JP7457587B2 - Heat exchangers, heat exchanger units, and refrigeration cycle equipment - Google Patents

Description

The present disclosure relates to a heat exchanger, a heat exchanger unit, and a refrigeration cycle device.

As a heat exchanger, a multi-flow heat exchanger is known that includes a plurality of flat tubes, a plurality of fins, and a pair of headers.
The plurality of flat tubes are inserted into the plurality of fins at intervals in the vertical direction. Each flat tube has a plurality of channels arranged at intervals in the width direction. The plurality of fins are arranged at intervals in the direction in which the flat tube extends.

The pair of headers each extend in the vertical direction. One header accommodates one end of the plurality of flat tubes and is connected to the plurality of flat tubes. The other header accommodates the other ends of the plurality of flat tubes and is connected to the plurality of flat tubes.

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 prevails 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 prevails and more liquid refrigerant is supplied to the flat tubes located above the header.

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.

On the other hand, the fins of the flat heat exchanger include a thin plate-shaped fin body that extends in the vertical direction, a plurality of flat tube insertion parts into which flat tubes are inserted, and and a communication part for guiding condensed water.
The flat tube insertion portion is formed in the fin body and extends in the left-right direction orthogonal to the up-down direction. The flat tube insertion portion is formed so that the flat tube insertion portion does not divide the fin body in the left-right direction.
The communication portion is comprised of a portion of the fin body located outside of the plurality of flat tube insertion portions. The communication portion extends continuously in the vertical direction.

When using fins with the above configuration, there is a problem in that the fins tend to collapse in the left-right direction of the communication section, where they face the flat tube insertion section. One technology aimed at solving this problem is the heat exchanger disclosed in Patent Document 2.

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, 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.

On the other hand, Patent Document 3 discloses that a distance between adjacent fins (fin pitch) is defined by first and second distance maintaining parts formed on a plate-shaped fin.
The first spacing section is formed on the front edge (edge located on the upstream side in the air flow direction) side of the flat tube with the flat tube disposed on the fin. The second spacing section is formed on a fin located between the flat tubes arranged in the vertical direction.

Patent Document 3 discloses that the first and second spacing parts are formed by bending a part of the fin.
Further, Patent Document 3 discloses that when forming the first spacing section, a part of the fin is bent so as to face the air flow direction.
Further, Patent Document 3 discloses a configuration in which the tip of the flat tube contacts only a portion of the first spacing section.

Patent No. 5754490 Patent No. 5397489 International Publication No. 2019/239519

By the way, in general, when there are a large number of flat tubes, the space inside the header is divided into multiple spaces by vertically arranging horizontal partition plates that extend horizontally inside the header. ing.
In order to equalize the distribution using the heat exchanger described in Patent Document 1, it is desirable that the first outflow space and the first loop space are arranged continuously in the vertical direction. For this reason, it becomes difficult to secure a space for providing the first internal space, and it may become difficult to provide the first internal space. Furthermore, the number of horizontal partition plates increases, which may complicate the manufacturing process.

Further, in Patent Document 1, in order to guide the refrigerant introduced into the first internal space to the first outflow space through two first inflow ports formed in the first rectifying plate, the refrigerant flows in the width direction of the flat tube. may be in different states. In this case, it may be difficult to suppress uneven distribution of refrigerant with respect to the plurality of channels formed in the width direction of each flat tube.

On the other hand, the heat transfer promotion section disclosed in Patent Document 2 is formed by pressing a plate-shaped base material member that serves as the base material for the fins. As a result, a depression with a bottom is formed on the other side of the heat transfer promotion section in the fin arrangement direction. This causes condensed water flowing through the communication section to accumulate at the bottom of the heat transfer promotion section, which can make it difficult to drain the condensed water downward through the communication section.

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 pressure loss of the air.
In addition, in Patent Document 3, the tip of the flat tube is in contact with only a portion of the first spacing retaining portion, which may make it difficult to improve thermal conductivity between the fins and the flat tube.

The present disclosure has been made in order to solve the above problems, and is capable of simplifying the manufacturing process and of each flat tube and each flat tube without depending on the flow rate of the refrigerant supplied into the header. It is an object of the present invention to provide a heat exchanger, a heat exchanger unit, and a refrigeration cycle device that can suppress uneven distribution of refrigerant to a plurality of channels formed in the width direction.
Further, the present disclosure has been made to solve the above problems, and provides a heat exchanger and a heat exchanger capable of suppressing the collapse of the fins while suppressing the flow of condensed water in the communication portion. The purpose of the present invention is to provide an exchanger unit and a refrigeration cycle device.
Furthermore, the present disclosure has been made to solve the above-mentioned problems, and it becomes possible to specify the fin pitch while suppressing air pressure loss, and also allows for heat conduction between the flat tube and the fins. An object of the present invention is to provide a heat exchanger, a heat exchanger unit, and a refrigeration cycle device that can improve performance.

In order to solve the above problems, a heat exchanger according to the present disclosure is a heat exchanger that exchanges heat between air and a refrigerant, and has a flat outer shape, extends in one direction, and is arranged in the width direction. , a plurality of flat tubes extending in the one direction and having a plurality of channels through which the refrigerant flows; and a plurality of fins disposed in the extending direction of the flat tubes in a state where the plurality of flat tubes are housed; a header connected to the plurality of flat tubes such that one end of the plurality of flat tubes is disposed inside and through which the refrigerant flows, the header having a cylindrical shape extending in the vertical direction; a header main body that partitions a columnar internal space ; a partition plate that divides the internal space into a first space and a second space in which one end of the plurality of flat tubes is arranged; a partition plate that is arranged below the first space, and the header a nozzle portion including an outlet that blows out the refrigerant supplied from the outside toward the bottom surface of the header body, and a part of the first space is located on both sides of the nozzle portion in the width direction. A refrigerant flow section is formed respectively.

According to the heat exchanger, heat exchanger unit, and refrigeration cycle device of the present disclosure, the production process can be suppressed from becoming complicated, and each flat Unbalanced refrigerant distribution to the plurality of channels formed in the width direction of the tube and each flat tube can be suppressed.
On the other hand, according to the heat exchanger, heat exchanger unit, and refrigeration cycle device of the present disclosure, it is possible to suppress the collapse of the fins while suppressing the flow of condensed water in the communication portion.
On the other hand, according to the heat exchanger, heat exchanger unit, and refrigeration cycle device of the present disclosure, the fin pitch can be defined while suppressing air pressure loss, and the thermal conductivity between the flat tubes and the fins is improved. can be done.

1 is a diagram schematically showing a schematic configuration of a refrigeration cycle device according to a first embodiment of the present disclosure. 2 is a diagram schematically showing main parts of the heat exchanger shown in FIG. 1. FIG. 3 is a perspective view of the flat tube shown in FIG. 2. FIG. FIG. 3 is a longitudinal cross-sectional view of the header surrounded by region B shown in FIG. 2; 5 is a cross-sectional view of the header shown in FIG. 4 taken along line C ₁ -C ₂ . FIG. 5 is a cross-sectional view of the header shown in FIG. ₄ along line D ₁ -D. It is a sectional view of the main part of the heat exchanger concerning the 1st modification of the 1st embodiment. FIG. 7 is a vertical cross-sectional view of the main parts of a heat exchanger according to a second embodiment. It is a longitudinal cross-sectional view of the main part of the heat exchanger based on the 1st modification of 2nd Embodiment. It is a longitudinal cross-sectional view of the main part of the heat exchanger based on the 2nd modification of 2nd Embodiment. It is a longitudinal cross-sectional view of the main part of the heat exchanger based on the 3rd modification of 2nd Embodiment. FIG. 7 is a vertical cross-sectional view of the main parts of a heat exchanger according to a third embodiment. It is a longitudinal cross-sectional view of the main part of the heat exchanger based on the 1st modification of 3rd Embodiment. It is a longitudinal cross-sectional view of the main part of the heat exchanger based on the 2nd modification of 3rd Embodiment. FIG. 7 is a longitudinal cross-sectional view of the main parts of a heat exchanger according to a fourth embodiment. It is a longitudinal cross-sectional view of the main part of the heat exchanger based on the 1st modification of 4th Embodiment. It is a longitudinal cross-sectional view of the main part of the heat exchanger based on the 2nd modification of 4th Embodiment. It is a longitudinal cross-sectional view of the main part of the heat exchanger based on the 3rd modification of 4th Embodiment. It is a longitudinal cross-sectional view of the main part of the heat exchanger based on the 4th modification of 4th Embodiment. It is a longitudinal cross-sectional view of the principal part of the heat exchanger concerning the 5th modification of a 4th embodiment. It is a figure which shows typically the schematic structure of the refrigeration cycle apparatus based on the 5th Embodiment of this indication. 22 is a diagram schematically showing main parts of the heat exchanger shown in FIG. 21. FIG. 23 is a view A of the flat tube and fins shown in FIG. 22. FIG. 23 is a perspective view of the flat tube shown in FIG. 22. FIG. FIG. 24 is a cross-sectional view of the fin shown in FIG. 23 in the E ₁ -E ₂ line direction, and is a diagram showing a cross section of one fin. FIG. 24 is a cross-sectional view of the fin shown in FIG. 23 in the direction of line F _{1 -F} , and is a cross-sectional view schematically showing a state in which the fin pitch defining portions are in contact with fins disposed at positions adjacent to each other. FIG. 23 is a cross-sectional view of the fin shown in FIG. 22 in the direction of _line G ₁ -G, and is a diagram showing a cross section of one fin. 23 is a plan view for explaining a pre-process of a cutting process performed when manufacturing a plurality of fins shown in FIG. 22. FIG. FIG. 23 is a plan view for explaining a cutting process performed when manufacturing a plurality of fins shown in FIG. 22; 23 is a plan view for explaining another arrangement example of a plurality of fins when manufacturing the plurality of fins shown in FIG. 22. FIG. FIG. 13 is a diagram showing a main part of a heat exchanger according to a sixth embodiment of the present disclosure. FIG. 32 is a cross-sectional view of the fin shown in FIG. 31 in the I ₁ -I ₂ line direction, and is a diagram showing a cross section of one fin. FIG. 7 is a diagram showing main parts of a heat exchanger according to a seventh embodiment of the present disclosure. 34 is a cross-sectional view of the fin shown in FIG. 33 in the direction of line K ₁ -K ₂ , and is a diagram showing a cross section of one fin. FIG. FIG. 7 is a diagram showing main parts of a heat exchanger according to an eighth embodiment of the present disclosure. FIG. 36 is a cross-sectional view of the fin shown in FIG. 35 in the L ₁ -L _2- line direction, and is a diagram showing a cross section of one fin. FIG. 36 is a cross-sectional view of the fin shown in FIG. 35 in the N ₁ -N ₂ line direction, and is a diagram showing a cross section of one fin. It is a figure showing the main part of the heat exchanger concerning the 1st modification of the 8th embodiment of this indication. It is a figure showing the main part of the heat exchanger concerning the 2nd modification of the 8th embodiment of this indication. It is a figure which shows typically the schematic structure of the refrigeration cycle apparatus based on the 9th Embodiment of this indication. FIG. 41 is a diagram showing a schematic view of a main part of the heat exchanger shown in FIG. 40 . 42 is a view A of the flat tube and fins shown in FIG. 41. FIG. FIG. 43 is a cross-sectional view of the fin shown in FIG. 42 in the Q ₁ -Q _2- line direction, and is a diagram showing a cross section of one fin. FIG. 43 is a cross-sectional view of the fin shown in FIG. 42 in the R ₁ -R ₂ line direction, and is a diagram showing a cross section of one fin. FIG. 43 is a cross-sectional view taken along line S ₁ -S ₂ of the fin shown in FIG. 42, and is a cross-sectional view illustrating a schematic state in which a first fin pitch defining portion is in contact with fins arranged in adjacent positions. 43 is a sectional view of the fin shown in FIG. 42 in the T ₁ -T ₂ line direction, and is a sectional view schematically showing a state in which the second fin pitch defining portions are in contact with fins disposed at positions adjacent to each other; FIG. It is. It is a figure for explaining the fin concerning the modification of the 9th embodiment of this indication.

<First embodiment>
With reference to FIG. 1, the overall configuration of a refrigeration cycle device 10 according to a first embodiment will be described. In FIG. 1, solid line arrows indicate the direction in which the refrigerant flows during heating operation, and dotted line arrows indicate the direction in which the refrigerant flows during cooling operation.
(Overall configuration of refrigeration cycle equipment)
The refrigeration cycle device 10 has a configuration in which 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 are connected by a refrigerant pipe 14. The refrigeration cycle device 10 includes an outdoor unit 11 and an indoor unit 12.

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

(Configuration of four-way valve)
The four-way valve 15 has connection parts 15A to 15D to which one of the ends of the first and second refrigerant pipes 14A, 14B constituting the refrigerant pipe 14 is connected.
One end of the first refrigerant pipe 14A is connected to the connection portion 15A, and the other end of the first refrigerant pipe 14A is connected to the connection portion 15B.
One end of the second refrigerant pipe 14B is connected to the connection portion 15C, and the other end of the second refrigerant pipe 14B is connected to the connection portion 15D.

