Heat Exchanger

Abstract

The heat exchanger of the present invention comprises: a plurality of heat transfer flat tubes (11) arranged in an area where air flows; and a header (12) connected to the ends of the plurality of heat transfer flat tubes (11), wherein each of the plurality of heat transfer flat tubes (11) has a plurality of windward side flow paths (44) and a plurality of leeward side flow paths (45) arranged on the leeward side relative to the plurality of windward side flow paths (44), and the header (12) comprises: a main body (20) having an internal space formed therein, wherein the internal space is connected to the plurality of windward side flow paths (44) and the plurality of leeward side flow paths (45). A main body (20) is connected to a passage (45); a partition component (22) which divides the internal space of the main body (20) into a windward side space (24) on a side close to the end of a plurality of windward side flow passages (44) and a leeward side space (25) on a side close to the end of a plurality of leeward side flow passages (45); and an inflow portion (27) which is used to supply refrigerant to the lower part of the leeward side space (25), and an upper connecting passage (28) which connects the leeward side space (25) with the windward side space (24) is formed at the upper part of the partition component (22).

Description

Technical Field

[0001] The present invention relates to a heat exchanger. Background Art

[0002] There is known a heat exchanger having a structure in which both ends of a heat transfer flat tube having a plurality of flow paths are respectively inserted and connected to two headers, thereby branching the refrigerant from one header to the heat transfer flat tubes (Patent Document 1).

[0003] In the air conditioner, the refrigerant changes from a gas-liquid two-phase state to a gas phase state while flowing through a heat exchanger used as an evaporator, and then flows out from the outlet side in a superheated state. Since the temperature difference ΔT between the superheated refrigerant and the air becomes smaller than when it is in a gas-liquid two-phase state, the heat exchange amount Φ (= K×ΔT×A, where K is the heat transfer coefficient and A is the heat transfer area) between the refrigerant and the air decreases. In addition, compared with the case where the dryness of the refrigerant flowing through the heat exchanger is 1.0, when the dryness of the refrigerant at the outlet of the heat exchanger is less than 1.0, the average dryness of the refrigerant flowing through the heat exchanger is lower. If the average dryness of the refrigerant flowing through the heat exchanger is lower, the flow rate of the refrigerant will decrease, causing the thermal conductivity on the refrigerant side to increase. When the thermal conductivity on the refrigerant side is higher, the heat transfer coefficient K between the refrigerant and the air decreases, resulting in a decrease in the heat exchange amount Φ between the refrigerant and the air. Therefore, ideally, when the heat exchanger is used as an evaporator, the refrigerant circulation rate is adjusted so that the dryness of the refrigerant flowing through the heat exchanger is exactly 1.0.

[0004] Patent Document 1: Japanese Patent Application Publication No. 2018-100800 Summary of the invention

[0005] On the other hand, when the heat exchanger is used to perform heat exchange between the outside air and the refrigerant, the temperature difference between the flow path on the windward side of the heat transfer flat tube and the air flowing therethrough is large, so the heat exchange amount is large. Therefore, when the heat exchanger is used as an evaporator, for example, there is a possibility that only the refrigerant flowing in the flow path on the windward side of the heat transfer flat tube becomes a gas phase state, and the gas phase refrigerant becomes a superheated state. In order to prevent the refrigerant flowing in the flow path on the windward side from being vaporized and becoming a superheated state, it is conceivable to allow a refrigerant with a lower dryness to flow into the heat transfer flat tube. However, the flow path on the leeward side of the heat transfer flat tube is a flow path with a smaller heat exchange amount than the flow path on the windward side of the heat transfer flat tube. Therefore, sufficient heat exchange cannot be performed between the refrigerant flowing in the flow path on the leeward side of the heat transfer flat tube and the air, and the dryness of the refrigerant flowing through the flow path does not reach 1.0. In this case, there is a problem that, compared to the ideal case where the refrigerant circulation amount is adjusted so that the dryness of the refrigerant flowing through the heat exchanger is exactly 1.0, the heat transfer coefficient K between the refrigerant and the air is reduced, causing the heat exchange amount Φ between the refrigerant and the air to decrease.

[0006] The technology of the present invention has been made in view of the above-mentioned problems, and an object of the present invention is to provide a heat exchanger capable of suppressing a decrease in the amount of heat exchange between air and refrigerant.

[0007] A heat exchanger according to one aspect of the present invention includes: a plurality of heat transfer flat tubes arranged in an area where air flows; and a header connected to the ends of the plurality of heat transfer flat tubes. A plurality of windward flow paths are formed inside each of the plurality of heat transfer flat tubes; and a plurality of leeward flow paths are arranged on the leeward side of the air relative to the plurality of windward flow paths. The header includes a main body, a partition member, and an inlet portion. The main body forms an internal space connected to the plurality of windward flow paths and the plurality of leeward flow paths. The partition member divides the internal space into a windward space and a leeward space. The windward space is located on a side close to the ends of the plurality of windward flow paths, and the leeward space is located on a side close to the ends of the plurality of leeward flow paths. The inlet portion is used to supply refrigerant to the lower part of the leeward space. An upper communicating path is formed on the upper part of the partition member, which communicates the leeward space with the windward space.

[0008] The heat exchanger of the present invention can suppress a decrease in the amount of heat exchange between air and refrigerant. BRIEF DESCRIPTION OF THE DRAWINGS

[0009] Figure 1 This is a diagram for explaining the structure of an air conditioner to which the heat exchanger according to Embodiment 1 of the present invention is applied.

[0010] Figure 2AIt is a top view showing the heat exchanger according to Embodiment 1 of the present invention.

[0011] Figure 2B It is a front view showing the heat exchanger according to Embodiment 1 of the present invention.

[0012] Figure 3 It is a front view showing the heat transfer flat tubes of the heat exchanger according to Embodiment 1 of the present invention.

[0013] Figure 4 This is a perspective view of a header of the heat exchanger according to Embodiment 1 of the present invention.

[0014] Figure 5 yes Figure 4 Horizontal cross-section of the header.

[0015] Figure 6 yes Figure 4 Vertical cross-section of the header.

[0016] Figure 7 It is a perspective view showing a header of a heat exchanger according to Embodiment 2 of the present invention.

[0017] Figure 8 yes Figure 7 Vertical cross-section of the header.

[0018] Fig. 9 yes Figure 7 Horizontal cross-section of the header.

