can flow into the flow path on the windward side in the flat heat transfer tube 11 .

[Embodiment 2]
FIG. 5 is a perspective view of a header 12A of a heat exchanger according to Embodiment 2 of the present invention. 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 shows (a) 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 12A of a heat exchanger according to Embodiment 2 of the present invention. is.

In the header 12A, the second partition member 22A provided in the space on the upper side partitioned by the first partition member 21 is a second partition member having a surface parallel to the stacking direction and the width direction of the flat heat transfer tubes 11. It has a leeward surface 22a and a second partition member leeward surface 22b parallel to the lengthwise direction and the widthwise direction of the flat heat transfer tube 11 . The heat exchanger 5 is arranged such that the other side is the upstream side (windward side) of the external air, and the one side is the downstream side (leeward side) of the external air.

Inside the main body 20, the space on the upper side partitioned by the first partition member 21 is divided into a return circulation path 25A, which is a space connected to the flat heat transfer tubes 11, and a return circulation path 22A, which is a space connected to the flat heat transfer tube 11. 25A and a separate outbound circulation path 24A. Outward circulation path 24A is provided on the leeward side and outside of main body 20 .

An upper communication port 27A is provided above the second partition member 22A and on one side in the width direction (horizontal direction) of the flat heat transfer tube 11, that is, above the second partition member windward surface 22b. A lower communication port 28A is provided in the lower part of the member 22 and on the leeward side in the direction of flow of external air, that is, in the lower part of the leeward surface 22a of the second partition member. The refrigerant that has flowed into the outward circulation path 24A from the refrigerant inlet 26 rises in the outward circulation path 24A and flows into the return circulation path 25A via the upper communication port 27A. The refrigerant that has flowed into the return circulation path 25A is divided into a plurality of flat heat transfer tubes 11 connected to the return circulation path 25A while descending, and part of the refrigerant flows into the outward circulation path 24A through the lower communication port 28A. In the header 12A, a circulating flow is formed by the forward circulation path 24A, the upper communication port 27A, the return circulation path 25A, and the lower communication port 28A. It is possible to reduce unevenness in the flow rate of the refrigerant due to the flat heat transfer tubes 11 and the flat heat transfer tubes 11 arranged at the bottom.

In the header 12A, as in the first embodiment, the second partition member 22A is arranged so that the horizontal cross-sectional area of the outward circulation path 24A is smaller than the horizontal cross-sectional area of the return circulation path 25A. This makes it easier for the refrigerant to rise in the forward circulation path 24A. Further, the horizontal cross-sectional area of the forward circulation path 24A is formed to be larger than the sum of the opening areas of the lower communication ports 28A, which will be described later. As a result, it is possible to prevent reverse flow of the refrigerant (the return circulation path 25A is the outward path and the outward circulation path 24A is the return path), thereby facilitating the formation of the circulation flow.

In the header 12A, the lower communication port 28A is provided on the other side in the width direction (horizontal direction) of the flat heat transfer tubes 11 (downwind side in the flow direction of the external air). By providing the lower communication port 28A on the leeward side, the refrigerant flowing on the leeward side is more likely to be drawn into the lower communication port 28A than the refrigerant flowing on the windward side of the return circulation path 25A. This makes it easier for the refrigerant to flow through the flow path located on the windward side of the flat heat transfer tubes 11 .

Further, in the header 12A, the upper communication port 27A is provided on one side (upwind side in the direction of flow of external air) of the flat heat transfer tubes 11 in the width direction (horizontal direction). Accordingly, the distance between the flow path on the windward side of the flat heat transfer tubes 11 connected to the header 12A and the upper communication port 27A is It becomes shorter than the distance of 27A. Although the distance between the flow path on the windward side and the upper communication port 27A and the distance between the flow path on the leeward side and the upper communication port 27A are larger than those in the first embodiment, the distance from the upper communication port 27A to the flow path of the flat heat transfer tubes 11 can be prevented, and a large amount of refrigerant can be diverted to the flow path on the windward side of the flat heat transfer tube 11 .

In the second embodiment, the outward circulation path 24A is provided outside the header 12A and on one side in the width direction (horizontal direction) of the flat heat transfer tubes 11 (downwind side of the external air flow), and the lower communication port 28A is provided in the flat heat transfer tube. By providing it on the other side (downwind side of the external air flow) in the width direction (horizontal direction) of the heat tube 11 , it is possible to allow more refrigerant to flow into the flow path on the windward side in the flat heat transfer tube 11 . .

[Embodiment 3]
FIG. 7 is a perspective view of a header 12B of a heat exchanger according to Embodiment 3 of the present invention. 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. 8 shows (a) 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.

In the header 12B, the second partition member 22B provided in the upper space partitioned by the first partition member 21 has a second partition member leeward surface 22c and a second partition member leeward surface 22c arranged orthogonal to each other. It is composed of the partition member windward surface 22 d and is provided over the entire vertical direction on the upper side of the first partition member 21 of the main body 20 .