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 in the order of the compressor 16, first heat exchanger unit 18, expansion valve 19, and second heat exchanger unit 23.
On the other hand, during heating operation, the refrigerant is circulated in the order of the compressor 16, the second heat exchanger unit 23, the expansion valve 19, and the first heat exchanger unit 18.

(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.

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

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

(Overall configuration of heat exchanger)
The heat exchanger 27 will be explained with reference to FIGS. 1 to 6. In FIGS. 2 to 4 and 6, the Z direction indicates the vertical direction. In FIGS. 2 to 5, the X direction indicates the direction in which the flat tube 41 extends orthogonally to the Z direction. In FIGS. 3, 5, and 6, the Y direction indicates the width direction of the flat tube 41 (the width direction of the nozzle portion 49), which is orthogonal to the X direction and the Z direction. In FIG. 2, air flows in the direction of the page (for example, in the direction toward the page). The arrows shown 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").

The heat exchanger 27 is used as a condenser and radiates heat to the outside during cooling operation, and is used as an evaporator and absorbs heat from the outside during heating operation.
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 includes a plurality of flat tubes 41, a plurality of fins 42, and a pair of headers 43.

(Structure of flat tube)
Next, the flat tube 41 will be explained with reference to FIGS. 2 and 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 channels 41A through which the refrigerant flows are formed at intervals in the Y direction.
The plurality of flat tubes 41 include a flat tube 41F placed at the bottom and a flat tube 41S placed second from the bottom.

The flat tube 41 has a pair of ends 41B, 41C arranged in the X direction. One end 41B is housed in one header 43. The other end 41C is housed in the other header 43. The flat tubes 41 are arranged with gaps in the Z direction, and are supported on both sides in the X direction by the pair of headers 43.

(Fin configuration)
Next, the plurality of fins 42 will be explained with reference to FIG. 2.
The plurality of fins 42 each have flat tube insertion portions 42A formed at intervals in the Z direction. The flat tube 41 is inserted into the flat tube insertion portion 42A.

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

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

(Header body structure)
Next, the header body 45 will be described with reference to Figures 4 to 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 in a position facing the nozzle portion 49 in the X direction.

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.

(Configuration of Partition Plate)
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 disposed on a side to which the first refrigerant pipe 14A is connected. The second space 55 is disposed on a side to which the plurality of flat tubes 41 are connected. The partition plate 47 forms a circulation path for the refrigerant.

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 cutout portion 47C.

The upper end surface 47a is located downwardly away from the header main body 45 that faces 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 header body 45 and the upper end surface 47a, which face the upper end surface 47a.

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.

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

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.

(Effect of the shape of the lower end of the partition plate)
For example, when a circular hole is used as the outlet 49A of the nozzle part 49, the refrigerant flows from the first space 54 to the second space via the notch 47C located between the lower end 47A and the lower end 47B. It is distributed to 55. 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.

(Configuration of nozzle part)
Next, the nozzle section 49 will be explained with reference to FIGS. 4 and 5.
The nozzle section 49 is arranged in the first space 54. The nozzle portion 49 is fixed to the header body 45 and the partition plate 47. Refrigerant flow portions 54A through which the refrigerant passes are formed on both sides of the nozzle portion 49 in the Y direction. The refrigerant flow section 54A is configured as a part of the first space 54.

The nozzle portion 49 has an air outlet 49A disposed on the lower end side thereof. 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 gas-liquid two-phase refrigerant) through the first refrigerant pipe 14A. The outlet 49A blows out the refrigerant in a direction toward the first bottom surface 45aa, causing the refrigerant to collide 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.

Note that when the heat exchanger 27 is operated as a condenser, the refrigerant flowing into the second space 55 from the plurality of flat tubes 41 flows into the first refrigerant pipe 14A via the outlet 49A.

(Effect of nozzle part)
By having the nozzle part 49 configured as described above, it is possible to cause the refrigerant blown out from the outlet 49A to collide with the first bottom surface 45aa of the header body 45, thereby reducing the difference in the state of the refrigerant in the Y direction. becomes. 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 where one end 41B of the plurality of flat tubes 41 is arranged). , it is possible to suppress uneven distribution of the refrigerant to the plurality of channels 41A formed in the Y direction of each flat tube 41, without depending on the flow rate of the refrigerant introduced into the header 43.

The nozzle portion 49 configured as described above is preferably disposed at a position lower than 1/2 of the height of the header body 45, and more preferably lower than 1/3 of the height of the header body 45. It is preferable to arrange it at a position lower than 1/4 of the height of the header main body 45.
Further, the nozzle section 49 having the above configuration is arranged, for example, between the flat tube 41F placed at the bottom and the flat tube 41S placed second from the bottom among the plurality of flat tubes 41. It's okay.

(Effect of position where nozzle part is installed)
For example, if the nozzle part 49 is arranged at a position higher than 1/2 of the height H of the header body 45, the distance between the air outlet 49A of the nozzle part 49 and the first bottom surface 45aa of the header body 45 becomes too long. Therefore, the flow of the refrigerant blown out from the outlet 49A may be attenuated, making it difficult to form a circulating flow of the refrigerant within the header 43.
Therefore, by arranging the nozzle part 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 air outlet 49A to the first bottom surface 45aa of the header body 45. Therefore, it becomes easier to form a circulating flow of the refrigerant within the header 43.

In addition, 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.

Furthermore, by arranging the nozzle part 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 air outlet 49A to the first bottom surface 45aa of the header body 45. Therefore, it becomes easier to form a circulating flow of the refrigerant within the header 43.

As described above, by arranging the nozzle portion 49 between the flat tube 41F placed at the bottom and the flat tube 41S placed second from the bottom, the circulating flow of the refrigerant within the header 43 is facilitated. can be formed into
Further, 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 plurality of flat tubes 41.

(Configuration of perforated plate)
Next, with reference to FIG. 4, the perforated plate 51 will be explained.
The porous plate 51 is arranged so as to horizontally cover a first space 54 located above the nozzle part 49. The porous plate 51 is fixed to the header body 45 and the partition plate 47. A plurality of holes 51A are formed in the perforated plate 51 to communicate the first space 54 in the Z direction.
As the perforated plate 51, for example, a punched plate can be used.
Although FIG. 4 shows a punched plate as an example of the perforated plate 51, for example, a mesh member, a porous plate, or the like may be used as the perforated plate 51.

(Effect of perforated plate)
By providing the perforated plate 51 with such a configuration, it is possible to suppress the movement of the gas (gas refrigerant) flowing backward from the bottom to the top of the first space 54. This makes it easier to form a circulating flow of refrigerant.

(Effect of heat exchanger)
According to the heat exchanger 27 of the first embodiment, by having the nozzle portion 49 configured as above, it is 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 plurality of flat tubes 41 is arranged), so that a circulation flow of the refrigerant (a flow that descends the first space 54 and ascends the second space 55) is formed in the header 43 without depending on the flow rate of the refrigerant introduced into 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.

(Effect of heat exchanger unit)
According to the first and second heat exchanger units 18 and 23 of the first embodiment, the heat exchange efficiency can be increased by having the heat exchanger 27 configured as described above.

(Configuration of the expansion valve)
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.

(Indoor unit configuration)
The indoor unit 12 has a second heat exchanger unit 23. The second heat exchanger unit 23 includes 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.

(Effects 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.

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

<First modification of the first embodiment>
With reference to FIG. 7, a heat exchanger 60 according to a modification of the first embodiment will be described. In FIG. 7, the same components as those of the structure shown in FIG. 5 are given 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 section 54A in the Y direction (hereinafter referred to as "width W2").

(Overall configuration of heat exchanger)
The heat exchanger 60 has a similar structure 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.

(Header configuration)
The header 61 has the same structure as the header 43 except that it includes a nozzle section 62 instead of the nozzle section 49 that constitutes the header 43.

(Configuration of nozzle part)
The nozzle portion 62 has a groove-shaped outlet 62A extending in the Y direction. The blower 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. Thereby, the width W2 of the pair of refrigerant flow parts 54A arranged on both sides of the nozzle part 62 in the Y direction is configured to be narrower than the width of the pair of refrigerant flow parts 54A shown in FIG.
For example, the total value (=2×W2) of the widths W2 of the pair of refrigerant flow portions 54A arranged on both sides of the nozzle portion 62 in the width direction (Y direction) is smaller than the value of the width W1 of the nozzle portion 62. It is best to configure it so that

(Effect of heat exchanger)
According to the heat exchanger 60 according to the modification of the first embodiment, by making the outlet 62A have a groove shape extending in the Y direction, compared to a case where the outlet has a circular shape, the refrigerant in the Y direction is The difference between the states can be further reduced.
Further, the total value (=2×W2) of the width W2 of the pair of refrigerant flow portions 54A arranged on both sides of the nozzle portion 62 in the width direction (Y direction) is made smaller than the value of the width W1 of the nozzle portion 62. Therefore, it is possible to reduce the flow path cross-sectional area of the pair of refrigerant flow portions 54A. This makes it possible to suppress the occurrence of a backflow of the refrigerant from below to above in the first space 54 .

<Second embodiment>
With reference to FIG. 8, a heat exchanger 70 according to a second embodiment will be described. In FIG. 8, the same components as those of the structure shown in FIG. 4 are given 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.

(Overall configuration of heat exchanger)
The heat exchanger 70 is configured in the same manner as the heat exchanger 27 except that it has a header 71 instead of the header 43 that constitutes the heat exchanger 27 of the first embodiment. The header 71 is configured similarly to the header 43 except that it includes a first refrigerant guide section 73.

(Configuration of the first refrigerant guide portion)
The first refrigerant guide portion 73 is provided on the 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 an 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 73 a, 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.

(Effect of heat exchanger)
According to the heat exchanger 70 according to the second embodiment, by including the first refrigerant guide section 73 configured as described above, the refrigerant blown out from the outlet 49A of the nozzle section 49 is transferred to the second space 55. At the same time, the difference in the state of the refrigerant in the width direction can be reduced by causing the refrigerant to collide with the inner wall surface 45b of the header body 45 that partitions the second space 55.
Further, when the refrigerant is a gas-liquid two-phase refrigerant and the flow rate of the refrigerant introduced into the header main body 45 is small, the refrigerant is separated into gas and liquid in the first space 54, and the first space 54 becomes a gas-liquid phase refrigerant. It becomes possible to suppress the refrigerant from rising. That is, it is possible to suppress the formation of a circulating flow of refrigerant within the header body 45.
Furthermore, by making the first guide surface 73a a concave curved surface concave in the 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.

Note that in the second embodiment, a nozzle section 62 shown in FIG. 7 may be used instead of the nozzle section 49 that constitutes the heat exchanger 70.

<First modification of the second embodiment>
With reference to FIG. 9, a heat exchanger 80 according to a first modification of the second embodiment will be described. In FIG. 9, the same components as those of the structure shown in FIG. 8 are given 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.

(Overall configuration of heat exchanger)
The heat exchanger 80 has a similar configuration 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 has a similar configuration to the header 71, except that a third refrigerant guiding portion 83 is provided in the configuration of the header 71.

(Configuration of third refrigerant guide section)
The third refrigerant guide portion 83 is provided at a portion of the lower end portion of the partition plate 47 that is upwardly away from the bottom surface 45a of the header body 45. The third refrigerant guide section 83 has a third guide surface 83a.
The third guide surface 83a is arranged to face the first guide surface 73a. The third guide surface 83a guides the refrigerant in the 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.

(Effect of heat exchanger)
According to the heat exchanger 80 according to the first modification of the second embodiment, by including the third refrigerant guide section 83 having the above configuration, the third guide surface 83a (the outer circumferential surface of the columnar member ) allows the refrigerant to be guided in the direction from the first space 54 to the second space 55.

In addition, in the first modified example of the second embodiment, the nozzle portion 62 shown in FIG. 7 may be used instead of the nozzle portion 49 constituting the heat exchanger 80.

<Second modification of second embodiment>
With reference to FIG. 10, a heat exchanger 90 according to a second modification of the second embodiment will be described. In FIG. 10, the same components as those of the structure shown in FIG. 8 are given 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.

(Overall configuration of heat exchanger)
The heat exchanger 90 is configured similarly to the heat exchanger 70 except that it includes a header 91 instead of the header 71 that configures the heat exchanger 70 of the second embodiment. The header 91 has the same structure as the header 71 except that a second refrigerant guide section 93 is provided in the structure of the header 71.

