JP2021139531A - Heat exchanger - Google Patents

Abstract

To provide a heat exchanger capable of acquiring target heat exchanging capacity without depending on a flow rate of a refrigerant.SOLUTION: A heat exchanger of this invention includes a plurality of flat heat transfer tubes, and a tubular header to which ends of the flat heat transfer tubes are connected. The header includes: a first partition member partitioning a tubular body portion in a stacking direction of the plurality of the flat heat transfer tubes; and a second partition member partitioning an upper side of the tubular body portion partitioned by the first partitioning member into a circulation returning passage which is a space where the flat heat transfer tubes are connected, and a circulation going passage which is a space where the flat heat transfer tubes are not connected, and having an upper refrigerant communication port in an upper portion, and a lower refrigerant communication port in a lower portion. The upper refrigerant communication port of the second partition member is provided in a windward side of a flow direction of outside air.SELECTED DRAWING: Figure 3

Description

The present invention relates to a heat exchanger.

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 the left and right headers, respectively, and a refrigerant is diverted from one header to the flat heat transfer tube. In an air conditioner using such a heat exchanger, when heat exchange between the refrigerant and the outside air is performed, a large amount of heat load is applied to the refrigerant in the flow path on the wind side, so that the flow of the same flat heat transfer tube is applied. A technique has been proposed in which a larger amount of refrigerant is circulated in a flow path located on the leeward side than in a flow path located on the leeward side even in a road (see, for example, Patent Documents 1 and 2).

Japanese Unexamined Patent Publication No. 2006-266521 JP-A-2018-100800

In the above-mentioned technique, the inside of the header is divided into a space on the leeward side and a space on the leeward side, and the refrigerant flows from the space on the leeward side to the space on the leeward side. 9A and 9B are cross-sectional views of the header 60 of Patent Document 1, in which FIG. 9A shows a case where the flow rate of the refrigerant is small and FIG. 9B shows a case where the flow rate of the refrigerant is large. Inside the header 60, a wall 61 extending from the side facing the side to which the flat heat transfer tube 63 is connected is provided, and the inside of the header 60 is divided into a leeward space 62a and a leeward space 62b by the wall 61. ing. When the flow rate of the refrigerant is small, as shown in FIG. 9A, most of the liquid phase refrigerants among the refrigerants flowing into the leeward space 62a from the pipe 50 do not reach the wall 61 (leeward space 62b). It flows into the windward flow path 63a 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 the inertial force, collides with the wall 61, and then is leeward along the wall 61. A large amount flows into 62b, and then flows into the leeward flow path 63b of the flat heat transfer tube 63. In such a case, the amount of the liquid phase refrigerant having a large amount of heat exchange flowing into the flow path of the flat heat transfer tube on the leeward side with a small heat load increases, and the heat flowing into the flow path on the wind side of the flat heat transfer tube having 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.

The present invention has been made in view of the above, and an object of the present invention is to provide a heat exchanger capable of obtaining a target heat exchange capacity regardless of the flow rate of the refrigerant.

In order to solve the above-mentioned problems and achieve the object, the heat exchanger according to the present invention has a plurality of flat heat transfer tubes laminated so that wide surfaces face each other, and end portions of the plurality of flat heat transfer tubes. A tubular header that divides the refrigerant into the plurality of flat heat transfer tubes, and the header divides the tubular main body into two spaces arranged in the stacking direction of the plurality of flat heat transfer tubes. The circulation return path and the plurality of flat transmissions, which are the spaces on the upper side of the tubular main body portion partitioned by the partition member 1 and the first partition member, on the side to which the plurality of flat heat transfer tubes are connected. It is divided into a circulation outward path, which is a space on the side where the heat pipe is not connected, and has a second partition member having an upper communication port at the upper part and a lower communication port at the lower part, and the tubular main body portion is the first partition. The space on the lower side partitioned by the members is a refrigerant inflow portion, and in the space on the upper side in which the tubular main body portion is partitioned by the first partition member, the first partition member has the circulation outward path. A refrigerant inflow port for flowing a refrigerant is provided in the second partition member, and an upper refrigerant 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 in the flow direction of external air. The wind side of.

