TWI768340B - Heat Exchangers and Refrigeration Cycle Devices - Google Patents

Abstract

The heat exchanger system includes: a plurality of heat transfer pipes, which are arranged in a first direction with a space between the plurality of heat transfer pipes, and allow a refrigerant to flow in a second direction intersecting with the first direction; and a refrigerant distributor, which is Extends in the first direction, connects with one end of each of the plurality of heat pipes, and distributes the refrigerant to the plurality of heat pipes; the refrigerant distributor forms the first flow path and the second flow path in which the refrigerant flows; the first The flow path is formed to extend in the first direction, communicates with a plurality of heat pipes, and is connected to an inflow pipe that allows the refrigerant to flow into the inside of the refrigerant distributor; the second flow path extends in the first direction , and is formed in such a way that both ends are connected to the first flow path; when the direction intersecting with the plane parallel to the first direction and the second direction is defined as the third direction, the first flow path is located in the first flow path. 3-directional way.

Description

Heat Exchangers and Refrigeration Cycle Devices

The present invention relates to a heat exchanger and a refrigeration cycle apparatus having the heat exchanger.

In recent years, in order to reduce the amount of refrigerant and improve the performance of the heat exchanger, the heat exchanger tube used in the heat exchanger for air conditioners has been narrowed. In the heat exchanger system, in order to reduce the increase in the pressure loss of the refrigerant, the number of passes (the number of branches) in the heat exchanger is increased compared to the conventional heat exchanger. Therefore, the heat exchanger is provided with a multi-branched refrigerant distributor (for example, refer to Patent Document 1). In order to balance the performance of the heat exchanger and the reduction of the amount of refrigerant used, a compact refrigerant distributor is required, which suppresses the uneven flow of refrigerant to each branch and reduces the volume of the distribution flow path by reducing the volume. The amount of refrigerant used, and the heat transfer area of the heat pipe is ensured to be wide, and the installation space of the heat exchanger will not be hindered.

The heat exchanger of Patent Document 1 includes: a plurality of heat transfer pipes arranged in parallel with each other; a header header of a refrigerant distributor, which is connected to one end of the heat transfer pipes and extends in the vertical direction; A plurality of fins joined by the tubes. The inner space of the header is divided by a partition into a first space connecting one end of the heat pipe, and a second space which is a space on the opposite side of the partition and the first space. Moreover, the upper end and the lower end of a separator are provided with the communication path which connects a 1st space and a 2nd space. By having this structure, the heat exchanger of Patent Document 1 circulates the refrigerant between the first space and the second space. Furthermore, the heat exchanger of Patent Document 1 is designed to suppress the uneven flow of the refrigerant by circulating the refrigerant between the first space and the second space. [Preceding Patent Documents] [Patent Literature]

[Patent Document 1] Japanese Patent Application Laid-Open No. 2015-68622

[The problem to be solved by the invention]

However, in the heat exchanger of Patent Document 1, the first space and the second space are located in the extending direction of the pipe of the heat transfer pipe, and the first space forms a flow path for the gas-liquid two-phase refrigerant to flow upward, and the second space is A circulation flow path is formed to return the refrigerant from the upper part to the lower part. The refrigerant distributor described in Patent Document 1 has a large size in the extension direction of the heat transfer pipe due to this structure. Therefore, due to structural limitations, the length of the heat transfer pipe system in the extension direction is shortened and the heat transfer of the heat transfer pipe is shortened. area becomes smaller. Therefore, the heat exchange performance of the heat exchanger of Patent Document 1 may be lower than that of the conventional heat exchanger.

The present disclosure has been developed in order to solve the above-mentioned problems, and an object of the present disclosure is to provide a heat exchanger and a refrigeration cycle device having a refrigerant distributor which ensures a wide heat transfer area of the heat transfer pipe, The extension direction of the pipeline will not become large and compact. [Means of Solving Problems]

The heat exchanger system of the present disclosure includes: a plurality of heat transfer pipes, which are arranged in a first direction at intervals from each other, and circulate a refrigerant in a second direction intersecting with the first direction; and refrigerant distribution The device extends in the first direction, is connected to one end of each of the plurality of heat pipes, and distributes the refrigerant to the plurality of heat pipes; the refrigerant distributor forms the first flow path and the second flow path in which the refrigerant flows. ; The first flow path is formed to extend in the first direction, communicated with a plurality of heat pipes, and is connected with an inflow pipe, which allows the refrigerant to flow into the interior of the refrigerant distributor; the second flow path is in the first It extends in one direction and is formed so that both ends are connected to the first flow path, and when the direction intersecting the plane parallel to the first direction and the second direction is defined as the third direction, the first The flow path is formed so that it is located in the third direction.

The refrigeration cycle apparatus of the present disclosure has the heat exchanger of the present disclosure. [Effect of invention]

According to the present disclosure, the heat exchanger includes a refrigerant distributor that forms a first flow path and a second flow path through which the refrigerant flows. The second flow path extends in the first direction, and is formed so that both ends are connected to the first flow path. This second flow path is formed so as to be positioned in the third direction with respect to the first flow path, when the direction intersecting the plane parallel to the first direction and the second direction is defined as the third direction. Therefore, the heat exchanger system can suppress the enlargement of the refrigerant distributor in the second direction in which the refrigerant flows, and the extension direction of the heat exchanger tube can be increased within the scope of structural constraints. Therefore, the heat exchanger 100 of the present disclosure can ensure that the heat transfer area of the heat transfer pipe is wide, and the refrigerant distributor is not large and compact in the extending direction of the pipe of the heat transfer pipe.

Hereinafter, the heat exchanger 100 and the refrigeration cycle apparatus 200 of Embodiment 1 will be described with reference to the drawings and the like. In addition, in the drawings including FIG. 1 and below, there are cases where the relative dimensional relationship and shape of each constituent element are different from the actual ones. In addition, in the following drawings, those attached with the same symbols are the same or equivalent, and this is common throughout the entire patent specification. In addition, for ease of understanding, terms indicating directions (such as "up", "down", "right", "left", "front" and "rear", etc.) are used appropriately. The description is not intended to limit the arrangement and orientation of devices or elements. In the patent specification, the positional relationship of each constituent element, the extending direction of each constituent element, and the arrangement direction of each constituent element are in principle when the outdoor heat exchanger 105 is installed in a usable state. Embodiment 1 [Refrigeration cycle device 200]

1 is a refrigerant circuit diagram showing the configuration of a refrigeration cycle apparatus 200 having a heat exchanger 100 according to Embodiment 1. In addition, in FIG. 1 , the arrows indicated by the dotted line indicate the flow direction of the refrigerant in the refrigerant circuit 110 during the cooling operation, and the arrows indicated by the solid line indicate the flow direction of the refrigerant during the heating operation. . First, the refrigeration cycle apparatus 200 provided with the heat exchanger 100 mentioned later is demonstrated using FIG. 1. FIG.