(Configuration of second refrigerant guide section)
The second refrigerant guide section 93 is provided on the second bottom surface 45ab. The second refrigerant guide section 93 has a second guide surface 93a. The second guide surface 93a allows the refrigerant flowing from the lower end of the first space 54 to the lower end of the second space 55 (by colliding with the first bottom surface 45aa, the difference in the state in the width direction is reduced). refrigerant) is guided from the bottom of the second space 55 to the top.
As the second guide surface 93a, for example, a concave curved surface recessed in a direction away from the lower end of the partition plate 47 can be used.

(Effect of heat exchanger)
According to the heat exchanger 90 according to the second modification of the second embodiment, by including the second refrigerant guide section 93 configured as described above, collision with the first bottom surface 45aa of the header main body 45 is avoided. The refrigerant generated in the second space 55 with a small difference in state in the width direction can be guided from the bottom to the top of the second space 55.
Furthermore, by making the second guide surface 93a a concave curved surface that is concave in the direction away from the lower end of the partition plate 47, the refrigerant with a small difference in condition in the width direction is directed from the bottom to the top of the second space 55. can be easily guided.

Note that in the heat exchanger 90 according to the second modification of the second embodiment, at least one of the first refrigerant guide section 73 and the third refrigerant guide section 83 shown in FIG. 9 may be provided.

<Third modification of second embodiment>
With reference to FIG. 11, a heat exchanger 100 according to a third modification of the second embodiment will be described. In FIG. 11, the same components as those of the structure shown in FIG. 10 are given 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.

(Overall configuration of heat exchanger)
The heat exchanger 100 is configured similarly to the heat exchanger 90 except that it includes a header 101 instead of the header 91 that configures the heat exchanger 90 according to the second modification of the second embodiment. The header 101 has the same configuration as the header 91 except that the first refrigerant guide section 73 is provided in the configuration of the header 91.

(Effect of heat exchanger)
According to the heat exchanger 100 according to the third modification of the second embodiment, the refrigerant having a small difference in state in the width direction generated by colliding with the first guide surface 73a is transferred to the second space 55. It can be smoothly guided from the bottom to the top.

In addition, in the heat exchanger 100 according to the third modified example of the second embodiment, a third refrigerant guide section 83 shown in FIG. 9 may be provided.

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.

(Overall configuration of heat exchanger)
The heat exchanger 110 has one end 41Fa of the flat tube 41F located closer to the first space 54 than the one end 41a of the other flat tube 41 with respect to the header 43 that constitutes the heat exchanger 27 of the first embodiment. It is configured similarly to the heat exchanger 27 except that it is retreated in the direction toward the second space 55.
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 longer than the distance Ds2 from the one end 41a of the other flat tube 41 to the second surface 47c of the partition plate 47. It is configured to be.

(Effect of heat exchanger)
According to the heat exchanger 110 according to the third embodiment, the distance Ds1 from the one end 41Fa of the flat tube 41F arranged at the bottom among the plurality of flat tubes 41 to the partition plate 47 is the same as that of the other flat tubes. By making the distance Ds2 from one end 41a of 41 to the partition plate 47 longer than the distance Ds2, the cross-sectional area of the refrigerant flow path formed between one end 41Fa of the flat tube 41F placed at the bottom and the partition plate 47 can be increased. It is possible to make it larger.
This makes it possible to reduce the degree of contracted flow at the height of the flat tube 41F, making it difficult for the refrigerant flow to separate, so that in the past, liquid phase refrigerant would flow in due to the effect of separation (contracted flow). The liquid phase refrigerant is now easily supplied even to the flat tubes 41F, which may otherwise have been difficult to supply, and as a result, the refrigerant distribution to each flat tube 41 can be equalized.

In the heat exchanger 110 according to the third embodiment, the first refrigerant guide section 73 shown in FIG. 9, the third refrigerant guide section 83 shown in FIG. 9, and the second refrigerant guide section shown in FIG. At least one of 93 may be provided.

<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.

(Overall configuration of heat exchanger)
The heat exchanger 120 is configured in the same manner as 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 flat tube 41F located at the bottom 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 section 73 may be provided.
Further, the heat exchanger 120 having the above-described configuration may be provided with a third refrigerant guide portion 83 shown in FIG.

<Second modification of third embodiment>
With reference to FIG. 14, a heat exchanger 130 according to a second modification of the third embodiment will be described. In FIG. 14, the same components as those of the structure shown in FIG. 4 are given 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.

(Overall configuration of heat exchanger)
The heat exchanger 130 has the same configuration as the heat exchanger 27 except that it includes a header 131 instead of the header 43 that constitutes the heat exchanger 27 of the first embodiment. The header 131 has the same structure as the header 43 except that it includes a partition plate 133 instead of the partition plate 47 that forms the header 43 of the first embodiment.
The positions of one ends 41a and 41Fa of the plurality of flat tubes 41 in the X direction are the same.

(Configuration of partition plate)
The partition plate 133 has a lower end 133A that faces one end 41Fa of the flat tube 41F in the X direction. The lower end portion 133A is disposed at a position shifted from the second space 55 toward the first space 54 with respect to the partition plate 133 excluding the lower end portion 133A.
As a result, the distance Ds1 from one end 41Fa of the flat tube 41F arranged at the bottom to the partition plate 47 is configured to be longer than the distance Ds2 from the one end 41a of the other flat tubes 41 to the partition plate 47. ing.

(Effect of heat exchanger)
According to the heat exchanger 130 according to the second modification of the third embodiment, the lower end portion 133A of the partition plate 133 faces the one end 41Fa of the flat tube 41F arranged at the bottom among the plurality of flat tubes 41. is formed between one end 41Fa of the flat tube 41F placed at the bottom and the partition plate 133. The cross-sectional area of the refrigerant flow path can be increased.

In the heat exchanger 130 according to the second modification of the third embodiment, the first refrigerant guide section 73 shown in FIG. 9, the third refrigerant guide section 83 shown in FIG. 9, and the third refrigerant guide section 83 shown in FIG. At least one of the two refrigerant guide sections 93 may be provided.

<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 of the structure shown in FIG. 4 are given 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.

(Overall configuration of heat exchanger)
The heat exchanger 140 has the same configuration as the heat exchanger 27 except that it has a header 141 instead of the header 43 that constitutes the heat exchanger 27 of the first embodiment. The header 141 has the same configuration as the header 43 of the first embodiment except that a rectifying member 143 is further provided.

(Configuration of rectifying member)
The flow regulating member 143 is a baffle plate 145 provided on the inner wall surface 45b of the header body 45 that partitions the second space 55.
The baffle plate 145 is disposed below the flat tube 41F and at a position away from the flat tube 41F. The baffle plate 145 extends from the inner wall surface 45b of the header body 45 in the direction 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.

(Effect of heat exchanger)
According to the heat exchanger 140 according to the fourth embodiment, by including the baffle plate 145 (straightening member 143) configured as described above, one end 41B of the flat tube 41F disposed at the bottom can be In the former stage, it becomes possible to separate the flow of the refrigerant and rectify the flow of the refrigerant at one end of the flat tube 41F.
As a result, liquid phase refrigerant can be easily supplied to the flat tubes 41F, to which liquid phase refrigerant might have been difficult to flow into due to the effect of separation (condensation), and as a result, each flat tube 41 The refrigerant distribution can be equalized.

<First modification of fourth embodiment>
With reference to FIG. 16, a heat exchanger 150 according to a first modification of the fourth embodiment will be described. In FIG. 16, the same components as those of the structure shown in FIG. 15 are given 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.

(Overall configuration of heat exchanger)
The heat exchanger 150 has the same configuration as the heat exchanger 140 except that it has a header 151 instead of the header 141 that configures the heat exchanger 140 of the fourth embodiment. The header 151 has the same configuration as the header 141 of the fourth embodiment except that a first refrigerant guide section 73 is further provided.
In this way, the baffle plate 145 described in the fourth embodiment and the first refrigerant guide section 73 described in the second embodiment may be used in combination.

<Second modification of fourth embodiment>
With reference to FIG. 17, a heat exchanger 160 according to a first modification of the fourth embodiment will be described. In FIG. 17, the same components as those of the structure shown in FIG. 15 are given 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.

(Overall configuration 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, which is a flow straightening member 163, instead of the baffle plate 145 constituting the heat exchanger 140 of the fourth embodiment.

(Block configuration)
The block 164 is arranged 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. The block 164 extends from the inner wall surface 45b of the header body 45 in the direction toward the partition plate 47.
The amount of protrusion of the block 164 with respect to the inner wall surface 45b of the header body 45 is equal to the amount of protrusion of one end 41B of the flat tube 41.

(Effect of heat exchanger)
According to the heat exchanger 160 according to the first modification of the fourth embodiment, by using the block 164 having the above configuration as the rectifying member 163, one end of the flat tube 41F disposed at the bottom It becomes possible to separate the flow of the refrigerant at the front stage of the section 41B and rectify the flow of the refrigerant at the end of the flat tube 41F.
As a result, liquid phase refrigerant can be easily supplied to the flat tubes 41F, to which liquid phase refrigerant might have been difficult to flow into due to the effect of separation (condensation), and as a result, each flat tube 41 The refrigerant distribution can be equalized.

<Third modification of fourth embodiment>
With reference to FIG. 18, a heat exchanger 170 according to a third modification of the fourth embodiment will be described. In FIG. 18, the same components as those of the structure shown in FIG. 17 are given 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.

(Overall configuration of heat exchanger)
The heat exchanger 170 is the same as the heat exchanger 160 except that it includes a block 174 that is a rectifying member 173 instead of the block 164 that constitutes the heat exchanger 160 according to the second modification of the fourth embodiment. It is composed of

(Block configuration)
The block 174 is arranged 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. 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.

(Effect of heat exchanger)
According to the heat exchanger 170 according to the third modification of the fourth embodiment, since the block 174 has the curved surface 174a, the refrigerant can be guided above the second space 55 without separation of the flow. Can be done.

<Fourth modification of the fourth embodiment>
With reference to FIG. 19, a heat exchanger 180 according to a fourth modification of the fourth embodiment will be described. In FIG. 19, the same components as those of the structure shown in FIGS. 11 and 17 are given 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.

(Overall configuration of heat exchanger)
The heat exchanger 180 has the structure of the heat exchanger 170 according to the third modification of the fourth embodiment, with the addition of a first refrigerant guide section 73 and a second refrigerant guide section 93 shown in FIG. Other than that, it is configured similarly to the heat exchanger 160.
In this way, the block 174, the first refrigerant guide section 73, and the second refrigerant guide section 93 may be used in combination.

Fifth Modification of the 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.

(Overall configuration of heat exchanger)
The heat exchanger 190 is the same as the heat exchanger 160 except that it has a partition plate 133 shown in FIG. 14 instead of the partition plate 47 that constitutes the heat exchanger 160 according to the second modification of the fourth embodiment. are configured similarly.
In this way, the block 174, the first refrigerant guide section 73, the second refrigerant guide section 93, and the partition plate 133 may be used in combination.

<Fifth embodiment>
A refrigeration cycle device 200 according to a fifth embodiment will be described with reference to FIG. 21. In FIG. 21, solid line arrows indicate the direction in which the refrigerant flows during heating operation, and dotted line arrows indicate the direction in which the refrigerant flows during cooling operation. In FIG. 21, the same components as those of the structure shown in FIG. 1 are given the same reference numerals.

(Overall configuration of the refrigeration cycle device)
The refrigeration cycle apparatus 200 is configured in the same manner as 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 it 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 .

(Overall configuration of heat exchanger)
The heat exchanger 205 will be described with reference to FIGS. 21 to 23. In FIG. 22, the same components as those of the structure shown in FIG. 2 are given the same reference numerals. Moreover, in FIG. 22, the X direction indicates the extending direction of the flat tube 41 orthogonal to the Z direction (vertical direction). In FIG. 23, the Y direction is the left-right direction perpendicular to the X and Z directions (the width direction of the flat tube 41 when the flat tube 41 is attached to the fin 206), and J is the direction in which air flows (hereinafter referred to as (referred to as "direction J").

The heat exchanger 205 has the same structure as the heat exchanger 27 except that it includes an entrance/exit header 35, a folding header 37, and fins 206 instead of the pair of headers 43 and fins 42.

(Configuration of entrance/exit header)
The entrance/exit header 35 is a cylindrical member extending in the Z direction, and has an upper end and a lower end closed. The inlet/outlet header 35 is connected to the first refrigerant pipe 14A and one end of the plurality of 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 pipe 14A to the flow paths in the plurality of flat tubes 41, and also guides the refrigerant that returns to the inlet/outlet header 35 via the folding header 37. is returned to the first refrigerant pipe 14A.

(Configuration of return header)
The folding header 37 is arranged to face the entrance/exit header 35 in the X direction. The folding header 37 is a cylindrical member extending in the Z direction, and its upper and lower ends are closed. The folding header 37 is connected to the other end of the plurality of flat tubes 41 (the end disposed on the other side in the X direction).
The return header 37 returns the refrigerant to the entrance/exit header 35 via the plurality of flat tubes 41 .