[0019] Fig.10 This is a vertical cross-sectional view showing a header of a heat exchanger according to Embodiment 3 of the present invention.

[0020] Fig.11 It is a vertical cross-sectional view showing a deformation example of the header.

[0021] Fig.12 It is a vertical cross-sectional view showing another modified example of the header. DETAILED DESCRIPTION

[0022] Hereinafter, a mode for implementing the present invention (hereinafter referred to as "embodiment") will be described with reference to the drawings. In the description of the embodiment, the same elements are always denoted by the same reference numerals.

[0023] Implementation Method 1

[0024] Air conditioner

[0025] Figure 1 1 is a diagram for explaining the structure of the 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. Figure 1As shown, the air conditioner 1 includes an indoor unit 2 and an outdoor unit 3. The indoor unit 2 includes an indoor heat exchanger 4, and the outdoor unit 3 includes a compressor 6, an expansion valve 7, and a four-way valve 8 in addition to an outdoor heat exchanger 5.

[0026] During 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 through the four-way valve 8, and the heat exchanger 4 functions as a condenser. Figure 1 The refrigerant flows in the direction indicated by the black arrow. In the heat exchanger 4, the inflowing gas refrigerant exchanges heat with the outside air and is liquefied. The liquefied high-pressure refrigerant flows through the expansion valve 7 and is decompressed, and then flows into the heat exchanger 5 as a low-temperature and low-pressure gas-liquid two-phase refrigerant, and the heat exchanger 5 functions as an evaporator. In the heat exchanger 5, the inflowing gas-liquid two-phase refrigerant exchanges heat with the outside air and is vaporized. The vaporized low-pressure refrigerant is sucked into the compressor 6 via the four-way valve 8.

[0027] During 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 through the four-way valve 8, and the heat exchanger 5 functions as a condenser. Figure 1 The refrigerant flows in the direction indicated by the white arrow in the middle. In the heat exchanger 5, the inflowing gas refrigerant exchanges heat with the outside air and is liquefied. The liquefied high-pressure refrigerant flows through the expansion valve 7 and is decompressed, and then flows into the heat exchanger 4 as a low-temperature and low-pressure gas-liquid two-phase refrigerant, and the heat exchanger 4 functions as an evaporator. In the heat exchanger 4, the inflowing gas-liquid two-phase refrigerant exchanges heat with the outside air and is vaporized. The vaporized low-pressure refrigerant is sucked into the compressor 6 via the four-way valve 8.

[0028] Heat Exchanger

[0029] The heat exchanger according to Embodiment 1 of the present invention can be applied to either the heat exchanger 4 or the heat exchanger 5 , and will be described here as being applied to the heat exchanger 5 functioning as an evaporator during heating operation. Figure 2A and Figure 2B 1 is a diagram for explaining the heat exchanger 5 according to the first embodiment of the present invention. Figure 2A is a top view of the heat exchanger 5, Figure 2B It is a front view of the heat exchanger 5.

[0030] The heat exchanger 5 includes: a plurality of heat transfer flat tubes 11 for refrigerant circulation, which are stacked in such a way that the wider surfaces face each other; a tubular header 12, which is connected to the ends of the plurality of heat transfer flat tubes 11 to distribute the refrigerant to the plurality of heat transfer flat tubes 11; a tubular header 13, which is connected to the other ends of the plurality of heat transfer flat tubes 11 to converge the refrigerant flowing out of the plurality of heat transfer flat tubes 11; and a plurality of flat plate-shaped fins 14, which are connected to the plurality of heat transfer flat tubes 11. The plurality of heat transfer flat tubes 11 are arranged along the same plane as the plurality of heat transfer flat tubes 11. Figure 2A The heat transfer flat tubes 11 extend in a direction perpendicular to the direction of the external air flow indicated by the arrow in the middle, and the cross section thereof is flat. Here, a fan (not shown) is used to blow air to circulate the external air. The plurality of heat transfer flat tubes 11 have a plurality of flow paths inside, which extend in the same direction as the extension direction of the heat transfer flat tubes. Figure 2B As shown, a plurality of heat transfer flat tubes 11 are stacked in the vertical direction so that the flat surfaces (surfaces with a larger width) of the side surfaces thereof face each other, and the left and right ends thereof are connected to the headers 12 and 13. In addition, a plurality of fins 14 are arranged between the headers 12 and 13 so as to be orthogonal to the plurality of heat transfer flat tubes 11. The low-temperature and low-pressure gas-liquid two-phase refrigerant having passed through the expansion valve 7 and reduced in pressure is supplied to the header 12 through the pipe 15, and then is divided into each of the plurality of heat transfer flat tubes 11. When the gas-liquid two-phase refrigerant flows through the plurality of heat transfer flat tubes 11, it exchanges heat with the air through the fins 14, is vaporized, and flows out to the header 13. The gas refrigerant that converges in the header 13 is sucked into the compressor through the pipe 16 and the four-way valve 8.

[0031] Heat transfer flat tube

[0032] like Figure 3 As shown, one heat transfer flat tube 41 among the plurality of heat transfer flat tubes 11 is disposed in a space where air flows along a flow direction 42 , and the flow direction 42 is perpendicular to the up-and-down direction in which the plurality of heat transfer flat tubes 11 are stacked. Figure 3: is a front view of the heat transfer flat tube 41 of the heat exchanger according to Embodiment 1 of the present invention. The heat transfer flat tube 41 is formed in a substantially flat belt shape. A straight line along the length direction of the heat transfer flat tube 41 is substantially perpendicular to the flow direction 42 and substantially perpendicular to the up-down direction. A plane along the wider surface of the heat transfer flat tube 41 is substantially perpendicular to the up-down direction, that is, substantially parallel to the flow direction 42. A plurality of flow paths 43 arranged in the flow direction 42 are formed inside the heat transfer flat tube 41. The plurality of flow paths 43 include: a plurality of windward side flow paths 44 located on the windward side relative to the center of the width direction of the cross section of the heat transfer flat tube 41; and a plurality of leeward side flow paths 45 located on the leeward side relative to the center of the width direction of the cross section of the heat transfer flat tube 41. The plurality of leeward side flow paths 45 are arranged on the leeward side compared to the plurality of windward side flow paths 44. The other heat transfer flat tubes 11 that are different from the heat transfer flat tubes 41 are formed similarly to the heat transfer flat tubes 41 and are arranged such that the plurality of flow paths 43 are aligned along the flow direction 42 .