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

FIG. 1 is a diagram illustrating a configuration of an air conditioner to which the heat exchanger according to the first embodiment of the present invention is applied. 2A and 2B are views for explaining the heat exchanger according to the first embodiment 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 the first embodiment of the present invention. 4A and 4B are a horizontal cross-sectional view of the middle portion of the header of FIG. 3, a horizontal cross-sectional view of the upper portion, and a horizontal cross-sectional view of the lower portion of the header. FIG. 5 is a perspective view of the header of the heat exchanger according to the second embodiment of the present invention. FIG. 6 is a horizontal sectional view of (a) an intermediate portion, (b) an upper horizontal sectional view, and (c) a lower horizontal sectional view of the header of the heat exchanger according to the second embodiment of the present invention. FIG. 7 is a perspective view of the header of the heat exchanger according to the third embodiment of the present invention. FIG. 8 is a horizontal sectional view of (a) an intermediate portion, (b) an upper horizontal sectional view, and (c) a lower horizontal sectional view of the header of the heat exchanger according to the third embodiment of the present invention. 9A and 9B are a cross-sectional view of the header of the prior art when the flow rate of the refrigerant is low, and FIG. 9B is a cross-sectional view of the header when the flow rate is high.

Hereinafter, embodiments for carrying out the present invention (hereinafter, referred to as “embodiments”) will be described with reference to the accompanying drawings. The same configuration is given the same number throughout the description of the embodiment.

[Embodiment 1]
(Air conditioner)
FIG. 1 is a diagram illustrating a configuration of an air conditioner 1 to which the heat exchanger 4 and the heat exchanger 5 according to the first embodiment 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 the heating operation, the high-temperature and high-pressure gas refrigerant discharged from the compressor 6 of the outdoor unit 3 flows into the heat exchanger 4 functioning as a condenser via the four-way valve 8. During the heating operation, the refrigerant is flowing in the direction indicated by the black arrow in FIG. In the heat exchanger 4, the refrigerant that has exchanged heat with the external air is liquefied. The liquefied high-pressure refrigerant passes through the expansion valve 7 and is depressurized, and flows into the heat exchanger 5 which functions 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 external air is gasified. The gasified low-pressure refrigerant is sucked into the compressor 6 via the four-way valve 8.

During the cooling operation, the high-temperature and high-pressure gas refrigerant discharged from the compressor 6 of the outdoor unit 3 flows into the heat exchanger 5 functioning as a condenser via the four-way valve 8. During the cooling operation, the refrigerant is flowing in the direction indicated by the white arrow in FIG. In the heat exchanger 5, the refrigerant that has exchanged heat with the external air is liquefied. The liquefied high-pressure refrigerant passes through the expansion valve 7 and is depressurized, and flows into the heat exchanger 4 which functions 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 external 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 the first embodiment of the present invention is applicable to both the heat exchanger 4 and the heat exchanger 5, but is applicable to the heat exchanger 5 that functions as an evaporator during the heating operation. explain. 2A and 2B are views for explaining the heat exchanger 5 according to the first embodiment of the present invention, in which FIG. 2A is a plan view of the heat exchanger 5 and FIG. 2B 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 in which the ends of the plurality of flat heat transfer tubes 11 are connected and the refrigerant is diverted to the flat heat transfer tubes 11, and a plurality of flat heat transfer tubes. It includes a tubular header 13 to which the other end of the heat pipe 11 is connected and joins the refrigerant flowing out from the flat heat transfer tube 11, and a plurality of flat plate-shaped fins 14 joined to the flat heat transfer tube 11. The flat heat transfer tube 11 extends in a direction orthogonal to the external air flow direction indicated by an arrow in FIG. 2A, and has a flat cross section. Inside the flat heat transfer tube 11, there are a plurality of flow paths extending in the same direction as the flat heat transfer tube extends. In this embodiment, the direction in which the external air flows is the width direction of the flat heat transfer tube 11, and the direction orthogonal to the direction in which the external air flows, which is the direction in which the flat heat transfer tube 11 extends, is the length direction of the flat heat transfer tube 11. And. As shown in FIG. 2B, the flat heat transfer tubes 11 are stacked in the vertical direction so that the flat surfaces (wide surfaces) of the side surfaces face each other, and the left and right ends are connected to the header 12 and the header 13. Has been done. Further, a plurality of fins 14 are arranged between the header 12 and the header 13 so as to be orthogonal to the flat heat transfer tube 11. The low-temperature, low-pressure gas-liquid two-phase refrigerant that has passed through the expansion valve 7 and has been decompressed is supplied to the header 12 by the pipe 15 and is divided into the flat heat transfer tubes 11. When flowing through the flat heat transfer tube 11, the gas-liquid two-phase refrigerant that exchanged heat with air through the fins 14 gasified and flowed out to the header 13, and the refrigerant that merged in the header 13 passed through the pipe 16 and the four-way valve 8. It is sucked into the compressor 6 via.

