WO2023218621A1

WO2023218621A1 - Heat exchanger and refrigeration cycle apparatus

Info

Publication number: WO2023218621A1
Application number: PCT/JP2022/020154
Authority: WO
Inventors: 敦森田; 剛志前田; 伸中村; 篤史 ▲高▼橋
Original assignee: 三菱電機株式会社
Priority date: 2022-05-13
Filing date: 2022-05-13
Publication date: 2023-11-16

Abstract

This heat exchanger comprises a flat tube which has a plurality of refrigerant passages formed as through-holes and which extends in a first direction. The heat exchanger exchanges heat between a refrigerant flowing through the refrigerant passages of the flat tube and air flowing in a second direction which is orthogonal to the first direction and in which the refrigerant passages are arranged in parallel. The heat exchanger comprises a distributor installed midway of the refrigerant passages of the flat tube. The distributor has a refrigerant flow path formed as a through-hole. Through the refrigerant flow path, the refrigerant is caused to flow out such that the levels of the dryness of the refrigerant flowing out from an upstream region in an outlet of the refrigerant flow path and the dryness of the refrigerant flowing out from a downstream region in the outlet of the refrigerant flow path are reversed from the levels of the dryness of the refrigerant, in the upstream and downstream regions, having entered through an inlet of the refrigerant flow path.

Description

Heat exchanger and refrigeration cycle equipment

The present disclosure relates to a heat exchanger and a refrigeration cycle device equipped with flat tubes.

Conventionally, there is a heat exchanger that includes a pair of headers that face each other at a distance, and a plurality of flat tubes that communicate between the pair of headers and have a plurality of refrigerant passages arranged in parallel. In this type of heat exchanger, there is a heat exchanger equipped with a mixing part having a confluence space that communicates with all of the refrigerant passages of at least one flat tube at an intermediate position of the flat tubes (for example, see Patent Document 1) .

Here, due to the structure of the flat tube, among the plurality of refrigerant passages, the refrigerant passages at both ends in the juxtaposed direction have a wider range of heat transfer area than the other refrigerant passages. For this reason, when the flat tube is viewed as a whole, the heat transfer coefficient becomes non-uniform, and the heat exchange efficiency decreases.

In the heat exchanger of Patent Document 1, the flat tubes are divided into flat tubes on the upstream side of the refrigerant from the mixing section and flat tubes on the downstream side of the refrigerant from the mixing section. In the heat exchanger of Patent Document 1, the refrigerants that have passed through the refrigerant passages of the flat tubes on the upstream side of the refrigerant are once merged in the mixing section, and then distributed again into a plurality of refrigerants to each of the flat tubes on the downstream side of the refrigerant. It is made to pass through the refrigerant passage. In this way, the heat exchanger of Patent Document 1 temporarily mixes the refrigerants that have passed through the refrigerant passages of the flat tube on the upstream side of the refrigerant in the mixing section, thereby reducing the heat transfer area due to the difference in heat transfer area shared by each refrigerant passage. The aim was to eliminate uneven transmission rates.

Japanese Patent Application Publication No. 09-113154

By the way, in a heat exchanger, the flat tubes are arranged in such a direction that a plurality of refrigerant passages are lined up in the air flow direction. Therefore, when the heat exchanger functions as an evaporator, the refrigerant flowing through the upwind refrigerant passage among the multiple refrigerant passages in the flat tube evaporates and dries out more preferentially than the refrigerant flowing through the leeward refrigerant passage. degree increases. The heat transfer coefficient of a refrigerant decreases as the degree of dryness increases. For this reason, in the flat tube, variations occur in the degree of dryness of the refrigerant between the windward side refrigerant passage and the leeward side refrigerant passage in the wake of the refrigerant flow path from one end of the flat tube to the other end. When such variations in dryness of the refrigerant occur within the flat tube, the heat transfer coefficient of the flat tube as a whole decreases, and the heat exchange efficiency of the entire heat exchanger decreases.

In the heat exchanger of Patent Document 1, the refrigerants flowing through the refrigerant passages of the flat tubes on the upstream side of the refrigerant are mixed in the mixing part, thereby eliminating uneven dryness and improving heat transfer. It is possible to eliminate uneven rates. However, in the heat exchanger of Patent Document 1, in the flat tube on the downstream side of the refrigerant from the mixing section, the evaporation of the refrigerant flowing through the refrigerant passage on the windward side becomes preferential to that on the leeward side, so that the flat tube as a whole There was room for improvement as the heat transfer coefficient of

The present disclosure has been made to solve the above-mentioned problems, and provides a heat exchanger and a refrigeration cycle device that can improve the heat transfer coefficient of the flat tubes and improve the heat exchange efficiency of the heat exchanger as a whole. The purpose is to

A heat exchanger according to the present disclosure includes a flat tube having a plurality of refrigerant passages formed with through holes and extending in a first direction, and a refrigerant flowing through the plurality of refrigerant passages of the flat tube and a flat tube extending in a first direction. A heat exchanger that exchanges heat with air flowing in a second direction that is orthogonal to each other and in which a plurality of refrigerant passages are arranged in parallel, the heat exchanger comprising a distributor provided in the middle of the plurality of refrigerant passages of flat tubes. , the distributor has a refrigerant flow path formed with a through hole, and the refrigerant flow path has a dryness of the refrigerant flowing out from an upwind region of the outlet of the refrigerant flow path and a leeward region of the exit of the refrigerant flow path. The degree of dryness of the refrigerant flowing out is opposite to the degree of dryness of the refrigerant in the windward region and the leeward region when it flows in from the entrance of the refrigerant flow path.

A refrigeration cycle device according to the present disclosure includes the above heat exchanger.

In the heat exchanger according to the present disclosure, the distributor provided in the middle of the plurality of refrigerant passages of the flat tube has the following refrigerant flow path. The refrigerant flow path determines the dryness of the refrigerant flowing out from the upwind region of the outlet of the refrigerant flow path and the dryness of the refrigerant flowing out from the leeward region of the exit of the refrigerant flow path when it flows in from the inlet of the refrigerant flow path. The dryness of the refrigerant in the upwind region and the leeward region of the refrigerant is reversed. Therefore, the heat exchanger can improve the heat transfer coefficient of the flat tube downstream of the distributor, and can improve the heat exchange efficiency of the heat exchanger as a whole.

1 is a schematic front view of a heat exchanger according to Embodiment 1. FIG. FIG. 2 is a cross-sectional view showing the configuration of flat tubes of the heat exchanger according to the first embodiment. It is an explanatory view of heat flux of each refrigerant passage of a flat tube. It is a figure showing the relationship between dryness and heat transfer coefficient. FIG. 2 is an exploded perspective view of the distributor of the heat exchanger according to the first embodiment. FIG. 3 is a diagram showing a change in the dryness of the refrigerant from the inlet to the outlet of the heat exchanger according to the first embodiment. As a comparative example, it is a diagram showing a change in the dryness of refrigerant from an inlet to an outlet in a heat exchanger that does not use a distributor. FIG. 3 is a schematic front view of a heat exchanger according to a second embodiment. FIG. 2 is an exploded perspective view of a distributor of a heat exchanger according to a second embodiment. FIG. 7 is a plan view of each plate-like member that constitutes the distributor of the heat exchanger according to Embodiment 2; FIG. 7 is a diagram illustrating a state in which two adjacent plate members are overlapped among a plurality of plate members constituting the distributor of the heat exchanger according to the second embodiment. FIG. 7 is an explanatory diagram of the flow of refrigerant in the first channel of the distributor of the heat exchanger according to the second embodiment. FIG. 7 is a diagram showing a change in the dryness of the refrigerant from the inlet to the outlet of the heat exchanger according to the second embodiment. FIG. 7 is a plan view of each plate-like member that constitutes a distributor of a heat exchanger according to Embodiment 3; FIG. 7 is a schematic perspective view of a heat exchanger according to Embodiment 4. FIG. 7 is an exploded perspective view of a distributor of a heat exchanger according to a fourth embodiment. FIG. 7 is a plan view of each plate-like member that constitutes a distributor of a heat exchanger according to Embodiment 4; FIG. 7 is a diagram showing a state in which two adjacent plate members are stacked on top of each other among a plurality of plate members configuring the distributor of the heat exchanger according to the fourth embodiment. FIG. 7 is an explanatory diagram of the flow of refrigerant in the first channel of the distributor of the heat exchanger according to Embodiment 4; FIG. 7 is a diagram showing a modification of the heat exchanger according to Embodiment 4. FIG. 3 is a refrigerant circuit diagram showing a schematic configuration of a refrigeration cycle device according to a fifth embodiment.

Hereinafter, embodiments will be described based on the drawings. Note that the present disclosure is not limited to the embodiments described below. Further, in the following drawings including FIG. 1, the relative dimensional relationships, shapes, etc. of each component may differ from the actual ones. In addition, in the following drawings, parts with the same reference numerals are the same or equivalent, and this is common throughout the entire specification. Note that terms such as top, bottom, right, and left used in the following description refer to directions when the heat exchanger is viewed from the front side. Terms related to these directions are only described as such for convenience of explanation, and do not limit the arrangement or orientation of the device or parts.

Embodiment 1.
A heat exchanger according to Embodiment 1 will be described. FIG. 1 is a schematic front view of a heat exchanger according to a first embodiment. The vertical direction in FIG. 1 represents the direction of gravity. The heat exchanger according to Embodiment 1 is an air heat exchanger that exchanges heat between air and refrigerant, and functions at least as an evaporator of a refrigeration cycle device. In the specification, the positional relationship between each component, the extending direction of each component, and the parallel direction of each component are, in principle, when the heat exchanger is installed in a usable state.

As shown in FIG. 1, the heat exchanger includes a plurality of flat tubes 10 arranged at intervals and through which refrigerant flows, and a pair of headers 20 arranged at both ends of the plurality of flat tubes 10 in the extending direction. It has a plurality of fins 30 arranged at intervals in the extending direction of the plurality of flat tubes 10. The heat exchanger further includes a distributor 40 arranged at the center of the plurality of flat tubes 10 in the extending direction. Each of the plurality of flat tubes 10 extends in the horizontal direction. The plurality of flat tubes 10 are arranged in parallel at intervals in the vertical direction.

The pair of headers 20 and distributor 40 extend in the vertical direction along the parallel direction of the plurality of flat tubes 10. Hereinafter, the stretching direction of the flat tube 10 will be referred to as a first direction, and the direction perpendicular to the first direction in which refrigerant passages 15 (described later in FIG. 2) of the flat tube 10 are parallel will be referred to as a second direction. The direction perpendicular to the second direction and the parallel direction of the flat tubes 10 is referred to as a third direction. In the first embodiment, the first direction is the left-right direction, the second direction is the depth direction, and the third direction is the up-down direction. The second direction is also the direction of air passage.

Each of the plurality of flat tubes 10 includes a flat tube 10a on the upstream side of the refrigerant (hereinafter referred to as the first flat tube 10a) and a flat tube 10b on the downstream side of the refrigerant (hereinafter referred to as the second flat tube 10b). ) and has. The first flat tube 10a and the second flat tube 10b have the same shape. The left ends of the plurality of first flat tubes 10a are connected to one of the pair of headers 20, and the right ends of the plurality of first flat tubes 10a are connected to the distributor 40. The left ends of the plurality of second flat tubes 10b are connected to the distributor 40, and the right ends of the plurality of second flat tubes 10b are connected to the other of the pair of headers 20. A refrigerant inlet 20a is provided in the lower part of one header 20, and a refrigerant outlet 20b is provided in the upper part of the other header 20.

The plurality of fins 30 are plate-shaped fins, and are arranged at intervals in the extending direction of the plurality of flat tubes 10. A plurality of flat tubes 10 penetrate through the plurality of fins 30. The fins 30 are not limited to plate-like fins, and may be corrugated fins. When the fins 30 are corrugated fins, the fins 30 are arranged between two adjacent flat tubes 10. Further, the heat exchanger may be a finless heat exchanger that does not include the fins 30.

When the heat exchanger functions as an evaporator of a refrigeration cycle device, refrigerant flows into one header 20 from the inlet 20a as shown by the arrow in FIG. The refrigerant that has flowed into one header 20 is distributed to each of the plurality of first flat tubes 10a, flows through each first flat tube 10a from the left end to the right end, and then flows into the distributor 40. Details of the distributor 40 will be described later, but the distributor 40 has independent refrigerant flow paths 400A (see FIG. 5 described later) formed by through holes corresponding to each of the plurality of flat tubes 10. It is formed. Therefore, the refrigerant flowing through each first flat tube 10a from the left end to the right end flows into each second flat tube 10b without mixing with the refrigerant flowing through other first flat tubes 10a in the distributor 40. Inflow. After the refrigerant flows through each second flat tube 10b from the left end to the right end, the refrigerant joins at the other header 20 and flows out from the outlet 20b.

FIG. 2 is a cross-sectional view showing the configuration of the flat tube of the heat exchanger according to the first embodiment. FIG. 2 shows a cross section of the flat tube 10 perpendicular to the stretching direction. In the following drawings, including FIG. 2, the direction of air flow is indicated by white arrows. As shown in FIG. 2, the flat tube 10 has a cross-sectional shape that is flat in one direction, such as an oval shape. The flat tube 10 has a first side end 11, a second side end 12, and a pair of

flat surfaces

13 and 14. In the cross section shown in FIG. 2, the first side end 11 is connected to one end of the flat surface 13 and one end of the flat surface 14. In the same cross section, the second side end 12 is connected to the other end of the flat surface 13 and the other end of the flat surface 14.