(Structure of flat tube)
The flat tube 41 will be explained with reference to FIGS. 22 to 24. In FIG. 24, the same components as those of the structure shown in FIGS. 22 and 23 are given the same reference numerals.

The flat tube 41 has a first end 41D disposed on one side in the width direction (Y direction) of the flat tube 41 and a second end portion 41D disposed on the other side in the width direction (Y direction) of the flat tube 41. It further includes an end portion 41E and an outer circumferential surface 41b.
The first and second end portions 41D and 41E have a circular or elliptical outer shape.

The plurality of flat tubes 41 are supported by the plurality of fins 206 at intervals in the Z direction. One end of the plurality of flat tubes 41 arranged in the X direction is connected to the entrance/exit header 35 . The other ends of the plurality of flat tubes 41 arranged in the X direction are connected to the folding header 37 .

(Overall configuration of fins)
The fins 206 will be described with reference to FIGS. 22, 23, and 25 to 27. 5 to 7, the same components as those of the structure shown in FIGS. 22 and 23 are given the same reference numerals.

The plurality of fins 206 are arranged at a predetermined pitch in the X direction. The fin 206 includes a fin main body 207 , a plurality of flat tube insertion portions 209 , a plurality of uneven portions 211 , a communication portion 213 , and a plurality of fin pitch defining portions 215 .

(Configuration of fin body)
The fin main body 207 is plate-shaped and extends in the Z direction. The fin main body 207 has first and second surfaces 207a and 207b arranged in the X direction, and a second plane portion 207A.
The first surface 207a is arranged to face the entrance/exit header 35. The second surface 207b is a surface located on the opposite side of the first surface 207a. The second surface 207b is arranged to face the folding header 37.

(Configuration of second plane part)
The second flat portion 207A is a portion of the fin main body 207 disposed between adjacent flat tube insertion portions 209 in the Z direction, excluding the uneven portion 211 and the fin pitch defining portion 215.
Of the first and second surfaces 207a, 207b, the first and second surfaces 207a, 207b that constitute the second plane portion 207A are perpendicular to the X direction, and are perpendicular to the Y direction and Z direction. It is a plane parallel to the surface.
A portion of the second plane portion 207A located on one side in the Y direction constitutes one end portion 206A of the fin 206.

(Configuration of flat tube insertion part)
A plurality of flat tube insertion portions 209 are formed in the fin body 207. The plurality of flat tube insertion sections 209 are arranged at intervals in the Z direction. The flat tube insertion portion 209 extends from one side to the other side in the Y direction. The flat tube insertion portion 209 has a distal end portion 209A disposed on the other side in the Y direction, and a rear end portion 209B disposed on one side in the Y direction.
The distal end portion 209A is closed and restricts the position of the second end portion 41E of the flat tube 41. The rear end portion 209B is open from the viewpoint of inserting the flat tube 41.

The rear end side of the flat tube insertion section 209 is open for inserting the flat tube 41 into the flat tube insertion section 209. The flat tube insertion portion 209 accommodates the flat tube 41 inserted from the first end 41D side.
The shape of the tip portion 209A is such that the outer peripheral surface of the second end portion 41E and the fin main body 207 that partitions the tip portion 209A come into surface contact. That is, when the second end 41E is circular, the tip 209A has a circular shape that makes surface contact with the second end 41E, and when the second end 41E is elliptical, the tip 209A has a circular shape that makes surface contact with the second end 41E. The shape of 209A is an ellipse that makes surface contact with the second end 41E.
With such a configuration, it is possible to increase the contact area between the flat tube 41 and the fin main body 207, so it is possible to improve the thermal conductivity between the flat tube 41 and the fin 206. can.

(Configuration of uneven parts)
The uneven portion 211 is formed on the fin main body 207 located between the flat tube insertion portions 209 adjacent to each other in the Z direction. The periphery of the uneven portion 211 is surrounded by a second flat portion 207A.
The uneven portion 211 is formed by alternately arranging peaks and valleys that protrude in a direction away from the first surface 207a of the second plane portion 207A. The uneven portions 211 are arranged at intervals in the Z direction.
By having the uneven portion 211 configured in this way, it is possible to increase the area of the fin body 207 and improve the heat transfer coefficient on the air side, so that the heat between the air and the fin body 207 can be improved. Exchange efficiency can be increased.

(Configuration of communication part)
The communication portion 213 is a portion of the fin body 207 that is disposed on the other side in the Y direction from the 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.

(Configuration of first plane part)
The first plane portions 207B are arranged on both sides of the condensed water guide portion 217 so as to sandwich the condensed water guide portion 217 from the Y direction.
Among the first and second surfaces 207a and 207b, the surface forming the first plane portion 207B is perpendicular to the X direction and parallel to the Y direction and the Z direction.
A portion of the first plane portion 207B located on the other side in the Y direction constitutes the other end portion 206B of the fin 206.
A surface of the second surface 207b that constitutes one end 206A of the fin 206 and a surface that constitutes the other end 206B of the second surface 207b are arranged on the same plane.

(Configuration of Condensed Water Guide Section)
The condensed water guide portion 217 is bent in a direction intersecting with the first surface 207a of the first flat portion 207B and protrudes toward 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 convex portion 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 portion 207B toward the first surface 207a.

(Configuration of fin pitch regulation part)
The fin pitch defining portion 215 is formed between the rear end portions of the flat tube insertion portions 209 that are adjacent to each other in the Z direction. The fin pitch defining portion 215 is arranged on one side of the uneven portion 211 in the Y direction.

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.

(Cutting process performed when manufacturing multiple fins)
Here, a cutting process performed when manufacturing a plurality of fins 206 will be described with reference to FIGS. 28 to 30. In FIGS. 28 to 30, the same components as those of the structure shown in FIG. 23 are given the same reference numerals. In FIGS. 28 and 30, Cp indicates a position (hereinafter referred to as "cutting position Cp") at which the structure shown in FIG. 28 is cut in the cutting process.

The fins 206 configured as described above are obtained by pressing a single plate material, cutting the structure 220 (see FIG. 28) in which a plurality of fins 206 are connected in the left-right direction, and cutting the structure 220 (see FIG. 28) to form a plurality of fins 206. Manufactured by cutting into pieces.

(Effect of arranging the second surfaces of both ends of the fin on the same plane)
As described above, among the second surfaces 207b, the surface forming one end 206A of the fin 206 and the surface forming the other end 206B are arranged on the same plane.
With this configuration, in the cutting process of the structure 220 that is performed after manufacturing the structure 220 in which the plurality of fins 206 are connected by pressing the plate material (base material of the plurality of fins 206), the cutting device is not used. It becomes possible to bring the second surface 207b corresponding to the cutting position Cp into contact with the upper surface of the stage. This allows the structure 220 to be placed on the stage in a stable state, so that the structure 220 can be cut with high precision.

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

The heat exchanger 205 configured as described above is used as a condenser and radiates heat to the outside during cooling operation, and is used as an evaporator and absorbs heat from the outside during heating operation.

(Effect of heat exchanger)
According to the heat exchanger 205 of the first embodiment, the condensed water guide portion 217 formed in the communication portion 213 is configured with the convex portion 218 protruding from the first surface 207a forming the first plane portion 207B. By doing so, it is possible to guide the condensed water in the direction from the upper side to the lower side along the first and second surfaces 207a and 207b forming the convex portion 218 while suppressing the obstruction of the flow of the condensed water. can.
Further, by providing the convex portion 218 having the above structure, it is possible to improve the strength of the communication portion 213. Thereby, it is possible to suppress the occurrence of fin breakage in the portion of the fin 206 that faces the flat tube insertion portion 209 in the Y direction (the portion where the strength of the fin 206 is weak).
Furthermore, by having the convex portion 218 configured as described above, it is possible to increase the surface area of the condensed water guide portion 217 and improve the heat transfer coefficient on the air side. Thereby, the heat exchange efficiency between the condensed water guide section 217 and the air can be increased.

(Effect of first heat exchanger unit)
By providing the heat exchanger 205 with excellent drainage performance of condensed water described above, the first heat exchanger unit 201 can be stably operated.

(Effects of refrigeration cycle equipment)
By providing the first and second heat exchanger units 201 and 203 described above, the performance of the refrigeration cycle device 200 can be improved and the refrigeration cycle device 200 can be stably operated.

<Sixth embodiment>
A heat exchanger 230 according to the sixth embodiment will be described with reference to FIGS. 31 and 32. In FIG. 31, the same components as those of the structure shown in FIG. 23 are given the same reference numerals. In FIGS. 31 and 32, the same components are denoted by the same reference numerals.

(Overall configuration of heat exchanger)
The heat exchanger 230 is configured similarly to the heat exchanger 205 except that it includes a plurality of fins 231 instead of the plurality of fins 206 that constitute the heat exchanger 205 of the fifth embodiment.

The fin 231 is configured in the same manner as the fin 206 except that it has a communication section 233 instead of the communication section 213 that constitutes the fin 206.
The communication part 233 is configured similarly to the communication part 213 except that it has a condensed water guide part 235 instead of the condensed water guide part 217 (convex part 218) formed in the communication part 213.

(Configuration of Condensed Water Guide Section)
The condensate guide portion 235 is composed of an uneven portion 236 that protrudes from the first surface 207a that constitutes 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.

The uneven portion 236 is bent in a direction crossing the first plane portion 207B, extends continuously in the Z direction, and has a cross-sectional shape when cut along a plane perpendicular to the Z direction (as shown in FIG. 32). In this case, the W-shape) is uniform in the Z direction.

(Effect of heat exchanger)
By using the uneven portion 236 configured as described above 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 condensation water guide portion 235, it is possible to improve the strength of the communication portion 233, thereby preventing fin breakage from occurring in the portion of the fin 231 that faces 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 a single protrusion 218. This makes it possible to increase the efficiency of heat exchange between the condensed water guide portion 235 and the air.

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.

(Overall configuration of heat exchanger)
The heat exchanger 240 has the same configuration as 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.

Fin 241 is configured similarly to fin 206, except that it has a communication portion 243 instead of the communication portion 213 that constitutes fin 206.

(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 part 245 is a stepped part 246 and includes a first part 243A and a second part 243B that constitute the first plane part 207B, a connecting part 248, and the condensed water guide part 245.

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

The second portion 243B constitutes the other end 206B of the fin 206 of the first plane portion 207B, and extends continuously in the Z direction.
The second portion 243B is located at a position offset to the other side in the X direction from the position where the first portion 243A is formed. The first and second surfaces 207a and 207b forming the second portion 243B are parallel to the first and second surfaces 207a and 207b forming the first portion 243A.

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 connecting 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 such that a step is formed in the X direction.

(Effect of heat exchanger)
By using the stepped portion 246 having such a configuration as the condensed water guide portion 245, the flow of condensed water is inhibited and the first and second surfaces 207a and 207b constituting the connecting portion 248 are Condensed water can be guided along the line in a direction from the upper side to the lower side.
In addition, by configuring the condensed water guide section 245 with the stepped section 246, it is possible to improve the strength of the communication section 243, so that the portion of the fin 241 facing the flat tube insertion section 209 in the Y direction It is possible to suppress the occurrence of fin breakage in the weakly strong portions of 241).
Furthermore, by configuring the condensed water guide section 245 with the stepped section 246, it is possible to increase the surface area of the condensed water guide section 245 and improve the heat transfer coefficient on the air side. Thereby, the heat exchange efficiency between the condensed water guide section 245 and the air can be increased.

<Eighth embodiment>
A heat exchanger 250 according to the eighth embodiment will be described with reference to FIGS. 35 to 37. In FIG. 35, the same components as those of the structure shown in FIG. 23 are given the same reference numerals. In FIGS. 35 to 37, the same components are denoted by the same reference numerals.

(Overall configuration of heat exchanger)
The heat exchanger 250 is configured similarly to the heat exchanger 205 except that it includes a plurality of fins 251 instead of the plurality of fins 206 that constitute the heat exchanger 205 of the fifth embodiment.

(Fin configuration)
The fin 251 has a base portion 252 that protrudes toward the first surface 207a of the first flat portion 207B around the flat tube insertion portion 209, and the height _H1 of the 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 the 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.

(Effect of heat exchanger)
In this way, the height _H1 of the convex part 218 in the X direction and the height _H2 of the pedestal part 252 are made equal, and the convex part 218 and the pedestal part 252 are connected at the position of the tip 218A of the convex part 218. By doing so, the first plane part 207B is not disposed between the pedestal part 252 and the convex part 218 in the Y direction. This makes it possible to make the first plane part 207B discontinuous in the Z direction between the pedestal part 252 and the convex part 218, thereby preventing fin breakage between the pedestal part 252 and the convex part 218. The occurrence can be suppressed.

In the eighth embodiment, the case where the convex part 218 (condensed water guide part 217) and the pedestal part 252 are connected is described as an example. The portion 238 and the base portion 252 may be connected.