(header)
Next, the header 12 according to the first embodiment of the present invention will be described with reference to FIGS. 3 and 4. In the present specification, the side of the header 12 facing the flat heat transfer tube 11 is referred to as the inside, and the side of the header 12 facing the flat heat transfer tube 11 is referred to as the outside. Further, the heat exchanger 5 is arranged so that the length direction and the width direction of the flat heat transfer tube 11, that is, the direction parallel to the flat surface of the flat heat transfer tube 11 is the horizontal direction. Further, the heat exchanger 5 is arranged so that the stacking direction of the flat heat transfer tubes 11, that is, the direction orthogonal to the flat plane 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 the blower fan sends external air to the heat exchanger 5. In FIG. 3, the fin 14 is not shown.

As shown in FIGS. 3 and 4, in the header 12, in the stacking direction (vertical direction) of the flat heat transfer tubes 11, the tubular main body 20 is arranged in two spaces arranged in the stacking direction, that is, the upper space and the lower side. It has a first partition member 21 for partitioning the space, and a second partition member 22 provided in the space on the upper side partitioned by the first partition member 21. The space on the upper side partitioned by the first partition member 21 has a circulation return path 25 which is a space connected to the flat heat transfer tube 11 and a circulation return path 24 separated from the circulation return path 25 by the second partition member 22. .. The first partition member 21 is provided over the entire horizontal direction of the main body 20. The second partition member 22 is provided over the entire space on the upper side of the first partition member 21 of the main body 20 in the vertical direction. The heat exchanger 5 is arranged so that the other space is on the upstream side (leeward side) of the external air and one space is on the downstream side (leeward side) of the external air. The second partition member 22 includes a second partition member wind upper surface 22a having a surface parallel to the stacking direction and the width direction of the flat heat transfer tube 11, and a surface parallel to the length direction and the width direction of the flat heat transfer tube 11. It has 2 partition member wind lower surfaces 22b. As shown in FIGS. 3 and 4, the header 12 has a cylindrical shape, but the header 12 is not limited to the cylindrical shape, and may have a prismatic shape with a hollow inside.

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

A refrigerant inflow port 26 is provided on the windward side and outside of the first partition member 21 inside the main body 20, that is, on the first partition member 21 which is the bottom surface of the circulation outward path 24. Refrigerant flows into the circulation outward path 24 from the refrigerant inflow section 23 via the refrigerant inflow port 26.

