WO2021149223A1

WO2021149223A1 - Heat exchanger and refrigeration cycle apparatus

Info

Publication number: WO2021149223A1
Application number: PCT/JP2020/002321
Authority: WO
Inventors: 篤史 ▲高▼橋; 前田　剛志; 真哉東井上
Original assignee: 三菱電機株式会社
Priority date: 2020-01-23
Filing date: 2020-01-23
Publication date: 2021-07-29
Also published as: EP4095476B1; JPWO2021149223A1; TW202129218A; TWI768340B; EP4095476A1; JP7278430B2; EP4095476A4

Abstract

A heat exchanger comprising: a plurality of heat transfer tubes positioned so as to leave gaps between each other in a first direction, the plurality of heat transfer tubes channeling a refrigerant in a second direction that intersects the first direction; and a refrigerant distributor extending in the first direction, the refrigerant distributor being connected to one end of each of the plurality of heat transfer tubes and distributing the refrigerant to the plurality of heat transfer tubes. The refrigerant distributor has formed in the interior thereof a first channel and a second channel in which the refrigerant flows. The first channel is formed so as to extend in the first direction. The first channel connects to an inflow tube, which communicates with the plurality of heat transfer tubes and causes the refrigerant to flow into the interior of the refrigerant distributor. The second channel is formed so as to extend in the first direction and so that both end sections connect to the first channel, and is formed so as to be located in a third direction relative to the first channel, where the third direction is defined as a direction that intersects a plane parallel to the first direction and the second direction.

Description

Heat exchanger and refrigeration cycle equipment

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

In recent years, in order to reduce the amount of refrigerant or improve the performance of heat exchangers, the heat transfer tubes used in heat exchangers for air conditioners have been made thinner. As heat exchangers are becoming thinner, the number of heat exchanger passes (number of branches) is increased compared to conventional heat exchangers in order to suppress an increase in refrigerant pressure loss. There is. Therefore, the heat exchanger is provided with a multi-branch refrigerant distributor (see, for example, Patent Document 1). In order to achieve both the performance of the heat exchanger and the reduction of the amount of refrigerant used, it is possible to suppress the drift of the refrigerant to each path, reduce the amount of refrigerant used by reducing the volume of the distribution flow path, and transfer heat. A compact refrigerant distributor that secures a large area but does not hinder the installation space of the heat exchanger is required.

The heat exchanger of Patent Document 1 has a plurality of heat transfer tubes arranged side by side, a header collecting pipe which is a refrigerant collecting pipe which is connected to one end of the heat transfer pipe and extends in the vertical direction, and a heat transfer pipe. It has multiple fins joined to. The internal space of the header collecting pipe is divided into a first space on the side where one end of the heat transfer tube is connected by a partition plate and a second space on the side opposite to the first space side with respect to the partition plate. It is partitioned. Further, at the upper end and the lower end of the partition plate, a communication passage for communicating the first space and the second space is provided. The heat exchanger of Patent Document 1 has such a configuration, so that the refrigerant is looped between the first space and the second space. The heat exchanger of Patent Document 1 is said to be able to suppress the drift of the refrigerant to a small value by looping the refrigerant between the first space and the second space.

JP-A-2015-68622

However, in the heat exchanger of Patent Document 1, a first space forming a flow path through which the gas-liquid two-phase refrigerant flows upward and a second space forming a circulation flow path for returning the refrigerant from the upper part to the lower part are transmitted. It is located in the extending direction of the conduit of the heat pipe. Since the refrigerant distributor described in Patent Document 1 is enlarged in the extending direction of the heat transfer tube line due to the configuration, the length of the heat transfer tube in the extension direction of the heat transfer tube is reduced due to the structural contract, and the heat transfer tube is transmitted. The heat area becomes small. Therefore, the heat exchanger of Patent Document 1 may have lower heat exchange performance than the conventional heat exchanger.

The present disclosure is for solving the above-mentioned problems, and provides a compact refrigerant distributor without increasing the size in the extending direction of the heat transfer pipe while ensuring a wide heat transfer area of the heat transfer pipe. It is an object of the present invention to provide a heat exchanger and a refrigeration cycle device provided.

The heat exchanger according to the present disclosure is a plurality of heat transfer tubes arranged at intervals in the first direction, and includes a plurality of heat transfer tubes for flowing a refrigerant in a second direction intersecting the first direction, and a first. A refrigerant distributor extending in one direction and connected to one end of each of the plurality of heat transfer tubes to distribute the refrigerant to the plurality of heat transfer tubes is provided, and the refrigerant distributor includes a first flow path and a second flow path through which the refrigerant flows. The flow path is formed inside, and the first flow path is formed so as to extend in the first direction, and is an inflow pipe that communicates with a plurality of heat transfer tubes and allows the refrigerant to flow into the inside of the refrigerant distributor. The second flow path is formed so as to extend in the first direction and both ends are connected to the first flow path, and intersect the planes parallel to the first direction and the second direction. When the direction is defined as the third direction, it is formed so as to be located in the third direction with respect to the first flow path.

The refrigeration cycle device according to the present disclosure is provided with the heat exchanger according to the present disclosure.

According to the present disclosure, the heat exchanger has a refrigerant distributor in which a first flow path and a second flow path through which the refrigerant flows are formed. The second flow path is formed so as to extend in the first direction and connect both ends to the first flow path. The second flow path is formed so as to be located in the third direction with respect to the first flow path when the direction intersecting the first direction and the plane parallel to the second direction is defined as the third direction. There is. Therefore, the heat exchanger can suppress the increase in size of the refrigerant distributor in the second direction in which the refrigerant flows, and the heat exchanger is enlarged in the direction in which the conduit of the heat transfer tube extends within the range of the structural contract. be able to. Therefore, in the heat exchanger 100 of the present disclosure, the heat transfer area of the heat transfer tube can be secured widely, and the refrigerant distributor can be made compact without increasing in size in the extending direction of the heat transfer tube line.

It is a refrigerant circuit diagram which shows the structure of the refrigerating cycle apparatus provided with the heat exchanger according to Embodiment 1. FIG. It is a side view which conceptually shows the main part structure of the heat exchanger which concerns on Embodiment 1. FIG. It is an exploded perspective view which conceptually shows the main part structure of the heat exchanger which concerns on Embodiment 1. FIG. It is sectional drawing which shows the structure of the heat transfer tube which comprises the heat exchanger which concerns on Embodiment 1. FIG. FIG. 5 is a cross-sectional view conceptually showing a communication position between a first flow path and a second flow path of the refrigerant distributor constituting the heat exchanger according to the first embodiment. It is a conceptual diagram which showed the flow of the refrigerant in the refrigerant distributor which comprises the heat exchanger which concerns on Embodiment 1. FIG. It is a figure which showed the flow rate distribution of the refrigerant in the refrigerant distributor which comprises the heat exchanger which concerns on Embodiment 1. FIG. It is an exploded perspective view which conceptually shows the main part structure of the heat exchanger which concerns on Embodiment 2. FIG. FIG. 5 is a cross-sectional view conceptually showing a communication position between a first flow path and a second flow path of a refrigerant distributor constituting the heat exchanger according to the second embodiment. It is a conceptual diagram which showed the flow of the refrigerant in the refrigerant distributor which comprises the heat exchanger which concerns on Embodiment 2. FIG. It is a figure which showed the flow rate distribution of the refrigerant in the refrigerant distributor which comprises the heat exchanger which concerns on Embodiment 2. FIG. It is an exploded perspective view which conceptually shows the main part structure of the heat exchanger which concerns on Embodiment 3. FIG. FIG. 5 is a cross-sectional view conceptually showing a communication position between a first flow path and a second flow path of the refrigerant distributor constituting the heat exchanger according to the third embodiment. It is a conceptual diagram which showed the flow of the refrigerant in the refrigerant distributor which comprises the heat exchanger which concerns on Embodiment 3. FIG. It is a figure which showed the flow rate distribution of the refrigerant in the refrigerant distributor which comprises the heat exchanger which concerns on Embodiment 3. FIG. It is an exploded perspective view which conceptually shows the main part structure of the heat exchanger which concerns on Embodiment 4. FIG. FIG. 5 is a cross-sectional view conceptually showing a communication position between a first flow path and a second flow path of the refrigerant distributor constituting the heat exchanger according to the fourth embodiment. It is a conceptual diagram which showed the flow of the refrigerant in the refrigerant distributor which comprises the heat exchanger which concerns on Embodiment 4. FIG. It is an exploded perspective view which conceptually shows the main part structure of the heat exchanger which concerns on Embodiment 5. It is a side view which conceptually shows the inside of the refrigerant distributor shown in FIG. FIG. 5 is a cross-sectional view conceptually showing a communication position between a first flow path and a second flow path of the refrigerant distributor constituting the heat exchanger according to the fifth embodiment. FIG. 5 is a cross-sectional view conceptually showing the communication position between the first flow path and the second flow path of the refrigerant distributor of the modified example constituting the heat exchanger according to the fifth embodiment. It is a conceptual diagram which showed the flow of the refrigerant in the refrigerant distributor which comprises the heat exchanger which concerns on Embodiment 5. FIG.

Hereinafter, the heat exchanger 100 and the refrigeration cycle device 200 according to the first embodiment will be described with reference to the drawings and the like. In the following drawings including FIG. 1, the relative dimensional relationships and shapes of the constituent members may differ from the actual ones. Further, in the following drawings, those having the same reference numerals are the same or equivalent thereof, and this shall be common to the entire text of the specification. In addition, terms that indicate directions (for example, "top", "bottom", "right", "left", "front", "rear", etc.) are used as appropriate for ease of understanding. For convenience of explanation, it is described as such, and does not limit the arrangement and orientation of the device or component. In the specification, the positional relationship between each component, the extension direction of each component, and the arrangement direction of each component are, in principle, those when the outdoor heat exchanger 105 is installed in a usable state. be.

Embodiment 1.
[Refrigeration Cycle Device 200]
FIG. 1 is a refrigerant circuit diagram showing a configuration of a refrigeration cycle device 200 including the heat exchanger 100 according to the first embodiment. In FIG. 1, the arrow indicated by the dotted line indicates the direction in which the refrigerant flows in the refrigerant circuit 110 during the cooling operation, and the arrow indicated by the solid line indicates the direction in which the refrigerant flows during the heating operation. .. First, the refrigeration cycle apparatus 200 provided with the heat exchanger 100, which will be described later, will be described with reference to FIG.

In the present embodiment, the air conditioner is exemplified as the refrigerating cycle device 200, but the refrigerating cycle device 200 is used for refrigerating, for example, a refrigerator or a freezer, a vending machine, an air conditioner, a refrigerating device, a water heater, and the like. Used for applications or air conditioning applications. The illustrated refrigerant circuit 110 is an example, and the configuration of circuit elements and the like is not limited to the contents described in the embodiment, and can be appropriately changed within the scope of the technique according to the embodiment. ..

The refrigerating cycle device 200 has a refrigerant circuit 110 in which a compressor 101, a flow path switching device 102, an indoor heat exchanger 103, a decompression device 104, and an outdoor heat exchanger 105 are cyclically connected via a refrigerant pipe. .. The refrigeration cycle device 200 has an outdoor unit 106 and an indoor unit 107. The outdoor unit 106 includes a compressor 101, a flow path switching device 102, an outdoor heat exchanger 105 and a decompression device 104, and an outdoor blower 108 that supplies outdoor air to the outdoor heat exchanger 105. The indoor unit 107 includes an indoor heat exchanger 103 and an indoor blower 109 that supplies air to the indoor heat exchanger 103. The outdoor unit 106 and the indoor unit 107 are connected via two

extension pipes

111 and 112 which are a part of the refrigerant pipe.