In the present embodiment, an air conditioner is shown as an example of the refrigeration cycle device 200, but the refrigeration cycle device 200 is used, for example, in refrigeration applications such as refrigerators, freezers, vending machines, air conditioners, refrigerating devices, and water heaters or air conditioner applications. In addition, the refrigerant circuit 110 shown in the figure is an example, and the structure etc. of a circuit element are not limited to the content demonstrated in the embodiment, and can be changed suitably within the technical scope of the embodiment.

The refrigeration cycle apparatus 200 includes a refrigerant circuit 110 which is annularly connected to the compressor 101 , the flow switching device 102 , the indoor heat exchanger 103 , the pressure reducing device 104 , and the outdoor heat exchanger 105 via refrigerant piping. The refrigeration cycle apparatus 200 has an outdoor unit 106 and an indoor unit 107 . The outdoor unit 106 houses the compressor 101 , the flow switching device 102 , the outdoor heat exchanger 105 , the pressure reducing device 104 , and the outdoor blower 108 that supplies outdoor air to the outdoor heat exchanger 105 . The indoor unit 107 houses the indoor heat exchanger 103 and the 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 part of the refrigerant pipes.

The compressor 101 is a fluid machine that compresses the sucked refrigerant and discharges it. 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 during cooling operation and heating operation under the control of a 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 heating operation, and functions as an evaporator during cooling operation.

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

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 heating operation, and functions as a condenser during cooling operation. The air supplied by the outdoor blower 108 is an example of the second heat exchange fluid.

At least one of the outdoor heat exchanger 105 and the indoor heat exchanger 103 is a heat exchanger 100 which will be described later. The refrigerant distributor 150 connected to the heat exchanger 100 is preferably arranged at a position where the liquid-phase refrigerant becomes larger in the heat exchanger 100 . Specifically, the refrigerant distributor 150 is preferably arranged on the inlet side of the heat exchanger 100 functioning as an evaporator, ie, the outlet side of the heat exchanger 100 functioning as a condenser, for the flow of refrigerant in the refrigerant circuit 110 . In addition, in FIG. 1, the refrigerant distributor 150 is used in the heat exchanger 100 of both the indoor heat exchanger 103 and the outdoor heat exchanger 105, but it may be used only in the indoor heat exchanger 103 or the outdoor heat exchanger 105. One of the heat exchangers 100 is used. [Operation of the refrigeration cycle apparatus 200]

Next, an example of the operation of the refrigeration cycle apparatus 200 will be described using FIG. 1 . During the heating operation of the refrigeration cycle apparatus 200 , the refrigerant in the gaseous state of high pressure and high temperature discharged from the compressor 101 flows into the indoor heat exchanger 103 via the flow switching device 102 , and exchanges heat with the air supplied by the indoor blower 109 and condensed. The condensed refrigerant is in a high-pressure liquid state, flows out from the indoor heat exchanger 103 , and is brought into a low-pressure gas-liquid two-phase state by the depressurizing device 104 . The refrigerant in the low-pressure gas-liquid two-phase state flows into the outdoor heat exchanger 105, and is evaporated by heat exchange with the air supplied by the outdoor blower 108. The evaporated refrigerant is in a low-pressure gas state, and is sucked into the compressor 101 . In addition, frost adheres to the outdoor heat exchanger 105 when the pressure saturation temperature of the outdoor heat exchanger 105 is below the dew point temperature of outdoor air and below the freezing point of water during the heating operation.

During the cooling operation of the refrigeration cycle apparatus 200, the refrigerant flowing in 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 refrigerant in the gaseous state of high pressure and high temperature discharged from the compressor 101 flows into the outdoor heat exchanger 105 through the flow switching device 102 , and is connected to the air supplied by the outdoor blower 108 . Condensation due to heat exchange. The condensed refrigerant is in a high-pressure liquid state, flows out from the outdoor heat exchanger 105 , and is brought into a low-pressure gas-liquid two-phase state by the pressure reducing device 104 . The refrigerant in the low-pressure gas-liquid two-phase state flows into the indoor heat exchanger 103, and is evaporated by heat exchange with the air supplied by the indoor blower 109. The evaporated refrigerant is in a low-pressure gas state, and is sucked into the compressor 101 . [Outdoor heat exchanger 105]

FIG. 2 is a side view schematically showing the configuration of the main part of the heat exchanger 100 according to the first embodiment. FIG. 3 is an exploded perspective view schematically showing the configuration of the 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 hatched arrow F indicates the direction of the refrigerant flowing in the first flow path portion 15 of the refrigerant distributor 150 . When the refrigerant distributor 150 is applied to the refrigeration cycle apparatus 200, the refrigerant distributor 150 is connected to the end of the heat transfer pipe 70 on the inlet side of the refrigerant when the heat exchanger 100 operates as an evaporator.

As shown in FIG. 2 , the heat exchanger 100 includes: a plurality of heat pipes 70 for circulating the refrigerant; Moreover, the heat exchanger 100 has a refrigerant inflow pipe 60 , and the refrigerant inflow pipe 60 is attached to the lower part of the refrigerant distributor 150 .

The plurality of heat transfer pipes 70 are arranged at intervals in the first direction (Z-axis direction), and circulate the refrigerant in the second direction (X-axis direction) intersecting with the first direction (Z-axis direction). The plurality of heat transfer pipes 70 are flat tubes. In addition, although the heat transfer pipe 70 is described as a flat pipe, the heat transfer pipe 70 is not limited to a flat pipe, and may be a round pipe, for example.

In the heat exchanger 100, the arrangement direction of the plurality of heat transfer pipes 70 and the extending 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 pipes 70 are arranged. In the heat exchanger 100, the arrangement direction of the heat transfer pipes 70 in the first direction (Z-axis direction) is regarded as the vertical direction. The vertical direction is, for example, the vertical direction. However, the arrangement direction of the heat transfer pipes 70 in the first direction (Z-axis direction) is not limited to the vertical direction and the vertical direction, and may be a direction inclined to the vertical direction or may be a horizontal direction.