The first side end portion 11 is a side end portion disposed on the windward side, that is, on the leading edge side in the flow of air passing through the heat exchanger. The second side end portion 12 is a side end portion disposed on the leeward side, that is, on the trailing edge side in the flow of air passing through the heat exchanger. Hereinafter, the direction perpendicular to the extending direction of the flat tube 10 and along the

flat surfaces

13 and 14 may be referred to as the longer diameter direction of the flat tube 10. In FIG. 2, the major diameter direction of the flat tube 10 is the left-right direction.

The flat tube 10 has a plurality of refrigerant passages 15 arranged between a first side end 11 and a second side end 12 along the major diameter direction. That is, the flat tube 10 is a flat porous tube having a plurality of refrigerant passages 15. Each of the plurality of refrigerant passages 15 is formed to extend parallel to the extending direction of the flat tube 10. Each of the plurality of refrigerant passages 15 is formed as a through hole extending in the extending direction within the flat tube 10.

The flat tube 10 is arranged in such a way that the plurality of refrigerant passages 15 are lined up in the air flow direction. Therefore, a heat flux distribution as shown in FIG. 3 below occurs in each of the plurality of refrigerant passages 15.

FIG. 3 is an explanatory diagram of the heat flux of each refrigerant passage of the flat tube. The horizontal axis is the second direction, and the vertical axis is the heat flux [W/m ² ]. The flat tube 10 is arranged with a plurality of refrigerant passages 15 aligned in the air flow direction. At this time, the heat flux of each refrigerant passage 15 is distributed due to the leading edge effect in the flat tube 10 and the temperature difference between the refrigerant and the air. As shown in FIG. 3, the heat flux of each refrigerant passage 15 has a distribution that decreases from the windward side toward the leeward side.

In this way, a heat flux distribution occurs in the flat tube 10. Therefore, when the heat exchanger functions as an evaporator, evaporation of the refrigerant progresses due to the large heat flux on the windward side, and the dryness of the refrigerant in the refrigerant passage 15 on the windward side increases. On the other hand, since the heat flux is smaller on the leeward side, the evaporation of the refrigerant does not progress as much as on the windward side, and the dryness of the refrigerant in the refrigerant passage 15 on the leeward side is lower than that in the refrigerant passage 15 on the windward side. It will be in a low state. In other words, a distribution of dryness occurs in each refrigerant passage 15 within the flat tube 10. Note that dryness refers to the ratio (ratio) of the mass of gas refrigerant to the mass of wet vapor (liquid refrigerant + gas refrigerant).

FIG. 4 is a diagram showing the relationship between dryness and heat transfer coefficient. The horizontal axis is dryness, and the vertical axis is heat transfer coefficient [W/(m·K)]. As shown in FIG. 4, the heat transfer coefficient of the refrigerant has a characteristic that it decreases as the degree of dryness increases. For this reason, the heat transfer coefficient of the refrigerant flowing through the windward side refrigerant passage 15 tends to decrease, and the heat exchange efficiency in the windward side refrigerant passage 15 decreases in the latter half of the flow of the refrigerant in the flat tube 10, and as a result, the heat exchanger This leads to a decrease in the overall heat exchange efficiency.

Therefore, in the heat exchanger of the first embodiment, the distributor 40 is provided in the middle of the plurality of refrigerant passages 15 of the flat tube 10, and the heat exchange efficiency in the second flat tube 10b located downstream of the refrigerant from the distributor 40 is increased. Improve. The distributor 40 allows a refrigerant with a low degree of dryness to flow into the refrigerant passage 15 on the windward side where the heat flux is large in the second flat tube 10b located downstream of the refrigerant of the distributor 40, and flows into the refrigerant passage 15 on the lee side where the heat flux is small. A refrigerant with a high degree of dryness is flowed into the refrigerant. The heat exchanger of Embodiment 1 improves the heat transfer coefficient in the second flat tube 10b by having the distributor 40, and aims to improve the heat exchange coefficient of the entire heat exchanger.

[Structure of distributor 40]
FIG. 5 is an exploded perspective view of the distributor of the heat exchanger according to the first embodiment. As shown in FIG. 1, the distributor 40 extends in the third direction, and forms independent refrigerant flow paths corresponding to each of the plurality of flat tubes 10 arranged in parallel in the third direction. In FIG. 5, constituent parts corresponding to one flat tube 10 are extracted and shown.

The distributor 40 includes a tube insertion plate member 400 into which the right end of the first flat tube 10a is inserted, four

plate members

410, 420, 430, and 440, and into which the left end of the second flat tube 10b is inserted. It has a plate-like member 460 for inserting a tube. The four

plate members

410, 420, 430, and 440 are, in order from the first flat tube 10a side, a first plate member 410, a second plate member 420, a third plate member 430, and a fourth plate member. It is 440. The distributor 40 further includes a fifth plate member 450 between the third plate member 430 and the fourth plate member 440. Plate member 400 for tube insertion, first plate member 410, second plate member 420, third plate member 430, fourth plate member 440, fifth plate member 450, and plate member 460 for tube insertion. Both are formed using flat metal plates.

Since FIG. 5 shows a part of the distributor 40, the tube insertion plate member 400, the first plate member 410, the second plate member 420, and the The third plate member 430, the fourth plate member 440, the fifth plate member 450, and the tube insertion plate member 460 have a belt-like shape that is long in the third direction. Further, a plate member 400 for tube insertion, a first plate member 410, a second plate member 420, a third plate member 430, a fourth plate member 440, a fifth plate member 450, and a plate member for tube insertion. The contours of the outer edges of each member 460 have the same shape. Plate member 400 for tube insertion, first plate member 410, second plate member 420, third plate member 430, fourth plate member 440, fifth plate member 450, and plate member 460 for tube insertion. are arranged so that the thickness direction of each plate is parallel to the stretching direction of the flat tube 10. In other words, the tube insertion plate member 400, the first plate member 410, the second plate member 420, the third plate member 430, the fourth plate member 440, the fifth plate member 450, and the tube insertion plate. The shaped members 460 are arranged so that each plate surface is perpendicular to the direction in which the flat tube 10 extends.

The distributor 40 includes a tube insertion plate member 400, a first plate member 410, a second plate member 420, a third plate member 430, a fifth plate member 450, a fourth plate member 440, and a tube insertion plate member 400. The plate-like members 460 are stacked in this order from the one closest to the first flat tube 10a. Adjacent members among these plate-like members are joined by brazing.

Hereinafter, the constituent parts of the distributor 40 that correspond to one flat tube 10 will be described with reference to FIG. 5. The distributor 40 has the same number of configurations as the flat tubes 10 as described below, but since each configuration is the same, only the component corresponding to one flat tube 10 will be described. Hereinafter, the entire heat exchanger including the distributor 40 will be divided into two regions on a plane extending in the first direction and the third direction and located at the center of the distributor 40 in the second direction (shaded plane in FIG. 5). The windward side of the divided regions is called a windward region 1a, and the leeward side is called a leeward region 1b.

(Plate member for tube insertion 400)
The tube insertion plate member 400 has an insertion hole 401 into which the right end of the first flat tube 10a is inserted. The insertion hole 401 penetrates the tube insertion plate member 400 in the thickness direction of the tube insertion plate member 400. The insertion hole 401 has a flat opening shape similar to the outer peripheral shape of the first flat tube 10a. The inner peripheral surface of the insertion hole 401 is joined to the outer peripheral surface of the first flat tube 10a over the entire circumference by brazing. The first flat tube 10a may be arranged such that the right end of the first flat tube 10a is accommodated in the insertion hole 401, or it may be arranged such that the right end of the first flat tube 10a is accommodated in the insertion hole 401, or it may be inserted into the through hole 411 of the first plate member 410, which will be described later. It may be arranged so that it is located in the middle. Note that the tube insertion plate member 400 is omitted from the configuration of the distributor 40, and the right end of the first flat tube 10a is arranged in the middle of the through hole 411 of the first plate member 410, which will be described later. Good too.

(First plate member 410)
The first plate member 410 has a through hole 411 that serves as an inlet for the refrigerant. The through hole 411 penetrates the first plate member 410 in the thickness direction of the first plate member 410 . The through hole 411 has a flat opening shape similar to the outer peripheral shape of the first flat tube 10a. The opening area of the through hole 411 is the same as or larger than the opening area of the insertion hole 401 of the tube insertion plate member 400. The through hole 411 overlaps with the insertion hole 401 of the tube insertion plate member 400 when viewed in the first direction, and communicates with the plurality of refrigerant passages 15 in the first flat tube 10a.

(Second plate member 420)
The second plate member 420 has a through hole 421 through which the refrigerant that has passed through the through hole 411 passes. The through hole 421 penetrates the second plate member 420 in the thickness direction of the second plate member 420. The through hole 421 has a shorter length in the second direction than the through hole 411 of the first plate-shaped member 410, a substantially same length in the third direction, and has a flat opening shape. The shape of the through hole 421 is not limited to a flat shape, but may be circular. The opening area of the through hole 421 is smaller than the opening area of the through hole 411 of the first plate member 410. The through hole 421 overlaps the through hole 411 of the first plate member 410 when viewed in the first direction, and is located at the center of the through hole 411 in the second direction.

(Third plate member 430)
The third plate member 430 has a through hole 431 through which the refrigerant that has passed through the through hole 421 passes. The through hole 431 penetrates the third plate member 430 in the thickness direction of the third plate member 430. The through hole 431 has a flat opening shape. The through hole 431 is formed so as to be inclined upward, which is the anti-gravity direction, from the windward region 1a to the leeward region 1b when viewed in the first direction. Further, when the through hole 431 is viewed in the first direction, both ends of the through hole 431 in the second direction are outside both ends of the through hole 421 in the second direction, and both ends of the through hole 411 in the second direction are outside. The length in the second direction is set so as to be located inside the section.

(Fifth plate member 450)
The fifth plate member 450 has two through holes 451a and 451b through which the refrigerant that has passed through the through hole 431 passes. The through holes 451a and 451b communicate with both ends of the through hole 431 in the second direction. Each of the through holes 451a and 451b penetrates the fifth plate member 450 in the thickness direction of the fifth plate member 450. Each of the through holes 451a and 451b has a flat opening shape extending in the third direction. The shape of the through holes 451a and 451b is not limited to being flat, but may be circular. The through holes 451a and 451b are arranged separately in the windward region 1a and the leeward region 1b.

More specifically, when the through hole 451a in the windward region 1a is viewed in the first direction, the upper part of the through hole 451a divided into upper and lower parts at the center in the third direction overlaps with the third plate member 430. The lower portion overlaps and communicates with the through hole 431 of the third plate member 430. When the through hole 451b in the leeward region 1b is viewed in the first direction, the upper part of the through hole 451b divided into upper and lower parts at the center in the third direction overlaps and communicates with the through hole 431 of the third plate member 430. However, the lower part overlaps with the third plate member 430 and is closed.

(Fourth plate member 440)
The fourth plate member 440 is configured to have the same shape as the first plate member 410. The fourth plate member 440 has a through hole 441 that serves as an outlet for the refrigerant. The through hole 441 passes through the fourth plate member 440 in the thickness direction of the fourth plate member 440 . The through hole 441 has a flat opening shape similar to the outer peripheral shape of the second flat tube 10b. The opening area of the through hole 441 is the same as or larger than the opening area of each insertion hole 461 of a tube insertion plate member 460, which will be described later. When viewed in the first direction, the through hole 441 overlaps and communicates with the through holes 451a and 451b of the fifth plate member 450, and also communicates with the plurality of refrigerant passages 15 in the second flat tube 10b. Further, the fourth plate member 440 communicates with the through hole 431 of the third plate member 430 via the through holes 451 a and 451 b of the fifth plate member 450 .

(Plate member for tube insertion 460)
The tube insertion plate member 460 is configured to have the same shape as the tube insertion plate member 400. The tube insertion plate member 460 has an insertion hole 461 into which the left end of the second flat tube 10b is inserted. The insertion hole 461 passes through the tube insertion plate member 460 in the thickness direction of the tube insertion plate member 460. The insertion hole 461 has a flat opening shape similar to the outer peripheral shape of the second flat tube 10b. The insertion hole 461 overlaps and communicates with the through hole 441 of the fourth plate member 440 when viewed in the first direction. The inner peripheral surface of the insertion hole 461 is joined to the outer peripheral surface of the second flat tube 10b over the entire circumference by brazing.

The second flat tube 10b may be arranged such that the left end of the second flat tube 10b is accommodated in the insertion hole 461, or it may be placed in the middle of the through hole 441 of the fourth plate member 440 by passing through the insertion hole 461. It may be arranged so that it is located. Note that the tube insertion plate member 460 may be omitted from the configuration of the distributor 40 and the left end of the second flat tube 10b may be located in the middle of the through hole 441 of the fourth plate member 440. . That is, the fourth plate member 440 may also serve as the tube insertion plate member 460.