[0033] Headers

[0034] Next, refer to Figures 4 to 6 The header 12 according to the first embodiment of the present invention will be described. Figure 4 It is a perspective view of the header 12 of the heat exchanger according to Embodiment 1 of the present invention. Figure 5 is a horizontal cross-sectional view of the header 12 . Figure 6 It is a vertical cross-sectional view of the header 12. In addition, in this specification, the side of the header 12 close to the plurality of heat transfer flat tubes 11 is called the inner side, the side of the header 12 opposite to the plurality of heat transfer flat tubes 11 is called the outer side, the upstream side of the external air is called the windward side, and the downstream side is called the leeward side. Figure 4 The fins 14 are not shown in the figure.

[0035] The header 12 includes a tubular main body 20, a first partition member 21 disposed in the main body 20, and a second partition member 22 disposed in the main body 20. The main body 20 includes a cylindrical tube 20a extending in the up-down direction, a lower wall 20b closing the lower end opening of the tube 20a, and an upper wall 20c closing the upper end opening of the tube 20a. That is, the main body 20 is hollow. Figure 4 and Figure 5 As shown in FIG. 1 , a cylindrical header 12 is used, but the header 12 is not limited to a cylindrical shape and may also be a square column shape with a hollow interior. Figure 4 and Figure 5As shown, the header 12 includes: a first partition member 21 that divides the tubular main body 20 into two spaces arranged in the vertical direction; and a second partition member 22 that divides the upper side of the main body 20 divided by the first partition member 21 into two spaces arranged in the flow direction of the external air. The first partition member 21 is provided in the entire horizontal direction of the main body 20, and the second partition member 22 is provided above the first partition member 21 of the main body 20 and in the entire vertical direction.

[0036] The lower side space of the main body 20 divided by the first partition member 21 is a refrigerant inflow space 23, and a low-temperature and low-pressure gas-liquid two-phase refrigerant flows into the space from the expansion valve 7 via the pipe 15. In addition, in the upper side of the main body 20 divided by the second partition member 22 and the first partition member 21, the space on the windward side of the outside air is a windward side space 24, and the space on the leeward side is a leeward side space 25.

[0037] A leeward inlet 27 is provided on the leeward side of the first partition member 21, that is, on the first partition member 21 as the bottom surface of the leeward space 25. Since the upper end of the second partition member 22 is separated from the upper wall 20c, an upper connecting path 28 is formed in the upper part of the second partition member 22 to connect the windward space 24 with the leeward space 25. Since the lower end of the second partition member 22 is separated from the first partition member 21, a lower connecting path 29 is formed near the lower part of the second partition member 22 to connect the windward space 24 with the leeward space 25.

[0038] The plurality of heat transfer flat tubes 11 are joined to the header 12 in a manner that one end thereof is arranged inside the main body 20. More specifically, the heat transfer flat tubes 41 are joined to the header 12 by being arranged such that the ends of the plurality of windward side flow paths 44 are arranged in the windward side space 24 and the ends of the plurality of leeward side flow paths 45 are arranged in the leeward side space 25. Other heat transfer flat tubes among the plurality of heat transfer flat tubes 11 that are different from the heat transfer flat tubes 41 are also joined to the header 12 in a manner that the ends of the plurality of windward side flow paths 44 are arranged in the windward side space 24 and the ends of the plurality of leeward side flow paths 45 are arranged in the leeward side space 25, similarly to the heat transfer flat tubes 41. In addition, the second partition member 22 is formed with cutouts arranged in the up-down direction so as not to interfere with one end of the heat transfer flat tube 41.

[0039] During heating operation

[0040] Regarding the heat exchanger 5, during the heating operation of the air conditioner 1, the gas-liquid two-phase refrigerant is supplied from the expansion valve 7 to the refrigerant inflow space 23 via the pipe 15. The gas-liquid two-phase refrigerant supplied to the refrigerant inflow space 23 is supplied to the lower part of the leeward space 25 via the leeward inlet 27 of the first partition member 21. The gas-liquid two-phase refrigerant supplied to the lower part of the leeward space 25 rises in the leeward space 25. The gas-liquid two-phase refrigerant rising in the leeward space 25 is supplied to the upper part of the windward space 24 via the upper communication passage 28 of the second partition member 22. The gas-liquid two-phase refrigerant supplied to the upper part of the windward space 24 descends in the windward space 24. The gas-liquid two-phase refrigerant descending in the windward space 24 is supplied to the lower part of the leeward space 25 via the lower communication passage 29 of the second partition member 22. The gas-liquid two-phase refrigerant supplied to the leeward side space 25 via the lower connecting passage 29 is pushed upward by the gas-liquid two-phase refrigerant rising in the leeward side space 25 , and rises in the leeward side space 25 together with the gas-liquid two-phase refrigerant rising in the leeward side space 25 .

[0041] The gas-liquid two-phase refrigerant in the windward space 24 enters the windward flow paths 44 of the plurality of heat transfer flat tubes 11 and flows in the windward flow paths 44. The gas-liquid two-phase refrigerant in the leeward space 25 enters the leeward flow paths 45 of the plurality of heat transfer flat tubes 11 and flows in the leeward flow paths 45. The gas-liquid two-phase refrigerant flowing in the windward flow paths 44 and the leeward flow paths 45 is heated by heat exchange with the air outside the plurality of heat transfer flat tubes 11, and the liquid refrigerant in the gas-liquid two-phase refrigerant is vaporized, thereby increasing the dryness and changing the state to gas refrigerant. The gas refrigerant flowing through the windward flow paths 44 and the leeward flow paths 45 is supplied to the inside of the header 13, supplied to the four-way valve 8 via the pipe 16, and then supplied to the compressor 6. In this way, during the heating operation of the air conditioner 1, the heat exchanger 5 functions appropriately as an evaporator.