In the heat exchanger 100, the extending direction of the pipe line of the heat transfer pipe 70 is defined as the second direction (X-axis direction). In addition, the piping of the heat transfer pipe 70 is a refrigerant passage 72 (refer to FIG. 4 ) which will be described later. Therefore, the second direction (X-axis direction) is also the flow direction of the refrigerant flowing through the conduit of the heat transfer pipe 70 . In the heat exchanger 100, the extending direction of the pipes of the plurality of heat transfer pipes 70 in the second direction (X-axis direction) is regarded as the horizontal direction. However, the extension direction of the pipes of the plurality of heat pipes 70 in the second direction (X-axis direction) is not limited to the horizontal direction, and may be a direction inclined to the horizontal direction, and may include the vertical direction up and down.

A gap 71 serving as a flow path of air is formed between two adjacent heat transfer pipes 70 among the plurality of heat transfer pipes 70 . A heat-conducting heat sink 75 may also be provided between two adjacent heat-conducting pipes 70 as shown in FIG. 2 . Moreover, the heat exchanger 100 has the heat-transfer fin 75 which is a heat-transfer promotion member in a part, and has the area|region where two adjacent heat-transfer pipes 70 are not connected by the heat-transfer promotion member in a part.

In addition, the adjacent heat pipes 70 among the plurality of heat pipes 70 may not have the heat conduction fins 75, and the heat pipes 70 are not connected to each other by the heat conduction promoting member. The heat conduction promoting member is a member that promotes heat conduction, for example, a flat heat sink such as the heat conduction heat sink 75, a corrugated heat sink, 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 the evaporator of the refrigerating cycle apparatus 200, in each branch of the plurality of heat pipes 70, the refrigerant flows in the pipes inside the heat pipes 70 from one end to the other end in the extending direction. When the heat exchanger 100 functions as a condenser of the refrigeration cycle apparatus 200, in each branch of the plurality of heat transfer pipes 70, the refrigerant flows from the other end to the one end in the extending direction of the pipes inside the heat transfer pipes 70. (heat pipe 70)

FIG. 4 is a cross-sectional view showing the configuration of the heat transfer pipe 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 pipe 70 . As shown in FIG. 4 , the heat transfer pipe 70 has a cross-sectional shape that is flat in one direction, such as a racetrack shape.

The heat transfer pipe 70 has a first side end portion 70a, a second side end portion 70b, and a pair of flat surfaces 70c and 70d. In the cross section shown in FIG. 4, the 1st side edge part 70a is connected to one end part of the flat surface 70c and one end part of the flat surface 70d. In this cross section, the second side end portion 70b is connected to the other end portion of the flat surface 70c and the other end portion of the flat surface 70d.

The 1st side edge part 70a is a side edge part arrange|positioned on the windward side, ie, the front edge side, in the flow of the air which passes through a heat exchanger. The second side end portion 70b is a side end portion disposed on the leeward side, ie, the rear edge side, in the flow of the air passing through the heat exchanger. Hereinafter, the direction perpendicular to the extending direction of the heat transfer pipe 70 and along the flat surface 70c and the flat surface 70d may be referred to as the long-axis direction of the heat transfer pipe 70 .

In the heat transfer pipe 70, a plurality of refrigerant passages 72 are formed along the longitudinal direction between the first side end portion 70a and the second side end portion 70b. The heat transfer pipe 70 is a flat porous pipe in which a plurality of refrigerant passages 72 through which the refrigerant flows are arranged in the flow direction of the air. Each of the plurality of refrigerant passages 72 is formed so as to extend parallel to the extending direction of the heat transfer pipe 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 body 151 of the refrigerant distributor 150 is connected to one end of each of the plurality of heat pipes 70 . The refrigerant distributor 150 distributes refrigerant to each of the plurality of heat pipes 70 connected to the main body 151 .

The body 151 of the refrigerant distributor 150 is formed to extend in the up-down direction along the arrangement direction of the plurality of heat pipes 70 . The main body 151 extends in the first direction, and forms a distribution flow path for distributing the refrigerant to each of the heat transfer pipes 70 inside. The body 151 of the refrigerant distributor 150 is formed with the refrigerant inlet 18 into which the refrigerant inlet pipe 60 is inserted, and a plurality of insertion holes 31 into which each of the plurality of heat pipes 70 is inserted.

The refrigerant inflow port 18 is formed on the side of one end portion 151a of the main body 151 in the first direction. A 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 pipes 70 . The respective holes of the plurality of insertion holes 31 are formed at intervals along the first direction (Z-axis direction) so as to correspond to the respective ones of the plurality of heat transfer pipes 70 .

The main body 151 of the refrigerant distributor 150 includes the first plate-shaped member 10 , the second plate-shaped member 20 , and the third plate-shaped member 30 . The first plate-like member 10 , the second plate-like member 20 , and the third plate-like member 30 are all formed using a metal flat plate, and have a strip-like shape long in one direction. The outlines of the respective 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. The first plate-shaped member 10, the second plate-shaped member 20, and the third plate-shaped member 30 are formed so that their respective plate thickness directions are parallel to the extending direction of the conduit of the heat transfer pipe 70, that is, their respective plate surfaces are parallel to each other. The extending direction of the piping of the heat transfer pipe 70 is arranged so that it is vertical.

The main body 151 of the refrigerant distributor 150 has a structure in which the first plate-shaped member 10 , the second plate-shaped member 20 , and the third plate-shaped member 30 are stacked in this order from the side farther away from the heat transfer pipe 70 . The first plate-shaped member 10 is arranged at the position where the main body 151 is the farthest from the heat transfer pipe 70 , and the third plate-shaped member 30 is arranged at the position where the main body 151 is the shortest distance from the heat transfer pipe 70 .

The second plate-shaped member 20 is disposed between the first plate-shaped member 10 and the heat transfer pipe 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 pipe 70 and is adjacent to the second plate-shaped member 20 . One end of each of the plurality of heat transfer pipes 70 is connected to the third plate-shaped member 30 .

The adjacent members among the first plate-shaped member 10 , the second plate-shaped member 20 , and the third plate-shaped member 30 are joined to each other by welding. 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).