The distributor 40 configured as described above includes a confluence section 40a having a first plate member 410 and a second plate member 420, and a gas-liquid separation unit having a third plate member 430 and a fifth plate member 450. It has a section 40b. The merging portion 40a is a portion that communicates with the plurality of refrigerant passages 15 in the first flat tube 10a and joins the refrigerant flowing out from the plurality of refrigerant passages 15. The gas-liquid separation part 40b is a part that is formed in communication with the confluence part 40a and separates the gas and liquid of the refrigerant that has passed through the confluence part 40a. Further, the gas-liquid separation unit 40b guides the liquid phase refrigerant to the refrigerant passage 15 in the upwind region 1a among the plurality of refrigerant passages 15 in the second flat tube 10b, and guides the gas phase refrigerant to the second flat tube 10b. This is a portion of the plurality of refrigerant passages that leads to the refrigerant passage 15 in the leeward region 1b. Hereinafter, in each of the first flat tube 10a and the second flat tube 10b, the refrigerant passage 15 in the windward region 1a will be referred to as the windward side refrigerant passage 15a, and the refrigerant passage 15 in the leeward region 1b will be referred to as the leeward side refrigerant passage 15b.

[Flow of refrigerant in distributor 40 and action of distributor 40]
In FIG. 5, solid line arrows indicate refrigerants with low dryness, and dotted line arrows indicate refrigerants with high dryness. Note that "small" and "large" do not represent the magnitude in comparison with a reference value, but are relative. This point also applies to the embodiments described below.

The refrigerants flowing out of each refrigerant passage 15 of the first flat tube 10a join together at the merging portion 40a. Specifically, both refrigerant A with a high degree of dryness that has flowed out of the windward side refrigerant passage 15a of the first flat tube 10a and refrigerant B with a low degree of dryness that has flown out of the leeward side refrigerant passage 15b of the first flat tube 10a pass through the passage. They flow into the hole 411 and merge. Then, the refrigerant after merging passes through the through hole 421, which has a smaller opening area than the through hole 411, and is throttled. In this way, the merging section 40a eliminates non-uniformity in the dryness of the refrigerants by merging and squeezing the refrigerant A with a high degree of dryness and the refrigerant B with a low degree of dryness.

After passing through the confluence section 40a, the refrigerant is divided into a refrigerant containing a large amount of liquid phase (hereinafter referred to as a refrigerant with a low degree of dryness) and a refrigerant containing a large amount of a gas phase (hereinafter referred to as a refrigerant with a high degree of dryness) in a gas-liquid separation section 40b. ) and are separated into. Specifically, the refrigerant that has flowed into the gas-liquid separation section 40b first flows into the through hole 431. As described above, the through hole 431 is formed to slope upward from the windward region 1a to the leeward region 1b. Therefore, among the refrigerants that have flowed into the through-holes 431, refrigerants with low dryness move downward along the slope of the through-holes 431 due to gravity, thereby moving to the windward region 1a. On the other hand, among the refrigerants that have flowed into the through holes 431, refrigerants with high dryness move upward along the slope of the through holes 431 to the leeward region 1b. Thereby, the refrigerant that has flowed into the gas-liquid separator 40b is separated into refrigerant C, which has a low degree of dryness, and refrigerant D, which has a high degree of dryness.

In addition, in the gas-liquid separation section 40b, the refrigerant that has passed through the through hole 421 passes through the through hole 431 and collides with the fifth plate member 450, and the refrigerant that has rebounded from the collision passes through the through hole 431 again. It collides with the second plate member 420. The gas-liquid separator 40b also separates the refrigerant into gas and liquid by repeating this collision.

Among the refrigerants separated into gas and liquid as described above, refrigerant C with a low degree of dryness and containing a large amount of liquid phase passes through the through hole 451a of the fifth plate member 450. On the other hand, the dry refrigerant D containing a large amount of gas phase passes through the through hole 451b of the fifth plate member 450.

In this way, the gas-liquid separator 40b separates the refrigerant that has flowed into the gas-liquid separator 40b into the refrigerant C with a low degree of dryness and the refrigerant D with a high degree of dryness, and transfers the refrigerant C with a low degree of dryness to an upwind region. 1a, and the refrigerant D having a high degree of dryness is guided to the leeward region 1b.

The refrigerant C with low dryness and the refrigerant D with high dryness flowing out from the gas-liquid separation part 40b flow into the second flat tube 10b through the through hole 441. Here, although the refrigerant C with a low degree of dryness and the refrigerant D with a high degree of dryness that flowed out from the gas-liquid separation part 40b are once merged in the through hole 441, the magnitude relationship of the degree of dryness remains substantially maintained. 2 into the flat tube 10b. Therefore, the refrigerant C with low dryness flows into the windward refrigerant passage 15a of the second flat tube 10b, and the refrigerant D with high dryness flows into the leeward refrigerant passage 15b.

In this way, the distributor 40 once merges the refrigerants flowing out from each refrigerant passage 15 of the first flat tube 10a in the merging section 40a, and then converts the refrigerant after the merging into a refrigerant with a low degree of dryness in the gas-liquid separation section 40b. It separates into refrigerant C and refrigerant D, which has a high degree of dryness. Then, the distributor 40 guides the refrigerant C with a low degree of dryness to the windward side refrigerant passage 15a of the second flat tube 10b, and guides the refrigerant D with a high degree of dryness to the leeward side refrigerant passage 15b of the second flat tube 10b. . That is, at the outlet (through hole 441) of the refrigerant flow path 400A formed inside the distributor 40, the dryness of the refrigerant flowing out from the upwind region 1a of the exit of the refrigerant flow path 400A and the refrigerant flow are determined. The dryness of the refrigerant flowing out from the leeward region 1b at the outlet of the refrigerant flow path 400A is defined as the degree of dryness of the refrigerant in the windward region 1a and the leeward region 1b when it flows in from the entrance (through hole 411) of the refrigerant flow path 400A. It flows out in the opposite direction.

Note that in the above description, the gas-liquid separation section 40b includes the third plate member 430 and the fifth plate member 450, but the fifth plate member 450 may be omitted. In the gas-liquid separation section 40b, when the fifth plate-like member 450 is omitted, the gas-liquid separation effect is lower than when the fifth plate-like member 450 is not omitted, but a certain gas-liquid separation effect cannot be obtained. It will be done. Therefore, the distributor 40 only needs to include at least four plate members: the first plate member 410, the second plate member 420, the third plate member 430, and the fourth plate member 440. Furthermore, the distributor 40 only needs to have the above-mentioned refrigerant flow path 400A. For this reason, the distributor 40 is not limited to the structure in which a plurality of plate-like members are stacked and joined together as described above, but is composed of a single plate-like member having the thickness of a plurality of plate-like members. You may. This point also applies to the embodiments described below.

[Operation of heat exchanger]
Next, the operation of the heat exchanger including the distributor 40 will be described, taking as an example the operation when the heat exchanger functions as an evaporator of a refrigeration cycle device. As shown by the arrow in FIG. 1, the refrigerant first flows into one header 20 from the inlet 20a. The refrigerant that has flowed into one header 20 is distributed to each first flat tube 10a. The refrigerant distributed to each first flat tube 10a passes through the plurality of refrigerant passages 15 from the left end to the right end of the first flat tube 10a, and flows into the distributor 40.

As described above, the distributor 40 joins the refrigerants that have passed through the refrigerant passages 15 of the first flat tube 10a at the merging portion 40a. Thereby, the heat exchanger can eliminate unevenness in the dryness of each refrigerant flowing out from each refrigerant passage 15 of the first flat tube 10a. As shown in FIG. 5, the distributor 40 guides the refrigerant C with low dryness to the windward side refrigerant passage 15a of the second flat tube 10b, and guides the refrigerant D with high dryness to the leeward side of the second flat tube 10b. It leads to the refrigerant passage 15b.

In this way, the heat exchanger guides the refrigerant C with low dryness to the upwind refrigerant passage 15a with respect to the second flat tube 10b located downstream of the refrigerant of the distributor 40. Therefore, compared to the case where the refrigerant with a high degree of dryness is directly guided to the windward side refrigerant passage 15a of the second flat tube 10b without providing the distributor 40, the heat exchanger The heat transfer coefficient can be improved. As a result, the heat exchanger can improve the heat exchange efficiency of the heat exchanger as a whole.

[Change in dryness]
FIG. 6 is a diagram showing a change in the dryness of the refrigerant from the inlet to the outlet of the heat exchanger according to the first embodiment. FIG. 7 is a diagram showing, as a comparative example, a change in the dryness of the refrigerant from the inlet to the outlet in a heat exchanger that does not use a distributor. In FIGS. 6 and 7, the horizontal axis indicates the position in the first direction, and the vertical axis indicates the dryness of the refrigerant. In FIGS. 6 and 7, the solid line indicates the refrigerant flowing in the windward region 1a, and the dashed line indicates the refrigerant flowing in the leeward region 1b.

In the comparative example shown in FIG. 7, the dryness of the refrigerant flowing in the windward region 1a from the inlet 20a to the outlet 20b is higher than the dryness of the refrigerant flowing in the leeward region 1b. Therefore, in the comparative example, the refrigerant evaporates preferentially in the windward region 1a and the dryness increases, and in the leeward region 1b, the refrigerant does not evaporate sufficiently and the dryness continues to be low.

On the other hand, in the first embodiment shown in FIG. 6, as is clear from the comparison with FIG. They have been replaced. Therefore, in the first embodiment, the evaporation of the refrigerant flowing in the windward region 1a after the distributor 40 is promoted again, and the degree of dryness is increased. As a result, the heat exchanger of the first embodiment can improve the heat transfer coefficient of the second flat tube 10b after passing through the distributor 40, compared to a configuration that does not use the distributor 40, and improves the heat exchanger as a whole. Heat exchange efficiency can be improved. Note that the arrows extending in the vertical direction in FIGS. 6 and 7 indicate the average amount of change in dryness from the inlet to the outlet. FIG. 6 shows that since the heat transfer coefficient is improved compared to FIG. 7, the average dryness change amount is large, that is, the amount of heat exchange is increased.

As described above, since the heat exchanger of the first embodiment includes the distributor 40, the heat transfer coefficient of the second flat tube 10b located downstream of the refrigerant of the distributor 40 can be improved compared to the comparative example. As a result, the heat exchange efficiency of the entire heat exchanger can be improved.

Note that although the case where the heat exchanger functions as an evaporator has been described above, it may also be used to function as a condenser of a refrigeration cycle device. When the heat exchanger functions as a condenser of a refrigeration cycle device, the direction in which the refrigerant flows is opposite to that described above.

Furthermore, in the above description, a configuration is shown in which the distributor 40 is formed extending in the third direction and is commonly formed in a plurality of flat tubes 10 arranged in parallel in the third direction. A correspondingly divided configuration may also be used. Moreover, although the heat exchanger has shown a configuration in which the distributor 40 corresponds to all of the flat tubes 10, it may be configured to correspond to not necessarily all of the flat tubes 10 but some of the flat tubes 10. These points also apply to the embodiments described below.

Furthermore, in the above description, the position of the distributor 40 in the first direction in the heat exchanger is assumed to be at the center of the flat tube 10 in the first direction, but it is not limited to the center, and may be located halfway in the first direction. Bye. The position of the distributor 40 in the first direction in the heat exchanger may be determined based on the heat flow velocity distribution in the second direction and the air volume distribution in the first direction. This point also applies to the embodiments described below.

[Effects of Embodiment 1]
As explained above, the heat exchanger according to the first embodiment includes the distributor 40 provided in the middle of the flat tube 10. The distributor 40 has a refrigerant flow path 400A formed of a through hole. The refrigerant flow path 400A calculates the dryness of the refrigerant flowing out from the upwind region 1a of the outlet of the refrigerant flow path 400A and the dryness of the refrigerant flowing out from the leeward region 1b of the exit of the refrigerant flow path 400A. The degree of dryness of the refrigerant in the windward region 1a and the leeward region 1b when it flows in from the inlet of the refrigerant is opposite to that of the refrigerant flowing out.

With the above configuration, the heat exchanger of Embodiment 1 can improve the heat transfer coefficient in the downstream portion of the refrigerant from the distributor 40 in the flat tube 10, and as a result, the heat exchange efficiency of the heat exchanger as a whole can be improved.

The distributor 40 is disposed in the middle of the flat tube 10 in the first direction. The flat tube 10 includes a first flat tube 10a upstream of the distributor 40 and a second flat tube 10b downstream of the distributor 40. The distributor 40 includes a confluence section 40a and a gas-liquid separation section 40b that communicate with the plurality of refrigerant passages 15 in the first flat tube 10a. The gas-liquid separation section 40b is formed in communication with the confluence section 40a, separates the gas and liquid of the refrigerant that has passed through the confluence section 40a, and guides the liquid phase refrigerant to the windward side refrigerant passage 15a of the second flat tube 10b. At the same time, the gaseous refrigerant is guided to the leeward refrigerant passage 15b of the second flat tube 10b.

With the above configuration, the heat exchanger of Embodiment 1 allows the refrigerant to flow into the confluence section 40a and the gas-liquid separation section 40b in the distributor 40, so that the heat in the second flat tube 10b, which is the refrigerant downstream section of the distributor 40, can be increased. The transfer coefficient can be improved, and as a result, the heat exchange efficiency of the heat exchanger as a whole can be improved.