The compressor 101 is a fluid machine that compresses and discharges the sucked refrigerant. The flow path switching device 102 is, for example, a four-way valve, and is a device that switches the flow path of the refrigerant between the cooling operation and the heating operation by controlling the control device (not shown). The refrigerant is the first heat exchange fluid.

The indoor heat exchanger 103 is a heat exchanger that exchanges heat between the refrigerant circulating inside and the indoor air supplied by the indoor blower 109. The indoor heat exchanger 103 functions as a condenser during the heating operation and as an evaporator during the cooling operation.

The pressure reducing device 104 is, for example, an expansion valve, which is a device for reducing the pressure of the refrigerant. As the pressure reducing device 104, an electronic expansion valve whose opening degree is adjusted by the control of the control device can be used.

The outdoor heat exchanger 105 is a heat exchanger that exchanges heat between the refrigerant circulating inside and the air supplied by the outdoor blower 108. The outdoor heat exchanger 105 functions as an evaporator during the heating operation and as a condenser during the cooling operation. The air supplied by the outdoor blower 108 is an example of a second heat exchange fluid.

A heat exchanger 100, which will be described later, is used for at least one of the outdoor heat exchanger 105 and the indoor heat exchanger 103. It is desirable that the refrigerant distributor 150 connected to the heat exchanger 100 is arranged at a position in the heat exchanger 100 where the amount of the liquid phase refrigerant is larger. Specifically, the refrigerant distributor 150 is arranged on the inlet side of the heat exchanger 100 that functions as an evaporator, that is, on the outlet side of the heat exchanger 100 that functions as a condenser in the flow of the refrigerant in the refrigerant circuit 110. Is desirable. In FIG. 1, the refrigerant distributor 150 is used in both the indoor heat exchanger 103 and the outdoor heat exchanger 105, but either the indoor heat exchanger 103 or the outdoor heat exchanger 105. It may be used only for one of the heat exchangers 100.

[Operation of refrigeration cycle device 200]
Next, an example of the operation of the refrigeration cycle apparatus 200 will be described with reference to FIG. During the heating operation of the refrigeration cycle device 200, the high-pressure and high-temperature gas-state refrigerant discharged from the compressor 101 flows into the indoor heat exchanger 103 via the flow path switching device 102, and the air supplied by the indoor blower 109. Heat exchange with and condenses. The condensed refrigerant is in a high-pressure liquid state, flows out of the indoor heat exchanger 103, and is in a low-pressure gas-liquid two-phase state by the decompression device 104. The low-pressure gas-liquid two-phase refrigerant flows into the outdoor heat exchanger 105 and evaporates by heat exchange with the air supplied by the outdoor blower 108. The evaporated refrigerant becomes a low-pressure gas state and is sucked into the compressor 101. During the heating operation, if the pressure saturation temperature of the outdoor heat exchanger 105 is equal to or lower than the dew point temperature of the outdoor air and lower than the freezing point of water, frost adheres to the outdoor heat exchanger 105.

During the cooling operation of the refrigeration cycle device 200, the refrigerant flowing through the refrigerant circuit 110 flows in the opposite direction to that during the heating operation. That is, during the cooling operation of the refrigeration cycle device 200, the high-pressure and high-temperature gas-state refrigerant discharged from the compressor 101 flows into the outdoor heat exchanger 105 via the flow path switching device 102 and is supplied by the outdoor blower 108. It exchanges heat with the air and condenses. The condensed refrigerant is in a high-pressure liquid state, flows out of the outdoor heat exchanger 105, and is in a low-pressure gas-liquid two-phase state by the decompression device 104. The low-pressure gas-liquid two-phase refrigerant flows into the indoor heat exchanger 103 and evaporates by heat exchange with the air supplied by the indoor blower 109. The evaporated refrigerant becomes a low-pressure gas state and is sucked into the compressor 101.

[Outdoor heat exchanger 105]
FIG. 2 is a side view conceptually showing the main configuration of the heat exchanger 100 according to the first embodiment. FIG. 3 is an exploded perspective view conceptually showing the configuration of a main part of the heat exchanger 100 according to the first embodiment. The heat exchanger 100 according to the first embodiment will be described with reference to FIGS. 2 to 3. In FIG. 2, the arrow F indicated by hatching indicates the direction of the refrigerant flowing through the first flow path portion 15 of the refrigerant distributor 150. When the refrigerant distributor 150 is applied to the refrigeration cycle device 200, the refrigerant distributor 150 is connected to the end of the heat transfer tube 70 which is the inlet side of the refrigerant when the heat exchanger 100 operates as an evaporator. There is.

As shown in FIG. 2, the heat exchanger 100 includes a plurality of heat transfer tubes 70 through which refrigerant is circulated, and a refrigerant distributor 150 connected to one end of each of the plurality of heat transfer tubes 70 in the extending direction. Have. Further, the heat exchanger 100 has a refrigerant inflow pipe 60 attached to the lower part of the refrigerant distributor 150.

The plurality of heat transfer tubes 70 are arranged at intervals in the first direction (Z-axis direction), and the refrigerant flows in the second direction (X-axis direction) intersecting the first direction (Z-axis direction). .. The plurality of heat transfer tubes 70 are flat tubes. Although the heat transfer tube 70 is described as a flat tube, the heat transfer tube 70 is not limited to the flat tube, and may be, for example, a circular tube.

In the heat exchanger 100, the arrangement direction of the plurality of heat transfer tubes 70 and the extension direction of the refrigerant distributor 150 are defined as the first direction (Z-axis direction). That is, the first direction is the direction in which the plurality of heat transfer tubes 70 are lined up. In the heat exchanger 100, the arrangement direction of the plurality of heat transfer tubes 70, which is the first direction (Z-axis direction), is the vertical direction. The vertical direction is, for example, the vertical direction. However, the arrangement direction of the plurality of heat transfer tubes 70, which is the first direction (Z-axis direction), is not limited to the vertical direction and the vertical direction, and may be a direction inclined with respect to the vertical direction, and is horizontal. It may be a direction.

In the heat exchanger 100, the extension direction of the pipeline of the heat transfer tube 70 is defined as the second direction (X-axis direction). The conduit of the heat transfer tube 70 is a refrigerant passage 72, which will be described later (see FIG. 4). Therefore, the second direction (X-axis direction) is also the flow direction of the refrigerant flowing through the conduit of the heat transfer tube 70. In the heat exchanger 100, the extension direction of the pipe lines of the plurality of heat transfer tubes 70, which is the second direction (X-axis direction), is the horizontal direction. However, the extension direction of the conduits of the plurality of heat transfer tubes 70 in the second direction (X-axis direction) is not limited to the horizontal direction, and may be a direction inclined with respect to the horizontal direction, and is vertical. It may be in the vertical direction including the direction.

A gap 71 that serves as an air flow path is formed between two adjacent heat transfer tubes 70 among the plurality of heat transfer tubes 70. As shown in FIG. 2, heat transfer fins 75 may be provided between two adjacent heat transfer tubes 70. Further, the heat exchanger 100 has a heat transfer fin 75 which is a heat transfer promoting member in a part thereof, and has a region in which the heat transfer tubes 70 adjacent to each other are not connected to each other by the heat transfer promoting member. You may.

Note that the heat transfer tubes 70 adjacent to each other among the plurality of heat transfer tubes 70 do not have the heat transfer fins 75, and the heat transfer tubes 70 may not be connected to each other by the heat transfer promotion member. The heat transfer promoting member is a member that promotes heat transfer, and is, for example, a plate fin such as a heat transfer fin 75, a corrugated fin, or the like. Therefore, the outdoor heat exchanger 105 may be configured as a so-called finless heat exchanger.

When the heat exchanger 100 functions as an evaporator of the refrigeration cycle device 200, the refrigerant flows from one end to the other end in the extension direction in each of the plurality of heat transfer tubes 70. Further, when the heat exchanger 100 functions as a condenser of the refrigeration cycle device 200, in each of the plurality of heat transfer tubes 70, the refrigerant flows from the other end in the extension direction toward one end in the inner pipeline of the heat transfer tube 70. ..

(Heat transfer tube 70)
FIG. 4 is a cross-sectional view showing the configuration of the heat transfer tube 70 constituting the heat exchanger 100 according to the first embodiment. FIG. 4 shows a cross section perpendicular to the extending direction of the heat transfer tube 70. As shown in FIG. 4, the heat transfer tube 70 has a unidirectionally flat cross-sectional shape such as an oval shape.

The heat transfer tube 70 has a first side end portion 70a and a second side end portion 70b, and a pair of flat surfaces 70c and flat surfaces 70d. In the cross section shown in FIG. 4, the first side end portion 70a is connected to one end portion of the flat surface 70c and one end portion of the flat surface 70d. In the same cross section, the second side end 70b is connected to the other end of the flat surface 70c and the other end of the flat surface 70d.

The first side end portion 70a is a side end portion arranged on the windward side, that is, on the front edge side in the flow of air passing through the heat exchanger. The second side end portion 70b is a side end portion arranged on the leeward side, that is, the trailing edge side in the flow of air passing through the heat exchanger. Hereinafter, the direction perpendicular to the extending direction of the heat transfer tube 70 and along the flat surface 70c and the flat surface 70d may be referred to as a major axis direction of the heat transfer tube 70.

The heat transfer tube 70 is formed with a plurality of refrigerant passages 72 arranged between the first side end portion 70a and the second side end portion 70b along the long axis direction. The heat transfer tube 70 is a flat perforated tube in which a plurality of refrigerant passages 72 through which the refrigerant flows are arranged in the air flow direction. Each of the plurality of refrigerant passages 72 is formed so as to extend in parallel with the extending direction of the heat transfer tube 70.

(Refrigerant distributor 150)
Returning to FIGS. 2 and 3, the refrigerant distributor 150 will be described. The refrigerant distributor 150 has a main body 151 extending in the first direction (Z-axis direction). The main body 151 of the refrigerant distributor 150 is connected to one end of each of the plurality of heat transfer tubes 70. The refrigerant distributor 150 distributes the refrigerant to each of the plurality of heat transfer tubes 70 connected to the main body 151.

The main body 151 of the refrigerant distributor 150 is formed so as to extend in the vertical direction along the arrangement direction of the plurality of heat transfer tubes 70. The main body 151 extends in the first direction, and a distribution flow path for distributing the refrigerant to each heat transfer tube 70 is formed inside. The main body 151 of the refrigerant distributor 150 is formed with a refrigerant inflow port 18 into which the refrigerant inflow pipe 60 is inserted and a plurality of insertion holes 31 into which each of the plurality of heat transfer pipes 70 is inserted.

The refrigerant inflow port 18 is formed on one end 151a side of the main body 151 in the first direction. The plurality of insertion holes 31 are formed on the side surface of the main body 151 on the side connected to the plurality of heat transfer tubes 70. Each of the plurality of insertion holes 31 is formed so as to correspond to each of the plurality of heat transfer tubes 70 so as to be spaced apart from each other along the first direction (Z-axis direction).