<First modification of the eighth embodiment>
With reference to FIG. 38, a heat exchanger 260 according to a first modification of the eighth embodiment will be described. In FIG. 38, the same components as those of the structure shown in FIG. 35 are given the same reference numerals.

(Overall configuration of heat exchanger)
The heat exchanger 260 has the same configuration as 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.

(Fin configuration)
The fin 261 has the same structure as the fin 251 except that it has a pedestal part 263 instead of the pedestal part 252 that constitutes the fin 251.

(Composition of pedestal part)
The pedestal part 263 has the same structure as the pedestal part 252, except that the upper side of the part connected to the convex part 218 is inclined diagonally downward from the pedestal part 263 toward the convex part 218.

(Effect of heat exchanger)
By having the pedestal section 263 having such a configuration, it is possible to suppress condensed water from accumulating on the upper side of the part where the pedestal section 263 and the convex section 218 are connected. This can prevent the flow of water from being obstructed.

<Second modification of the eighth embodiment>
With reference to FIG. 39, a heat exchanger 270 according to a second modification of the eighth embodiment will be described. In FIG. 39, the same components as those of the structure shown in FIG. 38 are given the same reference numerals.

(Overall configuration of heat exchanger)
The heat exchanger 270 has the same configuration as the heat exchanger 260 except that it has fins 271 instead of the fins 261 that configure the heat exchanger 260 according to the first modification of the eighth embodiment. .

(Fin configuration)
The fin 271 has the same structure as the fin 261 except that it has a pedestal section 273 instead of the pedestal section 263 that constitutes the fin 261.

(Composition of pedestal part)
The pedestal part 273 has the same structure as the pedestal part 263, except that the upper and lower sides of the portion connected to the convex part 218 are inclined diagonally downward from the pedestal part 273 toward the convex part 218.

(Effect of heat exchanger)
By having the pedestal part 273 having such a configuration, not only the upper side of the part where the pedestal part 273 and the convex part 218 are connected, but also the lower part of the back side of the pedestal part 273 (the back side of the page of FIG. 39) Since it is possible to suppress the condensed water from accumulating in the pedestal 273, it is possible to increase the effect of suppressing the pedestal portion 273 from obstructing the flow of the condensed water.

<Ninth embodiment>
A refrigeration cycle device 280 according to a ninth embodiment will be described with reference to FIG. 40. In FIG. 40, solid line arrows indicate the direction in which the refrigerant flows during heating operation, and dotted line arrows indicate the direction in which the refrigerant flows during cooling operation. In FIG. 40, the same components as those of the structure shown in FIG. 21 are given the same reference numerals.

(Overall configuration of refrigeration cycle equipment)
The refrigeration cycle device 280 has first and second heat exchanger units 281, 283 instead of the first and second heat exchanger units 201, 203 that constitute the refrigeration cycle device 200 of the second embodiment. The configuration is similar to that of the refrigeration cycle device 200 except for the following.
The first heat exchanger unit 281 has the same configuration as the first heat exchanger unit 201 except that it includes 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 it includes a heat exchanger 285 instead of the heat exchanger 205.

(Overall configuration of heat exchanger)
The heat exchanger 285 will be described with reference to FIGS. 40 to 42. In FIGS. 41 and 42, the Z direction indicates the first direction. In FIG. 41, the X direction indicates the direction in which the flat tube 41 extends orthogonally to the Z direction. In FIG. 42, the Y direction is a second direction perpendicular to the X and Z directions (the width direction of the flat tube 41 when the flat tube 41 is attached to the fin 290), and P is the direction in which air flows ( (hereinafter referred to as "direction P").
In addition, in this embodiment, the following description will be given as an example of the Z direction, taking as an example a case where the Z direction is an up-down direction (vertical direction).

The heat exchanger 285 has the same configuration as the heat exchanger 205 except that it has a plurality of fins 290 instead of the plurality of fins 206 that constitute the heat exchanger 205 described in the second embodiment.

(Overall configuration of fins)
The plurality of fins 290 will be described with reference to FIGS. 41 to 46. In FIGS. 43 to 46, the same components as those of the structure shown in FIGS. 41 and 42 are given the same reference numerals.

The plurality of fins 290 are arranged at a predetermined pitch in the X direction.
The fin 290 has a fin main body 291 instead of the fin main body 207 that constitutes the fin 206 described in the fifth embodiment, and further includes a plurality of heat conductive parts 305, a plurality of first fin pitch defining parts 307, and a fin main body 291. It has the same configuration as the fin 206 except that it includes a plurality of second fin pitch defining sections 308 .

(Configuration of fin body)
The fin main body 291 is plate-shaped and extends in the Z direction. The fin main body 291 has first and second surfaces 291a and 291b arranged in the X direction.
The first surface 291a is arranged to face the entrance/exit header 35. The second surface 291b is a surface located on the opposite side of the first surface 291a. The second surface 291b is arranged to face the folding header 37. The fin main body 291 is plate-shaped and has a communication portion 303 extending in the Z direction.

(Configuration of heat conduction part)
The heat conduction portion 305 is formed around the flat tube insertion portion 209 so as to rise toward the first surface 291a. The heat conduction section 305 protrudes in the X direction. In the state in which the flat tube 41 is inserted into the flat tube insertion portion 209, the inner circumferential surface 305a of the heat conduction section 305 is in surface contact with the outer circumferential surface 41b of the flat tube 41. The height of the heat conductive portion 305 in the X direction is such that when a plurality of fins 290 are arranged in the X direction, it does not come into contact with the fins 290 arranged on the first surface 291a side.

(Effect of heat conduction part)
By having the heat conduction part 305 configured in this way, it is possible to increase the contact area between the flat tube 41 and the plurality of fins 290. Thereby, thermal conductivity between the flat tube 41 and the plurality of fins 290 can be improved.
In addition, by setting the height of the heat conduction part 305 in the X direction to a height at which the heat conduction part 305 does not come into contact with the fins 290 arranged on the first surface 291a side, the first and second fin pitch regulations can be adjusted. After defining the fin pitch using the portions 307 and 308, the thermal conductivity between the flat tube 41 and the fins 290 can be improved.

(Configuration of the first fin pitch defining portion)
The first fin pitch defining 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 defining portion 307 is disposed on one side of the uneven portion 211 in the Y direction.

The first fin pitch defining portion 307 is formed by bending a part of the fin main body 291 downward (to one side in the Z direction). The first fin pitch defining portion 307 is formed to protrude toward the first surface 291a.
The first fin pitch defining portion 307 determines the pitch (fin pitch) of the fins 290 arranged in the X direction by coming into contact with the second surface 291b of the fins 290 arranged on one side in the X direction. Keep it at the desired value. It is preferable that the first fin pitch defining portion 307 has an L-shape, for example.

(Effect of forming the first fin pitch defining part on the rear end side of the flat tube insertion part)
In this way, by forming the first fin pitch defining portions 307 on the rear end sides of the flat tube insertion portions 209 that are adjacent to each other, it is possible to prevent the fin pitch from occurring in the initial stage when inserting the flat tube 41 into the flat tube insertion portion 209. Deformation and buckling of the fins 290, which tend to occur easily, can be suppressed.

(Effect of making the first fin pitch defining part L-shaped)
In this way, by making the first fin pitch defining part 307 L-shaped, the first fin pitch defining part 307 is shaped like an I, for example. 307 can increase the probability of contact with the second surface 291b.
Further, by making the first fin pitch defining portion 307 L-shaped, it is possible to increase the contact area between the first fin pitch defining portion 307 and the second surface 291b, so that the fin pitch can be increased. Can be maintained stably.

(Configuration of second fin pitch specifying section)
The second fin pitch specifying section 308 is a flat tube located above the first fin pitch specifying section 307 among the two flat tube insertion sections 209 that sandwich the first fin pitch specifying section 307 in the Z direction. It is arranged around the insertion section 209.
Specifically, the second fin pitch defining portion 308 is located below the flat tube insertion portion 209 and near the tip portion 209A (closer to the rear end of the flat tube insertion portion 209 than the tip portion 209A, and 209A side).
The second fin pitch defining portion 308 is formed by bending a portion of the fin body 291 downward (one side in the Z direction) and protruding toward the first surface 291a.

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, maintains 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 enables the fin pitch to be maintained at a desired value.
The second fin pitch defining portion 308 is preferably, for example, L-shaped. By forming the second fin pitch defining portion 308 in an L-shape, it is possible to obtain the same effect as the first fin pitch defining portion 307, which is L-shaped as described above.

The heat exchanger 285 configured as described above is used as a condenser and radiates heat to the outside during cooling operation, and is used as an evaporator and absorbs heat from the outside during heating operation.

(Effect of heat exchanger)
As described above, by bending a portion of the fin body 291 downward to form the first and second fin pitch defining portions 307 and 308, a portion of the fin body 291 is bent in the Y direction. Compared to the case, it is possible to suppress the first and second fin pitch defining portions 307 and 308 from becoming resistance bodies for air flowing in the P direction (direction from the other side to the one side in the second direction). Therefore, air pressure loss can be suppressed.

In addition, by arranging the first fin pitch regulating portion 307 on the rear end side of the flat tube insertion portion 209 and arranging the second fin pitch regulating portion 308 on the tip end portion 209A side of the flat tube insertion portion 209, it is possible to arrange the first and second fin pitch regulating portions 307, 308 at positions separated in the Z direction and Y direction. This makes it possible to stably regulate the fin pitch of the multiple fins 290 arranged in the X direction.

Furthermore, the outer shape of the second end 41E of the flat tube 41 is made circular or elliptical, and the shape of the tip 209A of the flat tube insertion part 209 that accommodates the second end 41E is changed to the second end 41E of the flat tube 41. By forming the outer circumferential surface 41b of the end portion 41E of 2 and the fin body 291 into surface contact, it is possible to increase the contact area between the flat tube 41 and the fin body 291. Thereby, the thermal conductivity between the flat tube 41 and the fins 290 can be improved.

That is, the fin pitch can be stably defined while suppressing air pressure loss, and the thermal conductivity between the flat tube 41 and the fins 290 can be improved.
Furthermore, by not forming the first and second fin pitch defining portions 307 and 308 in the communication portion 303 extending in the first direction (Z direction), condensed water drained in the first direction (Z direction) Since the flow is no longer obstructed by the first and second fin pitch defining sections 307 and 308, good drainage performance can be maintained.

Furthermore, by bending a part of the fin body 291 downward, a first fin pitch defining section 307 is formed, and in the Z direction, two flat tube inserting sections 209 sandwiching the first fin pitch defining section 307 are formed. By forming the second fin pitch defining part 308 around the flat tube insertion part 209 located above the first fin pitch defining part 307, the positions for defining the fin pitch can be set at equal intervals in the Z direction. Therefore, the fin pitch can be stably defined.

(Effect of first heat exchanger unit)
According to the first heat exchanger unit 281, by including the heat exchanger 285 described above, the performance of the first heat exchanger unit 281 is improved and the first heat exchanger unit 281 is stabilized. It can be operated by
Note that the second heat exchanger unit 283 including the heat exchanger 285 can also obtain the same effects as the first heat exchanger unit 281.

(Effects of refrigeration cycle equipment)
By including the first and second heat exchanger units 281 and 283 described above in the refrigeration cycle device 280, it is possible to improve the performance of the refrigeration cycle device 280 and to operate the refrigeration cycle device 280 stably. can.

(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.

The fin 320 forms a first fin pitch defining part 307 by bending a part of the fin main body 291 upward, and also includes two flat tube insertion parts 209 that sandwich the first fin pitch defining part 307 in the Z direction. The structure is the same as that of the fin 290 described above, except that the second fin pitch defining part 308 is formed around the flat tube insertion part 209 located below the first fin pitch defining part 307. has been done.

(Effect of modified fins)
In this way, the first fin pitch defining portion 307 is formed by bending a part of the fin main body 291 upward, and the two flat tube insertion portions 209 sandwich the first fin pitch defining portion 307 in the Z direction. By forming the second fin pitch defining part 308 around the flat tube insertion part 209 located below the first fin pitch defining part 307, the position defining the fin pitch can be made equal in the Z direction. It is possible to arrange them at intervals. Thereby, the fin pitch can be stably defined.

Although the 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 may be made within the scope of the gist of the present disclosure described within the scope of the claims. It is possible to transform and change.

<Additional notes>
Heat exchanger 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190, 205, 230, 240, 250, 260, 270 described in each embodiment , 285, heat exchanger units (first heat exchanger unit 18, 201, 281 and second heat exchanger unit 23, 203, 283), and refrigeration cycle apparatus 10, 200, 280, for example, as follows. It is understood as follows.

