HEAT EXCHANGER, HEAT EXCHANGER UNIT, AND REFRIGERATION CYCLE DEVICE

Abstract

To provide a heat exchanger, a heat exchanger unit, and a refrigeration cycle device capable of regulating fin pitches while suppressing pressure loss of air and improving heat conductivity between flat tubes and fins.SOLUTION: A heat exchanger includes a plurality of flat tubes and fins. The fin has: a flat tube insertion portion formed on a fin body; and a first fin pitch regulation portion and a second fin pitch regulation portion formed by bending a part of the fin bodies in a first direction to be projected to a first face side and kept into contact with the fins disposed at one side in an extension direction. An outer shape of a second end portion is circular or elliptical, and a shape of a tip end portion of the flat tube insertion portion for housing the second end portion is a shape on which an outer peripheral surface of the second end portion and the fin body are brought into surface contact with each other. The first fin pitch regulation portion is disposed at a rear end portion side of the flat tube insertion portion, and the second fin pitch regulation portion is disposed at a tip end portion side of the flat tube insertion portion.SELECTED DRAWING: Figure 42

Description

[Technical field]

[0001] The present disclosure relates to a heat exchanger, a heat exchanger unit, and a refrigeration cycle apparatus. [Background technology]

[0002] 2. Description of the Related Art A multi-flow type heat exchanger including a plurality of flat tubes, a plurality of fins, and a pair of headers is known as a heat exchanger. The flat tubes are inserted into the fins at intervals in the vertical direction. Each flat tube has a plurality of flow passages spaced apart in the width direction. The fins are spaced apart in the direction in which the flat tubes extend.

[0003] The pair of headers each extend in the vertical direction. One header is connected to the flat tubes while accommodating one end of each of the flat tubes. The other header is connected to the flat tubes while accommodating the other end of each of the flat tubes.

[0004] When the heat exchanger is used as an evaporator, a gas-liquid two-phase refrigerant is introduced from the outside into the header. In order to fully utilize the heat transfer area of ​​the heat exchanger, it is necessary to suppress bias in refrigerant distribution to each flat tube and to the multiple flow paths formed in each flat tube, regardless of the flow rate of refrigerant introduced into the header. However, in a simple configuration in which one end of each of the flat tubes is inserted into the header, the influence of inertia and gravity causes uneven distribution of the refrigerant to each of the flat tubes. That is, when the refrigerant flow rate is low, the influence of gravity becomes dominant and more liquid refrigerant is supplied to the flat tubes located below the header. On the other hand, when the refrigerant flow rate is high, the influence of inertia becomes dominant and more liquid refrigerant is supplied to the flat tubes located above the header.

[0005] Patent Document 1 discloses a heat exchanger intended to suppress uneven flow of a refrigerant caused by the amount of circulation of the refrigerant. Specifically, Patent Document 1 discloses a heat exchanger comprising a first straightening plate that separates a first internal space located at the bottom of the header's internal space from a space located above the first internal space, and a first partition plate that separates the space located above the first internal space into a first outlet space and a first loop space, and directs refrigerant introduced into the first internal space to the first outlet space through two first inlets formed in the first straightening plate, and circulates the refrigerant between the first outlet space and the first loop space.

[0006] On the other hand, some flat-shaped heat exchanger fins have a thin, plate-like fin body that extends in the vertical direction, a number of flat tube insertion sections into which flat tubes are inserted, and a communicating section that guides condensed water from the upper side to the lower side. The flat tube insertion portion is formed in the fin body and extends in a left-right direction perpendicular to the up-down direction. The flat tube insertion portion is formed so as not to divide the fin body in the left-right direction. The communication portion is formed by a portion of the fin body that is located outside the flat tube insertion portions. The communication portion extends continuously in the up-down direction.

[0007] When using fins configured as described above, there is a problem that the fins are easily toppled at the portion of the communication part that faces the flat tube insertion part in the left-right direction. As a technology aimed at solving such a problem, there is a heat exchanger disclosed in Patent Document 2.

[0008] Patent Document 2 discloses that a heat transfer promotion section is formed between fin interval adjustment sections formed in the communication section and spaced apart in the up-down direction, the heat transfer promotion section facing the flat tube insertion section in the left-right direction and protruding to one side in the arrangement direction of the multiple fins (hereinafter referred to as the "fin arrangement direction"). A plurality of heat transfer promotion sections are arranged at intervals in the up-down direction.

[0009] On the other hand, Patent Document 3 discloses that the interval (fin pitch) between adjacent fins is defined by first and second spacing portions formed on a plate-like fin. The first spacing portion is formed on the front edge (the edge located on the upstream side in the air flow direction) of the flat tube when the flat tube is arranged on the fin, and the second spacing portion is formed on the fin located between the flat tubes arranged in the vertical direction.

[0010] Patent Document 3 discloses that the first and second spacing portions are formed by bending parts of the fins. Furthermore, Patent Document 3 discloses that when forming the first spacing portion, a part of the fin is bent so as to face the air flow direction. Furthermore, Patent Document 3 discloses a configuration in which the tip end of the flat tube contacts only a part of the first spacing portion. [Prior art documents] [Patent documents]

[0011] [Patent Document 1] Patent No. 5754490 [Patent Document 2] Patent No. 5397489 [Patent Document 3] International Publication No. 2019 / 239519 Summary of the Invention [Problem to be solved by the invention]

[0012] Generally, when there are a large number of flat tubes, the space within the header is divided into multiple spaces by arranging horizontal partition plates extending horizontally in the vertical direction within the header. In order to achieve equal distribution using the heat exchanger described in Patent Document 1, it is desirable to arrange the first outlet space and the first loop space continuously in the vertical direction. This makes it difficult to secure the space for providing the first internal space, and it may be difficult to provide the first internal space. In addition, the number of horizontal partition plates may increase, which may complicate the manufacturing process.

[0013] In addition, in Patent Document 1, the refrigerant introduced into the first internal space is guided to the first outlet space through the two first inlets formed in the first straightening plate, so the state of the refrigerant may differ in the width direction of the flat tubes. In this case, it may be difficult to suppress bias in refrigerant distribution to the multiple flow paths formed in the width direction of each flat tube.

[0014] On the other hand, the heat transfer promotion portion disclosed in Patent Document 2 is formed by pressing a plate-shaped base material member that is the base material of the fins. Therefore, a depression with a bottom is formed on the other side of the heat transfer promotion portion in the fin arrangement direction. As a result, condensed water flowing through the communication portion may accumulate at the bottom of the heat transfer promotion portion, making it difficult to drain the condensed water downward through the communication portion.

[0015] On the other hand, in Patent Document 3, when forming the first spacing portion, a part of the fin is bent to face the air flow direction. Therefore, the first spacing portion may cause flow resistance, which may increase the air pressure loss. Furthermore, in Patent Document 3, the tip end of the flat tube contacts only a part of the first spacing portion, which may make it difficult to improve thermal conductivity between the fins and the flat tube.

[0016] The present disclosure has been made to solve the above-mentioned problems, and aims to provide a heat exchanger, a heat exchanger unit, and a refrigeration cycle device that can simplify the manufacturing process and suppress bias in refrigerant distribution to each flat tube and to multiple flow paths formed in the width direction of each flat tube, regardless of the flow rate of refrigerant supplied into the header. Furthermore, the present disclosure has been made to solve the above-mentioned problems, and aims to provide a heat exchanger, a heat exchanger unit, and a refrigeration cycle apparatus that are capable of suppressing the collapse of fins while suppressing the obstruction of the flow of condensed water in the communicating portion. Furthermore, the present disclosure has been made to solve the above-mentioned problems, and aims to provide a heat exchanger, a heat exchanger unit, and a refrigeration cycle apparatus that make it possible to specify the fin pitch while suppressing air pressure loss, and that can improve thermal conductivity between the flat tubes and the fins. [Means for solving the problem]

[0017] In order to solve the above problems, a heat exchanger according to the present disclosure includes a plurality of flat tubes having a flat outer shape, a flow path through which a refrigerant flows, and a first end portion disposed on one side in a width direction and a second end portion disposed on the other side in the width direction, and a plurality of fins arranged at a predetermined pitch in an extension direction of the flat tubes while accommodating the plurality of flat tubes, the plurality of fins being plate-shaped and including a fin body including a first surface disposed in the extension direction and a second surface disposed opposite to the first surface. a flat tube insertion section that is formed on the fin body and is arranged at intervals in a first direction perpendicular to the extension direction, extends from one side to the other side in a second direction perpendicular to the first direction and the extension direction, and accommodates the flat tube inserted from the second end side; a communication section that is arranged on the other side of the second direction relative to the flat tube insertion sections and extends continuously in the first direction; and a portion of the fin body located between the flat tube insertion sections adjacent to each other in the first direction is referred to as the first communication section. a first fin pitch defining portion that is formed by bending a part of the fin body in the first direction and protruding toward the first surface side and abuts against the fin arranged on one side in the extension direction, and a second fin pitch defining portion that is formed by bending a part of the fin body in the first direction and protruding toward the first surface side, is arranged around the flat tube insertion portion located on the rear end side relative to the tip end of the flat tube insertion portion, and abuts against the fin arranged on one side in the extension direction, and In the fin main body, the fin pitch determining portion is disposed on the rear end side of the flat tube insertion portion, and the second fin pitch determining portion is disposed on the tip end side of the flat tube insertion portion. The first direction is a vertical direction. The fin pitch determining portion is formed in the communication portion. The first fin pitch defining portion and the second fin pitch defining portion are arranged at a distance from each other in the second direction, and only one each of the first fin pitch defining portion and the second fin pitch defining portion is provided between the flat tubes. Effect of the Invention

[0018] The heat exchanger, heat exchanger unit, and refrigeration cycle apparatus disclosed herein can suppress imbalance in refrigerant distribution to each flat tube and to multiple flow paths formed in the width direction of each flat tube, while preventing the manufacturing process from becoming complicated, and without depending on the flow rate of refrigerant supplied into the header. On the other hand, according to the heat exchanger, heat exchanger unit, and refrigeration cycle apparatus of the present disclosure, it is possible to suppress the collapse of the fins while suppressing the obstruction of the flow of condensed water in the communication portion. On the other hand, according to the heat exchanger, heat exchanger unit, and refrigeration cycle apparatus of the present disclosure, the fin pitch can be specified while suppressing air pressure loss, and the thermal conductivity between the flat tubes and the fins can be improved. [Brief description of the drawings]

[0019] [Figure 1] 1 is a diagram illustrating a schematic configuration of a refrigeration cycle device according to a first embodiment of the present disclosure. [Diagram 2] FIG. 2 is a diagram showing a schematic view of a main part of the heat exchanger shown in FIG. [Diagram 3] FIG. 3 is a perspective view of the flat tube shown in FIG. 2. [Figure 4] 3 is a vertical cross-sectional view of the header surrounded by an area B shown in FIG. 2. [Diagram 5] 5 is a cross-sectional view of the header shown in FIG. 4 taken along line C1-C2. [Figure 6] 5 is a cross-sectional view of the header shown in FIG. 4 taken along line D1-D2. [Figure 7] 4 is a cross-sectional view of a main part of a heat exchanger according to a first modified example of the first embodiment. FIG. [Figure 8] FIG. 6 is a vertical cross-sectional view of a main part of a heat exchanger according to a second embodiment. [Figure 9] FIG. 11 is a vertical cross-sectional view of a main part of a heat exchanger according to a first modified example of the second embodiment. [Figure 10] FIG. 11 is a vertical cross-sectional view of a main part of a heat exchanger according to a second modified example of the second embodiment. [Figure 11] FIG. 11 is a vertical cross-sectional view of a main part of a heat exchanger according to a third modified example of the second embodiment. [Figure 12] FIG. 11 is a vertical cross-sectional view of a main part of a heat exchanger according to a third embodiment. [Figure 13] FIG. 13 is a vertical cross-sectional view of a main part of a heat exchanger according to a first modified example of the third embodiment. [Figure 14] FIG. 13 is a vertical cross-sectional view of a main part of a heat exchanger according to a second modified example of the third embodiment. [Figure 15] FIG. 11 is a vertical cross-sectional view of a main part of a heat exchanger according to a fourth embodiment. [Figure 16] FIG. 13 is a vertical cross-sectional view of a main part of a heat exchanger according to a first modified example of the fourth embodiment. [Figure 17] FIG. 13 is a vertical cross-sectional view of a main part of a heat exchanger according to a second modified example of the fourth embodiment. [Figure 18] FIG. 13 is a vertical cross-sectional view of a main part of a heat exchanger according to a third modified example of the fourth embodiment. [Figure 19] FIG. 13 is a vertical sectional view of a main part of a heat exchanger according to a fourth modified example of the fourth embodiment. [Figure 20] FIG. 13 is a vertical cross-sectional view of a main part of a heat exchanger according to a fifth modified example of the fourth embodiment. [Figure 21] FIG. 11 is a diagram illustrating a schematic configuration of a refrigeration cycle device according to a fifth embodiment of the present disclosure. [Figure 22] FIG. 22 is a diagram showing a schematic view of a main part of the heat exchanger shown in FIG. 21. [Figure 23] 23 is a view of the flat tubes and fins shown in FIG. 22 viewed from A. FIG. [Figure 24] FIG. 23 is a perspective view of the flat tube shown in FIG. 22. [Diagram 25] 24 is a cross-sectional view of the fin shown in FIG. 23 taken along line E1-E2, showing a cross-section of one fin. [Figure 26] 24 is a cross-sectional view of the fin shown in FIG. 23 taken along line F1-F2, and is a cross-sectional view showing a schematic state in which the fin pitch defining portion is in contact with fins arranged in adjacent positions. FIG. [Figure 27] 23 is a cross-sectional view taken along line G1-G2 of the fin shown in FIG. 22, showing a cross-section of one fin. FIG. [Figure 28]23 is a plan view for explaining a process prior to a cutting process performed when manufacturing the plurality of fins shown in FIG. 22. FIG. [Figure 29] 23 is a plan view for explaining a cutting step performed when manufacturing the multiple fins shown in FIG. 22. FIG. [Diagram 30] 23 is a plan view for explaining another example of the arrangement of the fins when the fins shown in FIG. 22 are manufactured. FIG. [Diagram 31] FIG. 13 is a diagram showing a main part of a heat exchanger according to a sixth embodiment of the present disclosure. [Diagram 32] 32 is a cross-sectional view of the fin shown in FIG. 31 taken along line I1-I2, showing a cross-section of one fin. [Diagram 33] FIG. 13 is a diagram showing a main part of a heat exchanger according to a seventh embodiment of the present disclosure. [Diagram 34] 34 is a cross-sectional view taken along line K1-K2 of the fin shown in FIG. 33, showing a cross-section of one fin. FIG. [Diagram 35] FIG. 13 is a diagram showing a main part of a heat exchanger according to an eighth embodiment of the present disclosure. [Diagram 36] 36 is a cross-sectional view of the fin shown in FIG. 35 taken along line L1-L2, showing a cross-section of one fin. [Figure 37] 36 is a cross-sectional view of the fin shown in FIG. 35 taken along line N1-N2, showing a cross-section of one fin. [Figure 38] FIG. 23 is a diagram showing a main part of a heat exchanger according to a first modified example of the eighth embodiment of the present disclosure. [Figure 39] FIG. 23 is a diagram showing a main part of a heat exchanger according to a second modified example of the eighth embodiment of the present disclosure. [Diagram 40] FIG. 13 is a diagram illustrating a schematic configuration of a refrigeration cycle device according to a ninth embodiment of the present disclosure. [Diagram 41] FIG. 41 is a diagram showing a schematic view of a main part of the heat exchanger shown in FIG. 40. [Diagram 42] 42 is a view of the flat tubes and fins shown in FIG. 41 viewed from A. FIG. [Diagram 43] 43 is a cross-sectional view of the fin shown in FIG. 42 taken along line Q1-Q2, showing a cross-section of one fin. [Diagram 44] 43 is a cross-sectional view of the fin shown in FIG. 42 taken along line R1-R2, showing a cross-section of one fin. [Diagram 45] 43 is a cross-sectional view of the fin shown in FIG. 42 taken along line S1-S2, and is a cross-sectional view illustrating a state in which a first fin pitch defining portion is in contact with fins arranged in adjacent positions. FIG. [Figure 46] 43 is a cross-sectional view taken along line T1-T2 of the fin shown in FIG. 42, and is a cross-sectional view illustrating a state in which second fin pitch defining portions are in contact with fins arranged in adjacent positions. FIG. [Figure 47] FIG. 13 is a diagram for explaining a fin according to a modified example of the ninth embodiment of the present disclosure. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0020] <First embodiment> The overall configuration of a refrigeration cycle device 10 of the first embodiment will be described with reference to Fig. 1. In Fig. 1, solid arrows indicate the direction in which the refrigerant flows during heating operation, and dotted arrows indicate the direction in which the refrigerant flows during cooling operation. (Overall configuration of the refrigeration cycle device) The refrigeration cycle apparatus 10 includes a four-way valve 15, a compressor 16, a first heat exchanger unit 18, an expansion valve 19, and a second heat exchanger unit 23, which are connected by a refrigerant piping 14. The refrigeration cycle apparatus 10 includes an outdoor unit 11 and an indoor unit 12.