[0042] When the flow rate of the refrigerant supplied to the leeward space 25 through the leeward inlet 27 is large, the liquid refrigerant in the gas-liquid two-phase refrigerant existing in the leeward space 25 is pushed upward by the gas-liquid two-phase refrigerant rising in the leeward space 25, and tends to be retained in the upper part of the leeward space 25. Therefore, there is a tendency that the ratio of the liquid refrigerant in the gas-liquid two-phase refrigerant supplied from the leeward space 25 to the windward space 24 through the upper communication path 28 is greater than the ratio of the liquid refrigerant in the gas-liquid two-phase refrigerant existing in the leeward space 25. Therefore, the ratio of the liquid refrigerant in the gas-liquid two-phase refrigerant existing in the windward space 24 is greater than the ratio of the liquid refrigerant in the gas-liquid two-phase refrigerant existing in the leeward space 25. Since the proportion of liquid refrigerant in the gas-liquid two-phase refrigerant in the windward side space 24 is greater than the proportion of liquid refrigerant in the gas-liquid two-phase refrigerant in the leeward side space 25, the mass flow rate of the gas-liquid two-phase refrigerant entering the multiple windward side flow paths 44 of the multiple heat transfer flat tubes 11 is greater than the mass flow rate of the gas-liquid two-phase refrigerant entering the multiple leeward side flow paths 45.

[0043] The air that performs heat exchange with the refrigerant flowing in the plurality of leeward side flow paths 45 is the air that has performed heat exchange with the refrigerant flowing in the plurality of windward side flow paths 44. Therefore, the temperature difference between the refrigerant flowing in the plurality of windward side flow paths 44 and the air is greater than the temperature difference between the refrigerant flowing in the plurality of leeward side flow paths 45 and the air. Therefore, the amount of heat transferred from the air to the gas-liquid two-phase refrigerant flowing in the plurality of windward side flow paths 44 is greater than the amount of heat transferred from the air to the gas-liquid two-phase refrigerant flowing in the plurality of leeward side flow paths 45. That is, a large amount of heat is transferred to the gas-liquid two-phase refrigerant that is larger in amount and flows in the plurality of windward side flow paths 44, while a small amount of heat is transferred to the gas-liquid two-phase refrigerant that is smaller in amount and flows in the plurality of leeward side flow paths 45. Therefore, in the heat exchanger 5, the dryness of the refrigerant flowing through the plurality of windward side flow paths 44 and the refrigerant flowing through the plurality of leeward side flow paths 45 in the plurality of heat transfer flat tubes 11 can be made equal. Thus, when the heat exchanger 5 is used as an evaporator, the dryness of the refrigerant flowing through the heat exchanger 5 can be made to be in an ideal state of about 1.0.

[0044] In other heat exchangers in which the refrigerant flows equally in the multiple flow paths 43, the following situation may occur: after the liquid refrigerant in the gas-liquid two-phase refrigerant flowing in the multiple windward flow paths 44 is completely vaporized, the heat is transferred from the air to the vaporized gas refrigerant, causing the gas refrigerant to overheat; on the other hand, the liquid refrigerant in the gas-liquid two-phase refrigerant flowing in the multiple leeward flow paths 45 cannot be completely evaporated due to insufficient heat exchange with the air. In this case, the heat exchange between the air and the refrigerant is not performed efficiently. In contrast, the heat exchanger 5 prevents the gas refrigerant from overheating by making the dryness of the refrigerant in the multiple windward flow paths 44 and the multiple leeward flow paths 45 flowing through the multiple heat transfer flat tubes 11 consistent, thereby preventing the gas refrigerant from overheating, thereby achieving an ideal state in which the dryness of the refrigerant flowing through the heat exchanger 5 is approximately 1.0 when the heat exchanger 5 is used as an evaporator.

[0045] During cooling operation

[0046] In the heat exchanger 5, during the cooling operation of the air conditioner 1, the gas refrigerant compressed by the compressor 6 is supplied from the four-way valve 8 to the header 13 via the pipe 16. The gas refrigerant supplied to the header 13 is supplied to the plurality of flow paths 43 of the plurality of heat transfer flat tubes 11 in a substantially uniform manner. The gas refrigerant flowing in the plurality of flow paths 43 is liquefied by heat exchange with the air flowing outside the plurality of heat transfer flat tubes 11, and the state is changed to liquid refrigerant. The liquid refrigerant flowing through the plurality of flow paths 43 is supplied to the windward side space 24 and the leeward side space 25 of the header 12. The liquid refrigerant supplied to the leeward side space 25 descends in the leeward side space 25 and stays in the lower part of the leeward side space 25. The liquid refrigerant staying in the lower part of the leeward side space 25 is supplied to the refrigerant inflow space 23 via the leeward side inlet 27 of the first partition member 21. The liquid refrigerant supplied to the windward space 24 descends in the windward space 24 and is retained in the lower part of the windward space 24. When the amount of the liquid refrigerant retained in the lower part of the leeward space 25 is sufficiently reduced, the liquid refrigerant retained in the lower part of the windward space 24 is supplied to the lower part of the leeward space 25 via the lower communication passage 29, and then is supplied to the refrigerant inflow space 23 via the leeward inlet 27. The liquid refrigerant supplied to the refrigerant inflow space 23 is supplied to the expansion valve 7 via the pipe 15. In this way, during the cooling operation of the air conditioner 1, the heat exchanger 5 can properly function as a condenser.

[0047] Implementation Method 2

[0048] like Figure 7 As shown, in the header 51 used in the heat exchanger 50 of the second embodiment, the second partition member 22 provided in the header 12 of the heat exchanger 5 of the first embodiment is replaced with other multiple partition members, and the other parts are the same as the header 12. Figure 7It is a perspective view showing a header 51 of a heat exchanger according to Embodiment 2 of the present invention.

[0049] That is, the header 51 includes a main body 20 and a first partition member 21, similarly to the above-mentioned header 12. The main body 20 is formed in a tubular shape, and an internal space is formed inside the main body 20. The first partition member 21 is formed in a disc shape. The first partition member 21 is arranged in the internal space of the main body 20 in such a manner that the internal space of the main body 20 is divided into a refrigerant inflow space 23 and an upper space 52, and is joined to the main body 20. The refrigerant inflow space 23 is formed on the lower side of the first partition member 21 in the internal space of the main body 20. The upper space 52 is formed on the upper side of the first partition member 21 in the internal space of the main body 20.

[0050] The header 51 further includes a windward side partitioning member 53, a leeward side partitioning member 54, and a circulation space partitioning member 55. The windward side partitioning member 53 and the leeward side partitioning member 54 are formed of a single flat plate. The windward side partitioning member 53 and the leeward side partitioning member 54 are arranged in the inner space of the main body 20 in such a manner as to divide the upper space 52 into a heat transfer tube insertion space 56 and a circulation space 57, and are joined to the main body 20 and the first partitioning member 21, wherein the heat transfer tube insertion space 56 is a space to which one end of the plurality of heat transfer flat tubes 11 is connected, and the circulation space 57 is a space to which one end of the plurality of heat transfer flat tubes 11 is not connected. The heat transfer tube insertion space 56 is formed on a side of the upper space 52 that is closer to the plurality of heat transfer flat tubes 11 relative to the windward side partitioning member 53 and the leeward side partitioning member 54. The circulation space 57 is formed on a side of the upper space 52 that is farther from the plurality of heat transfer flat tubes 11 relative to the windward side partitioning member 53 and the leeward side partitioning member 54.