The main body 151 of the refrigerant distributor 150 has a first plate-shaped member 10, a second plate-shaped member 20, and a third plate-shaped member 30. The first plate-shaped member 10, the second plate-shaped member 20, and the third plate-shaped member 30 are all formed by using a metal flat plate and have a strip-like shape long in one direction. The contours of the outer edges of the first plate-shaped member 10, the second plate-shaped member 20, and the third plate-shaped member 30 have the same shape as each other. Each of the first plate-shaped member 10, the second plate-shaped member 20, and the third plate-shaped member 30 has a plate thickness direction parallel to the extension direction of the pipe line of the heat transfer tube 70, that is, each plate surface. Is arranged so as to be perpendicular to the extending direction of the conduit of the heat transfer tube 70.

The main body 151 of the refrigerant distributor 150 has a configuration in which the first plate-shaped member 10, the second plate-shaped member 20, and the third plate-shaped member 30 are laminated in this order from the farthest distance from the heat transfer tube 70. ing. The first plate-shaped member 10 is arranged at the position farthest from the heat transfer tube 70 in the main body 151, and the third plate-shaped member 30 is arranged at the position closest to the heat transfer tube 70 in the main body 151. Has been done.

The second plate-shaped member 20 is arranged between the first plate-shaped member 10 and the heat transfer tube 70, and is adjacent to the first plate-shaped member 10 and the third plate-shaped member 30. The third plate-shaped member 30 is arranged between the second plate-shaped member 20 and the heat transfer tube 70, and is adjacent to the second plate-shaped member 20. One end of each of the plurality of heat transfer tubes 70 is connected to the third plate-shaped member 30.

The adjacent members of the first plate-shaped member 10, the second plate-shaped member 20, and the third plate-shaped member 30 are joined by brazing. The first plate-shaped member 10, the second plate-shaped member 20, and the third plate-shaped member 30 are arranged so that their respective longitudinal directions are along the first direction (Z-axis direction).

FIG. 5 is a cross-sectional view conceptually showing the communication position between the first flow path and the second flow path of the refrigerant distributor 150 constituting the heat exchanger 100 according to the first embodiment. The plate thickness direction of each of the first plate-shaped member 10, the second plate-shaped member 20, and the third plate-shaped member 30 is the vertical direction of FIG. 5, and is the extending direction of the conduit of the heat transfer tube 70. The lateral direction of each of the first plate-shaped member 10, the second plate-shaped member 20, and the third plate-shaped member 30 is the left-right direction in FIG. 5, and the major axis direction of the heat transfer tube 70. The configuration of the main body 151 of the refrigerant distributor 150 will be further described with reference to FIGS. 3 and 5.

As shown in FIGS. 3 and 5, the first plate-shaped member 10 has a first flow path portion 15 that bulges in a direction away from the heat transfer tube 70. The first flow path portion 15 is formed in a tubular shape, and a space is formed inside the bulge. Although the first plate-shaped member 10 and the first flow path portion 15 are integrally formed in the refrigerant distributor 150, they may be formed separately.

The first flow path portion 15 extends from one end in the longitudinal direction to the other end in the longitudinal direction of the first plate-shaped member 10 along the longitudinal direction of the first plate-shaped member 10. The first flow path portion 15 is formed in a semi-cylindrical shape. Both ends of the first flow path portion 15 in the stretching direction are closed. The first flow path portion 15 has a semicircular, semi-elliptical or semi-oval cross-sectional shape in a cross section perpendicular to the first direction (Z-axis direction). However, the cross-sectional shape of the first flow path portion 15 is not limited to a semicircular shape, a semi-elliptical shape, or a semi-elliptical shape, and may be, for example, a rectangular shape.

Further, the first plate-shaped member 10 has a flat plate portion 11a and a flat plate portion 11b formed in a flat plate shape on both sides of the first flow path portion 15. Both the flat plate portion 11a and the flat plate portion 11b extend from one end in the longitudinal direction to the other end in the longitudinal direction of the first plate-shaped member 10 along the longitudinal direction of the first plate-shaped member 10. In other words, the first flow path portion 15 is formed between the flat plate portion 11a and the flat plate portion 11b, and is opposite to the side on which the heat transfer tube 70 is arranged with respect to the flat plate portion 11a and the flat plate portion 11b. It is formed so as to bulge in the direction. The first flow path portion 15 is open on the arrangement side of the heat transfer tube 70. In the following description, the flat plate portion 11a and the flat plate portion 11b may be collectively referred to as the flat plate portion 11.

Inside the first flow path portion 15, a main flow path 15a extending in the vertical direction along the longitudinal direction of the first plate-shaped member 10 is formed. The main flow path 15a is the first flow path of the refrigerant distributor 150. The main flow path 15a, which is the first flow path, is connected to the refrigerant inflow pipe 60 connected to the refrigerant inflow port 18 and is formed so as to extend in the first direction (Z-axis direction) which is the arrangement direction of the plurality of heat transfer tubes 70. Has been done.

The main flow path 15a, which is the first flow path, extends so as to intersect with each of the plurality of heat transfer tubes 70 when viewed in the plate thickness direction of the first plate-shaped member 10. The main flow path 15a, which is the first flow path, communicates with the conduits of the plurality of heat transfer tubes 70 via the distribution hole portion 26 formed in the second plate-shaped member 20 which will be described later.

The main flow path 15a has a semicircular, semi-elliptical or semi-oval cross-sectional shape in a cross section perpendicular to the first direction (Z-axis direction). That is, the main flow path 15a is a space formed in a semi-cylindrical shape, a semi-elliptical cylinder shape, or a semi-long cylindrical shape. However, the cross-sectional shape of the main flow path 15a is not limited to a semicircular shape, a semi-elliptical shape, or a semi-elliptical shape, and may be, for example, a rectangular shape.

As described above, the main flow path 15a, which is the first flow path, is formed so as to extend in the first direction (Z-axis direction), communicates with the plurality of heat transfer tubes 70, and is in the first direction. At the lower end portion 15a2, it is connected to a refrigerant inflow pipe 60 that allows the refrigerant to flow into the refrigerant distributor 150. Then, the gas-liquid two-phase refrigerant flowing into the main flow path 15a through the refrigerant inflow pipe 60 flows upward in the main flow path 15a so as to go from one end 151a of the main body 151 to the other end 151b. It is distributed to each heat transfer tube 70.

A refrigerant inflow pipe 60 is connected to the lower end of the first flow path portion 15. The main flow path 15a and the internal space of the refrigerant inflow pipe 60 communicate with each other. The refrigerant inflow pipe 60 causes a gas-liquid two-phase refrigerant to flow into the main flow path 15a when the heat exchanger 100 functions as an evaporator. The connection position between the refrigerant inflow pipe 60 and the first flow path portion 15 is the refrigerant inflow port 18 through which the refrigerant flows into the refrigerant distributor 150. When the heat exchanger 100 functions as a condenser, the liquid refrigerant flows downward in the main flow path 15a and flows out through the refrigerant inflow pipe 60.

The second plate-shaped member 20 is formed with a sub-flow path 25 and a distribution hole portion 26. Here, the direction intersecting the plane P parallel to the first direction (Z-axis direction) and the second direction (X-axis direction) is defined as the third direction. The third direction includes the Y-axis direction. In the third direction (Y-axis direction), the distribution hole portion 26 is formed near the center of the second plate-shaped member 20, and the auxiliary flow path 25 is formed near the end of the second plate-shaped member 20. .. That is, in the third direction (Y-axis direction), the distribution hole portion 26 is formed near the center of the second plate-shaped member 20, and the auxiliary flow paths 25 are formed on both sides of the distribution hole portion 26, respectively. .. The formation positions of the sub-flow path 25 and the distribution hole portion 26 in the second plate-shaped member 20 are not limited to the above positions. The sub-flow paths 25 formed on both sides of the distribution hole portion 26 may be formed so that at least one end portion in the first direction communicates with each other.

The auxiliary flow path 25 is formed so as to extend in the first direction (Z-axis direction) in the second plate-shaped member 20. That is, the sub-channel 25 is formed by extending in the vertical direction along the longitudinal direction of the second plate-shaped member 20. The sub-flow path 25 is the second flow path of the refrigerant distributor 150. The sub-flow path 25, which is the second flow path, is formed in the main body 151 of the refrigerant distributor 150 so that both ends are connected to the main flow path 15a, which is the first flow path. The sub-flow path 25 communicates the upper end portion 15a1 and the lower end portion 15a2 of the main flow path 15a, and returns the refrigerant that has reached the upper end portion 15a1 of the main flow path 15a to the lower end portion 15a2 in which the refrigerant inlet 18 is formed. It forms a flow path for the refrigerant. The main body 151 of the refrigerant distributor 150 forms a refrigerant circulation flow path by the main flow path 15a and the sub flow path 25.

The main body 151 of the refrigerant distributor 150 has a main flow path 15a and a sub flow path 25 through which the refrigerant flows. As described above, the main flow path 15a is the first flow path, and the sub-flow path 25 is the second flow path. The sub-flow path 25, which is the second flow path, is formed so as to be located in the third direction with respect to the main flow path 15a, which is the first flow path. That is, the main flow path 15a and the sub-flow path 25 are formed so as to be located on the upstream side and the downstream side in the ventilation direction of the wind formed by the outdoor blower 108 or the indoor blower 109 shown in FIG.

The sub-flow path 25 has a central portion 25a, an inlet portion 25b, and an outlet portion 25c. The central portion 25a forms a flow path extending in the first direction (Z-axis direction). The inlet portion 25b is formed at one end portion 25a1 of the central portion 25a in the first direction (Z-axis direction). The outlet portion 25c is formed at the other end portion 25a2 of the central portion 25a in the first direction (Z-axis direction). The inlet portion 25b and the outlet portion 25c are formed as flow paths extending in the third direction (Y-axis direction) in the main body 151 of the refrigerant distributor 150.

The central portion 25a of the auxiliary flow path 25 has a flat plate portion 11 and a third plate shape of the first plate-shaped member 10 in the stacking direction of the first plate-shaped member 10, the second plate-shaped member 20, and the third plate-shaped member 30. It is sandwiched between the flat plate portion 34 of the member 30 and the flat plate portion 34.

Both ends of the subchannel 25 are composed of an inlet portion 25b and an outlet portion 25c. The inlet portion 25b and the outlet portion 25c are flat plates of the first flow path portion 15 and the third plate-shaped member 30 in the stacking direction of the first plate-shaped member 10, the second plate-shaped member 20, and the third plate-shaped member 30. It is sandwiched between the portion 34 and the portion 34. Therefore, the inlet portion 25b and the outlet portion 25c communicate with the main flow path 15a, which is the first flow path formed by the first flow path portion 15. On the other hand, the central portion 25a of the sub-flow path 25 does not communicate with the main flow path 15a, which is the first flow path.

In the main body 151 of the refrigerant distributor 150, the sub-flow path 25, which is the second flow path, has an inlet portion 25b and an outlet portion 25c so that both ends are connected to the main flow path 15a, which is the first flow path. It is formed. More specifically, the sub-flow path 25, which is the second flow path, is formed in the main body 151 of the refrigerant distributor 150 so that the inlet portion 25b communicates with the upper end portion 15a1 of the main flow path 15a. The sub-flow path 25, which is the second flow path, is formed in the main body 151 of the refrigerant distributor 150 so that the outlet portion 25c communicates with the lower end portion 15a2 of the main flow path 15a.