[0021] (Overall configuration of outdoor unit) The outdoor unit 11 has a four-way valve 15, a compressor 16, a first heat exchanger unit 18, and an expansion valve 19.

[0022] (Four-way valve configuration) Four-way valve 15 has connection parts 15A to 15D to which one of both ends of first and second refrigerant pipes 14A, 14B constituting refrigerant pipe 14 is connected. One end of first refrigerant pipe 14A is connected to connection part 15A, and the other end of first refrigerant pipe 14A is connected to connection part 15B. One end of second refrigerant pipe 14B is connected to connection part 15C, and the other end of second refrigerant pipe 14B is connected to connection part 15D.

[0023] The four-way valve 15 configured as described above switches the direction in which the refrigerant flows between heating operation and cooling operation. Specifically, during cooling operation, the refrigerant is circulated through the compressor 16, the first heat exchanger unit 18, the expansion valve 19, and the second heat exchanger unit 23 in this order. On the other hand, during heating operation, the refrigerant is circulated through the compressor 16, the second heat exchanger unit 23, the expansion valve 19, and the first heat exchanger unit 18 in this order.

[0024] (Compressor configuration) The compressor 16 is provided in the second refrigerant pipe 14B. The compressor 16 compresses the refrigerant flowing through the second refrigerant pipe 14B.

[0025] (Configuration of the first heat exchanger unit) The first heat exchanger unit 18 includes a first blower 26 and a heat exchanger 27 .

[0026] (Configuration of the first fan) The first blower 26 supplies air to the heat exchanger 27 .

[0027] (Overall structure of heat exchanger) The heat exchanger 27 will be described with reference to Figs. 1 to 6. In Figs. 2 to 4 and 6, the Z direction indicates the up-down direction. In Figs. 2 to 5, the X direction indicates the extension direction of the flat tubes 41 perpendicular to the Z direction. In Figs. 3, 5 and 6, the Y direction indicates the width direction of the flat tubes 41 (width direction of the nozzle portion 49) perpendicular to the X and Z directions. In Fig. 2, air flows in the direction of the paper (for example, the direction toward the paper). The arrows in Fig. 4 indicate the direction in which the refrigerant flows when the heat exchanger 27 is used as an evaporator, and H indicates the height of the header body 45 (hereinafter referred to as "height H").

[0028] During cooling operation, the heat exchanger 27 is used as a condenser and dissipates heat to the outside, and during heating operation, the heat exchanger 27 is used as an evaporator and absorbs heat from the outside. The heat exchanger 27 is provided in the first refrigerant pipe 14A located between the four-way valve 15 and the expansion valve 19. The heat exchanger 27 has a plurality of flat tubes 41, a plurality of fins 42, and a pair of headers 43.

[0029] (Flat tube configuration) Next, the flat tube 41 will be described with reference to Fig. 2 and Fig. 3. The flat tube 41 is a heat transfer tube having a flat outer shape. The flat tube 41 extends in the X direction. Inside the flat tube 41, a plurality of flow paths 41A through which a refrigerant flows are formed at intervals in the Y direction. The flat tubes 41 include a flat tube 41F arranged at the bottom and a flat tube 41S arranged second from the bottom.

[0030] The flat tube 41 has a pair of end portions 41B, 41C arranged in the X direction. One end portion 41B is housed in one header 43. The other end portion 41C is housed in the other header 43. The multiple flat tubes 41 are arranged at intervals in the Z direction, and are supported on both sides in the X direction by the pair of headers 43.

[0031] (Fin configuration) Next, the fins 42 will be described with reference to FIG. The multiple fins 42 each have a flat tube insertion portion 42A formed at intervals in the Z direction. The flat tubes 41 are inserted into the flat tube insertion portion 42A.

[0032] (Header structure) Next, the configuration of the pair of headers 43 will be described with reference to Fig. 2 and Fig. 4 to Fig. 6. The pair of headers are arranged to face each other in the X direction. One header 43 is connected to the flat tubes 41 such that one end 41B of the flat tubes 41 is arranged on the inside. The other header 43 is connected to the flat tubes 41 such that the other end 41C of the flat tubes 41 is arranged on the inside.

[0033] Here, the configuration of the header 43 on the evaporator inlet side out of the pair of headers 43 will be described. The header 43 includes a header body 45 , a partition plate 47 , a nozzle portion 49 , and a porous plate 51 .

[0034] (Header body structure) Next, the header body 45 will be described with reference to Fig. 4 to Fig. 6. The header body 45 is a cylindrical member that extends in the Z direction and has closed upper and lower ends. The header body 45 defines a columnar internal space 53 on the inside. The header body 45 has an opening 45A and a bottom surface 45a. The opening 45A is formed in a side wall of the header body 45. The tip end of the first refrigerant pipe 14A is inserted into the opening 45A. The opening 45A is formed at a position facing the nozzle portion 49 in the X direction.

[0035] The bottom surface 45a has a first bottom surface 45aa, a second bottom surface 45ab, and a third bottom surface 45ac. The first bottom surface 45aa is a surface that defines the lower end of the first space 54. The second bottom surface 45ab is a surface that defines the lower end of the second space 55. The third bottom surface 45ac is disposed between the first bottom surface 45aa and the second bottom surface 45ab, which are disposed in the X direction. The third bottom surface 45ac is connected to the first bottom surface 45aa and the second bottom surface 45ab.

[0036] (Partition plate configuration) Next, the partition plate 47 will be described with reference to FIGS. The partition plate 47 is disposed in the header body 45 while extending in the Z direction. Both ends of the partition plate 47 disposed in the Y direction are connected to the header body 45. The partition plate 47 divides the internal space 53 into a first space 54 and a second space 55 arranged in the X direction, with the refrigerant being able to flow through the upper and lower ends of the internal space 53. The first space 54 is arranged on the side to which the first refrigerant pipe 14A is connected. The second space 55 is arranged on the side to which the multiple flat tubes 41 are connected. The partition plate 47 forms a circulation path for the refrigerant.

[0037] The partition plate 47 has an upper end surface 47a, a first surface 47b, a second surface 47c, a pair of lower ends 47A, 47B (one lower end and the other lower end), and a notch 47C.

[0038] The upper end surface 47a is disposed at a position spaced downward from the header body 45 facing the upper end surface 47a in the Z direction. The refrigerant moves between the first space 54 and the second space 55 through an opening formed between the upper end surface 47a and the header body 45 facing the upper end surface 47a.

[0039] The first surface 47b is a plane perpendicular to the X direction, and defines the other side of the first space 54 in the X direction. The second surface 47c is a surface disposed on the opposite side to the first surface 47b. The second surface 47c is a plane perpendicular to the X direction, and defines one side of the second space 55 in the X direction.

[0040] The lower end portion 47A is disposed on one side in the Y direction. A lower end 47Aa of the lower end portion 47A reaches a bottom surface 45a of the header body 45. The lower end 47B is disposed on the other side in the Y direction. A lower end 47Ba of the lower end 47B reaches the bottom surface 45a of the header body 45.

[0041] The cutout portion 47C is formed between the lower end portion 47A and the lower end portion 47B. The cutout portion 47C is rectangular. The refrigerant moves between the first space 54 and the second space 55 through an opening defined by the cutout portion 47C and the bottom surface 45a.

[0042] (Effect of the shape of the bottom end of the partition plate) For example, when a circular hole is used as the air outlet 49A of the nozzle portion 49, the refrigerant flows from the first space 54 to the second space 55 through the cutout portion 47C located between the lower end portion 47A and the lower end portion 47B. At this time, the lower ends 47A and 47B can prevent the refrigerant from flowing back from the second space 55 to the first space 54.

[0043] (Nozzle configuration) Next, the nozzle portion 49 will be described with reference to FIGS. The nozzle portion 49 is disposed in the first space 54. The nozzle portion 49 is fixed to the header body 45 and the partition plate 47. A refrigerant flow portion 54A through which the refrigerant passes is formed on both sides of the nozzle portion 49 in the Y direction. The refrigerant flow portion 54A is configured as a part of the first space 54.

[0044] The nozzle portion 49 has an air outlet 49A disposed on the lower end side. The air outlet 49A has a circular shape when viewed from the Z direction. When the heat exchanger 27 is operated as an evaporator, the nozzle portion 49 is supplied with a refrigerant (a two-phase gas-liquid refrigerant) through the first refrigerant pipe 14A. The outlet 49A blows out the refrigerant in a direction toward the first bottom surface 45aa, thereby colliding the refrigerant with the first bottom surface 45aa and reducing the difference in the state of the refrigerant in the Y direction. After colliding with the first bottom surface 45aa, the refrigerant flows through the cutout portion 47C to the lower portion of the second space 55, and then flows toward the upper end of the second space 55, and is guided into the multiple flow paths 41A formed in each flat tube 41. The refrigerant that has moved to the upper end of the second space 55 flows to the upper end of the first space 54, and then flows toward the first bottom surface 45aa.

[0045] When the heat exchanger 27 is operated as a condenser, the refrigerant flowing from the flat tubes 41 into the second space 55 flows into the first refrigerant pipe 14A via the outlet 49A.

[0046] (Nozzle effect) The nozzle portion 49 having the above configuration makes it possible to reduce the difference in the state of the refrigerant in the Y direction by causing the refrigerant blown out from the blowout port 49A to collide with the first bottom surface 45aa of the header body 45. As a result, the refrigerant with a small difference in state in the Y direction flows from the first space 54 toward the second space 55 (the space in which one end 41B of the multiple flat tubes 41 is arranged), so that it is possible to suppress bias in refrigerant distribution to the multiple flow paths 41A formed in the Y direction of each flat tube 41, regardless of the flow rate of the refrigerant introduced into the header 43.

[0047] The nozzle portion 49 configured as described above is preferably positioned, for example, at a position lower than 1 / 2 of the height of the header body 45, more preferably at a position lower than 1 / 3 of the height of the header body 45, and even more preferably at a position lower than 1 / 4 of the height of the header body 45. Furthermore, the nozzle portion 49 configured as described above may be disposed, for example, between the flat tube 41F that is disposed at the bottom and the flat tube 41S that is disposed second from the bottom among the plurality of flat tubes 41.

[0048] (Effect of the nozzle location) For example, if the nozzle portion 49 is positioned at a position higher than 1 / 2 the height H of the header body 45, the distance from the outlet 49A of the nozzle portion 49 to the first bottom surface 45aa of the header body 45 becomes too long, so that the flow of refrigerant blown out from the outlet 49A is attenuated, which may make it difficult to form a circulating flow of refrigerant within the header 43. Therefore, by positioning the nozzle portion 49 at a position lower than 1 / 2 of the height H of the header body 45, it is possible to shorten the distance from the outlet 49A to the first bottom surface 45aa of the header body 45, making it easier to form a circulating flow of refrigerant within the header 43.

[0049] Furthermore, by positioning the nozzle portion 49 at a position lower than 1 / 3 of the height of the header body 45, it is possible to shorten the distance from the outlet 49A to the first bottom surface 45aa of the header body 45, making it easier to form a circulating flow of the refrigerant within the header 43.

[0050] Furthermore, by positioning the nozzle portion 49 at a position lower than 1 / 4 of the height of the header body 45, it is possible to further shorten the distance from the outlet 49A to the first bottom surface 45aa of the header body 45, making it easier to form a circulating flow of the refrigerant within the header 43.

[0051] As described above, by positioning the nozzle portion 49 between the lowest flat tube 41F and the second lowest flat tube 41S, a circulating flow of refrigerant can be easily formed within the header 43. Furthermore, when the heat exchanger 27 is used as a condenser, the refrigerant (liquid-phase refrigerant) flowing into the header 43 can be easily discharged to the outside of the header via the flat tubes 41.

[0052] (Configuration of perforated plate) Next, the porous plate 51 will be described with reference to FIG. The perforated plate 51 is disposed so as to horizontally cover the first space 54 located above the nozzle portion 49. The perforated plate 51 is fixed to the header body 45 and the partition plate 47. The perforated plate 51 has a plurality of holes 51A formed therein, which communicate with the first space 54 in the Z direction. As the perforated plate 51, for example, a punched plate can be used. In FIG. 4, a punched plate is shown as an example of the perforated plate 51, but the perforated plate 51 may be, for example, a mesh member or a porous plate.

[0053] (Effect of perforated plate) By providing a porous plate 51 configured in this manner, it is possible to suppress the movement of gas (gas refrigerant) flowing back from the bottom to the top of the first space 54, making it easier to form a circulating flow of refrigerant within the header 43.

[0054] (Heat exchanger effect) According to the heat exchanger 27 of the first embodiment, by having the nozzle portion 49 configured as above, it is possible to make the refrigerant blown out from the blowout port 49A collide with the first bottom surface 45aa of the header body 45, thereby making it possible to reduce the difference in the state of the refrigerant in the Y direction. As a result, the refrigerant with a small difference in state in the Y direction flows from the first space 54 toward the second space 55 (the space in which one end 41B of the plurality of flat tubes 41 is arranged), and therefore, without depending on the flow rate of the refrigerant introduced into the header 43, a circulating flow of the refrigerant (a flow that descends the first space 54 and ascends the second space 55) is formed in the header 43, and while suppressing the complication of the manufacturing process, it is possible to suppress the uneven distribution of the refrigerant to each flat tube 41, and also suppress the uneven distribution of the refrigerant to the plurality of flow paths 41A formed in the width direction (Y direction) of each flat tube 41.

[0055] (Effect of heat exchanger unit) According to the first and second heat exchanger units 18, 23 of the first embodiment, by having the heat exchanger 27 configured as described above, it is possible to improve the heat exchange efficiency.

[0056] (Expansion valve configuration) Next, the expansion valve 19 will be described with reference to FIG. The expansion valve 19 is provided in 14A located between the first heat exchanger unit 18 and the second heat exchanger unit 23. The expansion valve 19 expands the high-pressure refrigerant that has been liquefied through heat exchange, thereby reducing the pressure of the refrigerant.

[0057] (Indoor unit configuration) The indoor unit 12 has a second heat exchanger unit 23. The second heat exchanger unit 23 has a heat exchanger 27 and a second blower 32. The heat exchanger 27 constituting the second heat exchanger unit 23 is provided in the first refrigerant pipe 14A located between the expansion valve 19 and the four-way valve 15.

[0058] (Effect of refrigeration cycle device) According to the refrigeration cycle apparatus 10 of the first embodiment, by having the first and second heat exchanger units 18, 23 configured as described above, it is possible to improve the heat exchange efficiency.

[0059] Note that nozzle portion 49 and first refrigerant pipe 14A may be integrally configured. For example, first refrigerant pipe 14A may be inserted until it contacts partition plate 47, and a round hole (blowout port 49A) may be provided in the side surface near the tip of first refrigerant pipe 14A.

[0060] <First Modification of the First Embodiment> A heat exchanger 60 according to a modified example of the first embodiment will be described with reference to Fig. 7. In Fig. 7, the same components as those in the structure shown in Fig. 5 are denoted by the same reference numerals. In Fig. 7, W1 indicates the width of the nozzle portion 62 in the Y direction (hereinafter referred to as "width W1"), and W2 indicates the width of the refrigerant flow portion 54A in the Y direction (hereinafter referred to as "width W2").