5 is a cross-sectional view schematically showing a 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 in FIG. The short-side direction of each of the first plate-like member 10 , the second plate-like member 20 , and the third plate-like member 30 is the left-right direction in FIG. 5 , and is the long-axis direction of the heat transfer pipe 70 . 3 and 5, the structure of the main body 151 of the refrigerant distributor 150 will be further described.

As shown in FIGS. 3 and 5 , the first plate-shaped member 10 has a first flow path portion 15 that protrudes in a direction away from the heat transfer pipe 70 . The first flow path portion 15 is formed in a cylindrical shape, and a space is formed inside the protrusion. The refrigerant distributor 150 is formed integrally with the first plate-shaped member 10 and the first flow path portion 15, but may be formed separately.

The first flow path portion 15 extends along the longitudinal direction of the first plate-shaped member 10 from one end in the longitudinal direction of the first plate-shaped member 10 to the other end in the longitudinal direction. The first flow path portion 15 is formed in a semi-cylindrical shape. Both ends in the extending direction of the first flow path portion 15 are closed. The first flow path portion 15 has a cross-sectional shape of a semicircle, a semi-ellipse, or a half-track 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 semicircle, a semielliptical shape, or a semitrack shape, and may be, for example, a rectangle.

Moreover, the 1st plate-shaped member 10 has the flat-plate part 11a and the flat-plate part 11b which were formed in a flat-plate shape on both sides of the 1st channel part 15 interposed therebetween. Both the flat plate portion 11a and the flat plate portion 11b extend along the longitudinal direction of the first plate-shaped member 10 from one end in the longitudinal direction of the first plate-shaped member 10 to the other end in the longitudinal direction. 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 formed so as to protrude in the opposite direction to the flat plate portion 11a and the flat plate portion 11b and the side where the heat transfer pipe 70 is arranged. In addition, the first flow path portion 15 is opened on the arrangement side of the heat transfer pipe 70 . In addition, in the following description, the flat plate part 11a and the flat plate part 11b are collectively referred to as the flat plate part 11 in some cases.

Inside the first flow path portion 15 , a main flow path 15 a is formed, and the main flow path 15 a extends in the vertical direction along the longitudinal direction of the first plate-shaped member 10 . The main flow path 15a is the first flow path of the refrigerant distributor 150 . The main flow path 15a of 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) of the arrangement direction of the plurality of heat pipes 70. .

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

The main flow path 15a has a cross-sectional shape of a semicircle, a semi-elliptical shape, or a semi-racetrack 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 semicircular, semielliptical or semitrack shape. However, the cross-sectional shape of the main flow path 15a is not limited to a semicircle, a semielliptical shape, or a semitrack shape, and may be, for example, a rectangle.

As described above, the main flow path 15a of the first flow path is formed so as to extend in the first direction (Z-axis direction), communicates with the plurality of heat transfer pipes 70, and is at the lower end portion 15a2 in the first direction. , which is connected to the 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 channel 15a through the refrigerant inflow pipe 60 flows upward in the main flow channel 15a from one end 151a of the main body 151 to the other end 151b, and is distributed to each heat transfer channel Tube 70.

A refrigerant inflow pipe 60 is connected to the lower end portion of the first flow path portion 15 . Further, the main flow passage 15a communicates with the inner space of the refrigerant inflow pipe 60 . The refrigerant inflow pipe 60 allows the gas-liquid two-phase refrigerant to flow into the main flow passage 15a when the heat exchanger 100 functions as an evaporator. The connection position of the refrigerant inflow pipe 60 and the first flow path portion 15 serves as the refrigerant inflow port 18 of the refrigerant inflow refrigerant distributor 150 . In addition, when the heat exchanger 100 functions as a condenser, the liquid refrigerant flows downward through the main flow passage 15 a and then flows out through the refrigerant inflow pipe 60 .

In the second plate-shaped member 20, the sub-flow path 25 and the distribution hole portion 26 are formed. Here, the direction intersecting with the plane P parallel to the first direction (Z-axis direction) and the second direction (X-axis direction) is defined as a third direction. In addition, the third direction includes the Y-axis direction. In the third direction (Y-axis direction), the distribution hole portion 26 is formed in the vicinity of the center of the second plate-shaped member 20 , and the auxiliary flow path 25 is formed in the vicinity of the end portion of the second plate-shaped member 20 . That is, in the third direction (Y-axis direction), the distribution hole portion 26 is formed in the vicinity of 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. In addition, the formation position of the sub-flow path 25 and the distribution hole part 26 in the 2nd plate-shaped member 20 is not limited to the above-mentioned position. In addition, the auxiliary flow paths 25 formed on both sides of the distribution hole portion 26 may be formed so as to communicate with each other at at least one end portion in the first direction.

The secondary flow path 25 is formed so as to extend in the first direction (Z-axis direction) on the second plate-shaped member 20 . That is, the auxiliary flow path 25 is formed so as to extend in the vertical direction along the longitudinal direction of the second plate-shaped member 20 . The secondary flow path 25 is the second flow path of the refrigerant distributor 150 . The secondary flow path 25 which is the second flow path is formed on the main body 151 of the refrigerant distributor 150, and the both ends are connected to the main flow path 15a which is the first flow path. The secondary flow path 25 connects the upper end portion 15a1 and the lower end portion 15a2 of the main flow path 15a, and forms a flow path for the refrigerant, and the refrigerant flow path is used to return the refrigerant reaching the upper end portion 15a1 of the main flow path 15a to form a refrigerant flow. The lower end portion 15a2 of the inlet 18 is provided. The main body 151 of the refrigerant distributor 150 forms a circulation flow path of the refrigerant by the main flow path 15 a and the auxiliary flow path 25 .

The main body 151 of the refrigerant distributor 150 forms the main flow path 15a and the auxiliary flow path 25 in which the refrigerant flows. As described above, the main flow passage 15a is the first flow passage, and the secondary flow passage 25 is the second flow passage. The secondary flow path 25 of the second flow path is formed so as to be located in the third direction with respect to the main flow path 15a of the first flow path. That is, the main flow path 15a and the secondary flow path 25 are formed so that the ventilation directions of the wind generated by the outdoor fan 108 or the indoor fan 109 shown in FIG. 1 are located on the upstream side and the downstream side.

The secondary 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 in the first direction (Z-axis direction) at one end portion 25a1 of the central portion 25a. The outlet part 25c is formed in the other end part 25a2 of the center part 25a in the 1st direction (Z-axis direction). The inlet part 25b and the outlet part 25c are formed in the main body 151 of the refrigerant distributor 150 as a flow path extending in the third direction (Y-axis direction).