Embodiment 2.
FIG. 8 is a schematic front view of the heat exchanger according to the second embodiment. The heat exchanger of the second embodiment differs from the first embodiment in the configuration of the distributor. The other configurations are the same or equivalent to those of the first embodiment. Hereinafter, the structure of the second embodiment that is different from the first embodiment will be mainly explained, and the structures that are not explained in the second embodiment are the same as those of the first embodiment.

As shown in FIG. 8, the exchanger of the second embodiment includes a plurality of flat tubes 10 arranged at intervals and through which refrigerant flows, and a pair of flat tubes 10 arranged at both ends of the plurality of flat tubes 10 in the extending direction. It has a header 20 and a plurality of fins 30 arranged between two adjacent flat tubes. The heat exchanger further includes a distributor 50 arranged at the center of the plurality of flat tubes 10 in the extending direction. Each of the plurality of flat tubes 10 extends in the vertical direction. The plurality of flat tubes 10 are arranged in parallel with each other at intervals in the left-right direction.

The pair of headers 20 and distributor 50 extend in the left-right direction along the direction in which the plurality of flat tubes 10 are arranged in parallel. Hereinafter, similarly to Embodiment 1, the stretching direction of the flat tube 10 will be referred to as the first direction, and the direction perpendicular to the first direction in which the refrigerant passages 15 of the flat tube 10 are parallel will be referred to as the second direction. A direction perpendicular to the second direction is referred to as a third direction. In the second embodiment, the first direction is the up-down direction, the second direction is the depth direction, and the third direction is the left-right direction. The second direction is also the direction in which air passes.

Although FIG. 8 shows that the first direction in which the flat tube 10 extends is the vertical direction, which is the direction of gravity, it may be in the horizontal direction as in the first embodiment. Further, although FIG. 8 shows an example in which the fins 30 are corrugated fins, they may be plate-shaped fins as in the first embodiment. Furthermore, the heat exchanger of the second embodiment may be a finless heat exchanger that does not include the fins 30.

When the heat exchanger functions as an evaporator of a refrigeration cycle device, refrigerant flows into one header 20 from the inlet 20a. The refrigerant that has flowed into one header 20 is distributed to each of the first flat tubes 10a, flows through each first flat tube 10a from the lower end toward the upper end, and then flows into the distributor 50. Although details of the distributor 50 will be described later, independent refrigerant flow paths are formed in the distributor 50 corresponding to each of the flat tubes 10. Therefore, the refrigerant flowing through each first flat tube 10a from the lower end to the upper end flows into each second flat tube 10b without mixing with the refrigerant flowing through other first flat tubes 10a in the distributor 50. Inflow. After the refrigerant flows through each second flat tube 10b from the lower end to the upper end, the refrigerant joins at the other header 20 and flows out from the outlet 20b.

[Structure of distributor 50]
FIG. 9 is an exploded perspective view of the distributor of the heat exchanger according to the second embodiment. FIG. 10 is a plan view of each plate member that constitutes the distributor of the heat exchanger according to the second embodiment. FIG. 10(a) is a plan view of the first plate member. FIG. 10(b) is a plan view of the second plate member. FIG. 10(c) is a plan view of the third plate member. FIG. 10(d) is a plan view of the fourth plate member. FIG. 10(e) is a plan view of the fifth plate member. The distributor 50 extends in the third direction as shown in FIGS. 9 and 10, and forms independent refrigerant flow paths corresponding to each of the plurality of flat tubes 10 arranged in parallel in the third direction. .

The refrigerant flow path of the distributor 50 has a first flow path 500A (see FIG. 12) and a second flow path 500B (see FIG. 12). The first flow path 500A is a flow path that guides the refrigerant in the windward refrigerant passage 15a of the first flat tube 10a to the leeward refrigerant passage 15b of the second flat tube 10b. The second flow path 500B is a flow path that guides the refrigerant in the leeward refrigerant passage 15b of the first flat tube 10a to the upwind refrigerant passage 15a of the second flat tube 10b. The first flow path 500A and the second flow path 500B are composed of through holes, and the specific configuration will be described below.

The distributor 50 includes a first plate member 510, a second plate member 520, a third plate member 530, a fourth plate member 540, and a fifth plate member 550. The first plate member 510, the second plate member 520, the third plate member 530, the fourth plate member 540, and the fifth plate member 550 are all formed using flat metal plates.

The first plate member 510, the second plate member 520, the third plate member 530, the fourth plate member 540, and the fifth plate member 550 have a band-like shape that is long in the third direction. Further, the outer edges of the first plate member 510, the second plate member 520, the third plate member 530, the fourth plate member 540, and the fifth plate member 550 have the same shape. are doing. The first plate member 510, the second plate member 520, the third plate member 530, the fourth plate member 540, and the fifth plate member 550 have their thickness directions parallel to the extending direction of the flat tube 10. It is arranged so that In other words, the first plate member 510, the second plate member 520, the third plate member 530, the fourth plate member 540, and the fifth plate member 550 each have a plate surface that corresponds to the extending direction of the flat tube 10. arranged vertically.

The distributor 50 has a first plate member 510, a second plate member 520, a third plate member 530, a fourth plate member 540, and a fifth plate member 550 at a distance from the first flat tube 10a. It has a structure in which the layers are stacked in this order from the closest one. Adjacent members among these plate-like members are joined by brazing. Although not shown in FIGS. 9 and 10, the distributor 50 includes insertion holes into which the respective ends of the first flat tube 10a and the second flat tube 10b are inserted, as in the first embodiment. It is equipped with two plate-like members for inserting tubes. One of the two tube insertion plate members is arranged between the first flat tube 10a and the first plate member 510, and the other of the two plate members is arranged between the second flat tube 10b and the fifth plate member 510. It is arranged between the plate member 550 and the plate member 550 .

Although the distributor 40 of the first embodiment was configured to include a confluence section 40a and a gas-liquid separation section 40b, the distributor 50 of the second embodiment does not include these. The distributor 50 of the second embodiment guides refrigerant with a low degree of dryness to the windward side refrigerant passage 15a of the second flat tube 10b, and guides refrigerant with a high degree of dryness to the leeward side refrigerant passage 15b of the second flat tube 10b. This is common to the distributor 40 of Embodiment 1 in this respect, but the configuration for forming the flow is different.

Hereinafter, the constituent parts of the distributor 50 that correspond to one flat tube 10 will be explained with reference to FIGS. 9 and 10 and the following FIG. 11.

FIG. 11 is a diagram illustrating a state in which two adjacent plate members are stacked on top of each other among the plurality of plate members configuring the distributor of the heat exchanger according to the second embodiment. FIG. 11A is a plan view of the stacked state of the first plate member 510 and the second plate member 520, viewed from the second flat tube 10b side. FIG. 11(b) is a plan view of the stacked state of the second plate member 520 and the third plate member 530, viewed from the second flat tube 10b side. FIG. 11(c) is a plan view of a state in which the third plate member 530 and the fourth plate member 540 are stacked, viewed from the second flat tube 10b side. FIG. 11(d) is a plan view of the stacked state of the fourth plate-like member 540 and the fifth plate-like member 550, viewed from the second flat tube 10b side.

The configuration described below is formed in the distributor 50 for the number of flat tubes 10 arranged in parallel in the third direction, but since each configuration is the same, one flat tube 10 The corresponding components will be explained. In FIGS. 10 and 11, the portion surrounded by dotted lines corresponds to the component corresponding to one flat tube 10.

(First plate member 510)
The first plate member 510 has a first through hole 511 that serves as an inlet for the refrigerant. The first through hole 511 passes through the first plate member 510 in the thickness direction of the first plate member 510. The first through hole 511 has a flat opening shape similar to the outer peripheral shape of the first flat tube 10a. The opening area of the first through hole 511 is the same as or larger than the opening area of the insertion hole of the first flat tube 10a formed in the tube insertion plate member not shown in FIGS. 9 to 11. .

(Second plate member 520)
The second plate member 520 has two second through

holes

521a and 521b through which the refrigerant that has passed through the first through hole 511 passes. Each of the second through

holes

521a and 521b penetrates the second plate member 520 in the thickness direction of the second plate member 520. The second through

holes

521a and 521b have the same shape. Each of the second through

holes

521a and 521b has a rectangular shape, and the length in the third direction is longer than the length in the third direction of the first through hole 511, and the length in the second direction is longer than the length of the first through hole 511. shorter than the length in the second direction. The second through

holes

521a and 521b are arranged separately in the windward region 1a and the leeward region 1b. The second through-hole 521a in the windward region 1a (hereinafter referred to as the second windward-side through-hole 521a) and the second through-hole 521b in the leeward region 1b (hereinafter referred to as the second leeward-side through-hole 521b) are The position of the direction is different. The windward side second through hole 521a is arranged on the left side of the leeward side second through hole 521b, and the leeward side second through hole 521b is arranged on the right side of the windward side second through hole 521a.

Since the windward side second through hole 521a and the leeward side second through hole 521b are formed in the above arrangement and shape in the second plate member 520, there is no through hole in these through holes as shown in FIG. 10(b). As shown by solid line arrows and dotted line arrows inside the holes, flow paths are formed in which the refrigerant flows in directions away from each other in the third direction. The flow of the refrigerant indicated by solid line arrows and dotted line arrows will be explained again.

(Third plate member 530)
The third plate member 530 has two through holes, third through

holes

531a and 531b. The refrigerant that has passed through the second windward through hole 521a passes through the third through hole 531a, and the refrigerant that has passed through the second through hole 521b on the leeward side passes through the third through hole 531b. Each of the third through

holes

531a and 531b penetrates the third plate member 530 in the thickness direction of the third plate member 530. The third through

holes

531a and 531b have the same shape. Each of the third through

holes

531a and 531b has a flat opening shape similarly to the first through hole 511. The third through

holes

531a and 531b are spaced apart in the third direction.

Since the third through

holes

531a and 531b are formed in the above arrangement and shape in the third plate-like member 530, the solid lines inside the through holes in FIG. As shown by arrows and dotted line arrows, flow paths are formed in which the refrigerant flows in mutually opposite directions in the second direction. The flow of the refrigerant indicated by solid line arrows and dotted line arrows will be explained again.

(Fourth plate member 540)
The fourth plate member 540 has two through holes, fourth through

holes

541a and 541b. The refrigerant that has passed through the third through hole 531b passes through the fourth through hole 541a, and the refrigerant that has passed through the third through hole 531a passes through the fourth through hole 541b. Each of the fourth through

holes

541a and 541b penetrates the fourth plate member 540 in the thickness direction of the fourth plate member 540. The fourth through

holes

541a and 541b have the same shape. Each of the fourth through

holes

541a and 541b has a rectangular shape, and the length in the third direction is longer than the length in the third direction of the third through

holes

531a and 531b, and the length in the second direction is longer than the length in the third direction. It is shorter than the length in the second direction of the three through

holes

531a and 531b.

The fourth through

holes

541a and 541b are arranged separately in the windward region 1a and the leeward region 1b. The fourth through hole 541a in the windward region 1a and the fourth through hole 541b in the leeward region 1b have different positions in the third direction. The fourth through hole 541a in the windward region 1a (hereinafter referred to as the fourth through hole 541a on the windward side) is located on the right side and leeward of the fourth through hole 541b in the leeward region 1b (hereinafter referred to as the fourth through hole 541b on the leeward side). The fourth side through hole 541b is arranged on the left side of the windward side fourth through hole 541a.

In the fourth plate member 540, the windward side fourth through hole 541a and the leeward side fourth through hole 541b are formed in the above arrangement and shape, so that in these through holes, as shown in FIG. 10(d), As shown by the arrows in the through-hole, a flow path is formed in which the refrigerant flows in directions approaching each other in the third direction. The flow of refrigerant will be explained again.

(Fifth plate member 550)
The fifth plate member 550 has a fifth through hole 551 that serves as an outlet for the refrigerant. The fifth through hole 551 passes through the fifth plate member 550 in the thickness direction of the fifth plate member 550. The fifth through hole 551 has a flat opening shape similar to the outer peripheral shape of the first flat tube 10a. The opening area of the fifth through hole 551 is the same as the opening area of the first through hole 511 of the first plate member 510.

As shown in FIG. 11(a), when the first plate member 510 and the second plate member 520 are overlapped, the second through hole 521a on the windward side of the second plate member 520 is located in the right side area. It overlaps and communicates with the windward region 1a of the 1 through hole 511. On the other hand, the second through hole 521b on the leeward side of the second plate member 520 overlaps and communicates with the leeward region 1b of the first through hole 511 in the left side region. In the component surrounded by the dotted line in FIG. 11, dots indicate portions where through holes adjacent to each other in the first direction overlap and communicate with each other.

In this way, by overlapping the first plate member 510 and the second plate member 520, the through holes adjacent in the first direction are partially communicated with each other, and the refrigerant flowing out from the first flat tube 10a flows in. In the flow path, a windward side flow path and a leeward side flow path are formed independently.

As shown in FIG. 11(b), when the second plate member 520 and the third plate member 530 are overlapped, the third through hole 531a of the third plate member 530 is located in the windward region 1a. It overlaps and communicates with the left side region of the upper second through hole 521a. On the other hand, the third through hole 531b of the third plate member 530 overlaps and communicates with the right side region of the leeward second through hole 521b in the leeward region.

As shown in FIG. 11(c), when the third plate member 530 and the fourth plate member 540 are overlapped, the fourth through hole 541b on the leeward side of the fourth plate member 540 is located in the left side area. It overlaps and communicates with the leeward region 1b of the No. 3 through hole 531a. On the other hand, the fourth through hole 541a on the windward side of the fourth plate member 540 overlaps and communicates with the windward region 1a of the third through hole 531b in the right region.