[0061] (Overall structure of heat exchanger) The heat exchanger 60 is configured similarly to the heat exchanger 27, except that it has a pair of headers 61 instead of the pair of headers 43 constituting the heat exchanger 27 of the first embodiment.

[0062] (Header structure) The header 61 is configured similarly to the header 43 , except that the header 61 has a nozzle portion 62 instead of the nozzle portion 49 that configures the header 43 .

[0063] (Nozzle configuration) The nozzle portion 62 has an outlet 62A having a groove shape extending in the Y direction. The outlet 62A blows out the refrigerant toward the bottom surface of the header body 45. The width W1 of the nozzle portion 62 is configured to be wider than the width of the nozzle portion 49 shown in Fig. 5. As a result, the width W2 of the pair of refrigerant flow portions 54A arranged on both sides of the nozzle portion 62 in the Y direction is configured to be narrower than the width of the pair of refrigerant flow portions 54A shown in Fig. 5. The total value (= 2 × W2) of the widths W2 of a pair of refrigerant flow sections 54A arranged on both sides of the nozzle section 62 in the width direction (Y direction) may be configured to be smaller than the width W1 of the nozzle section 62, for example.

[0064] (Heat exchanger effect) According to the heat exchanger 60 of the modified example of the first embodiment, by making the air outlet 62A into a groove shape extending in the Y direction, the difference in the state of the refrigerant in the Y direction can be further reduced compared to when the air outlet is shaped like a circle. Moreover, by making the total value (=2×W2) of the widths W2 of the pair of refrigerant flow sections 54A arranged on both sides of the nozzle section 62 in the width direction (Y direction) smaller than the width W1 of the nozzle section 62, it is possible to reduce the flow path cross-sectional area of ​​the pair of refrigerant flow sections 54A. This makes it possible to suppress the occurrence of a backflow of the refrigerant from below to above in the first space 54.

[0065] <Second embodiment> A heat exchanger 70 according to a second embodiment will be described with reference to Fig. 8. In Fig. 8, the same components as those in the structure shown in Fig. 4 are denoted by the same reference numerals. The arrows shown in Fig. 8 indicate the direction in which the refrigerant flows when the heat exchanger 70 is used as an evaporator.

[0066] (Overall structure of heat exchanger) The heat exchanger 70 is configured similarly to the heat exchanger 27, except that it has a header 71 instead of the header 43 constituting the heat exchanger 27 of the first embodiment. The header 71 is configured similarly to the header 43, except that it has a first refrigerant guiding portion 73.

[0067] (Configuration of the first refrigerant guide portion) The first refrigerant guide portion 73 is provided on a first bottom surface 45aa of the header body 45. The first refrigerant guide portion 73 has a first guide surface 73a. The first guide surface 73a is disposed such that a portion of the first guide surface 73a faces the air outlet 49A in the Z direction. The first guide surface 73a guides the refrigerant in a direction from the first space 54 to the second space 55, and causes the refrigerant to collide with the inner wall surface 45b of the header body 45 that faces the first guide surface 73a in the X direction, thereby reducing the difference in the state of the refrigerant in the width direction. As the first guide surface 73a, for example, a concave curved surface that is concave in a direction away from the lower end of the partition plate 47 can be used.

[0068] (Heat exchanger effect) According to the heat exchanger 70 of the second embodiment, by being provided with the first refrigerant guide section 73 configured as described above, the refrigerant blown out from the outlet 49A of the nozzle section 49 is guided to the second space 55, and the refrigerant is collided with the inner wall surface 45b of the header body 45 that defines the second space 55, thereby reducing the difference in the state of the refrigerant in the width direction. Furthermore, when the refrigerant is a gas-liquid two-phase refrigerant and the flow rate of the refrigerant introduced into the header body 45 is small, it is possible to prevent the refrigerant from separating into gas and liquid in the first space 54, and to prevent the gas-phase refrigerant from rising in the first space 54. In other words, it is possible to prevent a circulating flow of the refrigerant from becoming difficult to form in the header body 45. Furthermore, by forming the first guide surface 73a as a concave curved surface recessed in a direction away from the lower end of the partition plate, the refrigerant can be smoothly guided from the first space 54 to the second space 55.

[0069] In the second embodiment, the nozzle portion 49 constituting the heat exchanger 70 may be replaced with a nozzle portion 62 shown in FIG.

[0070] <First Modification of the Second Embodiment> A heat exchanger 80 according to a first modified example of the second embodiment will be described with reference to Fig. 9. In Fig. 9, the same components as those in the structure shown in Fig. 8 are denoted by the same reference numerals. The arrows shown in Fig. 9 indicate the direction in which the refrigerant flows when the heat exchanger 80 is used as an evaporator.

[0071] (Overall structure of heat exchanger) The heat exchanger 80 is configured similarly to the heat exchanger 70, except that it has a header 81 instead of the header 71 constituting the heat exchanger 70 of the second embodiment. The header 81 is configured similarly to the header 71, except that a third refrigerant guiding portion 83 is provided in the configuration of the header 71.

[0072] (Configuration of the third refrigerant guide portion) The third refrigerant guide portion 83 is provided in a portion of the lower end portion of the partition plate 47 that is spaced upward from the bottom surface 45a of the header body 45. The third refrigerant guide portion 83 has a third guide surface 83a. The third guide surface 83a is disposed to face the first guide surface 73a. The third guide surface 83a guides the refrigerant in a direction from the first space 54 to the second space 55. As the third refrigerant guide portion 83, for example, a cylindrical member extending in the width direction of the partition plate 47 can be used.

[0073] (Heat exchanger effect) According to the heat exchanger 80 of the first modified example of the second embodiment, by being provided with the third refrigerant guide section 83 configured as described above, the refrigerant can be guided in the direction from the first space 54 to the second space 55 by the third guide surface 83a (the outer peripheral surface of the cylindrical member).

[0074] In the first modified example of the second embodiment, the nozzle portion 49 constituting the heat exchanger 80 may be replaced with a nozzle portion 62 shown in FIG.

[0075] <Second Modification of Second Embodiment> A heat exchanger 90 according to a second modified example of the second embodiment will be described with reference to Fig. 10. In Fig. 10, the same components as those in the structure shown in Fig. 8 are denoted by the same reference numerals. The arrows shown in Fig. 10 indicate the direction in which the refrigerant flows when the heat exchanger 90 is used as an evaporator.

[0076] (Overall structure of heat exchanger) The heat exchanger 90 is configured similarly to the heat exchanger 70, except that it has a header 91 instead of the header 71 constituting the heat exchanger 70 of the second embodiment. The header 91 is configured similarly to the header 71, except that a second refrigerant guiding portion 93 is provided in the configuration of the header 71.

[0077] (Configuration of the second refrigerant guide portion) The second refrigerant guide portion 93 is provided on the second bottom surface 45ab. The second refrigerant guide portion 93 has a second guide surface 93a. The second guide surface 93a guides the refrigerant (the refrigerant whose difference in state in the width direction is reduced by colliding with the first bottom surface 45aa) flowing from the lower end of the first space 54 to the lower end of the second space 55 in a direction from the lower side to the upper side of the second space 55. As the second guide surface 93a, for example, a concave curved surface that is concave in a direction away from the lower end of the partition plate 47 can be used.

[0078] (Heat exchanger effect) According to the heat exchanger 90 of the second modified example of the second embodiment, by being provided with the second refrigerant guide portion 93 configured as described above, the refrigerant which is generated by colliding with the first bottom surface 45aa of the header body 45 and has a small difference in state in the width direction can be guided in a direction from the bottom to the top of the second space 55. Furthermore, by making the second guide surface 93a a concave curved surface recessed in a direction away from the lower end of the partition plate 47, the refrigerant with little difference in state in the width direction can be easily guided in a direction from the bottom to the top of the second space 55.

[0079] In the heat exchanger 90 according to the second modified example of the second embodiment, at least one of the first refrigerant guiding portion 73 and the third refrigerant guiding portion 83 shown in FIG. 9 may be provided.

[0080] <Third Modification of Second Embodiment> A heat exchanger 100 according to a third modified example of the second embodiment will be described with reference to Fig. 11. In Fig. 11, the same components as those in the structure shown in Fig. 10 are denoted by the same reference numerals. The arrows shown in Fig. 11 indicate the direction in which the refrigerant flows when the heat exchanger 100 is used as an evaporator.

[0081] (Overall structure of heat exchanger) The heat exchanger 100 has a similar configuration to the heat exchanger 90, except that it has a header 101 instead of the header 91 constituting the heat exchanger 90 according to the second modified example of the second embodiment. The header 101 has a similar configuration to the header 91, except that a first refrigerant guiding portion 73 is provided in the configuration of the header 91.

[0082] (Heat exchanger effect) According to the heat exchanger 100 of the third modified example of the second embodiment, the refrigerant that collides with the first guide surface 73a and has a small difference in state in the width direction can be smoothly guided in the direction from the bottom to the top of the second space 55.

[0083] In the heat exchanger 100 according to the third modified example of the second embodiment, a third refrigerant guiding portion 83 shown in FIG. 9 may be provided.

[0084] <Third embodiment> A heat exchanger 110 according to a third embodiment will be described with reference to Fig. 12. In Fig. 12, the same components as those in the structure shown in Fig. 4 are denoted by the same reference numerals. The arrows shown in Fig. 12 indicate the direction in which the refrigerant flows when the heat exchanger 110 is used as an evaporator.

[0085] (Overall structure of heat exchanger) The heat exchanger 110 is configured in the same manner as the heat exchanger 27, except that one end 41Fa of the flat tube 41F is set back in the direction from the first space 54 to the second space 55 from the position of one end 41a of the other flat tube 41 relative to the header 43 that constitutes the heat exchanger 27 of the first embodiment. As a result, the distance Ds1 from one end 41Fa of the flat tube 41F to the second surface 47c of the partition plate 47 is configured to be longer than the distance Ds2 from one end 41a of the other flat tube 41 to the second surface 47c of the partition plate 47.

[0086] (Heat exchanger effect) According to the heat exchanger 110 of the third embodiment, by making the distance Ds1 from one end 41Fa of the flat tube 41F located at the bottom among the multiple flat tubes 41 to the partition plate 47 longer than the distance Ds2 from one end 41a of the other flat tubes 41 to the partition plate 47, it is possible to increase the cross-sectional area of ​​the refrigerant flow path formed between one end 41Fa of the flat tube 41F located at the bottom and the partition plate 47. This makes it possible to reduce the degree of flow contraction at the height position of the flat tube 41F, making the refrigerant flow less likely to separate, and makes it easier for liquid-phase refrigerant to be supplied to flat tube 41F, which would have been difficult for liquid-phase refrigerant to flow into due to separation (flow contraction) in the past, and as a result, the refrigerant can be distributed more evenly to each flat tube 41.

[0087] In addition, in the heat exchanger 110 according to the third embodiment, at least one of the first refrigerant guide portion 73 shown in FIG. 9, the third refrigerant guide portion 83 shown in FIG. 9, and the second refrigerant guide portion 93 shown in FIG. 10 may be provided.

[0088] <First Modification of the Third Embodiment> A heat exchanger 120 according to a first modified example of the third embodiment will be described with reference to Fig. 13. In Fig. 13, the same components as those in the structures shown in Fig. 8 and Fig. 12 are denoted by the same reference numerals. The arrows shown in Fig. 13 indicate the direction in which the refrigerant flows when the heat exchanger 120 is used as an evaporator.

[0089] (Overall structure of heat exchanger) The heat exchanger 120 is configured similarly to the heat exchanger 70, except that one end 41Fa of the flat tube 41F is set back in the direction from the first space 54 to the second space 55 from the position of one end 41a of the other flat tube 41 relative to the header 71 that constitutes the heat exchanger 70 of the second embodiment. In this way, the distance Ds1 from one end 41Fa of the bottommost flat tube 41F to the partition plate 47 may be made longer than the distance Ds2 from one end 41a of the other flat tubes 41 to the partition plate 47, and a first refrigerant guide portion 73 may be provided. Moreover, the heat exchanger 120 configured as above may be provided with a third refrigerant guide portion 83 shown in FIG.

[0090] <Second Modification of the Third Embodiment> A heat exchanger 130 according to a second modified example of the third embodiment will be described with reference to Fig. 14. In Fig. 14, the same components as those in the structure shown in Fig. 4 are denoted by the same reference numerals. The arrows shown in Fig. 14 indicate the direction in which the refrigerant flows when the heat exchanger 130 is used as an evaporator.

[0091] (Overall structure of heat exchanger) The heat exchanger 130 is configured similarly to the heat exchanger 27, except that it has a header 131 instead of the header 43 constituting the heat exchanger 27 of the first embodiment. The header 131 is configured similarly to the header 43, except that it has a partition plate 133 instead of the partition plate 47 constituting the header 43 of the first embodiment. The positions of the ends 41a, 41Fa of the flat tubes 41 in the X direction are the same.

[0092] (Partition plate configuration) The partition plate 133 has a lower end 133A facing one end 41Fa of the flat tube 41F in the X direction. The lower end 133A is disposed at a position shifted in the direction from the second space 55 toward the first space 54 with respect to the partition plate 133 excluding the lower end 133A. As a result, the distance Ds1 from one end 41Fa of the bottommost flat tube 41F to the partition plate 47 is configured to be longer than the distance Ds2 from one end 41a of the other flat tubes 41 to the partition plate 47.

[0093] (Heat exchanger effect) According to the heat exchanger 130 of the second variant of the third embodiment, the lower end 133A of the partition plate 133 facing one end 41Fa of the lowest flat tube 41F among the multiple flat tubes 41 is positioned at a position shifted in the direction from the second space 55 toward the first space 54, thereby making it possible to increase the cross-sectional area of ​​the refrigerant flow path formed between one end 41Fa of the lowest flat tube 41F and the partition plate 133.

[0094] In addition, in the heat exchanger 130 according to the second modified example of the third embodiment, at least one of the first refrigerant guide portion 73 shown in FIG. 9, the third refrigerant guide portion 83 shown in FIG. 9, and the second refrigerant guide portion 93 shown in FIG. 10 may be provided.

[0095] <Fourth embodiment> A heat exchanger 140 according to a fourth embodiment will be described with reference to Fig. 15. In Fig. 15, the same components as those in the structure shown in Fig. 4 are denoted by the same reference numerals. The arrows shown in Fig. 15 indicate the direction in which the refrigerant flows when the heat exchanger 140 is used as an evaporator.

[0096] (Overall structure of heat exchanger) The heat exchanger 140 is configured similarly to the heat exchanger 27, except that it has a header 141 instead of the header 43 constituting the heat exchanger 27 of the first embodiment. The header 141 is configured similarly to the header 43, except that a straightening member 143 is further provided in addition to the configuration of the header 43 of the first embodiment.

[0097] (Configuration of flow straightening member) The flow straightening member 143 is a baffle plate 145 provided on the inner wall surface 45 b of the header body 45 that defines the second space 55 . The baffle plate 145 is disposed below the flat tubes 41F and at a position away from the flat tubes 41F. The baffle plate 145 extends in a direction from the inner wall surface 45b of the header body 45 toward the partition plate. The amount of protrusion of the baffle plate 145 from the inner wall surface 45b is configured to be equal to the amount of protrusion of one end 41B of the flat tube 41F.

[0098] (Heat exchanger effect) According to the heat exchanger 140 of the fourth embodiment, by providing the baffle plate 145 (straightening member 143) configured as described above, it is possible to separate the refrigerant flow in front of one end 41B of the flat tube 41F located at the bottom, and straighten the refrigerant flow at one end of the flat tube 41F. This makes it easier for liquid-phase refrigerant to be supplied to flat tubes 41F, which in the past may have been difficult for liquid-phase refrigerant to flow into due to separation (contraction), and as a result, refrigerant distribution to each flat tube 41 can be made more equal.

[0099] <First Modification of the Fourth Embodiment> A heat exchanger 150 according to a first modified example of the fourth embodiment will be described with reference to Fig. 16. In Fig. 16, the same components as those in the structure shown in Fig. 15 are denoted by the same reference numerals. The arrows shown in Fig. 16 indicate the direction in which the refrigerant flows when the heat exchanger 150 is used as an evaporator.