The central portion 25a of the secondary flow path 25 is in the stacking direction of the first plate-like member 10, the second plate-like member 20, and the third plate-like member 30, and is sandwiched between the flat plate portion 11 of the first plate-like member 10 and the third plate-like member 10. between the flat plate portions 34 of the plate-like member 30 .

Both ends of the secondary flow path 25 are constituted by an inlet portion 25b and an outlet portion 25c. The inlet portion 25b and the outlet portion 25c are sandwiched between 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 . between the flat plate portions 34 . Therefore, the inlet part 25b and the outlet part 25c communicate with the main flow path 15a which is the first flow path formed by the first flow path part 15 . On the other hand, the central portion 25a of the secondary 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 secondary flow path 25, which is the second flow path, is connected to the main flow path 15a, which is the first flow path, at both ends by having an inlet portion 25b and an outlet portion 25c. form. More specifically, the secondary flow path 25 of the second flow path is formed on 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 secondary flow path 25 of the second flow path is formed on 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 inlet portion 25b passes the refrigerant flowing from the main flow path 15a, which is the first flow path, to the secondary flow path 25, which is the second flow path. That is, in the inlet part 25b, the refrigerant flows in from the main flow passage 15a which is the first flow passage. The outlet portion 25c passes the refrigerant flowing from the secondary flow path 25, which is the second flow path, to the main flow path 15a, which is the first flow path. That is, the outlet part 25c makes the refrigerant flow out to the main flow path 15a which is the first flow path. In addition, 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 to be described later.

In the second plate-shaped member 20, a plurality of distribution holes 26 each having a circular opening shape are formed. The plurality of distribution holes 26 form a flow path between the main flow path 15 a and the heat transfer pipe 70 , and distribute the refrigerant to each heat transfer pipe 70 . Each of the plurality of distribution hole portions 26 is a through hole that penetrates the second plate-shaped member 20 in the 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) serving as 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 so as to correspond to each of the plurality of heat transfer pipes 70 .

The opening shape of the distribution hole portion 26 is circular, but it is not limited to a circular shape, and may be, for example, a semicircle, a semielliptical shape, a half racetrack shape, or a rectangle. In addition, the cross-sectional area of the flow path of the plurality of distribution holes 26 is the same size, respectively. However, the cross-sectional areas of the flow passages of the plurality of distribution holes 26 are not limited to the same size, and may be formed to have different sizes.

In addition, in the main body 151 of the refrigerant distributor 150 according to the first embodiment, a plurality of distribution holes 26 are formed in the second plate-shaped member 20, but only one distribution hole 26 may be formed in the second plate-shaped member 20. . 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 pipes 70 .

The plurality of distribution hole portions 26 are all formed so as to overlap with the main flow path 15 a of the first plate-shaped member 10 when viewed in the plate thickness direction of the second plate-shaped member 20 . In addition, each of the plurality of distribution hole portions 26 is formed so as to overlap with each of the plurality of insertion holes 31 of the third plate-shaped member 30 to be described later when viewed in the plate thickness direction of the second plate-shaped member 20 . Furthermore, each of the plurality of distribution holes 26 is formed so as to overlap with each of the plurality of heat transfer pipes 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 pipe 70 and the main flow channel 15 a that is the first flow channel. Furthermore, the main flow path 15 a of the first plate-shaped member 10 and each branch of the plurality of heat transfer pipes 70 communicate with each other through the plurality of distribution holes 26 .

In addition, 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 15 a of the first plate-shaped member 10 when viewed in the thickness direction of the second plate-shaped member 20 . The closing portion 24 has the function of preventing the main flow path 15 a and each branch of the plurality of heat pipes 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 pipes 70 are respectively inserted. Each of the plurality of insertion holes 31 is a through hole penetrating the third plate-shaped member 30 in the thickness direction of the third plate-shaped member 30 .

The plurality of insertion holes 31 are arranged 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 so as to correspond to each of the plurality of heat pipes 70 . The insertion hole 31 has a flat opening shape like the outer peripheral shape of the heat transfer pipe 70 . The open end of the insertion hole 31 is joined to the outer peripheral surface of the heat transfer pipe 70 over the entire circumference by welding.

The third plate-shaped member 30 has a flat plate portion 34 in the shape of a flat plate. The flat plate portion 34 corresponds to the 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 thickness direction of the third plate-shaped member 30 . The secondary flow path 25 of the second flow path is in the second direction (X-axis direction), and is closed by the flat plate portion 34 and the flat plate portion 11 .

The main body 151 of the refrigerant distributor 150 is in the stacking direction of the first plate-shaped member 10, the second plate-shaped member 20, and the third plate-shaped member 30, and is the main flow path 15a of the first flow path and the secondary flow path of the second flow path. Both ends of the flow path 25 overlap. In addition, the main body 151 of the refrigerant distributor 150 is in the stacking direction of the first plate-shaped member 10 , the second plate-shaped member 20 and the third plate-shaped member 30 , and is the main flow path 15 a of the first flow path and the distribution hole portion 26 and the insertion holes 31 are formed in such a way that they overlap.

6 is a schematic diagram showing the flow of the refrigerant in the refrigerant distributor 150 constituting the heat exchanger 100 of the first embodiment. Next, with regard to the operation of the refrigerant distributor 150 according to the first embodiment, the operation when the heat exchanger 100 functions as the evaporator of the refrigeration cycle apparatus 200 will be described as an example.

When the refrigeration cycle apparatus 200 is in 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 FIG. 2 and FIG. 6 , as shown by the arrow UF in FIG. One end 151a flows vertically upward toward the other end 151b. The refrigerant that flows vertically upward passes through the distribution hole portion 26 of the second plate-shaped member 20 , and then passes through the insertion hole 31 formed in the third plate-shaped member 30 , and is distributed to each of the heat transfer pipes 70 .

Moreover, the refrigerant remaining in the upper portion of the main flow passage 15a flows into the inlet portion 25b provided in the second plate-shaped member 20, and the inlet portion 25b communicates with the upper end portion 15a1 of the main flow passage 15a. At this time, the refrigerant system flows from the main flow passage 15a of the first flow passage to the secondary flow passage 25 of the second flow passage to the outside in the third direction, as indicated by arrow OF. Then, the refrigerant flowing in from the inlet portion 25b of the secondary flow path 25 flows downward along the direction of gravity in the center portion 25a of the secondary flow path 25 formed in the second plate-shaped member 20, as indicated by the arrow DF. .