Inside the main body 20, the space on the upper side partitioned by the first partition member 21 is separated from the return circulation path 25B, which is a space connected to the flat heat transfer tubes 11, and the return circulation path 25B by the second partition member 22B. It has a circulating outbound route 24B. The outward circulation path 24B is provided outside the body portion 20 .

Above the second partition member 22B and on one side in the width direction (horizontal direction) of the flat heat transfer tube 11 (windward side in the direction of external air flow), that is, above the second partition member windward surface 22d. A communication port 27B is provided, and is connected to the lower portion of the second partition member 22 and the other side in the width direction (horizontal direction) of the flat heat transfer tube 11 (downwind side in the direction of flow of the external air), that is, the second partition member wind. A lower communication port 28B is provided in the lower portion of the lower surface 22c. The refrigerant that has flowed into the outward circulation path 24B from the refrigerant inlet 26 rises in the outward circulation path 24B and flows into the return circulation path 25B via the upper communication port 27B. The refrigerant that has flowed into the return circulation path 25B is divided into a plurality of flat heat transfer tubes 11 connected to the return circulation path 25B while descending, and part of the refrigerant flows into the outward circulation path 24B through the lower communication port 28B. In the header 12B, a circulating flow is formed by the forward circulation path 24B, the upper communication port 27B, the return circulation path 25B, and the lower communication port 28B. It is possible to reduce unevenness in the flow rate of the refrigerant due to the flat heat transfer tubes 11 and the flat heat transfer tubes 11 arranged at the bottom.

In the header 12B, as in the first embodiment, the second partition member 22B is arranged so that the horizontal cross-sectional area of the outward circulation path 24B is smaller than the horizontal cross-sectional area of the return circulation path 25B. This makes it easier for the refrigerant to rise in the forward circulation path 24B. Further, the horizontal cross-sectional area of the forward circulation path 24B is formed to be larger than the sum of the opening areas of the lower communication ports 28B, which will be described later. As a result, it is possible to prevent reverse flow of the refrigerant (the return circulation path 25B is the outward path and the outward circulation path 24B is the return path), making it easy to form a circulation flow.

In the header 12B, the lower communication port 28B is provided on the other side in the width direction (horizontal direction) of the flat heat transfer tubes 11 (downwind side in the flow direction of the external air). By providing the lower communication port 28B on the leeward side, the refrigerant flowing on the leeward side is more likely to be drawn into the lower communication port 28B than the refrigerant flowing on the windward side of the return circulation path 25B. This makes it easier for the refrigerant to flow into the flow path located on the windward side of the flat heat transfer tubes 11, and the flow rate of the refrigerant can be increased.

Further, in the header 12B, the upper communication port 27B is provided on one side in the width direction (horizontal direction) of the flat heat transfer tubes 11 (upwind side in the flow direction of the external air). As a result, the distance between the flow path on the windward side of the flat heat transfer tubes 11 connected to the header 12B and the upper communication port 27B is It becomes shorter than the distance of 27B. Although the distance between the flow path on the windward side and the upper communication port 27B and the distance between the flow path on the leeward side and the upper communication port 27B are larger than those in the first embodiment, the distance from the upper communication port 27B to the flow path of the flat heat transfer tubes 11 is increased. can be prevented, and a large amount of refrigerant can be diverted to the flow path on the windward side of the flat heat transfer tube 11 .

In the third embodiment, the forward circulation path 24B is provided outside the header 12B, and the lower communication port 28B is provided on the other side in the width direction (horizontal direction) of the flat heat transfer tubes 11 (on the leeward side of the external air flow). As a result, more refrigerant can flow into the windward flow path in the flat heat transfer tube 11 .

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, 22A, 22B Second partition member 23 Refrigerant inflow portions 24, 24A, 24B Circulation outward passages 25, 25A, 25B Circulation return passage 26 Refrigerant inflow ports 27, 27A, 27B Upper communication ports 28, 28A, 28B Lower communication 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 two spaces aligned in the stacking direction of the plurality of flat heat transfer tubes;
The space on the upper side of the tubular main body sectioned by the first partition member is a circulation return path that is the space on the side where the plurality of flat heat transfer tubes are connected, and the side where the plurality of flat heat transfer tubes are not connected. and a second partition member that partitions into an outward circulation path that is a space of and has an upper communication port at the top and a lower communication port at the bottom,
The space on the lower side of the tubular main body sectioned by the first partition member is a coolant inlet,
The first partition member is provided with a coolant inlet port through which coolant flows into the forward circulation path,
A heat exchanger in which the lower communication port of the second partition member is provided on one side in the width direction of the plurality of flat heat transfer tubes, and the one side is the leeward side in the flow direction of the external air. 2. The heat exchanger according to claim 1, wherein the horizontal cross-sectional area of the outward circulation path is smaller than the horizontal cross-sectional area of the return circulation path. 3. The heat exchanger according to claim 1, wherein the horizontal cross-sectional area of the forward circulation path is smaller than the sum of the areas of the lower communication ports. The heat exchanger according to any one of claims 1 to 3, wherein the outward circulation path is provided on the windward side of the flow of external air. The heat exchanger according to any one of claims 1 to 4, wherein the upper communication port is provided on the windward side of the external air flow.

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