[0100] (Overall structure of heat exchanger) The heat exchanger 150 has a similar configuration to the heat exchanger 140, except that the heat exchanger 150 has a header 151 instead of the header 141 constituting the heat exchanger 140 of the fourth embodiment. The header 151 has a similar configuration to the header 141 of the fourth embodiment, except that a first refrigerant guide portion 73 is further provided in addition to the configuration of the header 141 of the fourth embodiment. In this manner, the baffle plate 145 described in the fourth embodiment and the first refrigerant guiding portion 73 described in the second embodiment may be used in combination.

[0101] <Second Modification of the Fourth Embodiment> A heat exchanger 160 according to a first modified example of the fourth embodiment will be described with reference to Fig. 17. In Fig. 17, the same components as those in the structure shown in Fig. 15 are denoted by the same reference numerals. The arrows shown in Fig. 17 indicate the direction in which the refrigerant flows when the heat exchanger 160 is used as an evaporator.

[0102] (Overall structure of heat exchanger) The heat exchanger 160 is configured similarly to the heat exchanger 140, except that the heat exchanger 160 includes a block 164 that is a flow straightening member 163 instead of the baffle plate 145 that constitutes the heat exchanger 140 of the fourth embodiment.

[0103] (Block configuration) The block 164 is disposed below one end 41B of the flat tube 41F so as to be in contact with the lower surface of one end 41B of the flat tube 41F. The block 164 extends in a direction from the inner wall surface 45b of the header body 45 toward the partition plate 47. The amount of protrusion of the block 164 when the inner wall surface 45b of the header body 45 is used as a reference is equal to the amount of protrusion of one end 41B of the flat tube 41.

[0104] (Heat exchanger effect) According to the heat exchanger 160 of the first modified example of the fourth embodiment, by using the block 164 configured as described above as the straightening member 163, it is possible to separate the refrigerant flow in front of one end 41B of the flat tube 41F located at the bottom, and straighten the refrigerant flow at the end of the flat tube 41F. This makes it easier for liquid-phase refrigerant to be supplied to flat tubes 41F, which in the past may have been difficult for liquid-phase refrigerant to flow into due to separation (contraction), and as a result, refrigerant distribution to each flat tube 41 can be made more equal.

[0105] <Third Modification of the Fourth Embodiment> A heat exchanger 170 according to a third modified example of the fourth embodiment will be described with reference to Fig. 18. In Fig. 18, the same components as those in the structure shown in Fig. 17 are denoted by the same reference numerals. The arrows shown in Fig. 18 indicate the direction in which the refrigerant flows when the heat exchanger 170 is used as an evaporator.

[0106] (Overall structure of heat exchanger) The heat exchanger 170 is configured similarly to the heat exchanger 160, except that the heat exchanger 170 is provided with a block 174 which is a straightening member 173 instead of the block 164 which constitutes the heat exchanger 160 of the second modified example of the fourth embodiment.

[0107] (Block configuration) The block 174 is disposed below the one end 41B of the flat tube 41F so as to be in contact with the lower surface of the one end 41B of the flat tube 41F. The block 174 is formed on the partition plate 47 side and has a curved surface 174a that guides the flow of the refrigerant upward.

[0108] (Heat exchanger effect) According to the heat exchanger 170 according to the third modified example of the fourth embodiment, the block 174 has the curved surface 174a, so that the refrigerant can be guided upward into the second space 55 without the flow separating.

[0109] <Fourth Modification of the Fourth Embodiment> A heat exchanger 180 according to a fourth modified example of the fourth embodiment will be described with reference to Fig. 19. In Fig. 19, the same components as those in the structures shown in Fig. 11 and Fig. 17 are denoted by the same reference numerals. The arrows shown in Fig. 19 indicate the direction in which the refrigerant flows when the heat exchanger 180 is used as an evaporator.

[0110] (Overall structure of heat exchanger) The heat exchanger 180 has the same configuration as the heat exchanger 160, except that the heat exchanger 180 further includes a first refrigerant guide portion 73 and a second refrigerant guide portion 93 shown in FIG. 11 in addition to the configuration of the heat exchanger 170 according to the third modified example of the fourth embodiment. In this manner, the block 174, the first refrigerant guide portion 73, and the second refrigerant guide portion 93 may be used in combination.

[0111] <Fifth Modification of Fourth Embodiment> A heat exchanger 190 according to a fifth modified example of the fourth embodiment will be described with reference to Fig. 20. In Fig. 20, the same components as those in the structures shown in Fig. 14 and Fig. 19 are denoted by the same reference numerals. The arrows shown in Fig. 20 indicate the direction in which the refrigerant flows when the heat exchanger 190 is used as an evaporator.

[0112] (Overall structure of heat exchanger) The heat exchanger 190 is configured similarly to the heat exchanger 160, except that instead of the partition plate 47 constituting the heat exchanger 160 of the second variant of the fourth embodiment, the heat exchanger 190 has a partition plate 133 shown in FIG. 14. In this manner, the block 174, the first refrigerant guide portion 73, the second refrigerant guide portion 93, and the partition plate 133 may be used in combination.

[0113] <Fifth embodiment> A refrigeration cycle apparatus 200 according to a fifth embodiment will be described with reference to Fig. 21. In Fig. 21, solid arrows indicate the direction in which the refrigerant flows during heating operation, and dotted arrows indicate the direction in which the refrigerant flows during cooling operation. In Fig. 21, the same components as those in Fig. 1 are denoted by the same reference numerals.

[0114] (Overall configuration of the refrigeration cycle device) The refrigeration cycle apparatus 200 is configured similarly to the refrigeration cycle apparatus 10, except that it has first and second heat exchanger units 201, 203 instead of the first and second heat exchanger units 18, 23 that constitute the refrigeration cycle apparatus 10 of the first embodiment. The first heat exchanger unit 201 has the same configuration as the first heat exchanger unit 18 , except that the first heat exchanger unit 201 has a heat exchanger 205 instead of the heat exchanger 27 . The second heat exchanger unit 203 has the same configuration as the second heat exchanger unit 23 , except that it has a heat exchanger 205 instead of the heat exchanger 27 .

[0115] (Overall structure of heat exchanger) The heat exchanger 205 will be described with reference to Fig. 21 to Fig. 23. In Fig. 22, the same components as those in the structure shown in Fig. 2 are given the same reference numerals. In Fig. 22, the X direction indicates the extension direction of the flat tubes 41 perpendicular to the Z direction (up-down direction). In Fig. 23, the Y direction indicates the left-right direction perpendicular to the X direction and the Z direction (the width direction of the flat tubes 41 when the flat tubes 41 are attached to the fins 206), and J indicates the direction in which air flows (hereinafter referred to as "direction J").

[0116] The heat exchanger 205 is configured similarly to the heat exchanger 27 , except that instead of the pair of headers 43 and fins 42 , the heat exchanger 205 has an entrance / exit header 35 , a turn-back header 37 , and fins 206 .

[0117] (Entrance / Exit Header Configuration) The inlet / outlet header 35 is a cylindrical member extending in the Z direction, and has a closed upper end and lower end. The inlet / outlet header 35 is connected to the first refrigerant pipe 14A and one end of each of the flat tubes 41 (the end disposed on one side in the X direction). The inlet / outlet header 35 guides the refrigerant supplied via the first refrigerant piping 14A to a flow path within the multiple flat tubes 41, and returns the refrigerant returning to the inlet / outlet header 35 via the return header 37 to the first refrigerant piping 14A.

[0118] (Header configuration for wrapping) The turn-back header 37 is disposed to face the entrance / exit header 35 in the X direction. The turn-back header 37 is a tubular member extending in the Z direction, and has a closed upper end and lower end. The turn-back header 37 is connected to the other ends of the multiple flat tubes 41 (ends disposed on the other side in the X direction). The return header 37 returns the refrigerant to the inlet / outlet header 35 via a plurality of flat tubes 41 .

[0119] (Flat tube configuration) The flat tube 41 will be described with reference to Figures 22 to 24. In Figure 24, the same components as those in the structure shown in Figures 22 and 23 are denoted by the same reference numerals.

[0120] The flat tube 41 further has a first end 41D arranged on one side of the flat tube 41 in the width direction (Y direction), a second end 41E arranged on the other side of the flat tube 41 in the width direction (Y direction), and an outer circumferential surface 41b. The outer shape of the first and second ends 41D, 41E is circular or elliptical.

[0121] The flat tubes 41 are supported by the fins 206 with spaces between them in the Z direction. One end of each of the flat tubes 41 arranged in the X direction is connected to the entrance / exit header 35. The other end of each of the flat tubes 41 arranged in the X direction is connected to the turn-back header 37.

[0122] (Overall fin configuration) The fins 206 will be described with reference to Figures 22, 23, and 25 to 27. In Figures 5 to 7, the same components as those in the structure shown in Figures 22 and 23 are denoted by the same reference numerals.

[0123] The multiple fins 206 are arranged at a predetermined pitch in the X direction. The fin 206 has a fin body 207, multiple flat tube insertion portions 209, multiple concave-convex portions 211, a communication portion 213, and multiple fin pitch determining portions 215.

[0124] (Fin body configuration) The fin body 207 is plate-shaped and extends in the Z direction. The fin body 207 has first and second surfaces 207a, 207b arranged in the X direction, and a second flat surface portion 207A. The first surface 207a is disposed so as to face the entrance / exit header 35. The second surface 207b is disposed on the opposite side of the first surface 207a. The second surface 207b is disposed so as to face the turn-back header 37.

[0125] (Configuration of the second planar portion) The second flat surface portion 207A is a portion of the fin body 207 arranged between adjacent flat tube insertion portions 209 in the Z direction, excluding the concave-convex portions 211 and the fin pitch determining portion 215. Of the first and second surfaces 207a and 207b, the first and second surfaces 207a and 207b constituting the second flat surface portion 207A are surfaces that are perpendicular to the X direction and parallel to the Y and Z directions. Of the second flat surface portion 207A, a portion disposed on one side in the Y direction constitutes one end portion 206A of the fin 206.

[0126] (Configuration of flat tube insertion section) A plurality of flat tube insertion portions 209 are formed in the fin body 207. The plurality of flat tube insertion portions 209 are arranged at intervals in the Z direction. The flat tube insertion portions 209 extend from one side to the other side in the Y direction. The flat tube insertion portion 209 has a leading end portion 209A arranged on the other side in the Y direction and a trailing end portion 209B arranged on one side in the Y direction. The front end 209A is closed and regulates the position of the second end 41E of the flat tube 41. The rear end 209B is open from the viewpoint of inserting the flat tube 41.

[0127] The rear end side of the flat tube insertion portion 209 is opened so that the flat tube 41 can be inserted into the flat tube insertion portion 209. The flat tube insertion portion 209 accommodates the flat tube 41 inserted from the first end portion 41D side. The shape of tip portion 209A is such that the outer circumferential surface of second end portion 41E and fin body 207 defining tip portion 209A are in surface contact with each other. That is, when second end portion 41E is circular, tip portion 209A is in circular shape in surface contact with second end portion 41E, and when second end portion 41E is elliptical, tip portion 209A is in elliptical shape in surface contact with second end portion 41E. With this configuration, it is possible to increase the contact area between the flat tubes 41 and the fin body 207, thereby improving the thermal conductivity between the flat tubes 41 and the fins 206.

[0128] (Configuration of uneven parts) The uneven portion 211 is formed in the fin body 207 located between adjacent flat tube insertion portions 209 in the Z direction. The uneven portion 211 is surrounded by a second flat portion 207A. The uneven portion 211 is formed by alternating peaks and valleys that protrude in a direction away from the first surface 207a of the second flat portion 207A. The uneven portion 211 is disposed at intervals in the Z direction. By having the uneven portion 211 configured in this manner, it is possible to increase the area of ​​the fin body 207 while improving the heat transfer coefficient on the air side, thereby increasing the efficiency of heat exchange between the air and the fin body 207.

[0129] (Configuration of communication part) The communication portion 213 is a portion of the fin body 207 that is arranged on the other side in the Y direction from the multiple flat tube insertion portions 209, and extends continuously in the Z direction. The communication portion 213 has a first flat portion 207B and a condensed water guide portion 217.

[0130] (Configuration of the first planar portion) The first flat portions 207B are disposed on both sides of the condensed water guide portion 217 so as to sandwich the condensed water guide portion 217 from the Y direction. Of the first and second surfaces 207a and 207b, the surface that constitutes the first flat surface portion 207B is a surface that is perpendicular to the X direction and parallel to the Y and Z directions. The portion of the first flat surface portion 207B that is disposed on the other side in the Y direction constitutes the other end portion 206B of the fin 206. Of the second surface 207b, a surface that constitutes one end 206A of the fin 206 and a surface of the second surface 207b that constitutes the other end 206B are disposed on the same plane.

[0131] (Configuration of condensed water guide section) The condensed water guide portion 217 protrudes toward the first surface 207a of the first flat portion 207B in a state in which the condensed water guide portion 217 is bent in a direction intersecting with the first surface 207a of the first flat portion 207B. The condensed water guide portion 217 extends continuously in the Z direction. The condensed water guide portion 217 is a protrusion 218 whose cross-sectional shape when cut along a plane perpendicular to the Z direction is V-shaped and whose cross-sectional shape is uniform in the Z direction. The first surface 207a constituting the convex portion 218 protrudes in a V-shape from the second surface 207b of the first flat portion 207B toward the first surface 207a. The second surface 207b constituting the convex portion 218 is a surface recessed in a V-shape in a direction from the second surface 207b of the first flat surface portion 207B toward the first surface 207a.

[0132] (Configuration of fin pitch determining portion) The fin pitch determining portion 215 is formed between the rear end portions of the adjacent flat tube insertion portions 209 in the Z direction. The fin pitch determining portion 215 is disposed on one side of the concave-convex portion 211 in the Y direction.

[0133] The fin pitch determining portion 215 is formed by bending a part of the fin body 207 downward (to one side in the Z direction). The fin pitch determining portion 215 is formed so as to protrude towards the first surface 207a. The fin pitch determining portion 215 maintains the pitch (fin pitch) of the fins 206 arranged in the X direction at a desired value by being in contact with the second surfaces 207b of the fins 206 arranged on one side in the X direction. The shape of the fin pitch determining portion 215 can be, for example, an L-shape.

[0134] (Cutting process performed when manufacturing multiple fins) Now, with reference to Figures 28 to 30, a cutting step performed when manufacturing the multiple fins 206 will be described. In Figures 28 to 30, the same components as those in the structure shown in Figure 23 are denoted by the same reference numerals. In Figures 28 and 30, Cp indicates the position (hereinafter referred to as "cutting position Cp") at which the structure shown in Figure 28 is cut in the cutting step.

[0135] The fin 206 configured as described above is manufactured by pressing a single sheet of plate material, cutting the structure 220 (see FIG. 28 ) in which multiple fins 206 are connected in the left-right direction at cutting position Cp, and dividing the multiple fins 206 into individual pieces.

[0136] (The effect of having the second surfaces at both ends of the fins on the same plane) As described above, of second surface 207b, the surface that constitutes one end 206A of fin 206 and the surface that constitutes the other end 206B are disposed on the same plane. With this configuration, it becomes possible to bring the second surface 207b corresponding to the cutting position Cp into contact with the upper surface of the stage of the cutting device in a cutting process of the structure 220, which is performed after the plate material (the base material of the plurality of fins 206) is pressed to manufacture the structure 220 in which the plurality of fins 206 are connected. This makes it possible to place the structure 220 on the stage in a stable state, so that the structure 220 can be cut with high precision.

[0137] In Figure 28, an example of a structure serving as the base material for multiple fins 206 has been described in which multiple fins 206 are connected so that the tip ends 209A of the flat tube insertion sections 209 constituting adjacent fins 206 face the same direction. However, for example, as shown in Figure 30, a structure 225 may be used in which the rear ends 209B of the flat tube insertion sections 209 constituting a pair of adjacent fins 206 are arranged to face each other.

[0138] The heat exchanger 205 configured as described above is used as a condenser during cooling operation, dissipating heat to the outside, and is used as an evaporator during heating operation, absorbing heat from the outside.