As shown in FIG. 11(d), when the fourth plate member 540 and the fifth plate member 550 are overlapped, the fifth through hole 551 of the fifth plate member 550 is located in the windward region 1a. It communicates with the left side region of the upper fourth through hole 541a, and communicates with the right side region of the leeward fourth through hole 541b in the leeward region 1b.

By stacking the first plate-like member 510, second plate-like member 520, third plate-like member 530, fourth plate-like member 540, and fifth plate-like member 550 formed as described above, each plate-like member The through holes formed in the member partially communicate with each other to form a first flow path 500A and a second flow path 500B. Specifically, the first flow path 500A is a flow path through which the refrigerant flows as shown by a dotted arrow in FIG. 12, which will be described later. The first flow path 500A includes a first through hole 511, a second windward through hole 521a, a third through hole 531a communicating with the second windward through hole 521a, a fourth through hole 541b on the leeward side, and a fifth through hole 551. is formed. The second flow path 500B is a flow path through which the refrigerant flows as shown by solid arrows in FIG. 12, which will be described later. The second flow path 500B includes a first through hole 511, a second through hole 521b on the leeward side, a third through hole 531b communicating with the second through hole 521b on the leeward side, a fourth through hole 541a on the windward side, and a fifth through hole 551. is formed.

[Flow of refrigerant in distributor 50 and action of distributor 50]
FIG. 12 is an explanatory diagram of the flow of refrigerant in the first channel of the distributor of the heat exchanger according to the second embodiment. The refrigerant flowing out from each refrigerant passage 15 of the first flat tube 10a flows into the first through hole 511 of the first plate member 510. Here, the refrigerant that has passed through the windward refrigerant passage 15a of the first flat tube 10a has a high dryness, and the refrigerant that has passed through the leeward refrigerant passage 15b has a low dryness. Therefore, the dotted line arrow indicates a refrigerant with a high degree of dryness, and the solid line arrow indicates a refrigerant with a low degree of dryness. The dotted line arrows and solid line arrows in FIG. 12 correspond to the dotted line arrows and solid line arrows in FIG.

(Flow of highly dry refrigerant)
A refrigerant with a high degree of dryness flows through the first flow path 500A. That is, the refrigerant having a high degree of dryness flowing out from the windward region 1a of the first through hole 511 of the first plate member 510 first flows into the right region of the windward side second through hole 521a of the second plate member 520. After that, it flows toward the left side region of the windward side second through hole 521a as shown by the dotted line arrow. The refrigerant that has flowed to the left side region of the second through hole 521a on the windward side flows into the windward region 1a of the third through hole 531a of the third plate member 530, and flows to the leeward side of the third through hole 531a as shown by the dotted arrow. It flows towards region 1b. The refrigerant flowing toward the leeward region 1b of the third through hole 531a flows into the left region of the leeward fourth through hole 541b of the fourth plate member 540, and as shown by the dotted line arrow, the refrigerant flows into the leeward fourth through hole 541b of the fourth plate member 540. Flows toward the right region of 541b. The refrigerant flowing toward the right side region of the fourth leeward through hole 541b passes through the leeward region 1b of the fifth through hole 551 of the fifth plate member 550, and flows out from the distributor 50. The refrigerant flowing out from the distributor 50, here the refrigerant having a high degree of dryness, flows into the leeward refrigerant passage 15b of the second flat tube 10b.

(flow of refrigerant with low dryness)
The refrigerant with low dryness flows through the second flow path 500B. That is, after the refrigerant with low dryness flowing out from the leeward region 1b of the first through hole 511 of the first plate member 510 flows into the left region of the leeward side second through hole 521b of the second plate member 520, As shown by the solid line arrow, it flows toward the right region of the leeward second through hole 521b. The refrigerant flowing toward the right side area of the second leeward through hole 521b flows into the leeward area 1b of the third through hole 531b of the third plate member 530, and as shown by the solid arrow, the refrigerant flows into the leeward area 1b of the third through hole 531b of the third plate member 530. It flows toward the windward region 1a. The refrigerant flowing toward the windward region 1a of the third through hole 531b flows into the right region of the windward side fourth through hole 541a of the fourth plate member 540, and as shown by the solid line arrow, the refrigerant flows into the windward side fourth through hole 541a of the fourth plate member 540. It flows toward the left side region of the hole 541a. The refrigerant that has flowed toward the left side region of the fourth through hole 541 a on the windward side passes through the windward region 1 a of the fifth through hole 551 of the fifth plate member 550 and flows out from the distributor 50 . The refrigerant flowing out from the distributor 50, here a refrigerant with a low degree of dryness, flows into the upwind refrigerant passage 15a of the second flat tube 10b.

(Effect of distributor 50)
In this way, the distributor 50 guides the highly dry refrigerant flowing out from the windward refrigerant passage 15a of the first flat tube 10a to the leeward refrigerant passage 15b of the second flat tube 10b. Moreover, the distributor 50 guides the refrigerant having a low degree of dryness flowing out from the leeward side refrigerant passage 15b of the first flat tube 10a to the windward side refrigerant passage 15a of the second flat tube 10b. In other words, the distributor 50 determines the dryness of the refrigerant flowing out from the windward region 1a of the outlet of the refrigerant flow path and the refrigerant flow at the outlet of the refrigerant flow path (fifth through hole 551) formed in the distributor 50. The dryness of the refrigerant flowing out from the leeward region 1b at the outlet of the refrigerant flow path is defined as the degree of dryness of the refrigerant in the windward region 1a and the leeward region 1b when it flows in from the entrance of the refrigerant flow path (first through hole 511). It flows out in the opposite direction.

[Change in dryness]
FIG. 13 is a diagram showing a change in the dryness of the refrigerant from the inlet to the outlet of the heat exchanger according to the second embodiment. The horizontal axis indicates the position in the first direction, and the vertical axis indicates the dryness of the refrigerant. In FIG. 13, the solid line indicates the refrigerant flowing in the windward region 1a of the heat exchanger, and the dashed line indicates the refrigerant flowing in the leeward region 1b of the heat exchanger.

In the heat exchanger of the second embodiment, as described above, in the distributor 50 portion, the refrigerant with low dryness and the refrigerant with high dryness are exchanged between the windward region 1a and the leeward region 1b. Therefore, as shown in FIG. 13, the dryness of the refrigerant flowing in the windward region 1a and the refrigerant flowing in the leeward region 1b is different from the dryness at the inlet of the distributor 50 at the outlet of the distributor 50. Subsequently, the windward region 1a and the leeward region 1b are switched. As a result, the refrigerant flowing in the leeward region 1b, which has a low degree of dryness between the inlet 20a of the heat exchanger and the distributor 50, is evaporated and its dryness increases after passing through the distributor 50. . As a result, the heat exchanger of the second embodiment can improve the heat transfer coefficient of the second flat tube 10b after passing through the distributor 50, compared to the case where the distributor 50 is not provided, and the heat exchanger as a whole can improve the heat transfer coefficient of the second flat tube 10b after passing through the distributor 50. Heat exchange efficiency can be improved.

Note that although the case where the heat exchanger functions as an evaporator has been described above, it may also be used to function as a condenser of a refrigeration cycle device. When the heat exchanger functions as a condenser of a refrigeration cycle device, the direction in which the refrigerant flows is opposite to that described above. That is, the refrigerant flows into the header 20 from the outlet 20b, flows through the second flat tube 10b, the distributor 50, and the first flat tube 10a, flows into the header 20, and flows out from the inlet 20a. At this time, the distributor 50 guides refrigerant with a high degree of dryness to the windward side refrigerant passage 15a of the first flat tube 10a, which is the downstream side of the distributor 50, contrary to the case where the heat exchanger is used as an evaporator. , a refrigerant with a low degree of dryness is introduced into the leeward refrigerant passage 15b of the first flat tube 10a. This is because when the heat exchanger functions as a condenser, the dryness of the refrigerant flowing out from the windward side refrigerant passage 15a of the second flat tube 10b, which is the inlet side, is small, and This is because the dryness of the refrigerant flowing out is large.

[Effects of Embodiment 2]
As explained above, in the heat exchanger according to the second embodiment, the refrigerant flow path of the distributor 50 includes the first flow path 500A and the second flow path 500B. The first flow path 500A is a flow path that guides the refrigerant in the windward refrigerant passage 15a of the first flat tube 10a to the leeward refrigerant passage 15b of the second flat tube 10b. The second flow path 500B is a flow path that guides the refrigerant in the leeward refrigerant passage 15b of the first flat tube 10a to the upwind refrigerant passage 15a of the second flat tube 10b.

With the above configuration, the heat exchanger of the second embodiment can improve the heat transfer coefficient of the second flat tube 10b, and as a result, the heat exchange efficiency of the heat exchanger as a whole can be improved.

Embodiment 3.
The heat exchanger of the third embodiment differs from the second embodiment in the configuration of the distributor. The other configurations are the same or equivalent to those of the second embodiment. Hereinafter, the structure of the third embodiment that is different from the second embodiment will be mainly explained, and the structures that are not explained in the third embodiment are the same as those of the second embodiment.

FIG. 14 is a plan view of each plate member that constitutes the distributor of the heat exchanger according to the third embodiment. FIG. 14(a) is a plan view of the first plate member. FIG. 14(b) is a plan view of the second plate member. FIG. 14(c) is a plan view of the third plate member. FIG. 14(d) is a plan view of the fourth plate member. FIG. 14(e) is a plan view of the fifth plate member.

The distributor 50 of the third embodiment has a configuration in which the sizes of through holes provided in the second plate member 520 and the fourth plate member 540 are different from those of the distributor 50 of the second embodiment. Specifically, in the second plate member 520, the windward side second through hole 521a has a larger opening area than the leeward side second through hole 521b. Further, in the fourth plate member 540, the fourth through hole 541b on the leeward side has a larger opening area than the second through hole 521a on the windward side. Both the windward-side second through-hole 521a and the leeward-side fourth through-hole 541b, which have a larger opening area, are through-holes through which a refrigerant with a high degree of dryness passes. In other words, in the distributor 50 of the third embodiment, a part of the cross-sectional area of the first flow path 500A through which the refrigerant with high dryness passes is a part of the cross-sectional area of the second flow path 500B through which the refrigerant with low dryness passes. It has a configuration larger than a part of the road cross-sectional area.

The operation of the above configuration will be explained. A refrigerant with a high degree of dryness has a lower density than a refrigerant with a low degree of dryness, and its flow rate increases, resulting in an increase in pressure loss. In the above configuration, in the second plate-like member 520 and the fourth plate-like member 540, the opening area of the through-hole through which the refrigerant with high dryness passes is made larger than the through-hole through which the refrigerant with low dryness passes. It is possible to reduce the pressure loss of the refrigerant when it passes through the container.

[Effects of Embodiment 3]
As explained above, the heat exchanger of Embodiment 3 can obtain the same effects as Embodiment 2, and the pressure loss of the refrigerant when passing through the distributor is greater than the heat exchanger of Embodiment 2. can be reduced.

Embodiment 4.
In the first to third embodiments described above, the refrigerant flows in one direction in the distributor. Embodiment 4 has a configuration in which the refrigerant flows in one direction in the distributor and then flows back in the opposite direction. The following will mainly explain the configurations of Embodiment 4 that are different from Embodiments 1 to 3, and the configurations not described in Embodiment 4 are the same as Embodiments 1 to 3. be.

FIG. 15 is a schematic perspective view of a heat exchanger according to Embodiment 4. The heat exchanger of the fourth embodiment includes a first heat exchange section 60, a second heat exchange section 70, a pair of headers 20, and a distributor 80.

The first heat exchange section 60 includes a plurality of first flat tubes 10a arranged at intervals and through which refrigerant flows, and a plurality of fins 30. Each of the plurality of first flat tubes 10a extends in the horizontal direction. The plurality of first flat tubes 10a are arranged in parallel at intervals in the vertical direction.

The second heat exchange section 70 has a similar configuration to the first heat exchange section 60. The second heat exchange section 70 includes a plurality of second flat tubes 10b arranged at intervals and through which a refrigerant flows, and a plurality of fins 30. Each of the plurality of second flat tubes 10b extends in the horizontal direction. The plurality of second flat tubes 10b are arranged in parallel at intervals in the vertical direction.

The first flat tube 10a and the second flat tube 10b have the shapes shown in FIG. 2 above. Further, in the first heat exchange section 60 and the second heat exchange section 70, the fins 30 are illustrated as plate-shaped fins in FIG. 15, but may be corrugated fins. Further, the heat exchanger may be a finless heat exchanger that does not include the fins 30. In addition, below, when the 1st flat tube 10a and the 2nd flat tube 10b are not distinguished, they are collectively called the flat tube 10.

The pair of headers 20 are arranged at the ends of each of the first heat exchange section 60 and the second heat exchange section 70 in the first direction. The pair of headers 20 extend in the third direction.

The left end of the plurality of first flat tubes 10a of the first heat exchange section 60 is connected to the distributor 80, and the right end of the plurality of first flat tubes 10a is connected to the windward side header 20 of the pair of headers 20. has been done. The left ends of the plurality of second flat tubes 10b of the second heat exchange section 70 are connected to the distributor 80, and the right ends of the plurality of second flat tubes 10b are connected to the leeward side header 20 of the pair of headers 20. has been done.