An upper communication port 27 is provided above the second partition member 22 and on the windward side in the external air flow direction, that is, above the second partition member 22a, and is below the second partition member 22 and outside. A lower communication port 28 is provided on the windward side in the air flow direction of the above, that is, on the lower part of the windward upper surface 22a of the second partition member. The refrigerant that has flowed into the circulation outward path 24 from the refrigerant inflow port 26 rises in the circulation outward path 24 and flows into the circulation return path 25 through the upper communication port 27. The refrigerant flowing into the circulation return path 25 is divided into a plurality of flat heat transfer tubes 11 connected in the circulation return path 25 while descending, and a part of the refrigerant flows into the circulation outbound path 24 from the lower communication port 28. In the header 12, the difference in the arrangement position of the flat heat transfer tube 11 connected to the header 12 (arranged at the upper part) by forming a circulation flow by the circulation outward path 24, the upper communication port 27, the circulation return path 25, and the lower communication port 28. It is possible to reduce the deviation of the flow rate of the refrigerant by the flat heat transfer tube 11 and the flat heat transfer tube 11) arranged at the lower part.

The second partition member 22 is arranged so that the horizontal cross-sectional area of the circulation outward path 24 is smaller than the horizontal cross-sectional area of the circulation return path 25. As a result, the flow velocity of the refrigerant flowing in the circulation outward path 24 increases, so that the refrigerant tends to rise. Further, the horizontal cross-sectional area of the circulation outward path 24 is formed to be larger than the sum of the opening areas of the lower communication port 28, which will be described later. As a result, it is possible to prevent the backflow of the refrigerant (the circulation return path 25 becomes the outward path and the circulation outward path 24 becomes the return path), and the formation of the circulation flow becomes easy.

In the header 12, the upper communication port 27 is provided on one side of the flat heat transfer tube 11 in the width direction (horizontal direction). The heat exchanger 5 is used so that one side thereof is located on the windward side in the external air flow direction. As a result, the distance between the leeward flow path and the upper communication port 27 of the flat heat transfer tube 11 connected to the header 12 is the leeward flow path and the upper communication port of the flat heat transfer tube 11 connected to the header 12. It will be shorter than the distance of 27. The distance between the windward flow path of the flat heat transfer tube 11 and the upper communication port 27 is shorter than the distance between the leeward flow path and the upper communication port 27, so that the flow path on the windward side of the flat heat transfer tube 11 is increased. 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 located on the windward side in the external air flow direction. Since the lower communication port 28 is located on the windward side, the refrigerant mainly circulates on the windward side of the circulation return path 25. Can be inflowed.

In the first embodiment, the circulation outward path 24 is provided on the outside of the header 12 and on the windward side of the external air flow, and the upper communication port 27 is located on the windward side of the external air flow, whereby the flat heat transfer tube 11 is provided. It is possible to allow more refrigerant to flow into the inner flow path on the windward side.

In the first embodiment, since the lower communication port 28 is located on the windward side of the external air flow, a larger amount of refrigerant flows into the windward side flow path of the flat heat transfer tube 11 as compared with the leeward side flow path. However, the present invention is not limited to this, and the lower communication port 28 may be provided in the lower part of the second partition member 22b.

[Embodiment 2]
FIG. 5 is a perspective view of the header 12A of the heat exchanger according to the second embodiment of the present invention. Further, similarly to the first embodiment, the heat exchanger 5 is arranged so that the length direction and the width direction of the flat heat transfer tube 11, that is, the direction parallel to the flat surface of the flat heat transfer tube 11 is the horizontal direction. NS. Further, the heat exchanger 5 is arranged so that the stacking direction of the flat heat transfer tubes 11, that is, the direction orthogonal to the flat plane 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 the blower fan sends external air to the heat exchanger 5. 6A and 6B are a horizontal sectional view of an intermediate portion, FIG. 6B is a horizontal sectional view of an upper portion, and FIG. 6C is a horizontal sectional view of a lower portion of the header 12A of the heat exchanger according to the second embodiment 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 tube 11. It has a wind lower surface 22a and a second partition member wind upper surface 22b having a surface parallel to the stacking direction and the length direction of the flat heat transfer tube 11. The heat exchanger 5 is arranged so that the other side is on the upstream side (leeward side) of the external air and one side is on 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 separated from the circulation return path 25A, which is a space connected to the flat heat transfer tube 11, and the circulation return path 25A by the second partition member 22A. It has a circular outbound route 24A. The circulation outward path 24A is provided on the leeward side and outside of the main body 20.