[0051] The circulation space partitioning member 55 is formed in a flat plate shape and is disposed in the internal space of the main body 20 so as to divide the circulation space 57 into a windward space 58 and a leeward space 59 , and is joined to the main body 20 , the windward partitioning member 53 , and the leeward partitioning member 54 .

[0052] The first partition member 21 is formed with a leeward inlet 27 that allows the refrigerant inflow space 23 to communicate with the leeward space 59. The upper end of the circulation space partition member 55 is separated from the upper wall 20c, thereby forming an upper communication path 61 that allows the windward space 58 to communicate with the leeward space 59 in the upper part of the circulation space partition member 55. The lower end of the circulation space partition member 55 is separated from the first partition member 21, thereby forming a lower communication path 62 that allows the windward space 58 to communicate with the leeward space 59 in the vicinity of the lower part of the circulation space partition member 55.

[0053] Figure 8 yes Figure 7A cross-sectional view of the header 51 in the up-down direction (vertical direction). The windward side partition component 53 is formed with a plurality of windward side connecting holes 63 that connect the windward side space 58 with the heat transfer tube insertion space 56. The leeward side partition component 54 is formed with a plurality of leeward side connecting holes 64 that connect the leeward side space 59 with the heat transfer tube insertion space 56. Among them, the sum of the opening areas of the plurality of windward side connecting holes 63 is greater than the sum of the opening areas of the plurality of leeward side connecting holes 64. As a result, the mass flow rate of the gas-liquid two-phase refrigerant entering the plurality of windward side flow paths 44 is greater than the mass flow rate of the gas-liquid two-phase refrigerant entering the plurality of leeward side flow paths 45.

[0054] Fig. 9 yes Figure 7 5. A cross-sectional view of the header 51 in a direction perpendicular to the up-down direction (horizontal direction). The windward side space 58 is formed in a side region of the circulation space 57 close to the ends of the plurality of windward side flow paths 44. The leeward side space 59 is formed in a side region of the circulation space 57 close to the ends of the plurality of leeward side flow paths 45. Among them, the windward side partitioning component 53 is arranged between the heat transfer tube insertion space 56 and the windward side space 58 to divide the heat transfer tube insertion space 56 and the windward side space 58. The leeward side partitioning component 54 is arranged between the heat transfer tube insertion space 56 and the leeward side space 59 to divide the heat transfer tube insertion space 56 and the leeward side space 59.

[0055] During heating operation

[0056] The heat exchanger of Embodiment 2 operates in substantially the same manner as the heat exchanger 5 of Embodiment 1 described above. That is, for the heat exchanger 50, during the heating operation of the air conditioner 1, a gas-liquid two-phase refrigerant is supplied from the expansion valve 7 to the refrigerant inflow space 23 via the pipe 15. The gas-liquid two-phase refrigerant supplied to the refrigerant inflow space 23 is supplied to the lower portion of the leeward space 59 via the leeward inlet 27 of the first partition member 21. The gas-liquid two-phase refrigerant supplied to the lower portion of the leeward space 59 rises in the leeward space 59. The gas-liquid two-phase refrigerant rising in the leeward space 59 is supplied to the upper portion of the windward space 58 via the upper connecting passage 61 of the circulation space partition member 55. The gas-liquid two-phase refrigerant supplied to the upper portion of the windward space 58 descends in the windward space 58. The gas-liquid two-phase refrigerant descending in the windward space 58 is supplied to the lower part of the leeward space 59 via the lower connecting passage 62 of the circulation space partition member 55. The gas-liquid two-phase refrigerant supplied to the leeward space 59 via the lower connecting passage 62 is pushed upward by the gas-liquid two-phase refrigerant ascending in the leeward space 59, and ascends in the leeward space 59 together with the gas-liquid two-phase refrigerant ascending in the leeward space 59.

[0057] The gas-liquid two-phase refrigerant in the windward space 58 is supplied to the region near the end of the plurality of windward flow paths 44 in the heat transfer tube insertion space 56 through the plurality of windward communication holes 63 of the windward partition member 53. The gas-liquid two-phase refrigerant in the region near the end of the plurality of windward flow paths 44 in the heat transfer tube insertion space 56 enters the plurality of windward flow paths 44 of the plurality of heat transfer flat tubes 11 and flows in the plurality of windward flow paths 44. The gas-liquid two-phase refrigerant in the leeward space 59 is supplied to the region near the end of the plurality of leeward flow paths 45 in the heat transfer tube insertion space 56 through the plurality of leeward communication holes 64 of the leeward partition member 54. The gas-liquid two-phase refrigerant in the region near the end of the plurality of leeward flow paths 45 in the heat transfer tube insertion space 56 enters the plurality of leeward flow paths 45 of the plurality of heat transfer flat tubes 11 and flows in the plurality of leeward flow paths 45. The gas-liquid two-phase refrigerant flowing in the plurality of windward flow paths 44 and the plurality of leeward flow paths 45 is heated by heat exchange with the air outside the plurality of heat transfer flat tubes 11, and the liquid refrigerant in the gas-liquid two-phase refrigerant is vaporized, thereby changing its state to gas refrigerant. The gas refrigerant flowing through the plurality of windward flow paths 44 and the plurality of leeward flow paths 45 is supplied to the inside of the header 13, supplied to the four-way valve 8 via the pipe 16, and then supplied to the compressor 6. In this way, during the heating operation of the air conditioner 1, the heat exchanger 50 can properly function as an evaporator.