The refrigerant reaching the lower end of the central portion 25a of the secondary flow path 25 flows out to the main flow path 15a from the outlet portion 25c communicating with the lower end portion 15a2 of the main flow path 15a. At this time, the refrigerant system flows from the secondary flow path 25 which is the second flow path to the main flow path 15a which is the first flow path, as indicated by the arrow IF, to the inner side which is the third direction. Then, the refrigerant flowing out from the outlet portion 25c to the main flow passage 15a rises vertically in the main flow passage 15a together with the refrigerant flowing from the refrigerant inflow pipe 60 into the main body 151, 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 pipes 70 are arranged.

In FIG. 7 , the dotted line A indicates the flow rate of the refrigerant flowing in the main flow path 15a when the sub flow path 25 is not provided, and the solid line B indicates the flow rate of the refrigerant flowing in the main flow path 15a in the case where the auxiliary flow path 25 is provided. . In addition, the one-dot chain line C shows the case where the flow rate of the refrigerant flowing in the main flow passage 15a is constant in the vertical direction. In addition, when the flow rate of the refrigerant flowing in the main passage 15a is constant in the vertical direction, the inflow amount of the refrigerant flowing into each of the heat transfer pipes 70 arranged in the first direction becomes constant. Therefore, it is preferable that the flow rate of the refrigerant in the main flow path 15a be close to the flow rate of the refrigerant indicated by the one-dot chain line C.

As indicated by the dotted line A, in the case where the main body 151 is not provided with the secondary flow path 25 serving as the second flow path, the liquid refrigerant remains in the upper part of the main flow path 15a of the first flow path, and a large amount of the liquid refrigerant is formed. The distribution is in the upper part of the main flow path 15a of the first flow path.

On the other hand, when the main body 151 is provided with the secondary flow path 25 serving as the second flow path, the liquid refrigerant accumulated in the upper portion of the main flow path 15a passes through the secondary flow path 25 and returns to the lower portion of the main flow path 15a. Therefore, as indicated by the arrow MU between the dotted line A and the solid line B, the flow rate of the refrigerant decreases because the refrigerant returns to the lower part of the main flow path 15a in the upper part of the main flow passage 15a. In addition, as indicated by the arrow MD between the dotted line A and the solid line B, in the lower part of the main flow path 15a, the refrigerant flows back from the upper part of the main flow path 15a, so the flow rate of the refrigerant increases. Therefore, as indicated by the solid line B, the flow rate of the refrigerant flowing in the main flow path 15a with the sub flow path 25 is compared with the flow rate of the refrigerant flowing in the main flow path 15a without the auxiliary flow path 25. Approach the flow rate of the refrigerant shown by the one-point chain line C. Therefore, the refrigerant distributor 150 having the sub-flow path 25 can evenly distribute the refrigerant to each heat pipe 70 as compared with the refrigerant distributor having no sub-flow path 25 . [Effect of heat exchanger 100]

The heat exchanger 100 includes a refrigerant distributor 150, and the refrigerant distributor 150 forms the main flow path 15a and the auxiliary flow path 25 in which the refrigerant flows. The secondary 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. It is the case where the sub-flow path 25 of the second flow path defines the direction intersecting with the plane P parallel to the first direction (Z-axis direction) and the second direction (X-axis direction) as the third direction, so that The main flow path 15a of the first flow path is formed so that the main flow path 15a is located 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 refrigerant circulates, and can make the heat exchanger 100 a second extension of the piping of the heat pipe 70 within the scope of structural limitations. direction becomes larger. Therefore, the heat exchanger 100 can ensure a wide heat transfer area of the heat transfer pipe 70, and the refrigerant distributor 150 can be formed in the extending direction of the heat transfer pipe 70 without becoming large and compact.

In addition, the heat exchanger 100 can ensure a wider heat transfer area of the heat transfer pipe 70 than a heat exchanger having a first flow path and a second flow path in the extending direction of the pipe line of the heat transfer pipe 70 . Therefore, the heat exchanger 100 can improve the performance of heat exchange compared with the heat exchanger having the first flow path and the second flow path in the extending direction of the pipe line of the heat transfer pipe 70 . Therefore, the heat exchanger 100 can improve the suppression of uneven flow of refrigerant distribution in response to changes in refrigerant flow rate or dryness depending on the operating state of the air conditioner, and can improve distribution toughness in a widened range corresponding to refrigerant flow rate and the like.

In addition, the heat exchanger 100 is in a state where the liquid refrigerant is accumulated in the upper part of the main flow path 15a according to the operating state of the air conditioner, and by having the auxiliary flow path 25, the refrigerant circulates from the upper part of the main flow path 15a to the lower part of the main flow path 15a. , whereby the drift of the refrigerant can be suppressed. Therefore, the heat exchanger 100 including the refrigerant distributor 150 having the sub-flow path 25 can evenly distribute the refrigerant to each heat transfer pipe 70 compared to the heat exchanger including the refrigerant distributor 150 having no sub-flow path 25 . As a result, the heat exchanger 100 can improve the performance of heat exchange as compared with the heat exchanger provided with the refrigerant distributor 150 which does not have the sub-flow path 25 .

In addition, the refrigerant distributor 150 is in the stacking direction of the first plate-shaped member 10, the second plate-shaped member 20, and the third plate-shaped member 30, and the main channel 15a overlaps with both ends of the auxiliary channel 25, and the main channel 15a, the distribution hole portion 26, and the insertion hole 31 are formed so as to overlap. Therefore, the heat exchanger 100 can suppress the enlargement of the refrigerant distributor 150 in the second direction in which the pipes of the heat pipes 70 extend, and the heat exchanger 100 can be placed in the pipes of the heat pipes 70 within the limits of the structure. The second direction of extension becomes larger. Therefore, the heat exchanger 100 can ensure a wide heat transfer area of the heat transfer pipe 70, and the refrigerant distributor 150 can be formed in the extending direction of the heat transfer pipe 70 without becoming large and compact.