The refrigerant flowing from the main flow path 15a, which is the first flow path, to the sub-flow path 25, which is the second flow path, passes through the inlet portion 25b. That is, the refrigerant flows into the inlet portion 25b from the main flow path 15a, which is the first flow path. The refrigerant flowing from the sub-flow path 25, which is the second flow path, to the main flow path 15a, which is the first flow path, passes through the outlet portion 25c. That is, the outlet portion 25c causes the refrigerant to flow out to the main flow path 15a, which is the first flow path. In the main body 151 of the refrigerant distributor 150, the sub-flow path 25, which is the second flow path, does not communicate with the insertion hole 31 of the third plate-shaped member 30, which will be described later.

The second plate-shaped member 20 is formed with a plurality of distribution hole portions 26 each having a circular opening shape. The plurality of distribution holes 26 form a flow path between the main flow path 15a and the heat transfer tube 70, and distribute the refrigerant to each heat transfer tube 70. Each of the plurality of distribution hole portions 26 is a through hole that penetrates the second plate-shaped member 20 in the plate thickness direction of the second plate-shaped member 20. The plurality of distribution hole portions 26 are arranged along the first direction (Z-axis direction) which is the longitudinal direction of the second plate-shaped member 20. Each of the plurality of distribution hole portions 26 forms a through hole penetrating the second plate-shaped member 20, and is provided corresponding to each of the plurality of heat transfer tubes 70.

The opening shape of the distribution hole portion 26 is circular, but is not limited to a circular shape, and may be, for example, a semicircular shape, a semi-elliptical shape, a semi-elliptical shape, or a rectangular shape. The flow path cross-sectional areas of the plurality of distribution hole portions 26 are the same size. However, the flow path cross-sectional areas of the plurality of distribution hole portions 26 are not limited to those having the same size, and may be formed to have different sizes.

Further, in the main body 151 of the refrigerant distributor 150 according to the first embodiment, a plurality of distribution hole portions 26 are formed in the second plate-shaped member 20, but the distribution hole portion 26 is 1 in the second plate-shaped member 20. Only one may be formed. In this case, the distribution hole portion 26 is formed so as to extend in the first direction (Z-axis direction) in order to correspond to the plurality of heat transfer tubes 70.

Each of the plurality of distribution hole portions 26 is formed so as to overlap the main flow path 15a of the first plate-shaped member 10 when viewed in the plate thickness direction of the second plate-shaped member 20. Further, each of the plurality of distribution hole portions 26 is formed so as to overlap each of the plurality of insertion holes 31 of the third plate-shaped member 30, which will be described later, when viewed in the plate thickness direction of the second plate-shaped member 20. There is. Further, each of the plurality of distribution hole portions 26 is formed so as to overlap each of the plurality of heat transfer tubes 70 when viewed in the plate thickness direction of the second plate-shaped member 20. Therefore, in the stacking direction of the first plate-shaped member 10, the second plate-shaped member 20, and the third plate-shaped member 30, the distribution hole portion 26 is located between the heat transfer tube 70 and the main flow path 15a which is the first flow path. positioned. Then, the main flow path 15a of the first plate-shaped member 10 and each of the plurality of heat transfer tubes 70 communicate with each other via the plurality of distribution holes 26.

Further, the second plate-shaped member 20 has a flat plate-shaped closing portion 24. A part of the closing portion 24 overlaps with the main flow path 15a of the first plate-shaped member 10 when viewed in the plate thickness direction of the second plate-shaped member 20. The closing portion 24 has a function of preventing the main flow path 15a and each of the plurality of heat transfer tubes 70 from directly communicating with each other without passing through the distribution hole portion 26.

The third plate-shaped member 30 is formed with a plurality of insertion holes 31 into which one ends of the plurality of heat transfer tubes 70 are inserted. Each of the plurality of insertion holes 31 is a through hole that penetrates the third plate-shaped member 30 in the plate thickness direction of the third plate-shaped member 30.

The plurality of insertion holes 31 are arranged in parallel in the vertical direction along the longitudinal direction of the third plate-shaped member 30. The plurality of insertion holes 31 are provided independently of each other corresponding to each of the plurality of heat transfer tubes 70. The insertion hole 31 has a flat opening shape similar to the outer peripheral shape of the heat transfer tube 70. The open end of the insertion hole 31 is joined to the outer peripheral surface of the heat transfer tube 70 over the entire circumference by brazing.

The third plate-shaped member 30 has a flat plate-shaped flat plate portion 34. The flat plate portion 34 corresponds to a portion of the third plate-shaped member 30 that overlaps with the sub-flow path 25 of the second plate-shaped member 20 when viewed in the plate thickness direction of the third plate-shaped member 30. The sub-flow path 25, which is the second flow path, is blocked by the flat plate portion 34 and the flat plate portion 11 in the second direction (X-axis direction).

The main body 151 of the refrigerant distributor 150 has a main flow path 15a and a second flow, which are the first flow paths, in the stacking direction of the first plate-shaped member 10, the second plate-shaped member 20, and the third plate-shaped member 30. Both ends of the sub-flow path 25, which is a road, overlap each other. Further, the main body 151 of the refrigerant distributor 150 includes the main flow path 15a, which is the first flow path, in the stacking direction of the first plate-shaped member 10, the second plate-shaped member 20, and the third plate-shaped member 30. The distribution hole portion 26 and the insertion hole 31 are formed so as to overlap each other.

FIG. 6 is a conceptual diagram showing the flow of the refrigerant in the refrigerant distributor 150 constituting the heat exchanger 100 according to the first embodiment. Next, the operation of the refrigerant distributor 150 according to the first embodiment will be described by exemplifying the operation when the heat exchanger 100 functions as the evaporator of the refrigeration cycle device 200.

When the refrigeration cycle device 200 is in the heating operation, the refrigerant flowing into the refrigerant distributor 150 is a gas-liquid two-phase flow. The gas-liquid two-phase refrigerant flows into the main body 151 from the refrigerant inflow pipe 60 shown in FIGS. 2 and 6, and forms a main flow path 15a formed in the first plate-shaped member 10 as shown by the arrow UF in FIG. It flows vertically upward from one end 151a toward the other end 151b. The vertically rising and flowing refrigerant passes through the distribution hole 26 of the second plate-shaped member 20 and is distributed to each heat transfer tube 70 through the insertion hole 31 formed in the third plate-shaped member 30.

Further, the refrigerant staying in the upper part of the main flow path 15a flows into the inlet portion 25b provided in the second plate-shaped member 20 communicating with the upper end portion 15a1 of the main flow path 15a. At this time, as shown by the arrow OF, the refrigerant flows from the main flow path 15a, which is the first flow path, toward the sub-flow path 25, which is the second flow path, toward the outside, which is the third direction. Then, as shown by the arrow DF, the refrigerant flowing in from the inlet portion 25b of the sub-channel 25 flows downward along the central portion 25a of the sub-channel 25 formed in the second plate-shaped member 20. ..

The refrigerant that has reached the lower end of the central portion 25a of the sub-flow path 25 flows out to the main flow path 15a from the outlet portion 25c that communicates with the lower end portion 15a2 of the main flow path 15a. At this time, as shown by the arrow IF, the refrigerant flows inward in the third direction from the sub-flow path 25 which is the second flow path toward the main flow path 15a which is the first flow path. Then, the refrigerant flowing out from the outlet portion 25c to the main flow path 15a vertically rises up the main flow path 15a together with the refrigerant flowing into the main body 151 from the refrigerant inflow pipe 60, and is distributed to each heat transfer pipe 70.

FIG. 7 is a diagram showing the flow rate distribution of the refrigerant in the refrigerant distributor 150 constituting the heat exchanger 100 according to the first embodiment. In FIG. 7, the horizontal axis represents the refrigerant flow rate [kg / h], and the vertical axis represents the distance [m] from the refrigerant inflow port 18 in the first direction in which the heat transfer tubes 70 are arranged.

In FIG. 7, the dotted line A shows the flow rate of the refrigerant flowing through the main flow path 15a when the sub-flow path 25 is not provided, and the solid line B shows the flow rate of the refrigerant flowing through the main flow path 15a when the sub-flow path 25 is provided. Shown. Further, the alternate long and short dash line C shows a case where the flow rate of the refrigerant flowing through the main flow path 15a is constant in the vertical direction. When the flow rate of the refrigerant flowing through the main flow path 15a is constant in the vertical direction, the inflow amount of the refrigerant flowing into the heat transfer tubes 70 arranged in the first direction is constant. Therefore, it is desirable that the flow rate of the refrigerant in the main flow path 15a is close to the flow rate of the refrigerant indicated by the alternate long and short dash line C.

As shown by the dotted line A, when the main body 151 is not provided with the sub-flow path 25 which is the second flow path, the liquid refrigerant stays in the upper part of the main flow path 15a which is the first flow path. A large amount of liquid refrigerant is distributed above the main flow path 15a, which is one flow path.

On the other hand, when the main body 151 is provided with the sub-flow path 25 which is the second flow path, the liquid refrigerant staying in the upper part of the main flow path 15a is transferred to the lower part of the main flow path 15a via the sub-flow path 25. return. Therefore, as shown by the arrow MU between the dotted line A and the solid line B, the refrigerant returns to the lower part of the main flow path 15a in the upper part of the main flow path 15a, so that the flow rate of the refrigerant decreases. Further, as shown by the arrow MD between the dotted line A and the solid line B, the flow rate of the refrigerant increases in the lower part of the main flow path 15a because the refrigerant returns from the upper part of the main flow path 15a. Therefore, as shown by the solid line B, the flow rate of the refrigerant flowing through the main flow path 15a when the sub-flow path 25 is provided is compared with the flow rate of the refrigerant flowing through the main flow path 15a when the sub-flow path 25 is not provided. It is approaching the flow rate of the refrigerant indicated by the alternate long and short dash line C. Therefore, the refrigerant distributor 150 having the auxiliary flow path 25 can evenly distribute the refrigerant to each heat transfer tube 70 as compared with the refrigerant distributor having no auxiliary flow path 25.

[Effect of heat exchanger 100]
The heat exchanger 100 has a refrigerant distributor 150 in which a main flow path 15a through which the refrigerant flows and a sub-flow path 25 are formed therein. The sub-flow path 25, which is the second flow path, extends in the first direction (Z-axis direction) and is formed so that both ends are connected to the main flow path 15a, which is the first flow path. The sub-flow path 25, which is the second flow path, is the third direction when the direction intersecting the plane P parallel to the first direction (Z-axis direction) and the second direction (X-axis direction) is defined as the third direction. It is formed so as to be located in the third direction with respect to the main flow path 15a which is one flow path. Therefore, the heat exchanger 100 can suppress the increase in size of the refrigerant distributor 150 in the second direction in which the refrigerant flows, and extends the heat exchanger 100 through the conduit of the heat transfer tube 70 within the range of the structural contract. It can be increased in the second direction. Therefore, the heat exchanger 100 can make the refrigerant distributor 150 compact without increasing the size in the extending direction of the pipe line of the heat transfer tube 70, while securing a wide heat transfer area of the heat transfer tube 70.

Further, the heat exchanger 100 secures a wider heat transfer area of the heat transfer tube 70 as compared with a heat exchanger having a first flow path and a second flow path in the extending direction of the line of the heat transfer tube 70. Can be done. Therefore, the heat exchanger 100 can improve the heat exchange performance as compared with the heat exchanger having the first flow path and the second flow path in the extending direction of the conduit of the heat transfer tube 70. Therefore, the heat exchanger 100 can improve the suppression of the uneven flow of the refrigerant distribution with respect to the change in the refrigerant flow rate or the dryness depending on the operating state of the air conditioner, and has a distribution robustness that widens the range corresponding to the refrigerant flow rate and the like. Can be improved.