[0139] (Heat exchanger effect) According to the first embodiment of the heat exchanger 205, the condensed water guide portion 217 formed in the communicating portion 213 is configured as a convex portion 218 protruding from the first surface 207a constituting the first planar portion 207B, so that the condensed water can be guided in a direction from the upper side to the lower side along the first and second surfaces 207a, 207b constituting the convex portion 218 while suppressing obstruction of the flow of the condensed water. Furthermore, by providing the convex portion 218 having the above-described configuration, it is possible to improve the strength of the communication portion 213. This makes it possible to prevent the fin 206 from breaking in a portion facing the flat tube insertion portion 209 in the Y direction (a portion of the fin 206 where the strength is weak). Furthermore, by providing the convex portion 218 having the above-described configuration, it is possible to improve the heat transfer coefficient on the air side while increasing the surface area of ​​the condensed water guide portion 217. This makes it possible to increase the efficiency of heat exchange between the condensed water guide portion 217 and the air.

[0140] (Effect of the first heat exchanger unit) By providing the heat exchanger 205 having excellent drainage properties for condensed water, the first heat exchanger unit 201 can be operated stably.

[0141] (Effect of refrigeration cycle device) By providing the above-described first and second heat exchanger units 201, 203, the performance of the refrigeration cycle apparatus 200 can be improved and the refrigeration cycle apparatus 200 can be operated stably.

[0142] Sixth embodiment A heat exchanger 230 according to a sixth embodiment will be described with reference to Fig. 31 and Fig. 32. In Fig. 31, the same components as those in the structure shown in Fig. 23 are denoted by the same reference numerals. In Fig. 31 and Fig. 32, the same components are denoted by the same reference numerals.

[0143] (Overall structure of heat exchanger) The heat exchanger 230 is configured similarly to the heat exchanger 205, except that the heat exchanger 230 has a plurality of fins 231 instead of the plurality of fins 206 constituting the heat exchanger 205 of the fifth embodiment.

[0144] The fin 231 has the same configuration as the fin 206 , except that the fin 231 has a communication portion 233 instead of the communication portion 213 constituting the fin 206 . The communication portion 233 has a similar structure to the communication portion 213 , except that the communication portion 233 has a condensed water guide portion 235 instead of the condensed water guide portion 217 (protrusion 218 ) formed in the communication portion 213 .

[0145] (Configuration of condensed water guide section) The condensed water guide portion 235 is configured with an uneven portion 236 that protrudes from the first surface 207a constituting the first planar portion 207B and has convex portions 238 (two as an example in Figures 31 and 32) arranged in the left-right direction, and concave portions 239 (one as an example in Figures 31 and 32) arranged between adjacent convex portions 238 in the Y direction.

[0146] The uneven portion 236 is bent in a direction intersecting with the first flat portion 207B, extends continuously in the Z direction, and has a cross-sectional shape (W-shape in the case of Figure 32) that is uniform in the Z direction when cut by a plane perpendicular to the Z direction.

[0147] (Heat exchanger effect) By using the uneven portion 236 configured as described above as the condensed water guide portion 235, it is possible to guide the condensed water in a direction from the upper side to the lower side along the first and second surfaces 207a, 207b that constitute the uneven portion 236, while suppressing obstruction of the flow of the condensed water. Furthermore, by using the uneven portion 236 as the condensate guide portion 235, it is possible to improve the strength of the communicating portion 233, thereby preventing fin breakage from occurring in the portion of the fin 231 facing the flat tube insertion portion 209 in the left-right direction (Y direction) (the portion of the fin 231 where the strength is weak). Furthermore, by configuring the condensed water guide portion 235 with the uneven portion 236, it is possible to increase the surface area of ​​the condensed water guide portion 235 and improve the heat transfer coefficient on the air side, compared to the case where the condensed water guide portion 217 is configured with one protrusion 218. This makes it possible to increase the efficiency of heat exchange between the condensed water guide portion 235 and the air.

[0148] <Seventh embodiment> A heat exchanger 240 according to a seventh embodiment will be described with reference to Fig. 33 and Fig. 34. In Fig. 33, the same components as those in the structure shown in Fig. 23 are denoted by the same reference numerals. In Fig. 33 and Fig. 34, the same components are denoted by the same reference numerals.

[0149] (Overall structure of heat exchanger) The heat exchanger 240 is configured similarly to the heat exchanger 205 of the fifth embodiment, except that the heat exchanger 240 has a plurality of fins 241 instead of the plurality of fins 206 constituting the heat exchanger 205 of the fifth embodiment.

[0150] The fin 241 has the same configuration as the fin 206 , except that the fin 241 has a communication portion 243 instead of the communication portion 213 constituting the fin 206 .

[0151] (Configuration of communication part) The communication portion 243 has a condensed water guide portion 245 that extends continuously in the Z direction. The condensed water guide portion 245 is a step portion 246, and has a first portion 243A and a second portion 243B that configure the first flat surface portion 207B, a connection portion 248, and the condensed water guide portion 245.

[0152] The first portion 243A is a portion of the first flat surface portion 207B that is disposed on one end portion 206A side of the fin body 207, and extends continuously in the Z direction.

[0153] The second portion 243B constitutes the other end 206B of the fin 206 of the first flat surface portion 207B, and extends continuously in the Z direction. The second portion 243B is disposed at a position offset from the position where the first portion 243A is formed to the other side in the X direction. The first and second surfaces 207a, 207b constituting the second portion 243B are parallel to the first and second surfaces 207a, 207b constituting the first portion 243A.

[0154] The connection portion 248 is disposed between the first portion 243A and the second portion 243B, and extends continuously in the Z direction. One end of the connection portion 248 is connected to the first portion 243A, and the other end of the connection portion 248 is connected to the second portion 243B. The first and second surfaces 207a, 207b constituting the connection portion 248 are inclined with respect to the first and second surfaces 207a, 207b constituting the first and second portions 243A, 243B. The condensed water guide portion 245 (step portion 246) is configured so that a step is formed in the X direction.

[0155] (Heat exchanger effect) By using the step portion 246 configured in this manner as a condensed water guide portion 245, it is possible to suppress obstruction of the flow of condensed water and to guide the condensed water in a direction from the upper side to the lower side along the first and second surfaces 207a, 207b that constitute the connection portion 248. Furthermore, by configuring the condensate guide portion 245 with the step portion 246, it is possible to improve the strength of the communicating portion 243, thereby preventing fin breakage from occurring in the portion of the fin 241 facing the flat tube insertion portion 209 in the Y direction (the portion of the fin 241 where the strength is weak). Furthermore, by configuring the condensed water guide portion 245 with the step portion 246, it is possible to improve the heat transfer coefficient on the air side while increasing the surface area of ​​the condensed water guide portion 245. This makes it possible to increase the efficiency of heat exchange between the condensed water guide portion 245 and the air.

[0156] <Eighth embodiment> A heat exchanger 250 according to an eighth embodiment will be described with reference to Fig. 35 to Fig. 37. In Fig. 35, the same components as those in the structure shown in Fig. 23 are denoted by the same reference numerals. In Fig. 35 to Fig. 37, the same components are denoted by the same reference numerals.

[0157] (Overall structure of heat exchanger) The heat exchanger 250 has the same configuration as the heat exchanger 205 of the fifth embodiment, except that the heat exchanger 250 has a plurality of fins 251 instead of the plurality of fins 206 constituting the heat exchanger 205 of the fifth embodiment.

[0158] (Fin configuration) The fin 251 is configured in the same manner as the fin 206 described above, except that a base portion 252 is provided around the flat tube insertion portion 209 and protrudes toward the first surface 207a of the first flat portion 207B, and a height H1 of a tip 218A of the convex portion 218 (condensed water guide portion 217) in the X direction based on the first surface 207a of the first flat portion 207B is made equal to a height H2 of the base portion 252 in the X direction based on the first surface 207a of the first flat portion 207B, and the convex portion 218 and the base portion 252 are connected at the position of the tip 218A of the convex portion 218.

[0159] (Heat exchanger effect) In this way, by making height H1 of convex portion 218 and height H2 of pedestal portion 252 in the X direction equal, and connecting convex portion 218 and pedestal portion 252 at the position of tip 218A of convex portion 218, first flat portion 207B is not disposed between pedestal portion 252 and convex portion 218 in the Y direction. This makes it possible to make first flat portion 207B discontinuous in the Z direction between pedestal portion 252 and convex portion 218, and therefore it is possible to suppress the occurrence of fin breakage between pedestal portion 252 and convex portion 218.

[0160] In the eighth embodiment, an example has been described in which the convex portion 218 (condensed water guide portion 217) and the base portion 252 are connected, but for example, the convex portion 238 constituting the uneven portion 236 may be connected to the base portion 252.

[0161] <First Modification of Eighth Embodiment> A heat exchanger 260 according to a first modified example of the eighth embodiment will be described with reference to Fig. 38. In Fig. 38, the same components as those in the structure shown in Fig. 35 are denoted by the same reference numerals.

[0162] (Overall structure of heat exchanger) The heat exchanger 260 is configured similarly to the heat exchanger 250, except that the heat exchanger 260 has fins 261 instead of the fins 251 constituting the heat exchanger 250 of the eighth embodiment.

[0163] (Fin configuration) The fin 261 has a similar structure to the fin 251 , except that the fin 261 has a base portion 263 instead of the base portion 252 constituting the fin 251 .

[0164] (Configuration of the base) Pedestal portion 263 is configured similarly to pedestal portion 252 , except that the upper side of the portion connected to protrusion 218 is inclined obliquely downward from pedestal portion 263 toward protrusion 218 .

[0165] (Heat exchanger effect) By having the base portion 263 configured in this manner, it is possible to prevent condensed water from accumulating on the upper side of the part where the base portion 263 and the protrusion 218 are connected, and therefore it is possible to prevent the base portion 263 from obstructing the flow of condensed water.

[0166] <Second Modification of Eighth Embodiment> A heat exchanger 270 according to a second modified example of the eighth embodiment will be described with reference to Fig. 39. In Fig. 39, the same components as those in the structure shown in Fig. 38 are denoted by the same reference numerals.

[0167] (Overall structure of heat exchanger) The heat exchanger 270 is configured similarly to the heat exchanger 260, except that the heat exchanger 270 has fins 271 instead of the fins 261 constituting the heat exchanger 260 according to the first modified example of the eighth embodiment.

[0168] (Fin configuration) The fin 271 has a similar structure to the fin 261 , except that the fin 271 has a base portion 273 instead of the base portion 263 constituting the fin 261 .

[0169] (Configuration of the base) Pedestal portion 273 is configured similarly to pedestal portion 263 , except that the upper and lower sides of the portion connected to protrusion 218 are inclined obliquely downward from pedestal portion 273 toward protrusion 218 .

[0170] (Heat exchanger effect) By having base portion 273 configured in this manner, it is possible to prevent condensed water from accumulating not only on the upper side of the part where base portion 273 and convex portion 218 are connected, but also on the lower part of the back side of base portion 273 (the back side of the paper in Figure 39), thereby enhancing the effect of preventing base portion 273 from obstructing the flow of condensed water.

[0171] <Ninth embodiment> A refrigeration cycle apparatus 280 according to a ninth embodiment will be described with reference to Fig. 40. In Fig. 40, solid arrows indicate the direction in which the refrigerant flows during heating operation, and dotted arrows indicate the direction in which the refrigerant flows during cooling operation. In Fig. 40, the same components as those in the structure shown in Fig. 21 are denoted by the same reference numerals.

[0172] (Overall configuration of the refrigeration cycle device) The refrigeration cycle apparatus 280 is configured similarly to the refrigeration cycle apparatus 200, except that it has first and second heat exchanger units 281, 283 instead of the first and second heat exchanger units 201, 203 constituting the refrigeration cycle apparatus 200 of the second embodiment. The first heat exchanger unit 281 is configured similarly to the first heat exchanger unit 201, except that it has a heat exchanger 285 instead of the heat exchanger 205. The second heat exchanger unit 283 has the same configuration as the second heat exchanger unit 203 , except that the second heat exchanger unit 283 has a heat exchanger 285 instead of the heat exchanger 205 .

[0173] (Overall structure of heat exchanger) The heat exchanger 285 will be described with reference to Fig. 40 to Fig. 42. In Fig. 41 and Fig. 42, the Z direction indicates a first direction. In Fig. 41, the X direction indicates an extension direction of the flat tubes 41 perpendicular to the Z direction. In Fig. 42, the Y direction indicates a second direction perpendicular to the X direction and the Z direction (the width direction of the flat tubes 41 when the flat tubes 41 are attached to the fins 290), and P indicates the direction in which air flows (hereinafter referred to as "direction P"). In the present embodiment, the following description will be given taking, as an example of the Z direction, a case in which the Z direction is the up-down direction (vertical direction).

[0174] The heat exchanger 285 has the same configuration as the heat exchanger 205, except that the heat exchanger 285 has a plurality of fins 290 instead of the plurality of fins 206 constituting the heat exchanger 205 described in the second embodiment.

[0175] (Overall fin configuration) The fins 290 will be described with reference to Figures 41 to 46. In Figures 43 to 46, the same components as those in the structure shown in Figures 41 and 42 are denoted by the same reference numerals.

[0176] The multiple fins 290 are arranged at a predetermined pitch in the X direction. Fin 290 is configured similarly to fin 206, except that it has a fin body 291 instead of fin body 207 constituting fin 206 described in the fifth embodiment, and further has a plurality of heat conduction portions 305, a plurality of first fin pitch determining portions 307, and a plurality of second fin pitch determining portions 308.

[0177] (Fin body configuration) The fin body 291 is plate-shaped and extends in the Z direction. The fin body 291 has first and second surfaces 291a, 291b disposed in the X direction. The first surface 291a is disposed to face the entrance / exit header 35. The second surface 291b is disposed on the opposite side of the first surface 291a. The second surface 291b is disposed to face the turn-back header 37. The fin body 291 is plate-shaped and has a communication portion 303 extending in the Z direction.

[0178] (Structure of heat conduction part) The heat conductive portion 305 is formed around the flat tube insertion portion 209 so as to rise toward the first surface 291a. The heat conductive portion 305 protrudes in the X direction. When the flat tube 41 is inserted into the flat tube insertion portion 209, the inner peripheral surface 305a of the heat conductive portion 305 is in surface contact with the outer peripheral surface 41b of the flat tube 41. The height of the heat conductive portion 305 in the X direction is set to a height that does not contact the fins 290 arranged on the first surface 291a side when multiple fins 290 are arranged in the X direction.

[0179] (Effect of heat conduction part) By having the heat conductive portion 305 configured in this manner, it is possible to increase the contact area between the flat tube 41 and the plurality of fins 290. This makes it possible to improve the thermal conductivity between the flat tube 41 and the plurality of fins 290. Furthermore, by setting the height of the heat conductive portion 305 in the X direction to a height at which the heat conductive portion 305 does not come into contact with the fins 290 arranged on the first surface 291a side, the fin pitch can be determined using the first and second fin pitch determining portions 307, 308, and the thermal conductivity between the flat tubes 41 and the fins 290 can be improved.

[0180] (Configuration of the first fin pitch defining portion) The first fin pitch determining portion 307 is formed in the Z direction between the rear end portions of the adjacent flat tube insertion portions 209. The first fin pitch determining portion 307 is disposed on one side of the concave-convex portion 211 in the Y direction.

[0181] The first fin pitch determining portion 307 is formed by bending a part of the fin body 291 downward (to one side in the Z direction). The first fin pitch determining portion 307 is formed so as to protrude toward the first surface 291a. The first fin pitch determining portion 307 maintains the pitch (fin pitch) of the fins 290 arranged in the X direction at a desired value by being in contact with the second surfaces 291b of the fins 290 arranged on one side in the X direction. The first fin pitch determining portion 307 is preferably, for example, L-shaped.

[0182] (Effect of forming the first fin pitch defining portion on the rear end side of the flat tube insertion portion) In this way, by forming the first fin pitch determining portion 307 on the rear end side of adjacent flat tube insertion portions 209, deformation and buckling of the fins 290 that are likely to occur in the initial stages of inserting the flat tube 41 into the flat tube insertion portion 209 can be suppressed.