The distributor 80 extends in the third direction and is arranged at the left end of the first heat exchange section 60 and the second heat exchange section 70 so as to straddle the first heat exchange section 60 and the second heat exchange section 70. ing. The distributor 80 is connected to one end of the first flat tube 10a and the second flat tube 10b on the same side in the first direction, specifically, to the left end. The distributor 80 has the same functions as the distributors in each of the embodiments described above. In other words, the distributor 80 converts the dryness of the refrigerant flowing out from the upwind region 1a of the outlet of the refrigerant flow path and the dryness of the refrigerant flowing out from the leeward region 1b of the exit of the refrigerant flow path into The degree of dryness of the refrigerant in the windward region 1a and the leeward region 1b when it flows in is opposite to that of the refrigerant when it flows out. In addition, in the fourth embodiment, instead of considering the first heat exchange section 60 as an upwind region and the second heat exchange section 70 as a leeward region, each of the first heat exchange section 60 and the second heat exchange section 70 is , it is assumed that there is an upwind region and a leeward region.

When the heat exchanger functions as an evaporator of the refrigeration cycle device, the refrigerant flows into the header 20 on the windward side from the inlet 20a. The refrigerant that has flowed into the header 20 on the windward side is distributed to each of the plurality of first flat tubes 10a, flows through each first flat tube 10a from the right end to the left end, and then flows into the distributor 80. The refrigerant that has flowed into the distributor 80 flows from right to left within the distributor 80, and then flows back in the opposite direction.

Although details of the distributor 80 will be described later, independent refrigerant flow paths are formed in the distributor 80 corresponding to each of the flat tubes 10 arranged in parallel in the third direction. Therefore, the refrigerant flowing through each first flat tube 10a from the right end to the left end turns around and flows inside the distributor 80 without mixing with the refrigerant that has flowed through the other first flat tubes 10a in the distributor 80, It flows into each second flat tube 10b. After the refrigerant flows through each second flat tube 10b from the left end to the right end, the refrigerant joins at the header 20 on the leeward side and flows out from the outlet 20b. When the heat exchanger functions as a condenser of a refrigeration cycle device, the direction in which the refrigerant flows is opposite to that described above.

[Structure of distributor 80]
FIG. 16 is an exploded perspective view of the distributor of the heat exchanger according to the fourth embodiment. FIG. 17 is a plan view of each plate member forming the distributor of the heat exchanger according to the fourth embodiment. FIG. 17(a) is a plan view of the first plate member. FIG. 17(b) is a plan view of the second plate member. FIG. 17(c) is a plan view of the third plate member. FIG. 17(d) is a plan view of the fourth plate member. The distributor 80 extends in the third direction as shown in FIGS. 16 and 17, and forms independent refrigerant flow paths corresponding to each of the plurality of flat tubes 10 arranged in parallel in the third direction. .

The refrigerant flow path of the distributor 80 has a first flow path 800A (see FIG. 19) and a second flow path 800B (see FIG. 19). The first flow path 800A and the second flow path 800B allow the refrigerant flowing out from the left end of the first flat tube 10a to flow in the first direction, and then flow back in the opposite direction toward the left end of the second flat tube 10b. It is a flow path. The first flow path 800A is a flow path that causes the refrigerant flowing out from the windward refrigerant passage 15a of the first flat tube 10a to flow into the leeward refrigerant passage 15b of the second flat tube 10b. The second flow path 800B is a flow path that causes the refrigerant flowing out from the leeward refrigerant passage 15b of the first flat tube 10a to flow into the upwind refrigerant passage 15a of the second flat tube 10b. The first flow path 800A and the second flow path 800B are composed of through holes, and the specific configuration will be described below.

The distributor 80 has a first plate member 810, a second plate member 820, a third plate member 830, and a fourth plate member 840. The first plate member 810, the second plate member 820, the third plate member 830, and the fourth plate member 840 are all formed using flat metal plates.

The first plate-like member 810, the second plate-like member 820, the third plate-like member 830, and the fourth plate-like member 840 have a band-like shape that is long in the third direction. Furthermore, the outlines of the outer edges of the first plate member 810, the second plate member 820, the third plate member 830, and the fourth plate member 840 have the same shape. The first plate-like member 810, the second plate-like member 820, the third plate-like member 830, and the fourth plate-like member 840 are arranged so that their thickness directions are parallel to the extending direction of the flat tube 10. There is. In other words, the first plate member 810, the second plate member 820, the third plate member 830, and the fourth plate member 840 are arranged such that their respective plate surfaces are perpendicular to the extending direction of the flat tube 10. has been done.

The distributor 80 includes a first plate-like member 810, a second plate-like member 820, a third plate-like member 830, and a fourth plate-like member 840 in this order from the one closest to the flat tube 10 in the first direction. It has a laminated structure. Adjacent members among these plate-like members are joined by brazing. Although not shown in FIG. 16, the distributor 80 is made of a single sheet having insertion holes into which the respective ends of the first flat tube 10a and the second flat tube 10b are inserted, as in the first embodiment. It is equipped with a plate-like member for inserting a tube. The tube insertion plate member is provided between the flat tube 10 and the first plate member 810.

The flow path portion corresponding to one flat tube 10 (first flat tube 10a and second flat tube 10b) in the distributor 80 will be described below with reference to FIGS. 16 and 17 and the following FIG. 18. do.

FIG. 18 is a diagram illustrating a state in which two adjacent plate members of the plurality of plate members constituting the distributor of the heat exchanger according to Embodiment 4 are overlapped. FIG. 18(a) is a plan view of the stacked state of the first plate member 810 and the second plate member 820, viewed from the first flat tube 10a side. FIG. 18(b) is a plan view of the stacked state of the second plate member 820 and the third plate member 830, viewed from the first flat tube 10a side. FIG. 18(c) is a plan view of the stacked third plate member 830 and fourth plate member 840 viewed from the first flat tube 10a side.

Since the configuration of the flow path portion corresponding to each flat tube is the same, the configuration of the flow path portion corresponding to the uppermost flat tube will be described as a representative. In FIGS. 17 and 18, the portion surrounded by dotted lines corresponds to the component corresponding to the uppermost flat tube 10. In FIG. 18, dots indicate portions where through holes adjacent in the first direction overlap and communicate with each other in the component surrounded by dotted lines.

(First plate member 810)
The first plate member 810 has a first through hole 811a that serves as an inlet for the refrigerant to the distributor 80, and a second through hole 811b that serves as an outlet for the refrigerant from the distributor 80. The first through hole 811a and the second through hole 811b penetrate the first plate member 810 in the thickness direction of the first plate member 810. The first through hole 811a and the second through hole 811b have a flat opening shape similar to the outer peripheral shape of the flat tube 10. The first through hole 811a and the second through hole 811b are spaced apart in the second direction. The first through hole 811a and the second through hole 811b are at the same position in the third direction. The first through hole 811a is formed at a position facing the first flat tube 10a, and communicates with the plurality of refrigerant passages 15 of the first flat tube 10a. The second through hole 811b is formed at a position facing the second flat tube 10b, and communicates with the plurality of refrigerant passages 15 of the second flat tube 10b.

(Second plate member 820)
The second plate member 820 communicates with the first through hole 811a of the first plate member 810 and has two third through holes 821a1 and 821a2 spaced apart in the second direction. Further, the second plate member 820 has two fourth through holes 821b1 and 821b2 that communicate with the second through hole 811b of the first plate member 810 and are spaced apart in the second direction. The third through holes 821a1 and 821a2 penetrate the second plate-like member 820 in the thickness direction of the second plate-like member 820. The fourth through holes 821b1 and 821b2 penetrate the second plate-like member 820 in the thickness direction of the second plate-like member 820.

The third through holes 821a1 and 821a2 have a rectangular shape, and the length in the third direction is longer than the length in the third direction of the first through hole 811a, and the length in the second direction is longer than that of the first through hole 811a. It is shorter than the length in the second direction. The third through holes 821a1 and 821a2 are spaced apart in the second direction, and are arranged separately in the windward region 1a and the leeward region 1b. Further, the third through hole 821a1 in the windward region 1a (hereinafter referred to as the third through hole 821a1 on the windward side) and the third through hole 821a2 in the leeward region 1b (hereinafter referred to as the third through hole 821a2 on the leeward side) are arranged in the third direction. (vertical direction) positions are different.

The third through-hole 821a1 on the windward side is arranged above the third through-hole 821a2 on the leeward side, and the third through-hole 821a2 on the leeward side is arranged below the third through-hole 821a1 on the windward side. Specifically, the position of the windward side third through hole 821a1 in the third direction is that the windward side third through hole 821a1 is divided vertically into two at the center in the third direction, and the first through hole is located in the lower region. 811a. Moreover, the position of the leeward side third through hole 821a2 in the third direction is such that the leeward side third through hole 821a2 is divided into two vertically at the center in the third direction, and the upper region is connected to the first through hole 811a. It is set to communicate.

With the above configuration, as will be described in detail below, the windward side third through hole 821a1 and the leeward side third through hole 821a2 flow in a direction in which they mutually flow in the third direction as shown by the arrow in the through hole in FIG. 18(b). A flow path is formed through which the refrigerant flows.

The fourth through holes 821b1 and 821b2 have a rectangular shape, and the length in the third direction is longer than the length in the third direction of the second through hole 811b, and the length in the second direction is longer than that of the second through hole 811b. It is shorter than the length in the second direction. The fourth through holes 821b1 and 821b2 are spaced apart in the second direction, and are arranged separately in the windward region 1a and the leeward region 1b. Further, the fourth through hole 821b1 in the windward region 1a (hereinafter referred to as the fourth through hole 821b1 on the windward side) and the fourth through hole 821b2 in the leeward region 1b (hereinafter referred to as the fourth through hole 821b2 on the leeward side) are arranged in the third direction. (vertical direction) positions are different.

The fourth through-hole 821b1 on the windward side is arranged below the fourth through-hole 821b2 on the leeward side, and the fourth through-hole 821b2 on the leeward side is arranged above the fourth through-hole 821b1 on the windward side. The position of the windward side fourth through hole 821b1 in the third direction is the same as the position of the leeward side third through hole 821a2. The position of the leeward side fourth through hole 821b2 in the third direction is the same as the position of the windward side third through hole 821a1.

With the above configuration, as will be described in detail below, the windward side fourth through hole 821b1 and the leeward side fourth through hole 821b2 move toward each other in the third direction as shown by the arrows in the through holes in FIG. 18(b). A flow path is formed through which the refrigerant flows.

(Third plate member 830)
The third plate member 830 has a fifth through hole 831a and a sixth through hole 831b formed to extend in the second direction. The fifth through hole 831a and the sixth through hole 831b penetrate the third plate member 830 in the thickness direction of the third plate member 830. The fifth through hole 831a and the sixth through hole 831b have a flat opening shape. The fifth through hole 831a and the sixth through hole 831b are formed to extend in the second direction. The fifth through hole 831a and the sixth through hole 831b are spaced apart in the third direction, with the fifth through hole 831a being formed on the upper side and the sixth through hole 831b being formed on the lower side.

The fifth through hole 831a communicates with the windward side third through hole 821a1 and the leeward side fourth through hole 821b2. Specifically, when the fifth through hole 831a is viewed in the first direction, both ends of the fifth through hole 831a in the second direction are connected to the third through hole 821a1 on the windward side and the fourth through hole 821a1 on the leeward side of the second plate member 820. It is formed to extend in two directions so as to overlap the through hole 821b2. Further, the fifth through hole 831a is arranged so as to overlap the upper region of the upper and lower regions of the windward third through hole 821a1 and the leeward fourth through hole 821b2 at the center in the third direction.

The sixth through hole 831b communicates with the third through hole 821a2 on the leeward side and the fourth through hole 821b1 on the windward side. Specifically, when the sixth through hole 831b is viewed in the first direction, both ends of the sixth through hole 831b in the third direction are connected to the third through hole 821a2 on the leeward side and the fourth through hole on the windward side of the second plate member 820. It is formed to extend in the second direction so as to overlap the through hole 821b1. Further, the sixth through hole 831b is arranged so as to overlap the lower region of the leeward third through hole 821a2 and the windward fourth through hole 821b1, which are divided into two vertically at the center in the third direction. ing.

With the above configuration, as will be described in detail below, the fifth through hole 831a and the sixth through hole 831b provide a flow path for the refrigerant to flow from the windward side to the leeward side, as shown by the arrows in the through holes in FIG. 18(c). forming a road.

(Fourth plate member 840)
The fourth plate member 840 is a plate member in which no through hole is formed.

As shown in FIG. 18(a), when the first plate member 810 and the second plate member 820 are overlapped, the first through hole 811a is connected to the windward side third through hole 821a1 in the windward region 1a. It overlaps and communicates with the lower area. Further, the first through hole 811a overlaps and communicates with the upper region of the leeward third through hole 821a2 in the leeward region 1b. In the component area surrounded by dotted lines in FIG. 18, dots indicate portions where through holes adjacent to each other in the first direction overlap and communicate with each other.

In this way, by overlapping the first plate member 810 and the second plate member 820, the through holes adjacent in the first direction are partially communicated with each other, and the refrigerant flowing out from the first flat tube 10a flows in. In the flow path, a windward side flow path and a leeward side flow path are formed independently.