Further, the heat exchanger 100 has a sub-flow path 25 so that the refrigerant can be transferred from the upper part of the main flow path 15a to the lower part of the main flow path 15a in a state where the liquid refrigerant stays in the upper part of the main flow path 15a depending on the operating state of the air conditioner. By circulating the refrigerant, the drift of the refrigerant can be suppressed. Therefore, the heat exchanger 100 provided with the refrigerant distributor 150 having the auxiliary flow path 25 transfers the refrigerant to each heat transfer tube 70 as compared with the heat exchanger provided with the refrigerant distributor having no auxiliary flow path 25. It can be evenly distributed. As a result, the heat exchanger 100 can improve the heat exchange performance as compared with the heat exchanger provided with the refrigerant distributor which does not have the auxiliary flow path 25.

Further, in the refrigerant distributor 150, both ends of the main flow path 15a and the sub-flow path 25 overlap in the stacking direction of the first plate-shaped member 10, the second plate-shaped member 20, and the third plate-shaped member 30. , The main flow path 15a, the distribution hole portion 26, and the insertion hole 31 are formed so as to overlap each other. Therefore, the heat exchanger 100 can suppress the enlargement of the refrigerant distributor 150 in the second direction in which the conduit of the heat transfer tube 70 extends, and the heat exchanger 100 can be transferred to the heat transfer tube 70 within the range of the structural contract. It can be increased in the second direction in which the pipeline extends. Therefore, the heat exchanger 100 can make the refrigerant distributor 150 compact without increasing the size in the extending direction of the pipe line of the heat transfer tube 70, while securing a wide heat transfer area of the heat transfer tube 70.

Further, both ends of the sub-flow path 25 which is the second flow path flow out the refrigerant to the inlet portion 25b where the refrigerant flows in from the main flow path 15a which is the first flow path and the main flow path 15a which is the first flow path. It is composed of an outlet portion 25c and an outlet portion 25c. The inlet portion 25b and the outlet portion 25c are formed so as to extend in the third direction. Therefore, the heat exchanger 100 can suppress the enlargement of the refrigerant distributor 150 in the second direction in which the conduit of the heat transfer tube 70 extends, and the heat exchanger 100 can be transferred to the heat transfer tube 70 within the range of the structural contract. It can be increased in the second direction in which the pipeline extends. Therefore, the heat exchanger 100 can make the refrigerant distributor 150 compact without increasing the size in the extending direction of the pipe line of the heat transfer tube 70, while securing a wide heat transfer area of the heat transfer tube 70.

Further, the sub-flow path 25, which is the second flow path, is formed on both sides of the distribution hole portion 26 in the third direction. Therefore, the heat exchanger 100 can suppress the enlargement of the refrigerant distributor 150 in the second direction in which the conduit of the heat transfer tube 70 extends, and the heat exchanger 100 can be transferred to the heat transfer tube 70 within the range of the structural contract. It can be increased in the second direction in which the pipeline extends. Therefore, the heat exchanger 100 can make the refrigerant distributor 150 compact without increasing the size in the extending direction of the pipe line of the heat transfer tube 70, while securing a wide heat transfer area of the heat transfer tube 70.

Further, a plurality of distribution hole portions 26 are formed along the first direction (Z-axis direction). Each of the plurality of distribution hole portions 26 functions as a throttle hole having a high flow resistance in the refrigerant flow path between the main flow path 15a which is the first flow path and each of the plurality of heat transfer tubes 70. When the heat exchanger functions as an evaporator, each distribution hole 26 functions as a throttle hole, so that the pressure in the main flow path 15a rises, and the pressure in the main flow path 15a and the pressure in the plurality of insertion holes 31 are respectively. The pressure difference between the pressure and the pressure increases. Therefore, the pressure difference between the pressure of the main flow path 15a and the pressure of the upper insertion hole 31 and the pressure difference between the pressure of the main flow path 15a and the pressure of the lower insertion hole 31 become more uniform. As a result, the refrigerant in the main flow path 15a is evenly distributed to each insertion hole 31, and as a result, is evenly distributed to each heat transfer tube 70.

Embodiment 2.
FIG. 8 is an exploded perspective view conceptually showing the configuration of a main part of the heat exchanger 100 according to the second embodiment. FIG. 9 is a cross-sectional view conceptually showing the communication position between the first flow path and the second flow path of the refrigerant distributor 150 constituting the heat exchanger 100 according to the second embodiment. The components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted. The heat exchanger 100 according to the second embodiment is different from the heat exchanger 100 according to the first embodiment in that the refrigerant distributor 150 further includes the fourth plate-shaped member 40 and the fifth plate-shaped member 50.

The main body 151 of the refrigerant distributor 150 has a first plate-shaped member 10, a second plate-shaped member 20, a third plate-shaped member 30, a fourth plate-shaped member 40, and a fifth plate-shaped member 50. Both the fourth plate-shaped member 40 and the fifth plate-shaped member 50 are formed by using a metal flat plate and have a strip-like shape long in one direction. The contours of the outer edges of the first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, the fourth plate-shaped member 40, and the fifth plate-shaped member 50 have the same shape as each other. There is. The first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, the fourth plate-shaped member 40, and the fifth plate-shaped member 50 have their respective plate thickness directions extending in the conduit of the heat transfer tube 70. It is arranged so as to be parallel to the direction. That is, the plate surfaces of the first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, the fourth plate-shaped member 40, and the fifth plate-shaped member 50 are the conduits of the heat transfer tube 70. It is arranged so as to be perpendicular to the stretching direction.

In the main body 151 of the refrigerant distributor 150, the first plate-shaped member 10, the fourth plate-shaped member 40, the second plate-shaped member 20, the fifth plate-shaped member 50, and the third plate-shaped member 30 are from the heat transfer tube 70. It has a structure in which the layers are stacked in this order from the farthest distance. The first plate-shaped member 10 is arranged at the position farthest from the heat transfer tube 70 in the main body 151, and the third plate-shaped member 30 is arranged at the position closest to the heat transfer tube 70 in the main body 151. Has been done.

The fourth plate-shaped member 40 is arranged between the first plate-shaped member 10 and the second plate-shaped member 20, and the plate surface of the fourth plate-shaped member 40 is the first plate-shaped member 10 and the second plate-shaped member 20. Adjacent to the plate surface of the plate-shaped member 20. The fifth plate-shaped member 50 is arranged between the second plate-shaped member 20 and the third plate-shaped member 30, and the plate surface of the fifth plate-shaped member 50 is the second plate-shaped member 20 and the third plate-shaped member 20. Adjacent to the plate surface of the plate-shaped member 30.

The adjacent members of the first plate-shaped member 10, the fourth plate-shaped member 40, the second plate-shaped member 20, the fifth plate-shaped member 50, and the third plate-shaped member 30 are joined by brazing. The longitudinal direction of the first plate-shaped member 10, the fourth plate-shaped member 40, the second plate-shaped member 20, the fifth plate-shaped member 50, and the third plate-shaped member 30 is in the first direction (Z-axis direction). It is arranged along the line.

The fourth plate-shaped member 40 has a communication hole 45 located between the main flow path 15a, which is the first flow path, and both ends of the sub-flow path 25, and the main flow path 15a, which is the first flow path, and the second distribution. A second distribution hole 46 located between the hole 46 is formed. The communication hole 45 and the second distribution hole 46 are through holes.

Two communication holes 45 are formed in the fourth plate-shaped member 40 on one end 151a side and two on the other end 151b side. The communication hole 45 formed on the one end 151a side serves as an outlet when the refrigerant flows out from the sub flow path 25 to the main flow path 15a. The communication hole 45 formed on the other end 151b side serves as an inlet when the refrigerant flows from the main flow path 15a into the sub-flow path 25. The communication hole 45 is shown as a through hole forming a rectangular opening in FIG. 8, but the opening shape of the communication hole 45 is not limited to a rectangular shape.

The communication hole 45 is formed with the main flow path 15a and the inlet portion in the stacking direction of the first plate-shaped member 10, the fourth plate-shaped member 40, the second plate-shaped member 20, the fifth plate-shaped member 50, and the third plate-shaped member 30. It is formed so as to be located between 25b. Further, the communication hole 45 is formed with the main flow path 15a in the stacking direction of the first plate-shaped member 10, the fourth plate-shaped member 40, the second plate-shaped member 20, the fifth plate-shaped member 50, and the third plate-shaped member 30. It is formed so as to be located between the outlet portion 25c and the outlet portion 25c. Therefore, the communication hole 45 communicates with the main flow path 15a which is the first flow path and the sub flow path 25 which is the second flow path, and the main flow path 15a which is the first flow path and the sub flow path which is the second flow path. It serves as a flow path connecting the flow path 25.

The fourth plate-shaped member 40 is formed with a plurality of second distribution hole portions 46 each having a circular opening shape. The second distribution hole portion 46 is formed near the center of the fourth plate-shaped member 40 in the third direction (Y-axis direction). The plurality of second distribution hole portions 46 include the main flow path 15a and the heat transfer tube together with the distribution hole portion 26 formed in the second plate-shaped member 20 and the third distribution hole portion 51 formed in the fifth plate-shaped member 50 described later. A flow path is formed between the heat transfer tubes 70 and the refrigerant is distributed to each heat transfer tube 70.

Each of the plurality of second distribution hole portions 46 is a through hole that penetrates the fourth plate-shaped member 40 in the plate thickness direction of the fourth plate-shaped member 40. The plurality of second distribution hole portions 46 are arranged along the first direction (Z-axis direction) which is the longitudinal direction of the fourth plate-shaped member 40. Each of the plurality of second distribution hole portions 46 forms a through hole penetrating the fourth plate-shaped member 40, and is provided corresponding to each of the plurality of heat transfer tubes 70. Further, each of the plurality of second distribution hole portions 46 is provided corresponding to each of the distribution hole portions 26 formed in the second plate-shaped member 20. Further, each of the plurality of second distribution hole portions 46 is provided corresponding to each of the third distribution hole portions 51 formed in the fifth plate-shaped member 50, which will be described later.

The opening shape of the second distribution hole portion 46 is circular, but is not limited to a circular shape, and may be, for example, a semicircular shape, a semi-elliptical shape, a semi-elliptical shape, or a rectangular shape. The flow path cross-sectional areas of the plurality of second distribution hole portions 46 are the same size. However, the flow path cross-sectional areas of the plurality of second distribution holes 46 are not limited to those having the same size, and may be formed to have different sizes.

Further, in the main body 151 of the refrigerant distributor 150 according to the second embodiment, a plurality of second distribution hole portions 46 are formed in the fourth plate-shaped member 40, but the second distribution hole portion 46 has a fourth plate shape. Only one may be formed on the member 40. In this case, the second distribution hole portion 46 is formed so as to extend in the first direction (Z-axis direction) in order to correspond to the plurality of heat transfer tubes 70.