[0183] (Effect of making the first fin pitch defining portion L-shaped) In this way, by making the first fin pitch determining portion 307 L-shaped, the probability that the first fin pitch determining portion 307 will come into contact with the second surface 291b can be increased compared to, for example, when the first fin pitch determining portion 307 is I-shaped. Furthermore, by making the first fin pitch determining portion 307 L-shaped, it is possible to increase the contact area between the first fin pitch determining portion 307 and the second surface 291b, so that the fin pitch can be stably maintained.

[0184] (Configuration of the second fin pitch defining portion) The second fin pitch specifying portion 308 is arranged around the flat tube insertion portion 209 located above the first fin pitch specifying portion 307, of the two flat tube insertion portions 209 that sandwich the first fin pitch specifying portion 307 in the Z direction. Specifically, the second fin pitch determining portion 308 is positioned below the flat tube insertion portion 209 and near the tip portion 209A (closer to the rear end portion of the flat tube insertion portion 209 than the tip portion 209A and toward the tip portion 209A). The second fin pitch defining portion 308 is formed by bending a part of the fin body 291 downward (to one side in the Z direction) to protrude towards the first surface 291a.

[0185] The second fin pitch specifying portion 308 abuts against the second surface 291b of the fin 290 arranged on the other side in the X direction, and together with the first fin pitch specifying portion 307 described above, keeps the pitch (fin pitch) of the fins 290 arranged in the X direction at a desired value. The protruding amounts of the first and second fin pitch defining portions 307, 308 in the X direction are equal to each other, and are set to a size that allows the fin pitch to be maintained at a desired value. It is preferable that the second fin pitch determining portion 308 is, for example, L-shaped. By forming the second fin pitch determining portion 308 in an L-shape, it is possible to obtain the same effect as that of the first fin pitch determining portion 307, which is L-shaped as described above.

[0186] The heat exchanger 285 configured as described above is used as a condenser during cooling operation, dissipating heat to the outside, and is used as an evaporator during heating operation, absorbing heat from the outside.

[0187] (Heat exchanger effect) As described above, by forming the first and second fin pitch determining portions 307, 308 by bending a portion of the fin body 291 downward, it is possible to prevent the first and second fin pitch determining portions 307, 308 from becoming a resistor for air flowing in the P direction (the direction from the other side to one side of the second direction) compared to the case where a portion of the fin body 291 is bent in the Y direction, and therefore it is possible to suppress air pressure loss.

[0188] Furthermore, by arranging the first fin pitch specifying portion 307 on the rear end side of the flat tube insertion portion 209 and arranging the second fin pitch specifying portion 308 on the tip portion 209A side of the flat tube insertion portion 209, it becomes possible to arrange the first and second fin pitch specifying portions 307, 308 at positions separated in the Z direction and the Y direction. This makes it possible to stably specify the fin pitch of the multiple fins 290 arranged in the X direction.

[0189] Furthermore, by making the outer shape of the second end 41E of the flat tube 41 circular or elliptical, and by making the shape of the tip 209A of the flat tube insertion part 209 that accommodates the second end 41E such that the outer circumferential surface 41b of the second end 41E of the flat tube 41 comes into surface contact with the fin body 291, it is possible to increase the contact area between the flat tube 41 and the fin body 291. This makes it possible to improve the thermal conductivity between the flat tube 41 and the fin 290.

[0190] That is, the fin pitch can be stably defined while suppressing air pressure loss, and the thermal conductivity between the flat tubes 41 and the fins 290 can be improved. Furthermore, by not forming the first and second fin pitch specifying portions 307, 308 in the communicating portion 303 extending in the first direction (Z direction), the first and second fin pitch specifying portions 307, 308 do not obstruct the flow of condensed water drained in the first direction (Z direction), thereby maintaining good drainage performance.

[0191] Furthermore, a first fin pitch specifying portion 307 is formed by bending a portion of the fin body 291 downward, and a second fin pitch specifying portion 308 is formed around the flat tube insertion portion 209 located above the first fin pitch specifying portion 307, of the two flat tube insertion portions 209 that sandwich the first fin pitch specifying portion 307 in the Z direction.This makes it possible to arrange the positions that specify the fin pitch at equal intervals in the Z direction, thereby enabling the fin pitch to be stably specified.

[0192] (Effect of the first heat exchanger unit) According to the first heat exchanger unit 281, by being provided with the above-mentioned heat exchanger 285, it is possible to improve the performance of the first heat exchanger unit 281 and to operate the first heat exchanger unit 281 stably. The second heat exchanger unit 283 including the heat exchanger 285 can also provide the same effects as the first heat exchanger unit 281 .

[0193] (Effect of refrigeration cycle device) By providing the refrigeration cycle apparatus 280 with the above-described first and second heat exchanger units 281, 283, the performance of the refrigeration cycle apparatus 280 can be improved and the refrigeration cycle apparatus 280 can be operated stably.

[0194] (Modified Fin Configuration) A fin 320 according to a modification of the ninth embodiment will be described with reference to Fig. 47. In Fig. 47, the same components as those in the structure shown in Fig. 42 are denoted by the same reference numerals.

[0195] Fin 320 is configured in the same manner as fin 290 described above, except that a first fin pitch specifying portion 307 is formed by bending a part of the fin body 291 upward, and a second fin pitch specifying portion 308 is formed around the flat tube insertion portion 209 located below the first fin pitch specifying portion 307, of the two flat tube insertion portions 209 that sandwich the first fin pitch specifying portion 307 in the Z direction.

[0196] (Effect of modified fins) In this way, by bending a part of the fin body 291 upward to form the first fin pitch specifying portion 307, and by forming the second fin pitch specifying portion 308 around the flat tube insertion portion 209 located below the first fin pitch specifying portion 307, of the two flat tube insertion portions 209 that sandwich the first fin pitch specifying portion 307 in the Z direction, it becomes possible to arrange the positions that specify the fin pitch at equal intervals in the Z direction. This makes it possible to stably specify the fin pitch.

[0197] Although preferred embodiments of the present disclosure have been described in detail above, the present disclosure is not limited to such specific embodiments, and various modifications and variations are possible within the scope of the gist of the present disclosure described in the claims.

[0198] <Additional Notes> The heat exchangers 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190, 205, 230, 240, 250, 260, 270, 285, heat exchanger units (first heat exchanger units 18, 201, 281 and second heat exchanger units 23, 203, 283), and refrigeration cycle devices 10, 200, 280 described in each embodiment can be understood, for example, as follows.

[0199] (1) A heat exchanger 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190 according to a first aspect is a heat exchanger 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190 that exchanges heat between air and a refrigerant, and has a flat outer shape and extends in one direction (X direction) and a width direction. The refrigerant refrigerant passage includes a plurality of flat tubes 41 arranged in the one direction (Y direction), extending in the one direction (X direction), and having a plurality of flow paths 41A through which the refrigerant flows, a plurality of fins 42 arranged in the extension direction (X direction) of the flat tubes 41 while accommodating the plurality of flat tubes 41, and a header 43 connected to the plurality of flat tubes 41 so that one end 41B of the plurality of flat tubes 41 is arranged on the inside, and through which the refrigerant flows on the inside. The header 43 has a cylindrical shape extending in the vertical direction (Z direction) and a header body 45 that partitions a columnar internal space 53, a partition plate 47 that is housed in the header body 45 and extends in the vertical direction (Z direction), and divides the internal space 53 in the extension direction (X direction) into a first space 54 and a second space 55 in which one end 41B of the multiple flat tubes 41 is arranged, with the refrigerant being able to flow at the upper and lower ends of the internal space 53, and nozzle portions 49, 62 that are arranged at the lower part of the first space 54 and include outlets 49A, 62A that blow out the refrigerant supplied from outside the header 43 toward a bottom surface 45a (first bottom surface 45aa) of the header body 45, and a refrigerant flow portion 54A that is a part of the first space 54 is formed on both sides of the nozzle portions 49, 62 in the width direction (Y direction).

[0200] By having the nozzle parts 49, 62 configured as described above, it is possible to reduce the difference in the state of the refrigerant in the width direction (Y direction) by causing the refrigerant blown out from the blowout ports 49A, 62A to collide with the bottom surface 45a (first bottom surface 45aa) of the header body 45. As a result, the refrigerant with a small difference in state in the width direction (Y direction) flows from the first space 54 toward the second space 55 (the space in which one end 41B of the plurality of flat tubes 41 is arranged), and therefore, without depending on the flow rate of the refrigerant introduced into the header 43, a circulating flow of the refrigerant (a flow that descends the first space 54 and ascends the second space 55) is formed in the header 43, and while suppressing the complication of the manufacturing process, it is possible to suppress the uneven distribution of the refrigerant to each flat tube 41, and also suppress the uneven distribution of the refrigerant to the plurality of flow paths 41A formed in the width direction (Y direction) of each flat tube 41.

[0201] (2) A heat exchanger 70, 80, 100, 120, 150, 180, 190 according to a second aspect is the heat exchanger 70, 80, 100, 120, 150, 180, 190 of (1), wherein the bottom surface 45a of the header body 45 has a first bottom surface 45aa that defines the first space 54 and a second bottom surface 45ab that defines the second space 55, and may be provided with a first refrigerant guide portion 73 provided on the first bottom surface 45aa and having a first guide surface 73a that guides the refrigerant in a direction from the first space 54 to the second space 55.

[0202] By providing the first refrigerant guide section 73 configured in this manner, the refrigerant blown out from the outlets 49A, 62A of the nozzle sections 49, 62 can be guided to the second space 55, and the refrigerant can be collided with the inner wall surface 45b of the header body 45 that defines the second space 55, thereby reducing the difference in the state of the refrigerant in the width direction (Y direction). Furthermore, when the refrigerant is a gas-liquid two-phase refrigerant and the flow rate of the refrigerant introduced into the header body 45 is small, it is possible to prevent the refrigerant from separating into gas and liquid in the first space 54, and to prevent the gas-phase refrigerant from rising in the first space 54. In other words, it is possible to prevent a circulating flow of the refrigerant from becoming difficult to form in the header body 45.

[0203] (3) A heat exchanger 70, 80, 100, 120, 150, 180, 190 according to a third aspect may be the heat exchanger 70, 80, 100, 120, 150, 180, 190 of (2), in which the first guide surface 73a is a concave curved surface recessed in a direction away from the lower end of the partition plate 47.

[0204] In this manner, by making the first guide surface 73a a concave curved surface that is concave in the direction away from the lower end of the partition plate 47, the refrigerant can be smoothly guided from the first space 54 to the second space 55.

[0205] (4) A heat exchanger 90, 100, 180, 190 according to a fourth aspect is a heat exchanger 90, 100, 180, 190 according to any one of (1) to (3), wherein the bottom surface 45a of the header body 45 has a first bottom surface 45aa that defines the first space 54 and a second bottom surface 45ab that defines the second space 55, and may be provided with a second refrigerant guide portion 93 having a second guide surface 93a provided on the second bottom surface 45ab that guides the refrigerant in a direction from the bottom to the top of the second space 55.

[0206] By providing the second refrigerant guide portion 93 configured in this manner, the refrigerant that is generated by colliding with the first bottom surface 45aa of the header body 45 and has little difference in state in the width direction can be guided in a direction from the bottom to the top of the second space 55.

[0207] (5) A heat exchanger 90, 100, 180, 190 according to a fifth aspect is the heat exchanger 90, 100, 180, 190 according to (4), wherein the second guide surface 93a may be a concave curved surface that is concave in a direction away from the lower end of the partition plate 47.

[0208] In this way, by making the second guide surface 93a a concave curved surface recessed in a direction away from the lower end of the partition plate 47, refrigerant with little difference in state in the width direction (Y direction) can be easily guided in a direction from the bottom to the top of the second space 55.

[0209] (6) A heat exchanger 80 according to a sixth aspect is a heat exchanger 80 as described in any one of (1) to (5), and may be provided with a third refrigerant guide portion 83, the third refrigerant guide portion 83 being provided at a portion of the lower end of the partition plate 47, away from the bottom surface 45a of the header body 45 and including a third guide surface 83a that guides the refrigerant in a direction from the first space 54 to the second space 55.

[0210] By providing the third refrigerant guiding portion 83 configured in this manner, the refrigerant can be guided in the direction from the first space 54 to the second space 55 by the third guiding surface 83a.

[0211] (7) A heat exchanger 80 according to a seventh aspect is the heat exchanger 80 of (6), wherein the third refrigerant guide portion 83 may be a cylindrical member extending in the width direction (Y direction) of the partition plate 47.

[0212] In this way, by using a cylindrical member extending in the width direction of the partition plate 47 as the third refrigerant guide section 83, the refrigerant can be guided in the direction from the first space 54 to the second space 55 by the third guide surface 83a (the outer peripheral surface of the cylindrical member).

[0213] (8) The heat exchanger 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190 of the eighth aspect is a heat exchanger 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190 described in any one of (1) to (7), wherein the nozzle portion 49, 62 may be positioned at a position lower than 1 / 2 the height of the header body.

[0214] For example, if the nozzle portions 49, 62 are positioned at a position higher than 1 / 2 the height H of the header body 45, the distance from the outlets 49A, 62A of the nozzle portions 49, 62 to the bottom surface (first bottom surface 45aa) of the header body 45 becomes too long, so that the flow of refrigerant blown out from the outlets 49A, 62A is attenuated, which may make it difficult to form a circulating flow of refrigerant within the header 43. Therefore, by positioning the nozzle portions 49, 62 at a position lower than 1 / 2 of the height H of the header body 45, it is possible to shorten the distance from the outlets 49A, 62A to the bottom surface (first bottom surface 45aa) of the header body 45, making it easier to form a circulating flow of refrigerant within the header 43.

[0215] (9) The heat exchanger 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190 of the ninth aspect is a heat exchanger 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190 described in any one of (1) to (7), wherein the nozzle portion 49, 62 may be arranged between the flat tube 41F located at the bottom and the flat tube 41S located second from the bottom among the plurality of flat tubes 41.

[0216] In this way, by arranging the nozzle portions 49, 62 between the lowest flat tube 41F and the second lowest flat tube 41S, a circulating flow of refrigerant within the header 43 can be easily formed. Furthermore, when the heat exchangers 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, and 190 are used as condensers, the refrigerant (liquid-phase refrigerant) flowing into the header 43 can be easily discharged to the outside of the header via the multiple flat tubes 41.

[0217] (10) A heat exchanger 110, 120, 130, 190 according to a tenth aspect is a heat exchanger 110, 120, 130, 190 described in any one of (1) to (9), wherein in the direction in which the flat tubes 41 extend, one end of the plurality of flat tubes 41 is arranged to face the partition plate 47, and a distance Ds1 from one end of the flat tube 41F arranged at the bottom among the plurality of flat tubes 41 to the partition plate 47 may be longer than a distance Ds2 from one end of the other flat tubes 41, 41 to the partition plate 47.

[0218] In this way, by making the distance Ds1 from one end 41Fa of the flat tube 41F arranged at the bottom among the plurality of flat tubes 41 to the partition plate 47 longer than the distance Ds2 from one end 41a of the other flat tubes 41 to the partition plate 47, it is possible to increase the refrigerant flow path cross-sectional area formed between the one end 41Fa of the flat tube 41F arranged at the bottom and the partition plate 47. This makes it possible to reduce the degree of contraction at the height position of the flat tube 41F and makes it difficult for the refrigerant flow to separate, so that the liquid phase refrigerant is easily supplied to the flat tube 41F into which the liquid phase refrigerant may not flow due to the influence of separation (contraction) in the past, and as a result, the refrigerant can be distributed evenly to each flat tube 41.

[0219] (11) The heat exchanger 110, 120 according to the eleventh aspect is the heat exchanger 110, 120 of (10), wherein one end of the lowest located flat tube 41F may be positioned recessed in a direction from the first space 54 toward the second space 55 from the position of one end of the other flat tubes 41, 41S.

[0220] In this way, by positioning one end 41Fa of the bottommost flat tube 41F at a position retreated in the direction from the first space 54 to the second space 55 from the positions of the one ends 41a of the other flat tubes 41, the cross-sectional area of ​​the refrigerant flow path formed between one end 41Fa of the bottommost flat tube 41F and the partition plate 47 can be increased.