(1) The heat exchanger 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190 according to the first aspect exchanges heat with air and refrigerant. The heat exchangers 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190 have a flat outer shape and are arranged in one direction (X direction). A plurality of flat tubes 41 extending in the width direction (Y direction), extending in the one direction (X direction) and having a plurality of flow paths 41A through which the refrigerant flows, and accommodating the plurality of flat tubes 41. In this state, the plurality of fins 42 arranged in the extending direction (X direction) of the plurality of flat tubes 41 and one end 41B of the plurality of flat tubes 41 are arranged inside. a header 43 connected to the flat tube 41 and into which the refrigerant flows, the header 43 having a cylindrical shape extending in the vertical direction (Z direction), and defining a columnar internal space 53; a header main body 45; is accommodated in the header main body 45 and extends in the vertical direction (Z direction), and the refrigerant is allowed to flow in the upper and lower ends of the internal space 53 in the extending direction (X direction). A partition plate 47 that divides the internal space 53 into a first space 54 and a second space 55 in which one end 41B of the plurality of flat tubes 41 is arranged, and a partition plate 47 arranged below the first space 54. and has nozzle parts 49 and 62 including blow-off ports 49A and 62A that blow out the refrigerant supplied from the outside of the header 43 toward the bottom surface 45a (first bottom surface 45aa) of the header main body 45, Refrigerant flow portions 54A, which are part of the first space 54, are formed on both sides of the nozzle portions 49 and 62 in the width direction (Y direction), respectively.

By having the nozzle parts 49 and 62 configured as described above, the refrigerant blown out from the blow-off ports 49A and 62A collides with the bottom surface 45a (first bottom surface 45aa) of the header main body 45 in the width direction (Y direction). This makes it possible to reduce the difference in the state of the refrigerant between. As a result, the refrigerant with a small difference in state in the width direction (Y direction) is directed from the first space 54 to the second space 55 (the space where one end 41B of the plurality of flat tubes 41 is arranged). Therefore, a circulating flow of refrigerant (a flow descending through the first space 54 and ascending through the second space 55) is created within the header 43 without depending on the flow rate of the refrigerant introduced into the header 43. By forming a plurality of flow paths 41A formed in the width direction (Y direction) of each flat tube 41, while suppressing the complexity of the manufacturing process and suppressing bias in refrigerant distribution to each flat tube 41. It is also possible to suppress unevenness in refrigerant distribution.

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

By providing the first refrigerant guide section 73 having such a configuration, the refrigerant blown out from the outlet ports 49A, 62A of the nozzle sections 49, 62 is guided to the second space 55, and the refrigerant is guided to the second space 55. By causing the refrigerant to collide with the inner wall surface 45b of the header body 45 that partitions the header body 55, it is possible to reduce the difference in the state of the refrigerant in the width direction (Y direction).
Further, when the refrigerant is a gas-liquid two-phase refrigerant and the flow rate of the refrigerant introduced into the header main body 45 is small, the refrigerant is separated into gas and liquid in the first space 54, and the first space 54 becomes a gas-liquid phase refrigerant. It becomes possible to suppress the refrigerant from rising. That is, it is possible to suppress the formation of a circulating flow of refrigerant within the header body 45.

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

In this way, 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. can.

(4) The heat exchanger 90, 100, 180, 190 according to the fourth aspect is the heat exchanger 90, 100, 180, 190 according to any one of (1) to (3), and 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 include a second refrigerant guide portion 93 provided on the second bottom surface 45ab and having a second guide surface 93a that guides the refrigerant in a direction from below to above the second space 55.

By providing the second refrigerant guide section 93 having such a configuration, the refrigerant having a small difference in state in the width direction generated by colliding with the first bottom surface 45aa of the header body 45 is directed to the second space. 55 can be guided in a direction from below to above.

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

In this way, by making the second guide surface 93a a concave curved surface that is concave in the direction away from the lower end of the partition plate 47, the refrigerant with a small difference in state in the width direction (Y direction) is directed to the second space 55. It can be easily guided from below to above.

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

By providing the third refrigerant guide section 83 having such a configuration, the refrigerant can be guided in the direction from the first space 54 toward the second space 55 by the third guide surface 83a.

(7) The heat exchanger 80 according to the seventh aspect is the heat exchanger 80 according to (6), in which the third refrigerant guide section 83 extends in the width direction (Y direction) of the partition plate 47. It may be a cylindrical member.

In this way, by using the columnar member extending in the width direction of the partition plate 47 as the third refrigerant guide portion 83, the third guide surface 83a (outer circumferential surface of the columnar member) allows the third refrigerant to flow from the first space 54 to the third refrigerant guide portion 83. The refrigerant can be guided in the direction toward the space 55 of No. 2.

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

For example, if the nozzle parts 49, 62 are arranged at a position higher than 1/2 of the height H of the header body 45, the air outlet 49A, 62A of the nozzle part 49, 62 is connected to the bottom surface (first bottom surface) of the header body 45. 45aa) becomes too long, the flow of the refrigerant blown out from the blow-off ports 49A and 62A may be attenuated, making it difficult to form a circulating flow of the refrigerant within the header 43.
Therefore, by arranging the nozzle parts 49, 62 at a position lower than 1/2 of the height H of the header body 45, the distance from the air outlet 49A, 62A to the bottom surface (first bottom surface 45aa) of the header body 45 can be increased. Since it becomes possible to shorten the length, it becomes easier to form a circulating flow of the refrigerant within the header 43.

(9) The heat exchanger 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190 according to the ninth aspect includes (1) to (7). The heat exchanger 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190 according to any one of the above, wherein the nozzle part 49, 62 may be arranged between the flat tube 41F placed at the bottom and the flat tube 41S placed second from the bottom among the plurality of flat tubes 41.

In this way, by arranging the nozzle portions 49 and 62 between the flat tube 41F placed at the bottom and the flat tube 41S placed second from the bottom, the circulating flow of the refrigerant within the header 43 is controlled. Can be easily formed.
In addition, when using the heat exchangers 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190 as a condenser, The refrigerant (liquid phase refrigerant) flowing into the header 43 can be easily discharged to the outside of the header.

(10) The heat exchanger 110, 120, 130, 190 according to the tenth aspect is the heat exchanger 110, 120, 130, 190 described in any one of (1) to (9). 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 one end of the plurality of flat tubes 41 is arranged to face the partition plate 47, and one end of the plurality of flat tubes 41 is arranged to face the partition plate 47. The distance Ds1 from one end of the tube 41F to the partition plate 47 may be longer than the distance Ds2 from one end of the other flat tubes 41, 41 to the partition plate 47.

In this way, 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 is calculated as the distance Ds1 from the one end 41a of the other flat tubes 41 to the partition plate 47. By making it longer than Ds2, it becomes possible to increase the cross-sectional area of the refrigerant flow path formed between the partition plate 47 and one end 41Fa of the flat tube 41F arranged at the bottom.
This makes it possible to reduce the degree of contracted flow at the height of the flat tube 41F, making it difficult for the refrigerant flow to separate, so that in the past, liquid phase refrigerant would flow in due to the effect of separation (contracted flow). The liquid phase refrigerant is now easily supplied even to the flat tubes 41F, which may otherwise have been difficult to supply, and as a result, the refrigerant distribution to each flat tube 41 can be equalized.

(11) The heat exchangers 110, 120 according to the eleventh aspect are the heat exchangers 110, 120 of (10), in which one end of the flat tube 41F disposed at the bottom is connected to the other flat tube 41F. The pipes 41 and 41S may be arranged so as to be retreated in the direction from the first space 54 to the second space 55 relative to the position of one end of the pipes 41 and 41S.

In this way, one end 41Fa of the flat tube 41F disposed at the bottom is placed at a position retreating from the position of one end 41a of the other flat tubes 41 in the direction from the first space 54 toward the second space 55. By arranging them, the cross-sectional area of the refrigerant flow path formed between the partition plate 47 and one end 41Fa of the flat tube 41F arranged at the bottom can be increased.

(12) The heat exchanger 130, 190 according to the twelfth aspect is a heat exchanger 130, 190 according to any one of (10) and (11), in which 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 the direction from the second space 55 toward the first space 54.

In this way, the lower end 133A of the partition plate 133 facing the one end 41Fa of the flat pipe 41F arranged at the bottom among the plurality of flat pipes 41 is moved in the direction from the second space 55 toward the first space 54. By arranging the refrigerant at a shifted position, the cross-sectional area of the refrigerant flow path formed between the partition plate 133 and one end 41Fa of the flat tube 41F arranged at the bottom can be increased.

(13) The heat exchanger 140, 150, 160, 170, 180, 190 according to the thirteenth aspect is the heat exchanger 140, 150, 160 according to any one of (1) to (12), 170, 180, and 190, which are provided on the inner wall surface 45b of the header body 45 that partitions the second space 55, and which are arranged at the bottom of the plurality of flat tubes 41. A rectifying member 143, 163, 173 may be provided, which is disposed below one end 41B of the header body 45 and rectifies the refrigerant from the bottom surface 45a of the header body 45 toward one end of the flat tube 41F disposed at the bottom. good.

By providing the rectifying members 143, 163, and 173 with such a configuration, it is possible to prevent the liquid phase refrigerant from flowing into the flat pipe 41F, which conventionally had a possibility of being difficult to flow into due to the influence of separation (contraction). The liquid phase refrigerant is easily supplied, and as a result, the refrigerant distribution to each flat tube 41 can be equalized.

(14) The heat exchanger 140, 150 according to the fourteenth aspect is the heat exchanger 140, 150 of (13), in which the rectifying member 143 is one of the flat tubes 41F arranged at the bottom. is arranged at a position away from the end 41B of the header main body 45, extends in the direction toward the partition plate 47 from the inner wall surface 45b of the header main body 45, and the amount of protrusion from the inner wall surface 45b of the header main body 45 is equal to the one end 41B. The baffle plate 145 may have a protrusion amount equal to that of the baffle plate 145.

In this way, by using the baffle plate 145 having the above configuration as the rectifying member 143, the flow of the refrigerant is separated in the stage upstream of one end 41B of the flat tube 41F disposed at the bottom, so that the flow of the refrigerant is uniformly separated. It becomes possible to rectify the flow of the refrigerant at the end of the flat tube 41F arranged at the bottom.
As a result, liquid phase refrigerant can be easily supplied to the flat tubes 41F, to which liquid phase refrigerant might have been difficult to flow into due to the effect of separation (condensation), and as a result, each flat tube 41 The refrigerant distribution can be equalized.

(15) The heat exchanger 160 according to the fifteenth aspect is the heat exchanger 160 according to (13), in which the rectifying member 163 is arranged at one end 41B of the flat tube 41F arranged at the bottom. is arranged below the one end 41B so as to be in contact with the lower surface of the header body 45, extends in a direction from the inner wall surface 45b of the header body 45 toward the partition plate 47, and protrudes from the inner wall surface 45b of the header body 45. The block 164 may have an amount equal to the amount of protrusion of the one end portion 41B.

In this way, by using the block 164 having the above configuration as the rectifying member 163, the flow of the refrigerant is separated in the stage before one end 41B of the flat tube 41F arranged at the bottom, and It becomes possible to rectify the flow of the refrigerant at the end of the flat tube 41F arranged below.
As a result, liquid phase refrigerant can be easily supplied to the flat tubes 41F, to which liquid phase refrigerant might have been difficult to flow into due to the effect of separation (condensation), and as a result, each flat tube 41 The refrigerant distribution can be equalized.

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

By having the curved surface 174a having such a configuration, the refrigerant can be guided above the second space 55 without flow separation.

(17) The heat exchanger 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190 according to the seventeenth aspect includes (1) to (16) The heat exchanger 27, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150, 160, 170, 180, 190 according to any one of the above, wherein the first space a perforated plate provided between the header main body 45 and the partition plates 47, 133 that partition 54, and arranged in a portion of the first space 54 located above the nozzle parts 49, 62; 51 may be provided.

By providing a porous plate 51 configured in this way, it is possible to suppress the movement of gas (gas refrigerant) that flows 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.

(18) The heat exchanger 27 according to the eighteenth aspect is the heat exchanger 27 according to any one of (1) to (17), in which the air outlet 49A is a circular hole. , the partition plate 47 is arranged on one side in the width direction (Y direction), and has one lower end portion 47A whose lower end reaches the bottom surface 45a of the header main body 45, and the other side in the width direction (Y direction). the other lower end 47B which is arranged and whose lower end reaches the bottom surface 45a of the header main body 45; and a notch formed between the one lower end 47A and the other lower end 47B and through which the refrigerant flows. 47C.

In this way, when the circular hole is used as the air outlet 49A, the refrigerant flows from the first space 54 to the It is distributed to the space 55 of No. 2. At this time, the lower end portions 47A and 47B can prevent the refrigerant from flowing back from the second space 55 to the first space 54.

(19) The heat exchanger 60 according to the nineteenth aspect is the heat exchanger 60 according to any one of (1) to (17), in which the outlet 62A is the nozzle part 62. The total width W2 of the two refrigerant flow portions 54A, which are shaped like grooves extending in the width direction (Y direction) and arranged on both sides of the nozzle portion 62 in the width direction (Y direction), is equal to the width of the nozzle portion 62. It may be smaller than the value of the width W1 of 62.