Each of the plurality of second distribution hole portions 46 is formed so as to overlap the main flow path 15a of the first plate-shaped member 10 when viewed in the plate thickness direction of the fourth plate-shaped member 40. Further, each of the plurality of second distribution hole portions 46 is formed so as to overlap each of the distribution hole portions 26 of the second plate-shaped member 20 when viewed in the plate thickness direction of the fourth plate-shaped member 40. .. Further, each of the plurality of second distribution hole portions 46 is formed so as to overlap each of the third distribution hole portions 51 of the fifth plate-shaped member 50 when viewed in the plate thickness direction of the fourth plate-shaped member 40. ing. Further, each of the plurality of second distribution hole portions 46 is formed so as to overlap each of the plurality of insertion holes 31 of the third plate-shaped member 30 when viewed in the plate thickness direction of the fourth plate-shaped member 40. There is. Further, each of the plurality of second distribution hole portions 46 is formed so as to overlap each of the plurality of heat transfer tubes 70 when viewed in the plate thickness direction of the fourth plate-shaped member 40.

Therefore, in the stacking direction of the first plate-shaped member 10, the fourth plate-shaped member 40, the second plate-shaped member 20, the fifth plate-shaped member 50, and the third plate-shaped member 30, the second distribution hole portion 46 is transmitted. It is located between the heat pipe 70 and the main flow path 15a, which is the first flow path. Then, the main flow path 15a of the first plate-shaped member 10 and each of the plurality of heat transfer tubes 70 communicate with each other via the plurality of second distribution hole portions 46.

Further, the fourth plate-shaped member 40 has a flat plate-shaped closing portion 44. A part of the closing portion 44 overlaps with the main flow path 15a of the first plate-shaped member 10 when viewed in the plate thickness direction of the fourth plate-shaped member 40. The closing portion 44 has a function of preventing the main flow path 15a and each of the plurality of heat transfer tubes 70 from directly communicating with each other without passing through the second distribution hole portion 46.

Further, the closing portion 44 covers a part of the sub-flow path 25 from the arrangement side of the first plate-shaped member 10. The closing portion 44 covers at least the central portion 25a of the sub-flow path 25 from the arrangement side of the first plate-shaped member 10. The closing portion 44 forms a part of the pipeline forming the sub-flow path 25.

The fifth plate-shaped member 50 is formed with a third distribution hole 51 located between the distribution hole 26 and the insertion hole 31. The third distribution hole portion 51 is a through hole.

The fifth plate-shaped member 50 is formed with a plurality of third distribution holes 51 each having a circular opening shape. The third distribution hole portion 51 is formed near the center of the fifth plate-shaped member 50 in the third direction (Y-axis direction). The plurality of third distribution hole portions 51 include the main flow path 15a and the heat transfer tube 70 together with the distribution hole portion 26 formed in the second plate-shaped member 20 and the second distribution hole portion 46 formed in the fourth plate-shaped member 40. A flow path is formed between the heat transfer tubes 70 to distribute the refrigerant to each heat transfer tube 70.

Each of the plurality of third distribution hole portions 51 is a through hole that penetrates the fifth plate-shaped member 50 in the plate thickness direction of the fifth plate-shaped member 50. The plurality of third distribution hole portions 51 are arranged along the first direction (Z-axis direction) which is the longitudinal direction of the fifth plate-shaped member 50. Each of the plurality of third distribution hole portions 51 forms a through hole penetrating the fifth plate-shaped member 50, and is provided corresponding to each of the plurality of heat transfer tubes 70. Further, each of the plurality of third distribution hole portions 51 is provided corresponding to each of the distribution hole portions 26 formed in the second plate-shaped member 20. Further, each of the plurality of third distribution hole portions 51 is provided corresponding to each of the second distribution hole portions 46 formed in the fourth plate-shaped member 40.

The opening shape of the third distribution hole 51 is circular, but is not limited to a circular shape, and may be, for example, a semicircular shape, a semi-elliptical shape, a semi-elliptical shape, or a rectangular shape. The flow path cross-sectional areas of the plurality of third distribution holes 51 are the same size. However, the flow path cross-sectional areas of the plurality of third distribution holes 51 are not limited to those having the same size, and may be formed to have different sizes.

Further, in the main body 151 of the refrigerant distributor 150 according to the first embodiment, a plurality of third distribution hole portions 51 are formed in the fifth plate-shaped member 50, but the third distribution hole portion 51 has a fifth plate shape. Only one may be formed on the member 50. In this case, the third distribution hole 51 is formed so as to extend in the first direction (Z-axis direction) in order to correspond to the plurality of heat transfer tubes 70.

Each of the plurality of third distribution hole portions 51 is formed so as to overlap the main flow path 15a of the first plate-shaped member 10 when viewed in the plate thickness direction of the fifth plate-shaped member 50. Further, each of the plurality of third distribution hole portions 51 is formed so as to overlap each of the distribution hole portions 26 of the second plate-shaped member 20 when viewed in the plate thickness direction of the fifth plate-shaped member 50. .. Further, each of the plurality of third distribution hole portions 51 is formed so as to overlap each of the second distribution hole portions 46 of the fourth plate-shaped member 40 when viewed in the plate thickness direction of the fifth plate-shaped member 50. ing. Further, each of the plurality of third distribution hole portions 51 is formed so as to overlap each of the plurality of insertion holes 31 of the third plate-shaped member 30 when viewed in the plate thickness direction of the fifth plate-shaped member 50. There is. Further, each of the plurality of third distribution hole portions 51 is formed so as to overlap each of the plurality of heat transfer tubes 70 when viewed in the plate thickness direction of the fifth plate-shaped member 50.

Therefore, in the stacking direction of the first plate-shaped member 10, the fourth plate-shaped member 40, the second plate-shaped member 20, the fifth plate-shaped member 50, and the third plate-shaped member 30, the third distribution hole portion 51 is transmitted. It is located between the heat pipe 70 and the main flow path 15a, which is the first flow path. Then, the main flow path 15a of the first plate-shaped member 10 and each of the plurality of heat transfer tubes 70 communicate with each other via the plurality of third distribution hole portions 51.

Further, the fifth plate-shaped member 50 has a flat plate-shaped closing portion 53. A part of the closing portion 53 overlaps with the main flow path 15a of the first plate-shaped member 10 when viewed in the plate thickness direction of the fifth plate-shaped member 50. The closing portion 53 has a function of preventing the main flow path 15a and each of the plurality of heat transfer tubes 70 from directly communicating with each other without passing through the third distribution hole portion 51.

Further, the closing portion 53 covers a part of the sub-flow path 25 from the arrangement side of the third plate-shaped member 30. The closing portion 53 covers at least the central portion 25a of the sub-flow path 25 from the arrangement side of the third plate-shaped member 30. The closing portion 53 forms a part of the pipeline forming the sub-flow path 25.

FIG. 10 is a conceptual diagram showing the flow of the refrigerant in the refrigerant distributor 150 constituting the heat exchanger 100 according to the second embodiment. When the refrigeration cycle device 200 is in a heating operation, the refrigerant flowing into the refrigerant distributor 150 is a gas-liquid two-phase flow. The gas-liquid two-phase refrigerant flows into the main body 151 from the refrigerant inflow pipe 60, and as shown by the arrow UF in FIG. 10, the main flow path 15a formed in the first plate-shaped member 10 is formed from one end 151a to the other. Flows vertically upward toward the end 151b of. A part of the refrigerant that rises vertically and flows is the second distribution hole portion 46 of the fourth plate-shaped member 40, the distribution hole portion 26 of the second plate-shaped member 20, and the third distribution hole portion of the fifth plate-shaped member 50. It passes through 51 in this order and is distributed to each heat transfer tube 70 through an insertion hole 31 formed in the third plate-shaped member 30.

Further, the refrigerant staying in the upper part of the main flow path 15a flows into the inlet portion 25b provided in the second plate-shaped member 20 through the communication hole 45 communicating with the upper end portion 15a1 of the main flow path 15a. At this time, as shown by the arrow OF, the refrigerant flows from the main flow path 15a, which is the first flow path, toward the sub-flow path 25, which is the second flow path, toward the outside, which is the third direction. Then, as shown by the arrow DF, the refrigerant flowing in from the inlet portion 25b of the sub-channel 25 flows downward along the central portion 25a of the sub-channel 25 formed in the second plate-shaped member 20. ..

The refrigerant that has reached the lower end of the central portion 25a of the sub-flow path 25 flows out from the outlet portion 25c to the main flow path 15a through the communication hole 45 that communicates with the lower end portion 15a2 of the main flow path 15a. At this time, as shown by the arrow IF, the refrigerant flows inward in the third direction from the sub-flow path 25 which is the second flow path toward the main flow path 15a which is the first flow path. Then, the refrigerant flowing out from the outlet portion 25c to the main flow path 15a vertically rises up the main flow path 15a together with the refrigerant flowing into the main body 151 from the refrigerant inflow pipe 60, and is distributed to each heat transfer pipe 70.

FIG. 11 is a diagram showing the flow rate distribution of the refrigerant in the refrigerant distributor 150 constituting the heat exchanger 100 according to the second embodiment. In FIG. 11, the horizontal axis represents the refrigerant flow rate [kg / h], and the vertical axis represents the distance [m] from the refrigerant inlet 18 in the first direction in which the heat transfer tubes 70 are arranged.

Similar to the first embodiment, when the main body 151 is provided with the sub-flow path 25 which is the second flow path, the liquid refrigerant staying in the upper part of the main flow path 15a passes through the main flow path 25. Return to the bottom of 15a. Therefore, as shown by the arrow MU between the dotted line A and the solid line B, the refrigerant returns to the lower part of the main flow path 15a in the upper part of the main flow path 15a, so that the flow rate of the refrigerant decreases. Further, as shown by the arrow MD between the dotted line A and the solid line B, the flow rate of the refrigerant increases in the lower part of the main flow path 15a because the refrigerant returns from the upper part of the main flow path 15a. Therefore, as shown by the solid line B, the flow rate of the refrigerant flowing through the main flow path 15a when the sub-flow path 25 is provided is compared with the flow rate of the refrigerant flowing through the main flow path 15a when the sub-flow path 25 is not provided. It is approaching the flow rate of the refrigerant indicated by the alternate long and short dash line C. Therefore, the refrigerant distributor 150 having the auxiliary flow path 25 can evenly distribute the refrigerant to each heat transfer tube 70 as compared with the refrigerant distributor having no auxiliary flow path 25.

[Effect of heat exchanger 100]
The refrigerant distributor 150 has a fourth plate-shaped member 40 and a fifth plate-shaped member 50. The fourth plate-shaped member 40 is divided into a communication hole 45 located between the main flow path 15a, which is the first flow path, and both ends of the sub-flow path 25, and the main flow path 15a, which is the first flow path. A second distribution hole 46 located between the hole 26 is formed. Further, the fifth plate-shaped member 50 is formed with a third distribution hole portion 51 located between the distribution hole portion 26 and the insertion hole 31.

The main body 151 of the refrigerant distributor 150 has the above-mentioned penetration of the fourth plate-shaped member 40 and the fifth plate-shaped member 50, so that the refrigerant flows between the main flow path 15a and the sub-flow path 25 and the mainstream. It does not interfere with the flow of the refrigerant from the passage 15a to the heat transfer tube 70. Further, the main body 151 of the refrigerant distributor 150 can form a conduit for the sub-flow path 25 by the closing portion 44 of the fourth plate-shaped member 40 and the closing portion 53 of the fifth plate-shaped member 50. That is, the main body 151 of the refrigerant distributor 150 does not require the flat plate portion 11 of the first plate-shaped member 10 and the flat plate portion 34 of the third plate-shaped member 30 in order to form the conduit of the sub-flow path 25.