Furthermore, when the first plate-like member 810 and the second plate-like member 820 are overlapped, the second through-hole 811b overlaps and communicates with the upper region of the fourth windward-side through-hole 821b1 in the windward region 1a. Further, the second through hole 811b overlaps and communicates with the lower region of the fourth leeward through hole 821b2 in the leeward region 1b.

In this way, by overlapping the first plate member 810 and the second plate member 820, the through holes adjacent in the first direction are partially communicated with each other, and the refrigerant flows from the distributor 80 to the second flat tube 10b. In the flow path through which the air passes, a windward side flow path and a leeward side flow path are formed independently.

As shown in FIG. 18(b), when the second plate member 820 and the third plate member 830 are overlapped, the third through hole 821a1 on the windward side of the second plate member 820 and the fourth through hole on the leeward side The hole 821b2 communicates with the fifth through hole 831a of the third plate member 830. Specifically, the upper region of the windward-side third through-hole 821a1 and the leeward-side fourth through-hole 821b2 divided vertically at the center in the third direction communicates with the fifth through-hole 831a. Furthermore, the third through hole 821a2 on the leeward side and the fourth through hole 821b1 on the windward side of the second plate member 820 communicate with the sixth through hole 831b of the third plate member 830. Specifically, the lower region of the third leeward through-hole 821a2 and the fourth windward through-hole 821b1 divided vertically at the center in the third direction communicates with the sixth through-hole 831b.

In this way, by overlapping the second plate member 820 and the third plate member 830, the through holes adjacent in the first direction partially communicate with each other. Thereby, each through hole of the second plate member 820 forms a flow path through which the refrigerant flows, as shown by the arrow in FIG. 18(b). Specifically, the third through holes 821a1 and 821a2 form a flow path through which the refrigerant flows in a direction away from each other in the third direction. The fourth through holes 821b1 and 821b2 form a flow path through which the refrigerant flows in directions approaching each other in the third direction. The flow of refrigerant will be explained again.

As shown in FIG. 18(c), when the third plate member 830 and the fourth plate member 840 are overlapped, the end openings in the first direction of the fifth through hole 831a and the sixth through hole 831b are It is closed by a fourth plate member 840.

By overlapping the third plate member 830 and the fourth plate member 840, the fifth through hole 831a and the sixth through hole 831b move from the windward side to the leeward side as shown by the arrow in FIG. 18(c). It forms a flow path through which the refrigerant flows. The flow of refrigerant will be explained again.

By stacking the first plate member 810, second plate member 820, third plate member 830, and fourth plate member 840 formed as described above, a through hole is formed in each plate member. partially communicate with each other to form a first flow path 800A and a second flow path 800B. The first flow path 800A is formed by the first through hole 511, the third windward through hole 821a1, the fifth through hole 831a, the fourth through hole 821b2 on the leeward side, and the second through hole 811b. The second flow path 800B is formed by the first through hole 511, the third through hole 821a2 on the leeward side, the sixth through hole 831b, the fourth through hole 821b1 on the windward side, and the second through hole 811b.

[Flow of refrigerant in distributor 80 and action of distributor 80]
FIG. 19 is an explanatory diagram of the flow of refrigerant in the first channel of the distributor of the heat exchanger according to the fourth embodiment. In FIG. 19, the dotted arrow indicates the refrigerant flowing through the first flow path 800A, and indicates a refrigerant with a high degree of dryness. A solid arrow indicates a refrigerant flowing through the second flow path 800B, and indicates a refrigerant with a low degree of dryness. The dotted line arrows and solid line arrows in FIG. 19 correspond to the dotted line arrows and solid line arrows in FIG. 18.

(Flow of highly dry refrigerant)
The refrigerant having a high degree of dryness flowing out from the windward side refrigerant passage 15a of the first flat tube 10a is transferred to the lower side of the windward side third through hole 821a1 via the windward region 1a of the first through hole 811a, as shown by the dotted line arrow. flow into the area. The refrigerant that has flowed into the lower region of the third through hole 821a1 on the windward side moves upward within the third through hole 821a1 on the windward side, flows out from the third through hole 821a1 on the windward side, and flows into the fifth through hole 831a. do. The highly dry refrigerant that has flowed into the fifth through hole 831a turns around and flows into the leeward fourth through hole 821b2. In other words, the highly dry refrigerant that has flowed into the fifth through hole 831a moves from the windward side to the leeward side in the fifth through hole 831a extending in the second direction, and then flows into the upper region of the leeward fourth through hole 821b2. Inflow. The highly dry refrigerant that has flowed into the upper region of the fourth leeward through-hole 821b2 moves downward within the fourth leeward through-hole 821b2, and then flows out from the fourth leeward through-hole 821b2. The refrigerant having a high degree of dryness flowing out from the fourth leeward through hole 821b2 passes through the leeward region 1b of the second through hole 811b and flows into the leeward refrigerant passage 15b of the second flat tube 10b.

In this way, the dry refrigerant flowing out from the windward refrigerant passage 15a of the first flat tube 10a flows into the leeward refrigerant passage 15b of the second flat tube 10b after passing through the distributor 80. That is, the distributor 80 causes the refrigerant having a high degree of dryness flowing out from the windward region 1a of the first flat tube 10a to flow into the leeward side refrigerant passage 15b of the second flat tube 10b having a small heat flux.

(flow of refrigerant with low dryness)
The refrigerant with low dryness flowing out from the leeward refrigerant passage 15b of the first flat tube 10a passes through the leeward region 1b of the first through hole 811a to the upper region of the leeward third through hole 821a2, as shown by the solid arrow. Inflow. The refrigerant that has flowed into the upper region of the third leeward through-hole 821a2 moves downward within the third leeward through-hole 821a2, and then flows out of the third leeward through-hole 821a2 and flows into the sixth through-hole 831b. . The refrigerant with low dryness that has flowed into the sixth through hole 831b turns around and flows into the fourth through hole 821b1 on the windward side. In other words, the refrigerant with low dryness that has flowed into the sixth through hole 831b moves from the windward side to the leeward side in the sixth through hole 831b extending in the second direction, and then moves to the lower area of the windward side fourth through hole 821b1. flows into. The refrigerant with low dryness that has flowed into the lower region of the fourth windward through-hole 821b1 moves upward in the fourth windward through-hole 821b1, and then flows out from the fourth windward through-hole 821b1. The refrigerant with low dryness that has flowed out of the fourth windward through hole 821b1 passes through the windward region 1a of the second through hole 811b and flows into the windward refrigerant passage 15a of the second flat tube 10b.

(Effect of distributor 80)
In this way, the distributor 80 guides the highly dry refrigerant flowing out from the windward refrigerant passage 15a of the first flat tube 10a to the leeward refrigerant passage 15b of the second flat tube 10b. Moreover, the distributor 80 guides the refrigerant having a low degree of dryness flowing out from the leeward side refrigerant passage 15b of the first flat tube 10a to the windward side refrigerant passage 15a of the second flat tube 10b. In other words, the distributor 80 determines the dryness of the refrigerant flowing out from the windward region 1a of the outlet of the refrigerant flow path and the refrigerant flow at the refrigerant flow path outlet (second through hole 811b) formed in the distributor 80. The dryness of the refrigerant flowing out from the leeward region 1b at the outlet of the refrigerant flow path is defined as the degree of dryness of the refrigerant in the windward region 1a and the leeward region 1b when it flows in from the entrance of the refrigerant flow path (first through hole 811a). It flows out in the opposite direction.

Since the heat exchanger of the fourth embodiment includes the distributor 80 having the above configuration, the heat exchange in the second heat exchange section 70 which is downstream of the distributor 80 is more efficient than when the distributor 80 is not used. can be done efficiently. Therefore, the heat exchanger of Embodiment 4 can improve heat exchanger performance.

Note that although the case where the heat exchanger functions as an evaporator has been described above, it may also be used to function as a condenser of a refrigeration cycle device. When the heat exchanger functions as a condenser of a refrigeration cycle device, the direction in which the refrigerant flows is opposite to that described above. When the heat exchanger functions as a condenser of the refrigeration cycle device, the refrigerant flows in the opposite direction to the above, and the distributor 80 has the windward side refrigerant passage 15a of the first flat tube 10a downstream of the distributor 80. A refrigerant with a high degree of dryness is introduced into the refrigerant, and a refrigerant with a low degree of dryness is introduced into the leeward side refrigerant passage 15b of the first flat tube 10a. This is because when the heat exchanger functions as a condenser, the dryness of the refrigerant flowing out from the windward side refrigerant passage 15a of the second flat tube 10b, which is the inlet side, is small, and This is because the dryness of the refrigerant flowing out is large.

As explained above, the heat exchanger of Embodiment 4 has a plurality of rows of first heat exchange parts 60 and second heat exchange parts 70 in the second direction. The distributor 80 is connected to one end of the first flat tube 10a and the second flat tube 10b on the same side in the first direction. The distributor 80 allows the refrigerant that has flowed from the other end of the first flat tube 10a in the first direction to flow through the first flat tube 10a toward one end in the first direction, passes through the distributor 80, and then flows through the first flat tube 10a toward one end in the first direction. It has a flow path that flows into the two flat tubes 10b from one end in the first direction and flows toward the other end in the first direction. The refrigerant flow path of the distributor 80 is a first flow path in which the refrigerant flowing out from one end of the first flat tube 10a flows in a first direction and then turns back in the opposite direction toward one end of the second flat tube 10b. 800A and a second flow path 800B. The first flow path 800A is a flow path that causes the refrigerant flowing out from the windward refrigerant passage 15a of the first flat tube 10a to flow into the leeward refrigerant passage 15b of the second flat tube 10b. The second flow path 800B is a flow path that causes the refrigerant flowing out from the leeward refrigerant passage 15b of the first flat tube 10a to flow into the upwind refrigerant passage 15a of the second flat tube 10b.

With the above configuration, the heat exchanger of Embodiment 4 can improve the heat transfer coefficient in the downstream part from the distributor 80, and as a result, the heat exchange efficiency of the heat exchanger as a whole can be improved.

Although FIG. 15 shows an example in which the heat exchanger has a substantially I-shape as a whole, it may be configured as shown in FIG. 20 below.

FIG. 20 is a diagram showing a modification of the heat exchanger according to the fourth embodiment. As shown in FIG. 20, the heat exchanger may have a substantially L-shape as a whole, with a part of the heat exchanger bent. Furthermore, in FIG. 15, the heat exchanger has one set of the first heat exchange section 60 and the second heat exchange section 70, but as shown in FIG. It is also possible to have a configuration in which two sets of two heat exchange units 70 are provided and arranged one above the other, and a distributor 80 is commonly connected to these two sets.

Embodiment 5.
Embodiment 5 relates to a refrigeration cycle device such as an air conditioner in which the heat exchangers of Embodiments 1 to 4 are mounted.

FIG. 21 is a refrigerant circuit diagram showing a schematic configuration of a refrigeration cycle device according to Embodiment 5. The refrigeration cycle device 200 includes a compressor 100, a suction muffler 101, a four-way switching valve 102, an outdoor heat exchanger 103, a pressure reducer 104 such as an electric expansion valve, and an indoor heat exchanger 105. It has a refrigerant circuit connected to the The outdoor heat exchanger 103 and the indoor heat exchanger 105 function as a condenser or an evaporator by switching the four-way switching valve 102. In the refrigeration cycle device 200, the four-way switching valve 102 can be omitted. Therefore, the refrigeration cycle device 200 may be configured to include the compressor 100, a condenser, a pressure reducer, and an evaporator. In the air conditioner, the indoor heat exchanger 105 is installed in an indoor device, and the remaining compressor 100, four-way switching valve 102, outdoor heat exchanger 103, and pressure reducer 104 are installed in an outdoor device.

The compressor 100 sucks refrigerant and compresses the refrigerant to a high temperature and high pressure state. The compressor 100 is a positive displacement compressor whose operating frequency can be varied. Note that the compressor 100 is not limited to one that is driven with a variable operating frequency, but may be one that is driven at a constant speed. The four-way switching valve 102 is connected to the discharge side of the compressor 100 and switches the flow of refrigerant from the compressor 100.

The outdoor heat exchanger 103 is a heat exchanger equipped with any one of the

distributors

40, 50, and 80. The pressure reducer 104 expands the refrigerant. The pressure reducer 104 is formed of, for example, an electronic expansion valve or a temperature-type expansion valve whose opening degree can be adjusted, but may also be formed of a capillary tube or the like whose opening degree cannot be adjusted. The indoor heat exchanger 105 is a heat exchanger equipped with any one of the

distributors

40, 50, and 80.

In heating operation when the refrigeration cycle device 200 is applied to an air conditioner, the four-way switching valve 102 is connected to the solid line side in FIG. 21. The high-temperature, high-pressure refrigerant compressed by the compressor 100 flows into the indoor heat exchanger 105, where it is condensed and liquefied. The liquefied refrigerant is depressurized by the pressure reducer 104 and becomes a low-temperature, low-pressure two-phase state, flows to the outdoor heat exchanger 103, evaporates, gasifies, and returns to the compressor 100 through the four-way switching valve 102. That is, the refrigerant circulates as shown by the solid line arrows in FIG. Through this circulation, the refrigerant exchanges heat with outside air and absorbs heat in the outdoor heat exchanger 103, which is an evaporator. The refrigerant that has absorbed heat is sent to the indoor heat exchanger 105, which is a condenser, and exchanges heat with indoor air to warm the indoor air.