[0058] When the flow rate of the refrigerant supplied to the leeward space 59 through the leeward inlet 27 is large, the ratio of the liquid refrigerant in the gas-liquid two-phase refrigerant existing in the windward space 58 is larger than the ratio of the liquid refrigerant in the gas-liquid two-phase refrigerant existing in the leeward space 59, as in the case of the heat exchanger 5 of the first embodiment. Therefore, the ratio of the liquid refrigerant in the gas-liquid two-phase refrigerant existing in the region near the end of the plurality of windward flow paths 44 in the heat transfer tube insertion space 56 is also larger than the ratio of the liquid refrigerant in the gas-liquid two-phase refrigerant existing in the region near the end of the plurality of leeward flow paths 45 in the heat transfer tube insertion space 56. As a result, since the ratio of the liquid refrigerant in the gas-liquid two-phase refrigerant in the windward space 58 is larger than the ratio of the liquid refrigerant in the gas-liquid two-phase refrigerant in the leeward space 59, the mass flow rate of the gas-liquid two-phase refrigerant entering the plurality of windward flow paths 44 is larger than the mass flow rate of the gas-liquid two-phase refrigerant entering the plurality of leeward flow paths 45. Therefore, the heat exchanger 50 can make the dryness of the refrigerant flowing through the plurality of windward side flow paths 44 of the plurality of heat transfer flat tubes 11 and the refrigerant flowing through the plurality of leeward side flow paths 45 consistent with each other, similarly to the above-mentioned heat exchanger 5. Thus, when the heat exchanger 50 is used as an evaporator, the dryness of the refrigerant flowing through the heat exchanger 50 can be in an ideal state of about 1.0.

[0059] In other heat exchangers in which the refrigerant flows evenly in the plurality of flow paths 43, after all the liquid refrigerant in the gas-liquid two-phase refrigerant flowing in the plurality of windward flow paths 44 is vaporized, heat is transferred from the air to the vaporized gas refrigerant, causing the gas refrigerant to overheat, and the heat exchange performance is deteriorated. The heat exchanger 50 prevents the gas refrigerant from overheating by making the dryness of the refrigerant flowing in the plurality of windward flow paths 44 and the plurality of leeward flow paths 45 passing through the plurality of heat transfer flat tubes 11 consistent, thereby achieving an ideal state in which the dryness of the refrigerant flowing through the heat exchanger 50 is approximately 1.0 when the heat exchanger 50 is used as an evaporator.

[0060] During cooling operation

[0061] In the heat exchanger 50, during the cooling operation of the air conditioner 1, the gas refrigerant compressed by the compressor 6 is supplied from the four-way valve 8 to the header 13 via the pipe 16. The gas refrigerant supplied to the header 13 is divided into the plurality of flow paths 43 of the plurality of heat transfer flat tubes 11. The gas refrigerant flowing in the plurality of flow paths 43 is liquefied by heat exchange with the air flowing outside the plurality of heat transfer flat tubes 11, and the state is changed to liquid refrigerant. The liquid refrigerant flowing through the plurality of flow paths 43 is supplied to the heat transfer tube insertion space 56 of the header 51. The liquid refrigerant supplied to the heat transfer tube insertion space 56 is supplied to the windward side space 58 via the plurality of windward side communication holes 63, or supplied to the leeward side space 59 via the plurality of leeward side communication holes 64. The liquid refrigerant supplied to the leeward side space 59 descends in the leeward side space 59 and stays in the lower part of the leeward side space 59. The liquid refrigerant retained in the lower part of the leeward space 59 is supplied to the refrigerant inflow space 23 via the leeward inlet 27 of the first partition member 21. The liquid refrigerant supplied to the windward space 58 descends in the windward space 58 and is retained in the lower part of the windward space 58. When the amount of the liquid refrigerant retained in the lower part of the leeward space 59 is sufficiently reduced, the liquid refrigerant retained in the lower part of the windward space 58 is supplied to the lower part of the leeward space 25 via the lower connecting passage 29, and then supplied to the refrigerant inflow space 23 via the leeward inlet 27. The liquid refrigerant supplied to the refrigerant inflow space 23 is supplied to the expansion valve 7 via the pipe 15. In this way, during the cooling operation of the air conditioner 1, the heat exchanger 50 functions appropriately as a condenser.

[0062] Implementation 3

[0063] like Fig.10 As shown, a header 71 used in a heat exchanger according to Embodiment 3 is obtained by adding a plurality of partition members 72 to the header 51 of the heat exchanger 50 according to Embodiment 2. Fig.10: is a cross-sectional view in the up-down direction (vertical direction) of the header 71 of the heat exchanger according to Embodiment 3 of the present invention. The plurality of partition members 72 are respectively formed of a plate member having a substantially semicircular shape. The plurality of partition members 72 are arranged in the heat transfer tube insertion space 56 in such a manner as to divide the heat transfer tube insertion space 56 into a plurality of heat transfer tube insertion spaces 73, and are joined to the main body 20, the windward side partition member 53, and the leeward side partition member 54. The plurality of partition members 72 are arranged in such a manner that an end portion of any one of the plurality of heat transfer flat tubes 11 is arranged in each of the plurality of heat transfer tube insertion spaces 73. Furthermore, the plurality of partition members 72 are arranged in such a manner that the plurality of heat transfer tube insertion spaces 73 are respectively connected to the windward side space 58 via any one of the windward side connecting holes 63 of the plurality of windward side connecting holes 63.

[0064] During heating operation

[0065] The heat exchanger of Embodiment 3 operates in substantially the same manner as the heat exchanger 50 of Embodiment 2 described above. That is, in the heat exchanger of Embodiment 3, during the heating operation of the air conditioner 1, a gas-liquid two-phase refrigerant is supplied from the expansion valve 7 to the refrigerant inflow space 23 via the pipe 15. The gas-liquid two-phase refrigerant supplied to the refrigerant inflow space 23 rises in the leeward space 59 and descends in the windward space 58, thereby circulating in the circulation space 57. At this time, when the flow rate of the refrigerant supplied to the leeward space 59 via the leeward inlet 27 is large, the proportion of the liquid refrigerant in the gas-liquid two-phase refrigerant existing in the windward space 58 is greater than the proportion of the liquid refrigerant in the gas-liquid two-phase refrigerant existing in the leeward space 59.