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

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 circulation outward path 24A is smaller than the horizontal cross-sectional area of the circulation return path 25A. As a result, the refrigerant tends to rise in the circulation outward path 24A. Further, the horizontal cross-sectional area of the circulation outward path 24A is formed to be larger than the sum of the opening areas of the lower communication port 28A, which will be described later. As a result, it is possible to prevent the backflow of the refrigerant (the circulation return path 25A becomes the outward path and the circulation outward path 24A becomes the return path), and the formation of the circulation flow becomes easy.

In the header 12A, the upper communication port 27A is provided on one side (horizontal direction) of the flat heat transfer tube 11 (on the windward side in the external air flow direction). As a result, the distance between the leeward flow path and the upper communication port 27A of the flat heat transfer tube 11 connected to the header 12A is the leeward flow path and the upper communication port of the flat heat transfer tube 11 connected to the header 12A. It will be shorter than the distance of 27A. Although the distance between the leeward flow path and the upper communication port 27A and the distance between the leeward flow path 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 tube 11 A large amount of refrigerant can be diverted to the windward flow path of the flat heat transfer tube 11.

Further, the header 12A is provided with a lower communication port 28A on one side (horizontal direction) of the flat heat transfer tube 11 in the width direction (windward side in the external air flow direction). By providing the lower communication port 28A on the windward side, the refrigerant mainly circulates on the windward side of the circulation return path 25A. It can be inflowed.

In the second embodiment, the circulation outward path 24A is provided on the outside of the header 12A and on the other side (leeward side of the external air flow) in the width direction (horizontal direction) of the flat heat transfer tube 11, and the upper communication port 27A is provided on the outside. By providing it on the windward side of the air flow, it is possible to allow a larger amount of refrigerant to flow into the windward flow path in the flat heat transfer tube 11.

In the second embodiment, the lower communication port 28A is also provided on one side (the windward side of the external air flow) in the width direction (horizontal direction) of the flat heat transfer tube 11, so that the flow path on the windward side of the flat heat transfer tube 11 is provided. Although a larger amount of refrigerant can flow into the flow path on the leeward side, the flow is not necessarily limited to this, and the lower communication port 28A may be provided below the windward lower surface 22a of the second partition member. good.

[Embodiment 3]
FIG. 7 is a perspective view of the header 12B of the heat exchanger according to the third embodiment of the present invention. Further, similarly to the first embodiment, the heat exchanger 5 is arranged so that the length direction and the width direction of the flat heat transfer tube 11, that is, the direction parallel to the flat surface of the flat heat transfer tube 11 is the horizontal direction. NS. Further, the heat exchanger 5 is arranged so that the stacking direction of the flat heat transfer tubes 11, that is, the direction orthogonal to the flat plane 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 the blower fan sends external air to the heat exchanger 5. 8A and 8B are a horizontal sectional view of an intermediate portion, FIG. 8B is a horizontal sectional view of an upper portion, and FIG. 8C is a horizontal sectional view of a lower portion of the header 12B of the heat exchanger according to the third embodiment of the present invention. Is.

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

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

The upper part of the second partition member 22B and one side in the width direction (horizontal direction) of the flat heat transfer tube 11 (the wind side in the external air flow direction), that is, the upper part of the second partition member wind upper surface 22d. The communication port 27B is provided, and the lower part of the second partition member 22 and one side in the width direction (horizontal direction) of the flat heat transfer tube 11 (the wind side in the external air flow direction), that is, the wind of the second partition member. A lower communication port 28B is provided below the upper surface 22d. The refrigerant that has flowed into the circulation outward path 24B from the refrigerant inflow port 26 rises in the circulation outward path 24B and flows into the circulation return path 25B through the upper communication port 27B. The refrigerant flowing into the circulation return path 25B is divided into a plurality of flat heat transfer tubes 11 connected in the circulation return path 25B while descending, and a part of the refrigerant flows into the circulation outbound path 24B from the lower communication port 28B. In the header 12B, a difference in the arrangement position of the flat heat transfer tube 11 connected to the header 12B (arranged at the upper part) by forming a circulation flow by the circulation outward path 24B, the upper communication port 27B, the circulation return path 25B, and the lower communication port 28B. It is possible to reduce the deviation of the flow rate of the refrigerant by the flat heat transfer tube 11 and the flat heat transfer tube 11) arranged at the lower part.