[0221] (12) The heat exchanger 130, 190 according to the twelfth aspect is a heat exchanger 130, 190 described in any one of (10) or (11), wherein the lower end 133A of the partition plate 133 facing one end of the flat tube 41F located at the bottom may be positioned at a position shifted in a direction from the second space 55 toward the first space 54.

[0222] In this way, by positioning the lower end 133A of the partition plate 133 facing one end 41Fa of the lowest flat tube 41F among the multiple flat tubes 41, in a position shifted in the direction from the second space 55 toward the first space 54, the cross-sectional area of ​​the refrigerant flow path formed between one end 41Fa of the lowest flat tube 41F and the partition plate 133 can be increased.

[0223] (13) The heat exchanger 140, 150, 160, 170, 180, 190 according to the thirteenth aspect is the heat exchanger 140, 150, 160, 170, 180, 190 described in any one of (1) to (12), and may include a straightening member 143, 163, 173 that is provided on the inner wall surface 45b of the header body 45 that defines the second space 55 and is arranged below one end 41B of the lowest flat tube 41F among the plurality of flat tubes 41, and that straightens the refrigerant flowing from the bottom surface 45a of the header body 45 toward one end of the lowest flat tube 41F.

[0224] By providing straightening members 143, 163, 173 configured in this manner, liquid phase refrigerant can be more easily supplied to flat tubes 41F, into which liquid phase refrigerant would have been difficult to flow in the past due to separation (contraction), and as a result, refrigerant distribution to each flat tube 41 can be made more equal.

[0225] (14) The heat exchanger 140, 150 according to the fourteenth aspect is the heat exchanger 140, 150 of (13), wherein the straightening member 143 is arranged at a position away from one end 41B of the lowest-placed flat tube 41F, and may be a baffle plate 145 extending in a direction from the inner wall surface 45b of the header body 45 toward the partition plate 47, and the amount of protrusion from the inner wall surface 45b of the header body 45 may be equal to the amount of protrusion of the one end 41B.

[0226] In this way, by using the baffle plate 145 configured as described above as the straightening member 143, it is possible to separate the refrigerant flow in front of one end 41B of the lowest located flat tube 41F, and straighten the refrigerant flow at the end of the lowest located flat tube 41F. This makes it easier for liquid-phase refrigerant to be supplied to flat tubes 41F, which in the past may have been difficult for liquid-phase refrigerant to flow into due to separation (contraction), and as a result, refrigerant distribution to each flat tube 41 can be made more equal.

[0227] (15) A heat exchanger 160 according to a fifteenth aspect is the heat exchanger 160 of (13), wherein the straightening member 163 is a block 164 arranged below one end 41B of the lowest flat tube 41F so as to contact the lower surface of one end 41B, extending in a direction from the inner wall surface 45b of the header body 45 toward the partition plate 47, and having an amount of protrusion from the inner wall surface 45b of the header body 45 equal to the amount of protrusion of the one end 41B.

[0228] In this way, by using the block 164 configured as above as the straightening member 163, it is possible to separate the refrigerant flow in front of one end 41B of the lowest located flat tube 41F, and straighten the refrigerant flow at the end of the lowest located flat tube 41F. This makes it easier for liquid-phase refrigerant to be supplied to flat tubes 41F, which in the past may have been difficult for liquid-phase refrigerant to flow into due to separation (contraction), and as a result, refrigerant distribution to each flat tube 41 can be made more equal.

[0229] (16) A heat exchanger 170 according to a sixteenth aspect is the heat exchanger 170 of (15), wherein the block 174 is formed on the partition plate 47 side and may have a curved surface 174a that guides the flow of the refrigerant upward.

[0230] By having the curved surface 174a configured in this way, the coolant can be guided to the upper part of the second space 55 without the flow separating.

[0231] (17) The heat exchanger 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190 of the 17th aspect is the heat exchanger 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190 described in any one of (1) to (16), and may include a porous plate 51 provided between the header body 45 and the partition plate 47, 133 that partition the first space 54, and arranged in a portion of the first space 54 that is located above the nozzle portion 49, 62.

[0232] By providing a porous plate 51 configured in this manner, it is possible to suppress the movement of gas (gas refrigerant) flowing back from the bottom to the top of the first space 54, making it easier to form a circulating flow of refrigerant within the header 43.

[0233] (18) The heat exchanger 27 according to the 18th aspect is the heat exchanger 27 described in any one of (1) to (17), wherein the outlet 49A is a circular hole, and the partition plate 47 has one lower end portion 47A arranged on one side in the width direction (Y direction) and whose lower end reaches the bottom surface 45a of the header body 45, the other lower end portion 47B arranged on the other side in the width direction (Y direction) and whose lower end reaches the bottom surface 45a of the header body 45, and a cutout portion 47C formed between the one lower end portion 47A and the other lower end portion 47B, which allows the refrigerant to flow.

[0234] In this manner, when a circular hole is used as air outlet 49A, the refrigerant flows from first space 54 to second space 55 through cutout 47C located between one lower end 47A and the other lower end 47B. At this time, lower ends 47A and 47B can prevent the refrigerant from flowing back from second space 55 to first space 54.

[0235] (19) The heat exchanger 60 according to the 19th aspect is a heat exchanger 60 described in any one of (1) to (17), wherein the blow-out port 62A has a groove shape extending in the width direction (Y direction) of the nozzle portion 62, and the sum of the widths W2 of the two refrigerant flow sections 54A arranged on both sides of the nozzle portion 62 in the width direction (Y direction) may be smaller than the width W1 of the nozzle portion 62.

[0236] In this way, by making the air outlet 62A into a groove shape extending in the width direction (Y direction) of the nozzle portion 62, the difference in the state of the refrigerant in the width direction (Y direction) can be further reduced compared to when the air outlet is shaped like a circle. Moreover, by making the total value (=2×W2) of the widths W2 of the pair of refrigerant flow sections 54A arranged on both sides of the nozzle section 62 in the width direction (Y direction) smaller than the width W1 of the nozzle section 62, it is possible to reduce the flow path cross-sectional area of ​​the pair of refrigerant flow sections 54A. This makes it possible to suppress the occurrence of a backflow of the refrigerant from below to above in the first space 54.

[0237] (20) A heat exchanger unit (first and second heat exchanger units 18, 23) according to a twentieth aspect includes a heat exchanger described in any one of (1) to (19) and a blower (first and second blowers 26, 32) that blows air to the heat exchangers 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190.

[0238] By having the heat exchangers 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190 configured as described above, the heat exchange efficiency of the heat exchanger units (first and second heat exchanger units 18, 23) can be improved.

[0239] (21) A refrigeration cycle apparatus 10 according to a twenty-first aspect includes the heat exchanger unit (first and second heat exchanger units 18, 23) of (20).

[0240] By including the heat exchanger units (first and second heat exchanger units 18, 23) configured as described above, the heat exchange efficiency of the refrigeration cycle apparatus 10 can be improved.

[0241] (22) A heat exchanger 205, 230, 240, 250, 260, 270 according to a 22nd aspect is a heat exchanger 205, 230, 240, 250, 260, 270 that exchanges heat between air and a refrigerant, and includes a plurality of flat tubes 41 having a flat outer shape, a flow path 41A through which the refrigerant flows, a first end 41D arranged on one side in a width direction and a second end 41E arranged on the other side in the width direction, and a heat exchanger 205, 230, 240, 250, 260, 270 that exchanges heat between air and a refrigerant. The heat exchanger 205, 230, 240, 250, 260, 270 has a flat outer shape, a flow path 41A through which the refrigerant flows, and a first end 41D arranged on one side in a width direction and a second end 41E arranged on the other side in the width direction. and a plurality of fins 206, 231, 241, 251, 261, 271 arranged at a predetermined pitch in the extension direction (X direction) of the flat tube 41, the plurality of fins 206, 231, 241, 251, 261, 271 being plate-shaped, a fin body 207 including a first surface 207a arranged in the extension direction (X direction) and a second surface 207b arranged on the opposite side of the first surface 207a, and a fin body 207 formed on the fin body 207 and perpendicular to the extension direction (X direction). The flat tube insertion portion 209 includes a flat tube insertion portion 209 that is arranged at intervals in the up-down direction (Z direction) perpendicular to the up-down direction (Z direction) and the extension direction (X direction) and that accommodates the flat tube 41 inserted from the second end 41E side, and communication portions 213, 233, and 243 that are arranged on the other side of the flat tube insertion portions 209 in the left-right direction (Y direction) and extend continuously in the up-down direction (Z direction). 13, 233, 243 include a first flat surface portion 207B parallel to the vertical direction (Z direction) and the left-right direction (Y direction), and the communicating portions 213, 233, 243 are provided with condensed water guide portions 217, 235, 245 which are bent in a direction intersecting with the first flat surface portion 207B, extend continuously in the vertical direction (Z direction), and have a cross-sectional shape that is uniform in the vertical direction (Z direction) when cut by a plane perpendicular to the vertical direction (Z direction).

[0242] By having the condensed water guide portion 217, 235, 245 configured in this manner, it is possible to suppress obstruction of the flow of condensed water and to guide the condensed water in a direction from the upper side to the lower side along the first and second surfaces 207a, 207b that constitute the condensed water guide portion 217, 235, 245. Furthermore, by providing the condensed water guide portions 217, 235, 245 configured as described above, it is possible to improve the strength of the communication portions 213, 233, 243. This makes it possible to prevent fin breakage from occurring in the portions of the fins 206, 231, 241, 251, 261 that face the flat tube insertion portion 209 in the left-right direction (Y direction) (portions of the fins 206, 231, 241, 251, 261 where the strength is weak). Furthermore, by having the condensed water guide portion 217, 235, 245 configured as described above, it is possible to improve the thermal conductivity on the air side while increasing the surface area of ​​the condensed water guide portion 217, 235, 245. This makes it possible to increase the efficiency of heat exchange between the condensed water guide portion 217, 235, 245 and the air.

[0243] (23) The heat exchanger 205 according to a 23rd aspect is the heat exchanger 205 of (22), wherein the condensate guide portion 217 may be a convex portion 218 protruding from the first surface 207a constituting the first planar portion 207B.

[0244] In this way, by configuring the condensed water guide portion 217 formed in the communicating portion 213 as a convex portion 218 protruding from the first surface 207a constituting the first planar portion 207B, it is possible to suppress obstruction of the flow of the condensed water and guide the condensed water in a direction from the upper side to the lower side along the first and second surfaces 207a, 207b constituting the convex portion 218. Furthermore, by providing the convex portion 218 having the above-described configuration, it is possible to improve the strength of the communication portion 213. This makes it possible to prevent the fin 206 from breaking in a portion facing the flat tube insertion portion 209 in the Y direction (a portion of the fin 206 where the strength is weak). Furthermore, by providing the convex portion 218 having the above-described configuration, it is possible to improve the thermal conductivity on the air side while increasing the surface area of ​​the condensed water guide portion 217. This makes it possible to increase the efficiency of heat exchange between the condensed water guide portion 217 and the air.

[0245] (24) A heat exchanger 230 according to a 24th aspect is the heat exchanger 230 of (22), wherein the condensate guide portion 235 may be an uneven portion 236 protruding from the first surface 207a constituting the first planar portion 207B and having a plurality of convex portions 218 arranged in the left-right direction (Y direction) and concave portions 239 arranged between the convex portions 218 adjacent to each other in the left-right direction (Y direction).

[0246] By using the uneven portion 236 configured in this manner as a condensed water guide portion 235, it is possible to suppress obstruction of the flow of condensed water and to guide the condensed water in a direction from the upper side to the lower side along the first and second surfaces 207a, 207b that constitute the uneven portion 236. Furthermore, by using the uneven portion 236 as the condensate guide portion 235, it is possible to improve the strength of the communicating portion 233, thereby preventing fin breakage from occurring in the portion of the fin 231 facing the flat tube insertion portion 209 in the left-right direction (Y direction) (the portion of the fin 231 where the strength is weak). Furthermore, by configuring the condensed water guide portion 235 with the uneven portion 236, it is possible to increase the surface area of ​​the condensed water guide portion 235 and improve the thermal conductivity on the air side, compared to the case where the condensed water guide portion 217 is configured with one protrusion 218. This makes it possible to increase the efficiency of heat exchange between the condensed water guide portion 235 and the air.

[0247] (25) A heat exchanger 250 according to a 25th aspect is the heat exchanger 250 according to (23) or (24), wherein the flat tube insertion portion 209 is disposed on the other side of the left-right direction (Y direction) and has a tip portion 209A that accommodates the second end portion 41E, the fin body 207 is disposed between the tip portions 209A adjacent to each other in the up-down direction (Z direction) and has a second planar portion 207A that is parallel to the up-down direction (Z direction) and the left-right direction (Y direction), and A pedestal portion 252 is arranged protruding toward the first surface 207a of the second planar portion 207A, and a height H1 of a tip 218A of the convex portion 218 in the extension direction (X direction) based on the first surface 207a of the second planar portion 207A is equal to a height H2 of the pedestal portion 252 in the extension direction (X direction) based on the first surface 207a of the second planar portion 207A, and the convex portion 218 and the pedestal portion 252 may be connected at the position of the tip 218A of the convex portion 218.

[0248] In this way, by making the height H1 of the convex portion 218 in the X direction equal to the height H2 of the base portion 252 and connecting the convex portion 218 to the base portion 252 at the position of the tip 218A of the convex portion 218, the first flat portion 207B is not disposed between the base portion 252 and the convex portion 218 in the left-right direction (Y direction). This makes it possible to make the first flat portion 207B discontinuous in the up-down direction (Z direction) between the base portion 252 and the convex portion 218, so that the occurrence of fin breakage between the base portion 252 and the convex portion 218 can be suppressed.

[0249] (26) A heat exchanger 260 according to a 26th aspect is the heat exchanger 260 of (25), wherein the upper side of the portion of the base portion 263 connected to the condensate water guide portion 217 may be inclined diagonally downward from the base portion 263 toward the condensate water guide portion 217.

[0250] With this configuration, it is possible to prevent condensed water from accumulating on the upper side of the part where the base portion 263 and the condensed water guide portion 217 (convex portion 218) are connected, thereby preventing the base portion 263 from obstructing the flow of condensed water.

[0251] (27) A heat exchanger 240 according to a 27th aspect is the heat exchanger 240 of (22), wherein the first planar portion 207B has a first portion 243A arranged on one side of the left-right direction (Y direction) of the condensed water guide portion 245 and extending in the up-down direction (Z direction), and a second portion 243B arranged on the other side of the left-right direction (Y direction) of the condensed water guide portion 245, extending in the up-down direction (Z direction) and at a position different from that of the first portion 243A in the extension direction (X direction), and the condensed water guide portion 245 may be a step portion 246 constituted by the first portion 243A, the second portion 243B, and a connection portion 248 connecting the first portion 243A and the second portion 243B.

[0252] By using the step portion 246 configured in this manner as a condensed water guide portion 245, it is possible to suppress obstruction of the flow of condensed water and to guide the condensed water in a direction from the upper side to the lower side along the first and second surfaces 207a, 207b that constitute the connection portion 248. Furthermore, by configuring the condensate guide portion 245 with the step portion 246, it is possible to improve the strength of the communicating portion 243, thereby preventing fin breakage from occurring in the portion of the fin 241 facing the flat tube insertion portion 209 in the left-right direction (Y direction) (the portion of the fin 241 where the strength is weak). Furthermore, by configuring the condensed water guide portion 245 with the step portion 246, it is possible to increase the surface area of ​​the condensed water guide portion 245 and improve the thermal conductivity on the air side. This makes it possible to increase the efficiency of heat exchange between the condensed water guide portion 245 and the air.

[0253] (28) A heat exchanger 205, 230, 240, 250, 260 according to a 28th aspect is a heat exchanger 205, 230, 240, 250, 260 according to any one of (22) to (27), wherein the fins 206, 231, 241, 251, 261 have one end 206A arranged on one side in the left-right direction (Y direction) and the other end 206B arranged on the other side in the left-right direction, the condensed water guide portion 217, 235, 245 is arranged on the one end 206A side rather than the other end 206B, and the second surface 207b constituting the one end 206A and the other end 206B may be arranged on the same plane.