Therefore, the second plate-shaped member 20 has a side flow so as to overlap the main flow path 15a of the first plate-shaped member 10 and the insertion hole 31 of the third plate-shaped member 30 when viewed in the stacking direction of each plate-shaped member. The road 25 can be formed. In other words, the main body 151 of the refrigerant distributor 150 can increase the width of the sub-flow path 25 formed in the second plate-shaped member 20 in the third direction (Y-axis direction), and the sub-flow path 25 can be increased. The volume of the can be increased. Therefore, the refrigerant distributor 150 of the heat exchanger 100 can circulate a large amount of refrigerant staying in the upper part when the pressure loss on the sub-flow path 25 side is small and the circulation flow rate is high, and suppresses the refrigerant drift. The performance of the heat exchanger 100 can be improved.

Embodiment 3.
FIG. 12 is an exploded perspective view conceptually showing the main configuration of the heat exchanger 100 according to the third embodiment. FIG. 13 is a cross-sectional view conceptually showing the communication position between the first flow path and the second flow path of the refrigerant distributor 150 constituting the heat exchanger 100 according to the third embodiment. FIG. 14 is a conceptual diagram showing the flow of the refrigerant in the refrigerant distributor 150 constituting the heat exchanger 100 according to the third embodiment. The components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted. The heat exchanger 100 according to the third embodiment is different from the outlet portion 25c of the heat exchanger 100 according to the first embodiment in that the angle of the pipe axis of the outlet portion 25c1 is specified.

As shown in FIG. 12, the subchannel 25 has a central portion 25a, an inlet portion 25b, and an outlet portion 25c1. The central portion 25a forms a flow path extending in the first direction (Z-axis direction). The outlet portion 25c1 is formed at the other end portion 25a2 of the central portion 25a in the first direction (Z-axis direction).

The pipe axis TA of the outlet portion 25c1 is inclined with respect to the first direction (Z-axis direction) and the third direction (Y-axis direction) so as to approach the diagonal DL of the second plate-shaped member 20. Therefore, as shown by the arrows IF and UF in FIG. 14, the outlet portion 25c1 has a vector component in which the direction in which the refrigerant flowing out from the outlet portion 25c1 flows has a vector component in the direction in which the refrigerant flowing out from the refrigerant inflow pipe 60 flows. It is formed so as to be inclined with respect to the first direction and the third direction. That is, the refrigerant flowing out from the outlet portion 25c1 is directed in the direction along the flow of the refrigerant flowing through the main flow path 15a.

On the plate surface of the second plate-shaped member 20, the outlet angle θ, which is the angle between the pipe axis TA direction of the outlet portion 25c1 and the gravity direction GD, is formed to be an angle of 90 degrees or more.

FIG. 15 is a diagram showing the flow rate distribution of the refrigerant in the refrigerant distributor 150 constituting the heat exchanger 100 according to the third embodiment. In FIG. 12, the horizontal axis represents the refrigerant flow rate [kg / h], and the vertical axis represents the distance [m] from the refrigerant inflow port 18 in the first direction in which the heat transfer tubes 70 are arranged.

[Effect of heat exchanger 100]
As shown by the arrows IF and UF in FIG. 14, the outlet portion 25c1 has a vector component in the direction in which the refrigerant flowing out from the outlet portion 25c1 flows in the direction in which the refrigerant flows out from the refrigerant inflow pipe 60. It is formed so as to be inclined with respect to the first direction and the third direction. The direction of the outlet portion 25c1 of the sub-flow path 25 formed in the second plate-shaped member 20 is the vertical ascending direction, and the flow vector of the refrigerant when merging from the sub-flow path 25 to the main flow path 15a is upward. , The upward inertial force of the refrigerant increases. Therefore, the refrigerant distributor 150 of the heat exchanger 100 promotes the circulation of the refrigerant in the main flow path 15a and the sub-flow path 25. Then, the refrigerant distributor 150 of the heat exchanger 100 can circulate a large amount of refrigerant staying in the upper part of the main flow path 15a, and can suppress the drift of the refrigerant.

Embodiment 4.
FIG. 16 is an exploded perspective view conceptually showing the configuration of a main part of the heat exchanger 100 according to the fourth embodiment. FIG. 17 is a cross-sectional view conceptually showing the communication position between the first flow path and the second flow path of the refrigerant distributor 150 constituting the heat exchanger 100 according to the fourth embodiment. FIG. 18 is a conceptual diagram showing the flow of the refrigerant in the refrigerant distributor 150 constituting the heat exchanger 100 according to the fourth embodiment. The components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted. The heat exchanger 100 according to the fourth embodiment is different from the heat exchanger 100 according to the first embodiment in that the configuration of the main flow path 15a, which is the first flow path, is further specified.

As described above, the first flow path portion 15 forms the main flow path 15a, which is the first flow path, inside. In the heat exchanger 100 according to the fourth embodiment, the main flow path 15a, which is the first flow path, is cut off from one lower end portion 15a2 on the side communicating with the refrigerant inflow pipe 60 toward the other upper end portion 15a1. It is formed so that the area is small. When the first direction (Z-axis direction) is specified as the vertical direction, the main flow path 15a is formed so that the cross-sectional area of the flow path decreases as it goes upward. As shown in FIG. 17, the first flow path portion 15 has a rectangular cross-sectional shape. However, the cross-sectional shape of the first flow path portion 15 is not limited to a rectangle, and may be, for example, a semicircular shape, a semi-elliptical shape, or a semi-elliptical shape.

The first flow path portion 15 extends from one end portion 151a of the main body portion to the other end portion 151b along the longitudinal direction of the first plate-shaped member 10. Both ends of the first flow path portion 15 in the stretching direction are closed. In FIG. 16, the first flow path portion 15 has a side wall 15b formed in a trapezoidal shape when viewed in the stacking direction of the first plate-shaped member 10, the second plate-shaped member 20, and the third plate-shaped member 30. Have. The first flow path portion 15 is formed in a square columnar shape having a side wall 15b. The first flow path portion 15 is formed so as to taper from the lower end portion 15a2 on the refrigerant inflow port 18 side toward the other upper end portion 15a1 in the longitudinal direction of the first plate-shaped member 10. The first flow path portion 15 is not limited to the one formed in a square columnar shape having the side wall 15b, and may have another shape such as a truncated cone shape or a truncated cone shape. May be good.

[Effect of heat exchanger 100]
The main flow path 15a, which is the first flow path, is formed so that the cross-sectional area of the flow path decreases from one lower end portion 15a2 on the side communicating with the refrigerant inflow pipe 60 toward the other upper end portion 15a1. When the first direction (Z-axis direction) is set, the flow path cross-sectional area of the main flow path 15a is formed to be smaller toward the upper vertical direction, so that the refrigerant distributor 150 of the heat exchanger 100 is formed in the main flow path 15a. The flow velocity of the refrigerant can be increased. Therefore, even if the amount of refrigerant circulation becomes small depending on the operating state of the air conditioner, the refrigerant distributor 150 of the heat exchanger 100 can reach the uppermost part of the main flow path 15a and suppress the drift of the refrigerant. can do.

Embodiment 5.
FIG. 19 is an exploded perspective view conceptually showing the configuration of a main part of the heat exchanger 100 according to the fifth embodiment. FIG. 20 is a side view conceptually showing the inside of the refrigerant distributor 150 shown in FIG. FIG. 21 is a cross-sectional view conceptually showing the communication position between the first flow path and the second flow path of the refrigerant distributor 150 constituting the heat exchanger 100 according to the fifth embodiment. The components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted. The refrigerant distributors 150 of the first to fourth embodiments are configured by laminating the first plate-shaped members 10 to the fifth plate-shaped members 50 and the like. On the other hand, the main body 151 of the refrigerant distributor 150 of the fifth embodiment is configured by using a tubular member.

The refrigerant distributor 150 main body 151 extends in the first direction (Z-axis direction) and is connected to one end of each of the plurality of heat transfer tubes 70 to distribute the refrigerant to the plurality of heat transfer tubes 70.

The main body 151 of the refrigerant distributor 150 has a tubular portion 90 extending in the first direction (Z-axis direction) which is the arrangement direction of the plurality of heat transfer tubes 70. Further, in the hollow portion 95 in the tubular portion 90, the main body 151 of the refrigerant distributor 150 separates the main flow path 15a and the sub flow path 25 in the third direction, and inlets that are through holes at both ends in the first direction. It has a wall portion 91 in which a portion 92a and an outlet portion 92b are formed. Further, the main body 151 of the refrigerant distributor 150 has a lid portion 94 that closes both ends of the tubular portion 90, respectively.

The tubular portion 90 is formed in a hollow cylindrical shape extending in the arrangement direction of the heat transfer tubes 70. However, the tubular portion 90 is not limited to a cylindrical shape, and may be tubular, and may be formed in a rectangular parallelepiped box shape, for example. Further, in FIG. 19, the tubular portion 90 has a first tubular portion 90a connected to the refrigerant inflow pipe 60 and a second tubular portion 90b connected to the heat transfer pipe 70. The first tubular portion 90a and the second tubular portion 90b are formed in a semicircular shape in a cross section perpendicular to the first direction (Z-axis direction). The tubular portion 90 does not have a structure in which the first tubular portion 90a and the second tubular portion 90b are divided, but the first tubular portion 90a and the second tubular portion 90b are integrally lightly formed. It may have a structure.

The wall portion 91 has a strip-like shape that is long in one direction. The wall portion 91 is a plate-shaped portion extending in the arrangement direction of the plurality of heat transfer tubes 70, and the longitudinal direction of the wall portion 91 is the first direction (Z-axis direction) which is the arrangement direction of the plurality of heat transfer tubes 70. .. Further, the lateral direction of the wall portion 91 is the second direction (X-axis direction), which is the extending direction of the pipe line of the heat transfer tube 70. Further, the plate thickness direction of the wall portion 91 is the major axis direction of the heat transfer tube 70. The wall portion 91 forms a plate surface extending in the first direction (Z-axis direction) and the second direction (X-axis direction).

The wall portion 91 forms an outlet portion 92b at one end 91b on the side to which the refrigerant inflow pipe 60 is connected. Further, the wall portion 91 forms an inlet portion 92a at the other end portion 91a. The inlet portion 92a and the outlet portion 92b are through holes that penetrate the wall portion 91 in the plate thickness direction of the wall portion 91. In the main body 151, the direction of the flow path formed by the inlet portion 92a and the outlet portion 92b is the third direction.

The wall portion 91 is further formed with a plurality of insertion holes 93 into which one ends of the plurality of heat transfer tubes 70 are inserted. Each of the plurality of insertion holes 93 is a through hole that penetrates the wall portion 91 in the plate thickness direction of the wall portion 91. Further, each of the plurality of insertion holes 93 is also a notch portion cut out from the edge portion 91e extending in the first direction (Z-axis direction) toward the opposite edge portion 91d.

The plurality of insertion holes 93 are arranged in parallel in the vertical direction along the longitudinal direction of the wall portion 91. The plurality of insertion holes 93 are provided independently of each other corresponding to each of the plurality of heat transfer tubes 70. The insertion hole 93 has a flat opening shape similar to the outer peripheral shape of the heat transfer tube 70. The open end of the insertion hole 93 is joined to the outer peripheral surface of the heat transfer tube 70 over the entire circumference by brazing. By joining the plurality of heat transfer tubes 70 to the wall portion 91, the plurality of heat transfer tubes 70 communicate with the main flow path 15a, which is the first flow path, and the sub flow path 25, which is the second flow path. It is connected to the unit 91.