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 circulation outward path 24B is smaller than the horizontal cross-sectional area of the circulation return path 25B. As a result, the refrigerant tends to rise in the circulation outward path 24B. Further, the horizontal cross-sectional area of the circulation outward path 24B is formed to be larger than the sum of the opening areas of the lower communication port 28B, which will be described later. As a result, it is possible to prevent the backflow of the refrigerant (the circulation return path 25B becomes the outward path and the circulation outward path 24B becomes the return path), and the formation of the circulation flow becomes easy.

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

Further, the header 12B is provided with a lower communication port 28B on one side (horizontal direction) of the flat heat transfer tube 11 in the width direction (windward side in the external air flow direction). By providing the lower communication port 28B on the windward side, the refrigerant mainly circulates on the windward side of the circulation return path 25B. It can be inflowed.

In the third embodiment, the circulation outward path 24B is provided outside the header 12B, and the upper communication port 27B is provided on one side (windward side of the external air flow) in the width direction (horizontal direction) of the flat heat transfer tube 11. As a result, more refrigerant can flow into the windward flow path in the flat heat transfer tube 11.

In the third embodiment, the lower communication port 28B is also provided on one side (the windward side of the external air flow) in the width direction (horizontal direction) of the flat heat transfer tube 11, so that the flow path on the windward side of the flat heat transfer tube 11 is provided. Although a larger amount of refrigerant can flow into the flow path on the leeward side, the flow is not necessarily limited to this, and the lower communication port 28B may be provided below the windward lower surface 22c of the second partition member. good.

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

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 Piping 20 Main body 21 First partition member 22, 22A, 22B Second partition member 23 Refrigerant inflow section 24, 24A, 24B Circulation outward path 25, 25A, 25B Circulation return path 26 Refrigerant inflow port 27, 27A, 27B Upper communication port 28, 28A, 28B Lower communication port

Claims (6)

Multiple flat heat transfer tubes stacked so that their wide surfaces face each other,
The end portions of the plurality of flat heat transfer tubes are connected to each other, and a tubular header for distributing a refrigerant to the plurality of flat heat transfer tubes is provided.
The header is
A first partition member for partitioning a tubular main body into two spaces arranged in a stacking direction of the plurality of flat heat transfer tubes, and a first partition member.
The space on the upper side of the tubular main body portion partitioned by the first partition member is the space on the side where the plurality of flat heat transfer tubes are connected to the circulation return path and the side where the plurality of flat heat transfer tubes are not connected. It has a second partition member, which is divided into a circulation outward path, which is a space of the above, and has an upper communication port at the upper part and a lower communication port at the lower part.
The space on the lower side in which the tubular main body portion is partitioned by the first partition member is a refrigerant inflow portion.
The first partition member is provided with a refrigerant inflow port for flowing a refrigerant into the circulation outward path.
A heat exchanger in which the upper 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 on the windward side in the external air flow direction. The heat exchanger according to claim 1, wherein the lower communication port is provided on the windward side of an external air flow. The heat exchanger according to claim 1 or 2, wherein the horizontal cross-sectional area of the circulation outward path is smaller than the horizontal cross-sectional area of the circulation return path. The heat exchanger according to claim 2 or 3, wherein the horizontal cross-sectional area of the circulation outward 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 4, wherein the circulation outward path is provided on the windward side of an external air flow. The heat exchanger according to any one of claims 1 to 4, wherein the circulation outward path is provided on the leeward side of an external air flow.

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