[0254] With this configuration, in a cutting process of the structure 220 performed after the plate material (the base material of the plurality of fins 206, 231, 241, 251, 261) is pressed to manufacture the structure 220 in which the plurality of fins 206, 231, 241, 251, 261 are connected, the second surface 207b corresponding to the cutting position Cp can be brought into contact with the upper surface of the stage of the cutting device, and the structure 220 can be placed in a stable state on the stage. This allows the structure 220 to be cut with high accuracy. That is, the processing accuracy of the fins 206, 231, 241, 251, 261 can be improved.

[0255] (29) A heat exchanger unit (first and second heat exchanger units 201, 203) according to a 29th aspect includes a heat exchanger 205, 230, 240, 250, 260 according to any one of (22) to (28) and a blower (first and second blowers 26, 32) that blows air to the heat exchangers 205, 230, 240, 250, 260.

[0256] In this way, by having the heat exchanger units (first and second heat exchanger units 201, 203) with the above-mentioned heat exchangers 205, 230, 240, 250, 260, the heat exchanger units (first and second heat exchanger units 201, 203) can be operated stably.

[0257] (30) A refrigeration cycle apparatus 200 according to a thirteenth aspect includes the heat exchanger unit (first and second heat exchanger units 201, 203) of (29).

[0258] In this manner, by including the above-described heat exchanger units (the first and second heat exchanger units 201, 203), the refrigeration cycle apparatus 200 can be operated stably.

[0259] (31) A heat exchanger 285 according to a thirty-first aspect includes a plurality of flat tubes 41 having a flat outer shape, a flow path 41A through which a refrigerant flows formed therein, and having a first end 41D arranged on one side in a width direction (Y direction) and a second end 41E arranged on the other side in the width direction, and a plurality of fins 290 arranged at a predetermined pitch in an extension direction (X direction) of the flat tubes 41 while accommodating the plurality of flat tubes 41. The plurality of fins 290 are plate-shaped, and have a first surface 291a arranged in the extension direction (X direction) and a second surface 291b arranged on the opposite side of the first surface 291a. a fin body 291 including a second surface 291b disposed on the fin body 291; flat tube insertion sections 209 formed on the fin body 291 and disposed at intervals in a first direction (Z direction) perpendicular to the extension direction (X direction), extending from one side to the other side in a second direction (Y direction) perpendicular to the first direction (Z direction) and the extension direction (X direction), and accommodating the flat tube 41 inserted from the second end 41E side; and communication sections 30A and 30B disposed on the other side of the second direction (Y direction) of the flat tube insertion sections 209 and continuously extending in the first direction (Z direction). 3, a first fin pitch defining portion 307 that is formed by bending a part of the fin body 291 located between the adjacent flat tube insertion portions 209 in the first direction (Z direction) and protruding it toward the first surface 291a and abuts against the fin 290 arranged on one side of the extension direction (X direction), and a first fin pitch defining portion 307 that is formed by bending a part of the fin body 291 in the first direction (Z direction) and protruding it toward the first surface 291a and that is located on the rear end side of the front end 209A of the flat tube insertion portion 209. and a second fin pitch defining portion 308 arranged around the fin 290 arranged on one side of the extension direction (X direction), and air that exchanges heat with the refrigerant flows in a direction from the other side to the one side of the second direction (Y direction), the outer shape of the second end 41E is circular or elliptical, the shape of the tip portion 209A of the flat tube insertion portion 209 that accommodates the second end 41E is such that the outer peripheral surface 41b of the second end 41E and the fin main body 291 are in surface contact, and the first fin pitch defining portion 307 isThe second fin pitch determining portion 308 is disposed on the rear end side of the flat tube insertion portion 209, and the second fin pitch determining portion 308 is disposed on the tip end portion 209A side of the flat tube insertion portion 209.

[0260] As described above, by forming the first and second fin pitch determining portions 307, 308 by bending a portion of the fin body 291 in a first direction (Z direction), it is possible to prevent the first and second fin pitch determining portions 307, 308 from becoming resistors for air flowing in the direction from the other side to one side of the second direction (Y direction) (B direction), compared to the case where a portion of the fin body 291 is bent in the second direction (Y direction), and therefore it is possible to suppress air pressure loss. Furthermore, by arranging the first fin pitch defining portion 307 on the rear end side of the flat tube insertion portion 209 and arranging the second fin pitch defining portion 308 on the tip portion 209A side of the flat tube insertion portion 209, it is possible to arrange the first and second fin pitch defining portions 307, 308 at positions separated in the first direction (Z direction) and the second direction (Y direction). This makes it possible to stably define the fin pitch of the multiple fins 290 arranged in the extension direction (X direction).

[0261] Furthermore, by making the outer shape of the second end 41E of the flat tube 41 circular or elliptical, and by making the shape of the tip 209A of the flat tube insertion part 209 that houses the second end 41E such that the outer circumferential surface of the tip 209A of the flat tube 41 comes into surface contact with the fin body 291, it is possible to increase the contact area between the flat tube 41 and the fin body 291. This makes it possible to improve the thermal conductivity between the flat tube 41 and the fin 290. That is, the fin pitch can be stably defined while suppressing air pressure loss, and the thermal conductivity between the flat tubes 41 and the fins 290 can be improved. Furthermore, by not forming the first and second fin pitch specifying portions 307, 308 in the communicating portion 303 extending in the first direction (Z direction), the first and second fin pitch specifying portions 307, 308 do not obstruct the flow of condensed water drained in the first direction (Z direction), thereby maintaining good drainage performance.

[0262] (32) A heat exchanger 285 according to a 32nd aspect is the heat exchanger 285 of (31), wherein the first direction (Z direction) is an up-down direction, the first fin pitch determining portion 307 is configured by bending a part of the fin main body 291 downward, and the second fin pitch determining portion 308 may be formed around the flat tube insertion portion 209 located above the first fin pitch determining portion 307, of the two flat tube insertion portions 209 that sandwich the first fin pitch determining portion 307 in the first direction (Z direction).

[0263] In this way, a first fin pitch specifying portion 307 is formed by bending a portion of the fin body 291 downward, and a second fin pitch specifying portion 308 is formed around the flat tube insertion portion 209 located above the first fin pitch specifying portion 307, of the two flat tube insertion portions 209 that sandwich the first fin pitch specifying portion 307 in the first direction (Z direction).This makes it possible to arrange the positions that specify the fin pitch at equal intervals in the first direction (Z direction), so that the fin pitch can be stably specified.

[0264] (33) A heat exchanger 285 according to a 33rd aspect is the heat exchanger 285 of (31), wherein the first direction (Z direction) is an up-down direction, the first fin pitch specifying portion 307 is configured by bending a part of the fin main body 291 upward, and the second fin pitch specifying portion 308 may be formed around the flat tube insertion portion 209 located below the first fin pitch specifying portion 307, of the two flat tube insertion portions 209 that sandwich the first fin pitch specifying portion 307 in the first direction (Z direction).

[0265] In this way, a first fin pitch specifying portion 307 is formed by bending a portion of the fin body 291 upward, and a second fin pitch specifying portion 308 is formed around the flat tube insertion portion 209 located below the first fin pitch specifying portion 307, of the two flat tube insertion portions 209 that sandwich the first fin pitch specifying portion 307 in the first direction (Z direction).This makes it possible to arrange the positions that specify the fin pitch at equal intervals in the first direction (Z direction), so that the fin pitch can be stably specified.

[0266] (34) A heat exchanger 285 according to a thirty-fourth aspect is the heat exchanger 285 according to any one of (31) to (33), in which the first fin pitch determining portion 307 may be L-shaped.

[0267] In this way, by making the first fin pitch determining portion 307 L-shaped, the probability that the first fin pitch determining portion 307 will come into contact with the second surface 291b can be increased compared to, for example, when the first fin pitch determining portion 307 is I-shaped. Furthermore, by making the first fin pitch determining portion 307 L-shaped, it is possible to increase the contact area between the first fin pitch determining portion 307 and the second surface 291b, so that the fin pitch can be stably maintained.

[0268] (35) A heat exchanger 285 according to a thirty-fifth aspect is the heat exchanger 285 according to any one of (31) to (34), in which the second fin pitch determining portion 308 may be L-shaped.

[0269] In this way, by making the second fin pitch determining portion 308 L-shaped, the probability that the second fin pitch determining portion 308 will come into contact with the first surface 291a can be increased compared to, for example, when the second fin pitch determining portion 308 is I-shaped. Furthermore, by making the second fin pitch determining portion 308 L-shaped, it is possible to increase the contact area between the second fin pitch determining portion 308 and the second surface 291b, so that the fin pitch can be stably maintained.

[0270] (36) A heat exchanger 285 according to a 36th aspect is a heat exchanger 285 according to any one of (31) to (35), wherein the plurality of fins 290 are formed around the flat tube insertion portion 209, rise toward the first surface 291a, and further have a heat conductive portion 305 in contact with the outer peripheral surface 41b of the flat tube 41, and the height of the heat conductive portion 305 in the extension direction (X direction) may be set to a height such that, when the plurality of fins 290 are arranged in the extension direction (X direction), the heat conductive portion 305 does not abut against the fins 290 arranged on the first surface 291a side.

[0271] By having a heat conduction portion configured in this manner, the heat conductivity between the flat tubes 41 and the fins 290 can be improved after the fin pitch is determined using the first and second fin pitch determining portions 307, 308.

[0272] (37) A heat exchanger unit (first and second heat exchanger units 18, 23) according to a thirty-seventh aspect includes a heat exchanger 285 according to any one of (31) to (36) and a blower (first and second blowers 26, 32) that blows air to the heat exchanger 285.

[0273] In this way, by equipping the heat exchanger units (first and second heat exchanger units 281, 283) with the above-mentioned heat exchanger 285, the performance of the heat exchanger units (first and second heat exchanger units 281, 283) can be improved and the heat exchanger units (first and second heat exchanger units 281, 283) can be operated stably.

[0274] (38) A refrigeration cycle apparatus 10 according to a thirty-eighth aspect includes the heat exchanger unit (first and second heat exchanger units 281, 283) of (37).

[0275] In this way, by providing the refrigeration cycle apparatus 280 with the above-mentioned heat exchanger units (first and second heat exchanger units 281, 283), the performance of the refrigeration cycle apparatus 280 can be improved and the refrigeration cycle apparatus 280 can be operated stably. [Explanation of symbols]

[0276] 10,200,280...Refrigeration cycle equipment 11…Outdoor unit 12...Indoor unit 14…Refrigerant piping 14A…First refrigerant pipe 14B…Second refrigerant piping 15...Four-way valve 15A~15D,248...Connection 16…Compressor 18,201,281…First heat exchanger unit 19…Expansion valve 23,203,283…Second heat exchanger unit 26…First blower 27,60,70,80,90,100,110,120,130,140,150,160,170,180,190,205,230,240,250,260,270,285...Heat exchanger 32…Second blower 35…Entrance / Exit Header 37…Fold-over header 41,41F,41S…Flat tube 41a, 41Fa…One end 41A…Flow path 41b…Outer peripheral surface 41B, 206A...One end 41C, 206B...other end 41D...First end 41E...Second end 42,206,231,241,251,261,271,290,320...Fin 42A,209...Flat tube insertion section 43,61,71,81,91,101,131,141,151,191...Header 45...Header body 45a…Bottom surface 45aa…First bottom 45ab…Second bottom 45ac…3rd bottom 45b…Inner wall surface 45A…Opening 47,133…Partition plate 47a…Top end surface 47A, 47B, 133A…lower end 47Aa,47Ba…lower end 47b, 207a, 291a…First side 47c, 207b, 291b…Second side 47C…Cutout part 49,62…Nozzle section 49A,62A…Air outlet 51...Perforated plate 51A…hole 53…Interior space 54…First Space 54A…Refrigerant flow section 55...Second space 73...First refrigerant guide portion 73a...First guide surface 83...Third refrigerant guide section 83a…Third guide surface 93...Second refrigerant guide section 93a...Second guide surface 143, 163, 173... Straightening members 145…Baffle plate 164,174…blocks 174a...Curved surface 207,291…Fin body 207A…Second flat section 207B...First flat portion 209A…Tip 209B…Rear end 211,236...Uneven part 213,233,243,303...Communication part 215…Fin pitch regulation section 217, 235, 245…Condensate guide 218,238…Convex 218A…Tip 220,225...Structure 239…Recess 243A...First part 243B...Second part 246…Step 252, 263, 273…Pedestal 305…Heat conductive part 305a…Inner peripheral surface 307...First fin pitch determining portion 308...Second fin pitch determining portion B…Area Cp…cutting position Ds1,Ds2…distance H, H1, H2...Height J,P…direction Vp…Plane W1, W2…Width

Claims

1. a plurality of flat tubes each having a flat outer shape, a flow path through which a refrigerant flows formed therein, the flat tubes having a first end portion disposed on one side in a width direction and a second end portion disposed on the other side in the width direction; A plurality of fins arranged at a predetermined pitch in an extension direction of the flat tubes in a state in which the flat tubes are accommodated; Equipped with The plurality of fins are plate-shaped and include a fin body including a first surface arranged in the extension direction and a second surface arranged opposite to the first surface; a flat tube insertion portion that is formed on the fin body, is arranged at intervals in a first direction perpendicular to the extension direction, extends from one side to the other side in a second direction perpendicular to the first direction and the extension direction, and accommodates the flat tube inserted from the second end side; a communication portion disposed on the other side of the flat tube insertion portions in the second direction and extending continuously in the first direction; a first fin pitch defining portion formed by bending a portion of the fin body located between adjacent flat tube insertion portions in the first direction and protruding toward the first surface side in the first direction, and abutting against the fin arranged on one side in the extension direction; and a second fin pitch defining portion formed by bending a portion of the fin body in the first direction and protruding toward the first surface side, and arranged around the flat tube insertion portion located on the rear end side of the tip end of the flat tube insertion portion, and abutting against the fin arranged on one side in the extension direction. Each of them has Air that exchanges heat with the refrigerant flows in a direction from the other side of the second direction to the one side of the second direction, The second end has a circular or elliptical outer shape, The shape of a tip end of the flat tube insertion portion that accommodates the second end portion is such that an outer peripheral surface of the second end portion and the fin body are in surface contact with each other, the first fin pitch defining portion is disposed on a rear end side of the flat tube insertion portion, and the second fin pitch defining portion is disposed on a tip end side of the flat tube insertion portion, the first direction is an up-down direction, No fin pitch defining portion is formed in the communicating portion, the first fin pitch defining portion and the second fin pitch defining portion are spaced apart from each other in the second direction, A heat exchanger in which each of the first fin pitch defining portions and the second fin pitch defining portions is provided only one each between adjacent flat tubes in the vertical direction.

2. The first fin pitch defining portion is configured by bending a part of the fin body downward, 2. The heat exchanger according to claim 1, wherein the second fin pitch defining portion is formed around the flat tube insertion portion that is located above the first fin pitch defining portion, of the two flat tube insertion portions that sandwich the first fin pitch defining portion in the first direction.

3. The first fin pitch defining portion is configured by bending a part of the fin body upward, 2. The heat exchanger according to claim 1, wherein the second fin pitch defining portion is formed around the flat tube insertion portion that is located below the first fin pitch defining portion, of the two flat tube insertion portions that sandwich the first fin pitch defining portion in the first direction.

4. The heat exchanger according to claim 1 , wherein the first fin pitch defining portion is L-shaped.

5. The heat exchanger according to claim 1 , wherein the second fin pitch defining portion is L-shaped.

6. The plurality of fins are formed around the flat tube insertion portion, and further have a heat conductive portion that rises toward the first surface side and contacts an outer peripheral surface of the flat tube, A heat exchanger as described in any one of claims 1 to 5, wherein the height of the heat conduction portion in the extension direction is such that, when multiple fins are arranged in the extension direction, the heat conduction portion does not abut against the fins arranged on the first surface side.

7. A heat exchanger according to any one of claims 1 to 6; A blower for blowing air into the heat exchanger; A heat exchanger unit comprising:

8. A refrigeration cycle device comprising the heat exchanger unit according to claim 7.

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