The lid portion 94 closes both ends of the tubular portion 90 in the extending direction. The lid portion 94 may be a plate-shaped member as long as it closes both ends of the tubular portion 90 in the extending direction, or may be a member that covers the end portions of the tubular portion 90.

The hollow portion 95 in the tubular portion 90 is formed by the tubular portion 90 and the lid portion 94 that closes both ends of the tubular portion 90. Further, as shown in FIG. 21, the hollow portion 95 in the tubular portion 90 is separated into two spaces, a first space S1 and a second space S2, by a wall portion 91. The first space S1 and the second space S2 communicate with each other via the inlet portion 92a and the outlet portion 92b.

The main body 151 of the refrigerant distributor 150 has a first space S1 as a main flow path 15a. The main flow path 15a is a flow path in which the refrigerant flows from one end 151a on the side to which the refrigerant inflow pipe 60 of the main body 151 is connected to the other end 151b. When the first direction (Z-axis direction) is the vertical direction, the main flow path 15a is a flow path through which the refrigerant rises. The main flow path 15a, which is the first flow path, is formed so as to extend in the first direction, communicates with a plurality of heat transfer tubes 70, and has a refrigerant in the refrigerant distributor 150 at the lower end portion 15a2 in the first direction. Is connected to the refrigerant inflow pipe 60.

The main body 151 of the refrigerant distributor 150 includes a second space S2, an inlet portion 92a, and an outlet portion 92b as a sub-flow path 25. The sub-flow path 25 is a flow path through which the refrigerant flows from the other end 151b to one end 151a on the side to which the refrigerant inflow pipe 60 of the main body 151 is connected. When the first direction (Z-axis direction) is the vertical direction, the sub-flow path 25 is a flow path through which the refrigerant drops. The sub-flow path 25, which is the second flow path, extends in the first direction and is formed so that both ends of the inlet portion 92a and the outlet portion 92b are connected to the main flow path 15a, which is the first flow path. The sub-flow path 25, which is the second flow path, is formed so as to be located in the third direction with respect to the main flow path 15a, which is the first flow path. That is, the main flow path 15a and the sub-flow path 25 are formed so as to be located on the upstream side and the downstream side in the ventilation direction of the wind formed by the outdoor blower 108 or the indoor blower 109 shown in FIG.

The main body 151 of the refrigerant distributor 150 has a main flow path 15a, which is a first flow path through which the refrigerant flows, and a sub flow path 25, which is a second flow path, formed therein. The main body 151 of the refrigerant distributor 150 forms a flow path through which the refrigerant circulates by the main flow path 15a and the sub flow path 25.

FIG. 22 is a cross-sectional view conceptually showing the communication position between the first flow path and the second flow path of the refrigerant distributor of the modified example constituting the heat exchanger according to the fifth embodiment. The tubular portion 90 is not limited to the cylindrical shape as shown in FIG. 21. The tubular portion 90 may be tubular, and may be formed in a semi-cylindrical shape as shown in FIG. 22, for example.

FIG. 23 is a conceptual diagram showing the flow of the refrigerant in the refrigerant distributor 150 constituting the heat exchanger 100 according to the fifth embodiment. Similar to the first embodiment, the refrigerant staying in the upper part of the main flow path 15a flows into the inlet portion 92a provided in the second plate-shaped member 20 communicating with the upper end portion 15a1 of the main flow path 15a. At this time, as shown by the arrow OF, the refrigerant flows in the third direction from the main flow path 15a, which is the first flow path, toward the sub-flow path 25, which is the second flow path. Then, as shown by the arrow DF, the refrigerant flowing in from the inlet portion 92a of the sub-flow path 25 flows downward along the sub-flow path 25 formed in the second plate-shaped member 20 in the direction of gravity.

The refrigerant that has reached the lower end of the sub-flow path 25 flows out to the main flow path 15a from the outlet portion 92b that communicates with the lower end portion 15a2 of the main flow path 15a. At this time, as shown by the arrow IF, the refrigerant flows in the third direction from the sub-flow path 25, which is the second flow path, toward the main flow path 15a, which is the first flow path. Then, the refrigerant flowing out from the outlet portion 92b to the main flow path 15a vertically rises up the main flow path 15a together with the refrigerant flowing into the main body 151 from the refrigerant inflow pipe 60, and is distributed to each heat transfer pipe 70.

[Effect of heat exchanger 100]
The refrigerant distributor 150 separates the tubular portion 90, the lid portion 94, the main flow path 15a which is the first flow path, and the sub flow path 25 which is the second flow path in the third direction, and both ends in the first direction. The portion has a wall portion 91 in which an inlet portion 92a and an outlet portion 92b, which are through holes, are formed. The plurality of heat transfer tubes 70 are connected to the wall portion 91 so as to communicate with the main flow path 15a which is the first flow path and the sub flow path 25 which is the second flow path. Even if the main body 151 of the heat exchanger 100 is a tubular body such as a circular pipe, it is possible to suppress an increase in the size of the refrigerant distributor 150 in the second direction in which the refrigerant flows, and the range of structural contracts can be concluded. Within, the heat exchanger 100 can be enlarged in the second direction in which the conduit of the heat transfer tube 70 extends. Therefore, the heat exchanger 100 can make the refrigerant distributor 150 compact without increasing the size in the extending direction of the pipe line of the heat transfer tube 70, while securing a wide heat transfer area of the heat transfer tube 70.

The refrigeration cycle device 200 includes the heat exchanger 100 according to any one of the first to fifth embodiments. Therefore, the refrigeration cycle device 200 can obtain the same effect as that of any one of the first to fifth embodiments.

Each of the above embodiments 1 to 5 can be implemented in combination with each other. Further, the configuration shown in the above embodiment is an example, and can be combined with another known technique, and a part of the configuration is omitted or changed without departing from the gist. It is also possible. For example, the refrigerant distributors 150 and the like according to the first to fifth embodiments may be of a vertical type in which the main body 151 extends in the vertical direction or a horizontal type in which the main body 151 extends in the horizontal direction. Further, the refrigerant distributor 150 and the like according to the first to fifth embodiments may have a configuration in which the main body 151 is tilted with respect to the vertical direction.

10 1st plate-shaped member, 11 flat plate, 11a flat plate, 11b flat plate, 15 1st flow path, 15a main flow path, 15a1 upper end, 15a2 lower end, 15b side wall, 18 refrigerant inlet, 20 2nd plate Shaped member, 24 closed part, 25 auxiliary flow path, 25a central part, 25a1 end part, 25a2 end part, 25b inlet part, 25c outlet part, 25c1 outlet part, 26 distribution hole part, 30 third plate-shaped member, 31 insertion Hole, 34 flat plate part, 40 fourth plate-shaped member, 44 closed part, 45 communication hole, 46 second distribution hole part, 50 fifth plate-shaped member, 51 third distribution hole part, 53 closed part, 60 refrigerant inflow pipe , 70 heat transfer tube, 70a first side end, 70b second side end, 70c flat surface, 70d flat surface, 71 gap, 72 refrigerant passage, 75 heat transfer fin, 90 tubular part, 90a first tubular part , 90b 2nd tubular part, 91 wall part, 91a end part, 91b end part, 91d edge part, 91e edge part, 92a inlet part, 92b outlet part, 93 insertion hole, 94 lid part, 95 hollow part, 100 heat Exchanger, 101 compressor, 102 flow path switching device, 103 indoor heat exchanger, 104 decompression device, 105 outdoor heat exchanger, 106 outdoor unit, 107 indoor unit, 108 outdoor blower, 109 indoor blower, 110 refrigerant circuit, 111 Extension pipe, 112 extension pipe, 115 flow path, 150 refrigerant distributor, 151 main body, 151a end, 151b end, 200 refrigeration cycle device.

Claims

A plurality of heat transfer tubes arranged at intervals in the first direction, and the plurality of heat transfer tubes for flowing a refrigerant in a second direction intersecting with the first direction.
A refrigerant distributor that extends in the first direction and is connected to one end of each of the plurality of heat transfer tubes to distribute the refrigerant to the plurality of heat transfer tubes.
With
The refrigerant distributor is
The first flow path and the second flow path through which the refrigerant flows are formed inside.
The first flow path is
It is formed so as to extend in the first direction, communicates with the plurality of heat transfer pipes, and is connected to an inflow pipe for flowing the refrigerant into the inside of the refrigerant distributor.
The second flow path is
It is formed so as to extend in the first direction and connect both ends to the first flow path.
Heat exchange formed so as to be located in the third direction with respect to the first flow path when the direction intersecting the first direction and the plane parallel to the second direction is defined as the third direction. vessel.
The refrigerant distributor is
The first plate-shaped member on which the first flow path is formed and
A distribution hole portion which is a through hole located between the plurality of heat transfer tubes and the first flow path, and a second plate-shaped member in which the second flow path is formed.
A third plate-shaped member having an insertion hole, which is a through hole into which the plurality of heat transfer tubes are inserted,
Have,
The first plate-shaped member, the second plate-shaped member, and the third plate-shaped member are laminated.
In the stacking direction of the first plate-shaped member, the second plate-shaped member, and the third plate-shaped member, the first flow path and both ends thereof overlap, and the first flow path and the distribution hole The heat exchanger according to claim 1, wherein the portion and the insertion hole are formed so as to overlap each other.
The distribution hole is
The heat exchanger according to claim 2, wherein a plurality of heat exchangers are formed along the first direction.
The second flow path is
The heat exchanger according to claim 2 or 3, which is formed on both sides of the distribution hole in the third direction, respectively.
The refrigerant distributor is
A fourth plate-shaped member is provided between the first plate-shaped member and the second plate-shaped member.
A fifth plate-shaped member is provided between the second plate-shaped member and the third plate-shaped member.
The fourth plate-shaped member has
A communication hole, which is a through hole located between the first flow path and both ends thereof, and a second distribution hole portion, which is a through hole located between the first flow path and the distribution hole portion, are formed. Has been formed and
The fifth plate-shaped member has
The heat exchanger according to any one of claims 2 to 4, wherein a third distribution hole portion, which is a through hole located between the distribution hole portion and the insertion hole, is formed.
Both ends
The inlet where the refrigerant flows in from the first flow path and
An outlet portion that allows the refrigerant to flow out to the first flow path, and an outlet portion.
Consists of
The heat exchanger according to any one of claims 2 to 5, wherein the inlet portion and the outlet portion are formed so as to extend in the third direction.
Both ends
An inlet portion into which the refrigerant flows from the first flow path and
An outlet portion for flowing out the refrigerant to the first flow path and
Consists of
The exit part
The flow direction of the refrigerant flowing out from the outlet portion is formed to be inclined with respect to the first direction and the third direction so as to have a vector component of the flow direction of the refrigerant flowing out from the inflow pipe. The heat exchanger according to any one of claims 2 to 5.
The first flow path is
The heat exchanger according to any one of claims 1 to 7, which is formed so that the cross-sectional area of the flow path decreases from one end on the side connected to the inflow pipe toward the other end. ..
The refrigerant distributor is
The tubular portion extending in the first direction and
A lid that closes both ends of the tubular portion and
In the hollow portion of the tubular portion, the first flow path and the second flow path are separated in the third direction, and inlet portions and outlet portions, which are through holes, are formed at both ends of the first direction. With the wall
Have,
The plurality of heat transfer tubes
The heat exchanger according to claim 1, which is connected to the wall portion so as to communicate with the first flow path and the second flow path.
A refrigeration cycle apparatus including the heat exchanger according to any one of claims 1 to 9.