[0066] The gas-liquid two-phase refrigerant existing in the windward space 58 is supplied to the region near the end of the plurality of windward flow paths 44 of the plurality of heat transfer tube insertion spaces 73 through the plurality of windward communication holes 63 of the windward partition member 53. The gas-liquid two-phase refrigerant existing in the region near the end of the plurality of windward flow paths 44 of the plurality of heat transfer tube insertion spaces 73 enters the plurality of windward flow paths 44 of the plurality of heat transfer flat tubes 11 and flows in the plurality of windward flow paths 44. The gas-liquid two-phase refrigerant existing in the leeward space 59 is supplied to the region near the end of the plurality of leeward flow paths 45 of the plurality of heat transfer tube insertion spaces 73 through the plurality of leeward communication holes 64 of the leeward partition member 54. The gas-liquid two-phase refrigerant existing in the region near the end of the plurality of leeward flow paths 45 of the plurality of heat transfer flat tubes 11 enters the plurality of leeward flow paths 45 of the plurality of heat transfer flat tubes 11 and flows in the plurality of leeward flow paths 45. The gas-liquid two-phase refrigerant flowing in the plurality of windward flow paths 44 and the plurality of leeward flow paths 45 is heated by heat exchange with the air outside the plurality of heat transfer flat tubes 11, and the liquid refrigerant in the gas-liquid two-phase refrigerant is vaporized, thereby changing its state to gas refrigerant. The gas refrigerant flowing through the plurality of windward flow paths 44 and the plurality of leeward flow paths 45 is supplied to the interior of the header 13, supplied to the four-way valve 8 via the pipe 16, and then supplied to the compressor 6. In this way, during the heating operation of the air conditioner 1, the heat exchanger of Embodiment 3 can appropriately function as an evaporator.

[0067] In each of the plurality of heat transfer tube insertion spaces 73, the ratio of the liquid refrigerant in the gas-liquid two-phase refrigerant near the end of the plurality of windward side flow paths 44 is greater than the ratio of the liquid refrigerant in the gas-liquid two-phase refrigerant near the end of the plurality of leeward side flow paths 45. Therefore, the mass flow rate of the gas-liquid two-phase refrigerant entering the plurality of windward side flow paths 44 is greater than the mass flow rate of the gas-liquid two-phase refrigerant entering the plurality of leeward side flow paths 45. As a result, the heat exchanger of Embodiment 3 can make the dryness of the refrigerant flowing through the plurality of windward side flow paths 44 of the plurality of heat transfer flat tubes 11 and the refrigerant flowing through the plurality of leeward side flow paths 45 consistent, similarly to the above-mentioned heat exchanger 50. Thus, when the heat exchanger is used as an evaporator, it is possible to achieve an ideal state in which the dryness of the refrigerant flowing through the heat exchanger is approximately 1.0.

[0068] In the heat exchanger 50 described above, the ratio of liquid refrigerant in the gas-liquid two-phase refrigerant in the lower portion of the heat transfer tube insertion space 56 may be greater than the ratio of liquid refrigerant in the gas-liquid two-phase refrigerant in the upper portion of the heat transfer tube insertion space 56 due to gravity. In contrast, the heat exchanger of Embodiment 3 divides the heat transfer tube insertion space 56 into a plurality of heat transfer tube insertion spaces 73, and thus can divide the refrigerant in such a way that the amount of refrigerant supplied to the plurality of heat transfer flat tubes 11 is more evenly distributed than in the heat exchanger 50 described above. Since the amount of refrigerant supplied to the plurality of heat transfer flat tubes 11 becomes evenly distributed, the heat exchanger of Embodiment 3 can improve heat exchange performance.

[0069] During cooling operation

[0070] In the heat exchanger of Embodiment 3, during the cooling operation of the air conditioner 1, the gas refrigerant compressed by the compressor 6 is supplied from the four-way valve 8 to the header 13 via the pipe 16. The gas refrigerant supplied to the header 13 is supplied to the plurality of flow paths 43 of the plurality of heat transfer flat tubes 11 substantially evenly. The gas refrigerant flowing in the plurality of flow paths 43 is liquefied by heat exchange with the air flowing outside the plurality of heat transfer flat tubes 11, and the state is changed to liquid refrigerant. The liquid refrigerant flowing through the plurality of flow paths 43 is supplied to the plurality of heat transfer tube insertion spaces 73 of the header 51. The liquid refrigerant supplied to the plurality of heat transfer tube insertion spaces 73 is supplied to the windward side space 58 via the plurality of windward side communication holes 63, or is supplied to the leeward side space 59 via the plurality of leeward side communication holes 64. The liquid refrigerant supplied to the leeward side space 59 descends in the leeward side space 59 and stays in the lower part of the leeward side space 59. The liquid refrigerant retained in the lower part of the leeward space 59 is supplied to the refrigerant inflow space 23 via the leeward inlet 27 of the first partition member 21. The liquid refrigerant supplied to the windward space 58 descends in the windward space 58 and is retained in the lower part of the windward space 58. When the amount of the liquid refrigerant retained in the lower part of the leeward space 59 is sufficiently reduced, the liquid refrigerant retained in the lower part of the windward space 58 is supplied to the lower part of the leeward space 59 via the lower connecting passage 29, and then is supplied to the refrigerant inflow space 23 via the leeward inlet 27. The liquid refrigerant supplied to the refrigerant inflow space 23 is supplied to the expansion valve 7 via the pipe 15. In this way, during the cooling operation of the air conditioner 1, the heat exchanger of embodiment 3 can function appropriately as a condenser.

[0071] In addition, in the heat exchangers of the above-mentioned embodiments 2 and 3, the total area of ​​the plurality of windward-side communication holes 63 is greater than the total area of ​​the plurality of leeward-side communication holes 64, but the total area of ​​the plurality of windward-side communication holes 63 may be equal to the total area of ​​the plurality of leeward-side communication holes 64. In this case, since the proportion of liquid refrigerant in the gas-liquid two-phase refrigerant in the windward-side space 58 is greater than the proportion of liquid refrigerant in the gas-liquid two-phase refrigerant in the leeward-side space 59, the heat exchanger can also make the amount of gas-liquid two-phase refrigerant in the plurality of windward-side flow paths 44 greater than the amount of gas-liquid two-phase refrigerant in the plurality of leeward-side flow paths 45. Therefore, in this case, the heat exchanger can also improve the heat exchange performance between air and refrigerant.

[0072] In addition, the leeward partition member 54 in the heat exchanger of the above-mentioned Embodiments 2 and 3 is formed with a plurality of leeward communication holes 64, but it is also possible not to form a plurality of leeward communication holes 64. In this case, the plurality of windward flow paths 44 of the plurality of heat transfer flat tubes 11 are closer to the plurality of windward communication holes 63 than the plurality of leeward flow paths 45, so the mass flow rate of the gas-liquid two-phase refrigerant supplied to the plurality of windward flow paths 44 is greater than the mass flow rate of the gas-liquid two-phase refrigerant supplied to the plurality of leeward flow paths 45. Therefore, the heat exchanger of Embodiments 2 and 3 can also improve the heat exchange performance between air and refrigerant.