In addition, the secondary flow path 25, which is the second flow path, is composed of an inlet portion 25b through which the refrigerant flows from the main flow path 15a, which is the first flow path, and an outlet portion 25c, where the refrigerant flows toward the The main flow path 15a of the first flow path flows out. The inlet portion 25b and the outlet portion 25c are formed 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 pipes of the heat pipes 70 extend, and the heat exchanger 100 can be reduced in size to the pipes of the heat pipes 70 within the limits of the structure. The second direction of extension becomes larger. Therefore, the heat exchanger 100 can ensure a wide heat transfer area of the heat transfer pipe 70, and the refrigerant distributor 150 can be formed in the extending direction of the heat transfer pipe 70 without becoming large and compact.

In addition, the sub-flow passages 25 of the second flow passage are formed on both sides of the distribution hole portion 26 in the third direction, respectively. Therefore, the heat exchanger 100 can suppress the enlargement of the refrigerant distributor 150 in the second direction in which the pipes of the heat pipes 70 extend, and the heat exchanger 100 can be placed in the pipes of the heat pipes 70 within the limits of the structure. The second direction of extension becomes larger. Therefore, the heat exchanger 100 can ensure a wide heat transfer area of the heat transfer pipe 70, and the refrigerant distributor 150 can be formed in the extending direction of the heat transfer pipe 70 without becoming large and compact.

In addition, 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 is a refrigerant flow path between the main flow path 15a of the first flow path and each branch of the plurality of heat transfer pipes 70, and functions as an orifice having a large flow resistance. When the heat exchanger functions as an evaporator, each distribution hole portion 26 functions as an orifice with a large flow resistance, so that the pressure of the main flow passage 15a rises, and the pressure of the main flow passage 15a is related to the pressure of each of the plurality of insertion holes 31. The pressure difference increases. Therefore, the pressure difference between the pressure in the main flow passage 15a and the pressure in the upper insertion hole 31 and the pressure difference between the pressure in the main flow passage 15a and the pressure in the lower insertion hole 31 become more uniform. Thereby, the refrigerant system in the main flow path 15a is uniformly distributed to each insertion hole 31, and as a result, is uniformly distributed to each heat transfer pipe 70. Embodiment 2

FIG. 8 is an exploded perspective view schematically showing the configuration of the main part of the heat exchanger 100 according to the second embodiment. 9 is a cross-sectional view schematically showing a 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. In addition, the same code|symbol is attached|subjected to the structural element which has the same function and effect as Embodiment 1, and the description is abbreviate|omitted. The heat exchanger 100 of the second embodiment is different from the heat exchanger 100 of 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 includes 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-like member 40 and the fifth plate-like member 50 are formed using a metal flat plate, and have a belt-like shape long in one direction. The outlines of the respective 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. 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 serve as conduits with the heat transfer pipe 70 in their respective thickness directions. It is arranged so that the extending direction is parallel. That 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 are connected by the respective plate surfaces and the pipeline of the heat transfer pipe 70 . The extending direction is arranged so as to be vertical.

The main body 151 of the refrigerant distributor 150 has 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 from the heat transfer pipe 70 . A structure where layers are stacked in sequence on the far side. The first plate-shaped member 10 is arranged at the position where the main body 151 is the farthest from the heat transfer pipe 70 , and the third plate-shaped member 30 is arranged at the position where the main body 151 is the shortest distance from the heat transfer pipe 70 .

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 connected to the first plate-shaped member 10 and the second plate-shaped member 20 . The boards are adjacent to each other. 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 connected to the second plate-shaped member 20 and the third plate-shaped member 30 . The boards are adjacent to each other.

The adjacent members among 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 welding. The respective longitudinal directions 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 arranged along the first direction (Z axis direction).

The fourth plate-shaped member 40 is formed with a communication hole 45 located between the main flow path 15a of the first flow path and both ends of the secondary flow path 25, and a second distribution hole 46 located in the second distribution hole 46. Between the main flow path 15 a of the flow path and the distribution hole portion 26 . The communication hole 45 and the second distribution hole portion 46 are through holes.

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

The communication hole 45 is located 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 so as to be located between the main flow path 15 a and the inlet. formed in a manner between the parts 25b. In addition, the communication hole 45 is located in 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. 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 secondary flow path 25 which is the second flow path, so as to connect the main flow path 15a which is the first flow path and the secondary flow path which is the second flow path. The task of the flow path between the flow paths 25 .

In the fourth plate-shaped member 40, a plurality of second distribution hole portions 46 each having a circular opening shape are formed. The second distribution hole portion 46 is formed in the vicinity of the center of the fourth plate-shaped member 40 in the third direction (Y-axis direction). The plurality of second distribution holes 46 together with the distribution holes 26 formed in the second plate-shaped member 20 and the third distribution holes 51 formed in the fifth plate-shaped member 50 to be described later form the main flow path 15a and the heat conduction. The flow paths between the pipes 70 are formed, and the refrigerant is distributed to each of the heat transfer pipes 70 .

Each of the plurality of second distribution hole portions 46 is a through hole penetrating the fourth plate-shaped member 40 in the 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) serving as 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 so as to correspond to each of the plurality of heat transfer pipes 70 . In addition, each of the plurality of second distribution hole portions 46 is provided so as to correspond to each of the distribution hole portions 26 formed in the second plate-shaped member 20 . Furthermore, each of the plurality of second distribution hole portions 46 is provided so as to correspond to each of the third distribution hole portions 51 formed in the fifth plate-shaped member 50 to be described later.

The opening shape of the second distribution hole portion 46 is circular, but it is not limited to a circular shape, and may be, for example, a semicircle, a semielliptical shape, a half racetrack shape, or a rectangle. In addition, the cross-sectional area of the flow path of the plurality of second distribution hole portions 46 is the same size, respectively. However, the channel cross-sectional areas of the plurality of second distribution holes 46 are not limited to the same size, but may be formed to have different sizes.

Furthermore, in the main body 151 of the refrigerant distributor 150 according to the second embodiment, a plurality of second distribution holes 46 are formed in the fourth plate-shaped member 40, but the second distribution holes 46 may be formed in the fourth plate-shaped member 40. Formed only one. 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 pipes 70 .

The plurality of second distribution hole portions 46 are all formed so as to overlap with the main flow path 15 a of the first plate-shaped member 10 when viewed in the plate thickness direction of the fourth plate-shaped member 40 . In addition, each of the plurality of second distribution hole portions 46 is formed so as to overlap with 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 . In addition, each of the plurality of second distribution hole portions 46 is formed so as to overlap with 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 . Further, each of the plurality of second distribution hole portions 46 is formed so as to overlap with 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 . In addition, each of the plurality of second distribution hole portions 46 is formed so as to overlap with each of the plurality of heat transfer pipes 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 located in the thermally conductive Between the pipe 70 and the main flow path 15a which is the first flow path. Furthermore, the main flow path 15 a of the first plate-shaped member 10 communicates with each branch of the plurality of heat transfer pipes 70 via the plurality of second distribution hole portions 46 .