In this way, by making the outlet 62A into a groove shape extending in the width direction (Y direction) of the nozzle part 62, the state of the refrigerant in the width direction (Y direction) can be improved compared to a case where the outlet has a circular shape. The difference can be further reduced.
Further, the total value (=2×W2) of the width W2 of the pair of refrigerant flow portions 54A arranged on both sides of the nozzle portion 62 in the width direction (Y direction) is made smaller than the value of the width W1 of the nozzle portion 62. Therefore, it is possible to reduce the flow path cross-sectional area of the pair of refrigerant flow portions 54A. This makes it possible to suppress the occurrence of a backflow of the refrigerant from below to above in the first space 54 .

(20) The heat exchanger unit (first and second heat exchanger units 18, 23) according to the twentieth aspect is the heat exchanger described in any one of (1) to (19). , blowers (first and second blowers 26, 32 ) and.

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

(21) The refrigeration cycle device 10 according to the twenty-first aspect includes the heat exchanger unit (first and second heat exchanger units 18 and 23) of (20).

By having the heat exchanger unit (first and second heat exchanger units 18 and 23) configured as described above, the heat exchange efficiency of the refrigeration cycle device 10 can be improved.

(22) The heat exchanger 205, 230, 240, 250, 260, 270 according to the 22nd aspect is a heat exchanger 205, 230, 240, 250, 260, 270 that exchanges heat between air and a refrigerant. , has a flat outer shape, has a flow path 41A through which the refrigerant flows inside, has a first end 41D disposed on one side in the width direction, and a first end 41D disposed on the other side in the width direction. A plurality of flat tubes 41 having two end portions 41E, and a plurality of fins 206 arranged at a predetermined pitch in the extending direction (X direction) of the flat tubes 41 while housing the plurality of flat tubes 41. , 231, 241, 251, 261, 271, and the plurality of fins 206, 231, 241, 251, 261, 271 are plate-shaped and arranged in the extending direction (X direction). a fin body 207 including a first surface 207a and a second surface 207b disposed on the opposite side of the first surface 207a; A plurality of them are arranged at intervals in the vertical direction (Z direction) perpendicular to the vertical direction (Z direction), and from one side in the horizontal direction (Y direction) perpendicular to the vertical direction (Z direction) and the extension direction (X direction). A flat tube insertion section 209 extending to the other side and accommodating the flat tube 41 inserted from the second end 41E side, and the other side in the left-right direction (Y direction) than the plurality of flat tube insertion sections 209. communicating portions 213, 233, and 243 that are arranged on the sides and continuously extend in the vertical direction (Z direction), and the communicating portions 213, 233, and 243 are arranged in the vertical direction (Z direction) and in the vertical direction (Z direction). The communication portions 213, 233, 243 include a first plane portion 207B parallel to the left-right direction (Y direction), and the communication portions 213, 233, and 243 include the first plane portion 207B that is bent in a direction crossing the first plane portion 207B. A condensed water guide that extends continuously in the vertical direction (Z direction) and has a uniform cross-sectional shape in the vertical direction (Z direction) when cut along a plane perpendicular to the vertical direction (Z direction). Sections 217, 235, and 245 are formed.

By having the condensed water guide sections 217, 235, 245 configured as described above, the first and second condensed water guide sections 217, 235, 245 that constitute the condensed water guide sections 217, 235, 245 can suppress obstruction of the flow of condensed water. Condensed water can be guided from the upper side to the lower side along the surfaces 207a and 207b.
Further, by providing the condensed water guide portions 217, 235, 245 having the above configuration, it is possible to improve the strength of the communication portions 213, 233, 243. As a result, 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 where the strength of the fins 206, 231, 241, 251, 261 is weak) are provided with fins. It is possible to suppress the occurrence of folding.
Furthermore, by having the condensed water guide parts 217, 235, 245 configured as described above, it is possible to increase the surface area of the condensed water guide parts 217, 235, 245 and improve the thermal conductivity on the air side. . Thereby, the heat exchange efficiency between the condensed water guide portions 217, 235, 245 and the air can be increased.

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

In this way, by configuring the condensed water guide section 217 formed in the communication section 213 with the convex section 218 that protrudes from the first surface 207a that constitutes the first plane section 207B, the flow of condensed water can be prevented. The condensed water can be guided in a direction from the upper side to the lower side along the first and second surfaces 207a and 207b forming the convex portion 218 while suppressing the condensed water.
Further, by providing the convex portion 218 having the above structure, it is possible to improve the strength of the communication portion 213. Thereby, it is possible to suppress the occurrence of fin breakage in the portion of the fin 206 that faces the flat tube insertion portion 209 in the Y direction (the portion where the strength of the fin 206 is weak).
Furthermore, by having the convex portion 218 configured as described above, it is possible to increase the surface area of the condensed water guide portion 217 and improve the thermal conductivity on the air side. Thereby, the heat exchange efficiency between the condensed water guide section 217 and the air can be increased.

(24) The heat exchanger 230 according to the 24th aspect is the heat exchanger 230 according to (22), and the condensed water guide portion 235 may be an uneven portion 236 that protrudes from the first surface 207a constituting the first flat surface portion 207B and has 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).

By using the uneven portion 236 having such a configuration as the condensed water guide portion 235, the flow of condensed water is inhibited and the first and second surfaces 207a and 207b forming the uneven portion 236 are Condensed water can be guided along the line in a direction from the upper side to the lower side.
Furthermore, by using the uneven portion 236 as the condensed water guide portion 235, it is possible to improve the strength of the communication portion 233. It is possible to suppress the occurrence of fin breakage in a portion (a portion where the strength of the fin 231 is weak).
Furthermore, by configuring the condensed water guide portion 235 with the uneven portion 236, compared to the case where the condensed water guide portion 217 is configured with one convex portion 218, the surface area of the condensed water guide portion 235 is increased and It becomes possible to improve the thermal conductivity of. Thereby, the heat exchange efficiency between the condensed water guide section 235 and the air can be increased.

(25) The heat exchanger 250 according to the twenty-fifth aspect is the heat exchanger 250 of (23) or (24), in which the flat tube insertion portion 209 is located on the other side in the left-right direction (Y direction). The fin main body 207 is disposed between the distal end portions 209A that are arranged adjacent to each other in the vertical direction (Z direction), and has a distal end portion 209A that accommodates the second end portion 41E. It has a second plane part 207A that is parallel to the vertical direction (Z direction) and the horizontal direction (Y direction), and the flat tube insertion part 209 is surrounded by the second plane part 207A of the second plane part 207A. A pedestal portion 252 protruding toward the first surface 207a side is disposed, and the tip end 218A of the convex portion 218 in the extending direction (X direction) with respect to the first surface 207a of the second plane portion 207A. The height _H1 of the convex part 218 is equal to the height _H2 of the pedestal part 252 in the extending direction (X direction) with respect to the first surface 207a of the second plane part 207A. The convex portion 218 and the pedestal portion 252 may be connected at the position of the tip 218A.

In this way, the height _H1 of the convex part 218 in the X direction and the height _H2 of the pedestal part 252 are made equal, and the convex part 218 and the pedestal part 252 are connected at the position of the tip 218A of the convex part 218. By doing so, the first plane part 207B is not disposed between the pedestal part 252 and the convex part 218 in the left-right direction (Y direction). This makes it possible to make the first plane part 207B discontinuous in the vertical direction (Z direction) between the pedestal part 252 and the convex part 218. The occurrence of fin breakage can be suppressed.

(26) The heat exchanger 260 according to the 26th aspect is the heat exchanger 260 according to (25), and the upper side of the portion of the base portion 263 that is connected to the condensed water guide portion 217 may be inclined obliquely downward from the base portion 263 toward the condensed water guide portion 217.

With this configuration, it is possible to suppress condensed water from accumulating on the upper side of the part where the pedestal part 263 and the condensed water guide part 217 (convex part 218) are connected, so that the pedestal part 263 can prevent condensation. Obstruction of water flow can be suppressed.

(27) The heat exchanger 240 according to the twenty-seventh aspect is the heat exchanger 240 of (22), in which the first plane portion 207B is arranged in the left-right direction (Y direction) of the condensed water guide portion 245. The first portion 243A is disposed on one side of the condensed water guide portion 245 and extends in the vertical direction (Z direction), and the first portion 243A is disposed on the other side of the condensed water guide portion 245 in the horizontal direction (Y direction) and extends in the vertical direction (Z direction). ) and a second portion 243B disposed at a different position from the first portion 243A in the extending direction (X direction), and the condensed water guide portion 245 The stepped portion 246 may be configured by a portion 243A, the second portion 243B, and a connecting portion 248 that connects the first portion 243A and the second portion 243B.

By using the step portion 246 configured in this manner as a condensate water guide portion 245, it is possible to suppress obstruction of the flow of condensate water and to guide the condensate 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 that faces 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, thereby increasing the efficiency of heat exchange between the condensed water guide portion 245 and the air.

(28) The heat exchanger 205, 230, 240, 250, 260 according to the twenty-eighth aspect is the heat exchanger 205, 230, 240, 250 according to any one of (22) to (27), 260, the fins 206, 231, 241, 251, 261 have one end 206A disposed on one side in the left-right direction (Y direction) and the other end 206A disposed on the other side in the left-right direction. The condensed water guide portions 217, 235, 245 are arranged closer to the one end 206A than the other end 206B, and the one end 206A and The second surface 207b constituting the other end 206B may be arranged on the same plane.

With this configuration, a structure in which a plurality of fins 206, 231, 241, 251, 261 are connected by pressing a plate material (base material of the plurality of fins 206, 231, 241, 251, 261) can be obtained. In the cutting process of the structure 220 performed after manufacturing the structure 220, the second surface 207b corresponding to the cutting position Cp is brought into contact with the upper surface of the stage of the cutting device, and the structure 220 is stably placed on the stage. becomes possible. Thereby, the structure 220 can be cut with high precision. That is, the processing accuracy of the fins 206, 231, 241, 251, and 261 can be improved.

(29) The heat exchanger unit (first and second heat exchanger units 201, 203) according to the twenty-ninth aspect is the heat exchanger 205 described in any one of (22) to (28). , 230, 240, 250, 260, and blowers (first and second blowers 26, 32) that send air to the heat exchangers 205, 230, 240, 250, 260.

In this way, by including the heat exchangers 205, 230, 240, 250, and 260 described above in the heat exchanger units (first and second heat exchanger units 201, 203), the heat exchanger unit (first and the second heat exchanger units 201, 203) can be stably operated.

(30) The refrigeration cycle device 200 according to the 30th aspect includes a heat exchanger unit (first and second heat exchanger units 201, 203) according to (29).

In this way, by providing the above-described heat exchanger units (first and second heat exchanger units 201 and 203), the refrigeration cycle apparatus 200 can be stably operated.

(31) The heat exchanger 285 according to the 31st aspect has a flat outer shape, a flow path 41A through which a refrigerant flows inside, and a heat exchanger 285 arranged on one side in the width direction (Y direction). A plurality of flat tubes 41 having one end 41D and a second end 41E disposed on the other side in the width direction, and an extension of the flat tube 41 in a state where the plurality of flat tubes 41 are accommodated. a plurality of fins 290 arranged at a predetermined pitch in the direction (X direction), the plurality of fins 290 having a plate shape, and a first surface arranged in the extending direction (X direction); 291a, and a second surface 291b disposed on the opposite side of the first surface 291a; A plurality of them are arranged at intervals in a first direction (Z direction), and a second direction (Y direction) perpendicular to the first direction (Z direction) and the extension direction (X direction). A flat tube insertion section 209 that extends from one side to the other side and accommodates the flat tube 41 inserted from the second end 41E side, and a flat tube insertion section 209 that extends from the second end 41E side to the second direction ( a communication portion 303 disposed on the other side of the Y direction (direction Y) and extending continuously in the first direction (Z direction); and a communication portion 303 disposed on the other side of the flat tube insertion portion 209 adjacent to each other in the first direction (Z direction). A part of the fin main body 291 located between is bent in the first direction (Z direction) to protrude toward the first surface 291a side, and is formed on one side in the extending direction (X direction). The first fin pitch defining portion 307 that comes into contact with the fin 290 disposed in It is formed by protruding, is arranged around the flat tube insertion part 209 located on the rear end side of the tip part 209A of the flat tube insertion part 209, and is on one side in the extending direction (X direction). and a second fin pitch defining portion 308 that abuts the fins 290 arranged in the fins 290, and the refrigerant and the heat in the direction from the other side to the one side in the second direction (Y direction). Air to be exchanged is flowing, and the outer shape of the second end 41E is circular or elliptical, and the tip 209A of the flat tube insertion section 209 that accommodates the second end 41E is The shape is such that the outer circumferential surface 41b of the second end portion 41E and the fin main body 291 are in surface contact, and the first fin pitch defining portion 307 is located on the rear end side of the flat tube insertion portion 209. The second fin pitch defining section 308 is disposed on the distal end 209A side of the flat tube insertion section 209.