[0073] The upper communication passage 28 is formed by separating the upper end of the second partition member 22 from the member forming the upper end of the internal space in the main body 20. Fig.11 As shown in FIG. 2 , the upper communication passage 28 may be formed by forming an upper communication hole 22a in the upper portion of the second partition member 22. Similarly, the upper communication passage 61 is formed by separating the upper end of the circulation space partition member 55 from the member forming the upper end of the internal space in the main body 20, but Fig.12As shown, the upper communication passage 61 may be formed by forming an upper communication hole 55a on the upper part of the circulation space partitioning member 55. The heat exchanger of the embodiment can also improve the heat exchange performance between the air and the refrigerant when the upper communication passage 28 or the upper communication passage 61 is formed in the above manner. For example, when the upper communication passage 28 is formed by the upper communication hole 22a, a bulge is formed between the upper end of the leeward space 25 and the upper end of the windward space 24, and the liquid refrigerant retained in the upper part of the leeward space 25 may not be smoothly supplied to the windward space 24. Since the upper end of the leeward space 25 and the upper end of the windward space 24 are formed flush with each other in the heat exchanger 5 of the above-mentioned embodiment 1, the liquid refrigerant can be supplied from the leeward space 25 to the windward space 24 more smoothly than when the upper communication passage 28 is formed by the upper communication hole 22a. Similarly, compared with the case where the upper communicating passage 61 is formed by the upper communicating hole 55a, the heat exchanger of the above-mentioned embodiments 2 and 3 can smoothly supply the liquid refrigerant from the leeward space 59 to the windward space 58. As a result, compared with the case where the upper communicating passage 28 is formed by the upper communicating hole 22a or the case where the upper communicating passage 61 is formed by the upper communicating hole 55a, the heat exchanger of the above-mentioned embodiment can improve the heat exchange performance between the air and the refrigerant.

[0074] In addition, the heat exchanger of the above embodiment is formed with the lower connecting passages 29 and 62, but it is also possible not to form the lower connecting passages 29 and 62. In this case, since the ratio of the liquid refrigerant in the gas-liquid two-phase refrigerant in the windward side spaces 24 and 58 is greater than the ratio of the liquid refrigerant in the gas-liquid two-phase refrigerant in the leeward side spaces 25 and 59, the heat exchanger can also make the amount of the gas-liquid two-phase refrigerant in the plurality of windward side flow passages 44 greater than the amount of the gas-liquid two-phase refrigerant in the plurality of leeward side flow passages 45. Therefore, the heat exchanger in this case can also improve the heat exchange performance between the air and the refrigerant.

[0075] The above describes the embodiment, but the embodiment is not limited to the above content. In addition, the above-mentioned structural elements include structural elements that are easily thought of by a person skilled in the art, substantially the same, and within the so-called equivalent scope. Furthermore, the above-mentioned structural elements can be appropriately combined. In addition, within the scope of not departing from the gist of the embodiment, the structural elements can be omitted, replaced, and changed at least one of them.

[0076] Explanation of symbols

[0077] 1: Air conditioner

[0078] 4, 5: Heat exchanger

[0079] 11: Multiple heat transfer flat tubes

[0080] 12: Header

[0081] 13: Header

[0082] 20: Main body

[0083] 21: First partition member

[0084] 22: Second partition member

[0085] 23: Refrigerant flows into the space

[0086] 24: Windward side space

[0087] 25: Leeward side space

[0088] 27: Windward side flow inlet

[0089] 28: Upper connecting road

[0090] 29: Lower connecting road

[0091] 42: Circulation direction

[0092] 44: Multiple windward flow paths

[0093] 45: Multiple leeward flow paths

[0094] 50: Heat exchanger

[0095] 51: Header

[0096] 53: Windward side partition

[0097] 54: Leeward side partition

[0098] 55: Circular space separator

[0099] 56: Heat transfer tube insertion space

[0100] 57: Circular Space

[0101] 58: Windward side space

[0102] 59: Leeward side space

[0103] 61: Upper connecting road

[0104] 62: Lower connecting road

[0105] 63: Multiple windward side connecting holes

[0106] 64: Multiple leeward side connecting holes

[0107] 71: Header

[0108] 72: Multiple separator components

[0109] 73: Multiple heat transfer tubes inserted into the space

Claims

1. A heat exchanger, It is characterized in that include: A plurality of heat transfer flat tubes are arranged in the air flow area; as well as a header connected to ends of the plurality of heat transfer flat tubes, Each of the plurality of heat transfer flat tubes has: Multiple windward flow paths; as well as a plurality of leeward side flow paths, which are arranged on the leeward side of the air relative to the plurality of windward side flow paths, The header comprises: a main body portion, which forms an internal space, the internal space being connected to the plurality of windward side flow paths and the plurality of leeward side flow paths; a partition member that divides the internal space into a windward side space and a leeward side space, the windward side space being located on a side close to the ends of the plurality of windward side flow paths, and the leeward side space being located on a side close to the ends of the plurality of leeward side flow paths; an inflow portion for supplying refrigerant to a lower portion of the leeward side space; a windward-side partition member that divides the internal space into an insertion space and the windward-side space, wherein the ends of the plurality of windward-side flow paths and the ends of the plurality of leeward-side flow paths are arranged in the insertion space; a leeward side partitioning member, which partitions the insertion space from the leeward side space; and a plurality of partition members, which divide the insertion space into a plurality of spaces, The windward side partition member is formed with a plurality of windward side communication holes, and the plurality of windward side communication holes connect the insertion space with the windward side space. The plurality of windward-side communication holes respectively connect the plurality of spaces with the windward-side space. The plurality of spaces are each provided with an end portion of any one of the plurality of heat transfer flat tubes. An upper communicating passage is formed at the upper portion of the partition member, and the upper communicating passage connects the leeward side space with the windward side space. The upper communication passage is formed so that an upper end of the leeward-side space is connected flush with an upper end of the windward-side space.

2. The heat exchanger according to claim 1, It is characterized in that A lower communicating passage is further formed at a lower portion of the partition member, and the lower communicating passage allows the leeward-side space to communicate with the windward-side space.

3. The heat exchanger according to claim 1, It is characterized in that The leeward partition member is formed with a plurality of leeward communication holes that allow the insertion space to communicate with the leeward space.

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