In cooling operation, the four-way switching valve 102 is connected to the dashed line side in FIG. 21. When the heating operation changes to the cooling operation, the indoor heat exchanger 105 changes from a condenser to an evaporator, and the outdoor heat exchanger 103 changes from an evaporator to a condenser. The high-temperature, high-pressure refrigerant compressed by the compressor 100 flows into the outdoor heat exchanger 103, where it is condensed and liquefied. The liquefied refrigerant is depressurized by the pressure reducer 104 and becomes a two-phase state of low temperature and low pressure. The low-temperature, low-pressure two-phase refrigerant flows to the indoor heat exchanger 105, evaporates and gasifies, and returns to the compressor 100 again through the four-way switching valve 102. That is, the refrigerant circulates as shown by the broken line arrows in FIG. Through this circulation, the refrigerant exchanges heat with indoor air and absorbs heat in the indoor heat exchanger 105, which is an evaporator, thereby cooling the indoor air. The refrigerant that has absorbed heat is sent to the outdoor heat exchanger 103, which is a condenser, exchanges heat with the outside air, and radiates heat to the outside air.

Here, the refrigerant used is R407C refrigerant, R410A refrigerant, or R32 refrigerant.

The refrigeration cycle apparatus 200 having the above configuration can improve the operating efficiency of the refrigeration cycle apparatus 200 by including the heat exchanger of any one of Embodiments 1 to 4. Therefore, the refrigeration cycle device 200 can reduce the power consumption of the refrigeration cycle device.

Note that the refrigeration cycle device 200 can be applied to systems other than air conditioners, and can be applied to refrigeration cycle devices used for refrigerators, freezers, vending machines, refrigeration equipment, water heaters, and the like.

1 heat exchanger, 1a windward region, 1b leeward region, 10 flat tube, 10a first flat tube, 10b second flat tube, 11 first side end, 12 second side end, 13 flat surface, 14 flat surface, 15 refrigerant passage, 15a windward refrigerant passage, 15b leeward refrigerant passage, 20 header, 20a inlet, 20b outlet, 30 fin, 40 distributor, 40a confluence section, 40b gas-liquid separation section, 50 distributor, 60 First heat exchange section, 70 Second heat exchange section, 80 Distributor, 100 Compressor, 101 Suction muffler, 102 Four-way switching valve, 103 Outdoor heat exchanger, 104 Pressure reducer, 105 Indoor heat exchanger, 200 Refrigeration cycle device, 400 Plate member for tube insertion, 400A Refrigerant channel, 401 Insertion hole, 410 First plate member, 411 Through hole, 420 Second plate member, 421 Through hole, 430 Third plate member, 431 Through hole, 440 Fourth plate member, 441 Through hole, 450 Fifth plate member, 451a Through hole, 451b Through hole, 460 Pipe insertion plate member, 461 Insertion hole, 500A First channel, 500B No. 2 flow path, 510 first plate member, 511 first through hole, 520 second plate member, 521a second through hole (windward second through hole), 521b second through hole (leeward second through hole ), 530 third plate member, 531a third through hole, 531b third through hole, 540 fourth plate member, 541a fourth through hole (windward side fourth through hole), 541b fourth through hole (leeward side 4th through hole), 550 fifth plate member, 551 fifth through hole, 800A first flow path, 800B second flow path, 810 first plate member, 811a first through hole, 811b second through hole, 820 Second plate member, 821a1 Third through hole (third through hole on the windward side), 821a2 third through hole (third through hole on the leeward side), 821b1 fourth through hole (fourth through hole on the leeward side), 821b2 Fourth through hole (fourth through hole on windward side), 830 third plate member, 831a fifth through hole, 831b sixth through hole, 840 fourth plate member.

Claims

A flat tube having a plurality of refrigerant passages formed by through holes and extending in a first direction, the refrigerant flowing through the plurality of refrigerant passages of the flat tube in a direction perpendicular to the first direction, A heat exchanger that exchanges heat with air flowing in a second direction in which the plurality of refrigerant passages are parallel,
comprising a distributor provided in the middle of the plurality of refrigerant passages of the flat tube,
The distributor has a refrigerant flow path formed with a through hole,
The refrigerant flow path adjusts the dryness of the refrigerant flowing out from the upwind region of the outlet of the refrigerant flow path and the dryness of the refrigerant flowing out from the leeward region of the exit of the refrigerant flow path, based on the dryness of the refrigerant flowing out from the windward region of the outlet of the refrigerant flow path A heat exchanger in which the dryness of the refrigerant in an upwind region and a leeward region is opposite to that of the refrigerant when the refrigerant flows out from the windward region.
The distributor is arranged in the middle of the flat tube in the first direction,
The flat tube has a first flat tube upstream of the distributor and a second flat tube downstream of the distributor,
The distributor is
a merging portion communicating with the plurality of refrigerant passages in the first flat tube;
The gas-liquid refrigerant that has passed through the merging portion is separated from the merging portion, and the refrigerant in the liquid phase is transferred to the refrigerant in the upwind region of the plurality of refrigerant passages in the second flat tube. The heat exchanger according to claim 1, further comprising: a gas-liquid separation section that guides the refrigerant in a gas phase to the refrigerant passage in a leeward region of the plurality of refrigerant passages in the second flat tube. vessel.
The distributor includes at least four plate-like members between the first flat tube and the second flat tube,
When the four plate members are, in order from the first flat tube side, a first plate member, a second plate member, a third plate member, and a fourth plate member,
The merging part is
comprising the first plate member and the second plate member,
A through hole communicating with the plurality of refrigerant passages in the first flat tube is formed in the first plate member,
A through hole is formed in the second plate member, communicating with the center of the through hole in the second direction, and having a smaller opening area than the through hole;
The gas-liquid separation section is
comprising the third plate-like member;
A through hole is formed in the third plate member, the through hole is connected to the through hole of the second plate member and is inclined upward from the windward region to the leeward region;
3. The heat exchanger according to claim 2, wherein the fourth plate-like member is formed with a through-hole that communicates with the through-hole of the third plate-like member and communicates with the plurality of refrigerant passages in the second flat tube. exchanger.
The gas-liquid separation section further includes a fifth plate member,
The fifth plate-like member is formed with two through-holes that communicate with both ends of the through-hole of the third plate-like member in the second direction,
The heat exchanger according to claim 3, wherein the through hole of the fourth plate member communicates with the through hole of the third plate member via the two through holes of the fifth plate member.
The distributor is arranged in the middle of the flat tube in the first direction,
The flat tube has a first flat tube upstream of the distributor and a second flat tube downstream of the distributor,
The refrigerant flow path of the distributor is
A first flow path that guides the refrigerant in the refrigerant path in the upwind region of the plurality of refrigerant paths in the first flat tube to the refrigerant path in the leeward region among the plurality of refrigerant paths in the second flat tube; ,
a second flow path that guides the refrigerant in the refrigerant passage in the leeward region of the plurality of refrigerant passages in the first flat tube to the refrigerant passage in the upwind region among the plurality of refrigerant passages in the second flat tube; The heat exchanger according to claim 1, comprising:
The distributor has a configuration including at least five plate-like members between the first flat tube and the second flat tube,
When the five plate members are, in order from the first flat tube side, a first plate member, a second plate member, a third plate member, a fourth plate member, and a fifth plate member,
A first through hole communicating with the plurality of refrigerant passages in the first flat tube is formed in the first plate member,
The second plate-like member has the refrigerant in communication with the first through hole, spaced apart in the second direction, and spaced apart from each other in a third direction perpendicular to the first direction and the second direction. A second through hole on the windward side and a second through hole on the leeward side are formed to form a flow path through which the
The third plate-like member is configured to communicate with each of the windward-side second through-hole and the leeward-side second through-hole, to be spaced apart in the third direction, and to supply the refrigerant in mutually opposite directions in the second direction. Two third through holes are formed that form flow channels,
The fourth plate-like member has an upwind side that communicates with each of the two third through-holes and forms a flow path that allows the refrigerant to flow in a direction that is spaced apart in the second direction and approaches each other in the third direction. A fourth through hole and a fourth through hole on the leeward side are formed,
A fifth through hole is formed in the fifth plate member, and the fifth through hole communicates with the fourth through hole on the windward side and the fourth through hole on the leeward side, and also communicates with the plurality of refrigerant passages in the second flat tube. Ori,
The first flow path is
the first through hole, the second windward through hole, the third through hole that communicates with the second windward through hole among the two third through holes, the fourth through hole on the leeward side, and the fifth through hole. Formed with a through hole,
The second flow path is
The first through hole, the second through hole on the leeward side, the third through hole that communicates with the second through hole on the leeward side among the two third through holes, the fourth through hole on the windward side, and the fifth through hole. The heat exchanger according to claim 5, wherein the heat exchanger is formed of through holes.
The heat exchanger according to claim 5 or 6, wherein a part of the cross-sectional area of the first flow path of the distributor is formed larger than a part of the cross-sectional area of the second flow path. .
The windward side second through hole forming the first flow path is formed to have a larger opening area than the leeward side second through hole forming the second flow path,
Claim 6 or dependent on claim 6, wherein the fourth through hole on the leeward side forming the first flow path is formed to have a larger opening area than the fourth through hole on the windward side forming the second flow path. The heat exchanger according to claim 7.
A plurality of the flat tubes are arranged in parallel in a third direction orthogonal to the first direction and the second direction, and a pair of headers are connected to both ends of the plurality of flat tubes in the first direction,
The heat exchanger according to any one of claims 1 to 8, wherein the refrigerant flow path is independently formed in the distributor to correspond to each of a part of the plurality of flat tubes.
having a plurality of rows of heat exchange parts having the flat tubes in the second direction;
Among the plurality of rows of heat exchange sections, the windward side is a first heat exchange section, the flat tube of the first heat exchange section is a first flat tube, the leeward side is a second heat exchange section, and the second heat exchange section. When the flat tube of the section is a second flat tube,
The distributor is connected to one end of the first flat tube and the second flat tube on the same side in the first direction,
The refrigerant flowing from the other end of the first flat tube in the first direction flows through the first flat tube toward one end of the first direction, passes through the distributor, and then flows into the second flat tube. A flow path is formed in the pipe that flows from one end in the first direction and flows toward the other end in the first direction,
The refrigerant flow path of the distributor is
A first flow path and a second flow path through which the refrigerant flowing out from the one end of the first flat tube flows in the first direction and then turns back toward the one end of the second flat tube. has
The first flow path is
A flow that causes the refrigerant flowing out from the refrigerant passage in an upwind region of the plurality of refrigerant passages of the first flat tube to flow into the refrigerant passage in a leeward region of the plurality of refrigerant passages of the second flat tube. road,
The second flow path is
A flow that causes the refrigerant flowing out from the refrigerant passage in a leeward region of the plurality of refrigerant passages of the first flat tube to flow into the refrigerant passage in an upwind region among the plurality of refrigerant passages of the second flat tube. The heat exchanger according to claim 1, which is a duct.
The distributor is
It has a configuration including at least four plate-like members,
The four plate members are, in order from the side connected to the first flat tube and the second flat tube, a first plate member, a second plate member, a third plate member, and a fourth plate member. When
The first plate member includes a first through hole that communicates with the plurality of refrigerant passages in the first flat tube, and a second through hole that communicates with the plurality of refrigerant passages in the second flat tube. formed spaced apart in a second direction;
The second plate member includes:
two through holes communicating with the first through hole and spaced apart in the second direction, the refrigerant flowing in a direction away from each other in a third direction orthogonal to the first direction and the second direction; two third through holes forming a flow path;
two fourth through holes communicating with the second through hole and spaced apart in the second direction, forming a flow path through which the refrigerant flows toward each other in the third direction; and are formed,
The third plate member includes:
It is formed to extend in the second direction and communicates with the windward side third through hole on the windward side of the two said third through holes and the leeward side fourth through hole on the leeward side among the two said fourth through holes. and a fifth through hole forming a flow path for flowing the refrigerant from the windward side to the leeward side;
It is formed to extend in the second direction and communicates with the leeward side third through hole on the leeward side of the two said third through holes and the windward side fourth through hole on the windward side among the two said fourth through holes. and a sixth through hole forming a flow path for flowing the refrigerant from the windward side to the leeward side,
No through hole is formed in the fourth plate member,
The first flow path is
formed of the first through hole, the windward third through hole, the fifth through hole, the leeward fourth through hole, and the second through hole,
The second flow path is
The heat exchanger according to claim 10, wherein the heat exchanger is formed by the first through hole, the third through hole on the leeward side, the sixth through hole, the fourth through hole on the windward side, and the second through hole.
A plurality of the first flat tubes and the second flat tubes are arranged in parallel in a third direction orthogonal to the first direction and the second direction, and the plurality of first flat tubes and the plurality of second flat tubes are arranged in parallel. A pair of headers are connected to the end,
The heat refrigerant according to claim 10 or claim 11, wherein the refrigerant flow path is independently formed in the distributor to correspond to each of the plurality of first flat tubes and a part of the plurality of second flat tubes. exchanger.
A refrigeration cycle device comprising the heat exchanger according to any one of claims 1 to 12.