As described above, by bending a part of the fin body 291 in the first direction (Z direction) to form the first and second fin pitch defining parts 307 and 308, a part of the fin body 291 can be bent. Compared to the case where the first and second fin pitch defining portions 307 and 308 are bent in the second direction (Y direction), the direction (B Since it becomes possible to suppress the air from becoming a resistance body for the air flowing in the direction (direction), it is possible to suppress the pressure loss of the air.
Furthermore, by arranging the first fin pitch regulating section 307 on the rear end side of the flat tube insertion section 209 and arranging the second fin pitch regulating section 308 on the distal end section 209A side of the flat tube insertion section 209, , it becomes possible to arrange the first and second fin pitch defining parts 307 and 308 at positions separated from each other with respect to the first direction (Z direction) and the second direction (Y direction). Thereby, the fin pitch of the plurality of fins 290 arranged in the extending direction (X direction) can be stably defined.

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 a shape that allows the outer peripheral surface of the tip 209A of the flat tube 41 to be in 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.

(32) A heat exchanger 285 according to a thirty-second aspect is the heat exchanger 285 according to (31), in which the first direction (Z direction) is an up-down direction, and the first fin pitch regulation The portion 307 is formed by bending a part of the fin main body 291 downward, and the second fin pitch defining portion 308 is formed by bending a part of the fin main body 291 downward, and the second fin pitch defining portion 308 is formed by bending a part of the fin main body 291 downward. Of the two flat tube insertion sections 209 sandwiching the pitch regulation section 307 , it may be formed around the flat tube insertion section 209 located above the first fin pitch regulation section 307 .

In this way, the first fin pitch defining portion 307 is formed by bending a part of the fin main body 291 downward, and the first fin pitch defining portion 307 is sandwiched in the first direction (Z direction). A second fin pitch defining section 308 is formed around the flat tube inserting section 209 located above the first fin pitch defining section 307 among the two flat tube inserting sections 209 to define the fin pitch. Since it becomes possible to arrange the positions at equal intervals in the first direction (Z direction), the fin pitch can be stably defined.

(33) A heat exchanger 285 according to a thirty-third aspect is the heat exchanger 285 according to (31), in which the first direction (Z direction) is an up-down direction, and the first fin pitch regulation The section 307 is formed by bending a part of the fin main body 291 upward, and the second fin pitch defining section 308 is configured by bending a part of the fin main body 291 upward, and the second fin pitch defining section 308 adjusts the first fin pitch in the first direction (Z direction). Of the two flat tube insertion sections 209 sandwiching the regulation section 307, it may be formed around the flat tube insertion section 209 located below the first fin pitch regulation section 307.

In this way, by bending a part of the fin main body 291 upward, the first fin pitch defining part 307 is formed, and the two parts sandwiching the first fin pitch defining part 307 in the first direction (Z direction) are formed. The fin pitch is defined by forming a second fin pitch defining section 308 around the flat tube inserting section 209 located below the first fin pitch regulating section 307 among the two flat tube inserting sections 209. Since the positions can be arranged at equal intervals in the first direction (Z direction), the fin pitch can be stably defined.

(34) The heat exchanger 285 according to the 34th aspect is a heat exchanger 285 according to any one of (31) to (33), and the first fin pitch defining portion 307 may be L-shaped.

In this way, by making the first fin pitch defining part 307 L-shaped, the first fin pitch defining part 307 is shaped like an I, for example. 307 can increase the probability of contact with the second surface 291b.
Further, by making the first fin pitch defining portion 307 L-shaped, it is possible to increase the contact area between the first fin pitch defining portion 307 and the second surface 291b, so that the fin pitch can be increased. Can be maintained stably.

(35) The heat exchanger 285 according to the thirty-fifth aspect is the heat exchanger 285 described in any one of (31) to (34), wherein the second fin pitch defining section 308 is It may be L-shaped.

In this way, by making the second fin pitch defining part 308 L-shaped, for example, compared to the case where the second fin pitch defining part 308 is I-shaped, the second fin pitch defining part 308 is 308 can increase the probability that it contacts the first surface 291a.
Furthermore, by forming the second fin pitch defining portion 308 into an L-shape, it is possible to increase the contact area between the second fin pitch defining portion 308 and the second surface 291b. Can be maintained stably.

(36) The heat exchanger 285 according to the 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, and further have a heat conductive portion 305 that rises toward the first surface 291a and contacts 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 the heat conductive portion 305 does not come into contact with the fins 290 arranged on the first surface 291a side when the plurality of fins 290 are arranged in the extension direction (X direction).

By having a heat conduction section configured in this manner, the fin pitch is defined using the first and second fin pitch regulating sections 307 and 308, and the heat between the flat tube 41 and the fin 290 is Conductivity can be improved.

(37) The heat exchanger unit (first and second heat exchanger units 18, 23) according to the thirty-seventh aspect is the heat exchanger 285 described in any one of (31) to (36). and a blower (first and second blowers 26 and 32) that sends air to the heat exchanger 285.

In this way, by including the heat exchanger 285 described above in the heat exchanger units (first and second heat exchanger units 281, 283), the heat exchanger units (first and second heat exchanger units 281, 283) 281, 283), and the heat exchanger units (first and second heat exchanger units 281, 283) can be stably operated.

(38) The refrigeration cycle device 10 according to the thirty-eighth aspect includes the heat exchanger unit (first and second heat exchanger units 281 and 283) of (37).

In this way, by equipping the refrigeration cycle device 280 with the above-mentioned heat exchanger units (first and second heat exchanger units 281, 283), the performance of the refrigeration cycle device 280 can be improved and the refrigeration cycle device 280 can be operated stably.

10, 200, 280... Refrigeration cycle device 11... Outdoor unit 12... Indoor unit 14... Refrigerant piping 14A... First refrigerant piping 14B... Second refrigerant piping 15... Four-way valve 15A to 15D, 248... Connection portion 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... Inlet/outlet header 37... Turn-around header 41, 41F, 41S... Flat tube 41a, 41Fa... One end 41A... Flow path 41b... Outer 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 portion 43, 61, 71, 81, 91, 101, 131, 141, 151, 191... Header 45... Header body 45a... Bottom surface 45aa... First bottom surface 45ab... Second bottom surface 45ac... Third bottom surface 45b... Inner wall surface 45A... Opening 47, 133... Partition plate 47a... Upper end surface Reference Signs: 47A, 47B, 133A...lower end 47Aa, 47Ba...lower end 47b, 207a, 291a...first surface 47c, 207b, 291b...second surface 47C...notch portion 49, 62...nozzle portion 49A, 62A...blowout port 51...perforated plate 51A...hole 53...internal space 54...first space 54A...refrigerant flow portion 55...second space 73...first refrigerant guide portion 73a...first guide surface 83...third refrigerant guide portion 83a...third guide surface 93...second refrigerant guide portion 93a...second guide surface 143, 163, 173...flow straightening member 145...baffle plate 164, 174...block 174a...curved surface 207, 291...fin body 207A...second flat portion 207B...first flat portion 209A...tip portion 209B...rear end portion 211, 236...uneven portion 213, 233, 243, 303...communicating portion 215...fin pitch defining portion 217, 235, 245...condensed water guide portion 218, 238...convex portion 218A...tip 220, 225...structure 239...concave portion 243A...first portion 243B...second portion 246...step portion 252, 263, 273...pedestal portion 305...heat conductive portion 305a...inner circumferential surface 307...first fin pitch defining portion 308...second fin pitch defining portion B...area Cp...cutting position Ds1, Ds2...distance H, H ₁ , H ₂ ...height J, P...direction Vp...plane W1, W2...width

Claims (21)

A heat exchanger that exchanges heat between air and a refrigerant,
a plurality of flat tubes having a flat outer shape and extending in one direction, arranged in the width direction, extending in the one direction, and having a plurality of channels through which the refrigerant flows; and a state in which the plurality of flat tubes are accommodated. , a plurality of fins arranged in the extending direction of the flat tube;
a header connected to the plurality of flat tubes such that one end of the plurality of flat tubes is arranged inside, and into which the refrigerant flows;
Equipped with
The header has a cylindrical shape extending in the vertical direction, and a header main body defining a columnar internal space;
The header is housed in the header body and extends in the vertical direction, and the internal space is connected to the first space and the plurality of flat surfaces in the extending direction in a state where the refrigerant can flow at the upper and lower ends of the internal space. a partition plate dividing the space into a second space in which one end of the pipe is arranged;
a nozzle portion disposed at a lower part of the first space and including a blowout port that blows out the refrigerant supplied from the outside of the header toward the bottom surface of the header body;
A heat exchanger in which refrigerant flow portions, which are part of the first space, are formed on both sides in the width direction of the nozzle portion. a bottom surface of the header body includes a first bottom surface that defines the first space and a second bottom surface that defines the second space;
2. The heat exchanger according to claim 1, further comprising a first refrigerant guide portion provided on the first bottom surface and having a first guide surface that guides the refrigerant in a direction from the first space toward the second space. 3. The heat exchanger according to claim 2, wherein the first guide surface is a concave curved surface recessed in a direction away from the lower end of the partition plate. The bottom surface of the header body has a first bottom surface that partitions the first space, and a second bottom surface that partitions the second space,
Claims 1 to 3 include a second refrigerant guide section provided on the second bottom surface and having a second guide surface that guides the refrigerant in a direction from below to above the second space. The heat exchanger according to any one of the items. 5. The heat exchanger according to claim 4, wherein the second guide surface is a concave curved surface recessed in a direction away from the lower end of the partition plate. A third guide surface is provided at a portion of the lower end of the partition plate that is upwardly away from the bottom surface of the header body, and guides the refrigerant in a direction from the first space to the second space. The heat exchanger according to any one of claims 1 to 5, further comprising a third refrigerant guide section. The heat exchanger according to claim 6, wherein the third refrigerant guide portion is a cylindrical member extending in the width direction of the partition plate. 8. The heat exchanger according to claim 1, wherein the nozzle portion is located at a position lower than 1/2 of the height of the header body. Any one of claims 1 to 7, wherein the nozzle portion is disposed between a flat tube placed at the bottom and a flat tube placed second from the bottom among the plurality of flat tubes. The heat exchanger described in item (1) above. In the direction in which the flat tubes extend, one end of the plurality of flat tubes is arranged to face the partition plate,
The distance from one end of the lowest flat tube of the plurality of flat tubes to the partition plate is longer than the distance from one end of the other flat tubes to the partition plate. The heat exchanger described in any one of these. 11. The flat tube according to claim 10, wherein one end of the flat tube placed at the bottom is placed backward from the position of one end of the other flat tube in the direction from the first space to the second space. Heat exchanger. The heat exchanger according to claim 10 or 11, wherein the lower end of the partition plate facing one end of the lowest flat tube is positioned at a position offset in a direction from the second space toward the first space. The header body is provided on an inner wall surface of the header body that partitions the second space, and is located below one end of the lowest flat tube among the plurality of flat tubes. 13. The heat exchanger according to claim 1, further comprising a rectifying member that rectifies the refrigerant from the bottom surface of the tube toward one end of the flat tube disposed at the bottom. The rectifying member is disposed at a position away from one end of the flat tube disposed at the bottom, extends in a direction from the inner wall surface of the header body toward the partition plate, and extends from the inner wall surface of the header body. 14. The heat exchanger according to claim 13, wherein the baffle plate has a protrusion amount equal to the protrusion amount of the one end portion. The rectifying member is disposed below the one end of the flat tube disposed at the bottom so as to be in contact with the lower surface of the one end of the flat tube disposed at the lowest position. 14. The heat exchanger according to claim 13, wherein the block is a block that extends in the direction toward which the header body is directed, and has an amount of protrusion from an inner wall surface of the header body equal to an amount of protrusion of the one end. 16. The heat exchanger according to claim 15, wherein the block has a curved surface that is formed on the partition plate side and guides the flow of the refrigerant upward. Claim comprising: a perforated plate provided between the header main body and the partition plate that partition the first space, and arranged in a portion of the first space located above the nozzle part. The heat exchanger according to any one of items 1 to 16. The air outlet is a circular hole,
The partition plate is arranged on one side in the width direction, with a lower end reaching the bottom surface of the header main body, and on the other side in the width direction, the lower end reaching the bottom surface of the header main body. 18. The refrigerant according to any one of claims 1 to 17, further comprising: the other lower end; and a notch formed between the one lower end and the other lower end, through which the refrigerant flows. Heat exchanger. The air outlet has a groove shape extending in the width direction of the nozzle portion,
18. The heat exchanger according to claim 1, wherein the total width of the two refrigerant flow sections disposed on both sides of the nozzle section in the width direction is smaller than the width of the nozzle section. exchanger. A heat exchanger according to any one of claims 1 to 19,
a blower that sends air to the heat exchanger;
A heat exchanger unit comprising: A refrigeration cycle device comprising the heat exchanger unit according to claim 20.

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