In addition, 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 15 a of the first plate-shaped member 10 when viewed in the thickness direction of the fourth plate-shaped member 40 . The closing portion 44 has a function of preventing the main flow path 15 a and each of the plurality of heat pipes 70 from being directly communicated without passing through the second distribution hole portion 46 .

In addition, the closing portion 44 covers a part of the auxiliary flow path 25 from the arrangement side of the first plate-shaped member 10 . The closing portion 44 covers at least the central portion 25 a of the secondary flow path 25 from the side where the first plate-shaped member 10 is arranged. The closed portion 44 forms a part of the piping constituting the secondary flow path 25 .

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

In the fifth plate-shaped member 50, a plurality of third distribution hole portions 51 each having a circular opening shape are formed. The third distribution hole portion 51 is formed in the vicinity of the center of the fifth plate-shaped member 50 in the third direction (Y-axis direction). The plurality of third distribution hole portions 51 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 form the main flow path 15 a and the heat transfer pipe 70 . The flow path between them is distributed, and the refrigerant is distributed to each of the heat transfer pipes 70 .

Each of the plurality of third distribution hole portions 51 is a through hole penetrating the fifth plate-shaped member 50 in the 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) serving as 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 so as to correspond to each of the plurality of heat pipes 70 . In addition, each of the plurality of third distribution hole portions 51 is provided so as to correspond to each of the distribution hole portions 26 formed in the second plate-shaped member 20 . Furthermore, each of the plurality of third distribution hole portions 51 is provided so as to correspond 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 portion 51 is circular, but it is not limited to a circular shape, and may be, for example, a semicircle, a semiellipse, a half racetrack shape, or a rectangle. In addition, the cross-sectional area of the flow path of the plurality of third distribution hole portions 51 is the same size, respectively. However, the channel cross-sectional areas of the plurality of third distribution hole portions 51 are not limited to the same size, and may be formed to have different sizes.

Furthermore, in the main body 151 of the refrigerant distributor 150 according to the second embodiment, a plurality of third distribution holes 51 are formed in the fifth plate-shaped member 50, but the third distribution holes 51 may be formed in the fifth plate-shaped member 50. Formed only one. In this case, the third distribution hole portion 51 is formed so as to extend in the first direction (Z-axis direction) in order to correspond to the plurality of heat transfer pipes 70 .

The plurality of third distribution hole portions 51 are all formed so as to overlap with the main flow path 15 a of the first plate-shaped member 10 when viewed in the plate thickness direction of the fifth plate-shaped member 50 . In addition, each of the plurality of third distribution hole portions 51 is formed so as to overlap with 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 with 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 . Moreover, each of the plurality of third distribution hole portions 51 is formed so as to overlap with 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 . In addition, each of the plurality of third distribution hole portions 51 is formed so as to overlap with each of the plurality of heat transfer pipes 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 located in the thermally conductive Between the pipe 70 and the main flow path 15a which is the first flow path. Furthermore, the main flow path 15 a of the first plate-shaped member 10 communicates with each branch of the plurality of heat transfer pipes 70 via the plurality of third distribution hole portions 51 .

In addition, the fifth plate-shaped member 50 has a flat plate-shaped closing portion 53 . A part of the closing part 53 overlaps with the main flow path 15 a 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 15 a and each of the plurality of heat transfer pipes 70 from directly communicating with each other without passing through the third distribution hole portion 51 .

In addition, the closing portion 53 covers a part of the auxiliary flow path 25 from the arrangement side of the third plate-shaped member 30 . The closing portion 53 covers at least the central portion 25 a 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 piping constituting the sub-flow path 25 .

FIG. 10 is a schematic diagram showing the flow of the refrigerant in the refrigerant distributor 150 constituting the heat exchanger 100 of the second embodiment. When the refrigeration cycle apparatus 200 is in 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, as shown by the arrow UF in FIG. The end 151b flows vertically upward. A part of the refrigerant that flows vertically upward passes through the second distribution hole 46 of the fourth plate-shaped member 40 , the distribution hole 26 of the second plate-shaped member 20 , and the third distribution of the fifth plate-shaped member 50 in this order. The hole portion 51 is distributed to each heat transfer pipe 70 after passing through the insertion hole 31 formed in the third plate-shaped member 30 .

Further, the refrigerant remaining in the upper portion of the main flow passage 15a flows into the inlet portion 25b provided in the second plate member 20 through the communication hole 45 which communicates with the upper end portion 15a1 of the main flow passage 15a. At this time, the refrigerant system flows from the main flow passage 15a of the first flow passage to the secondary flow passage 25 of the second flow passage to the outside in the third direction, as indicated by arrow OF. Then, the refrigerant flowing in from the inlet portion 25b of the secondary flow path 25 flows downward along the direction of gravity in the center portion 25a of the secondary flow path 25 formed in the second plate-shaped member 20, as indicated by the arrow DF. .

The refrigerant reaching the lower end of the central portion 25a of the secondary flow passage 25 flows out from the outlet portion 25c to the main passage 15a through a communication hole 45 that communicates with the lower end 15a2 of the main passage 15a. At this time, the refrigerant system flows from the secondary flow path 25 which is the second flow path to the main flow path 15a which is the first flow path, as indicated by the arrow IF, to the inner side which is the third direction. Then, the refrigerant flowing out from the outlet portion 25c to the main flow passage 15a rises vertically in the main flow passage 15a together with the refrigerant flowing from the refrigerant inflow pipe 60 into the main body 151, 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 inflow port 18 in the first direction in which the heat transfer pipes 70 are arranged.

As in the first embodiment, when the main body 151 is provided with the secondary flow path 25 serving as the second flow path, the liquid refrigerant accumulated in the upper portion of the main flow path 15a is returned to the lower portion of the main flow path 15a via the secondary flow path 25 . Therefore, as indicated by the arrow MU between the dotted line A and the solid line B, the flow rate of the refrigerant decreases because the refrigerant returns to the lower part of the main flow path 15a in the upper part of the main flow passage 15a. In addition, as indicated by the arrow MD between the dotted line A and the solid line B, in the lower part of the main flow path 15a, the refrigerant flows back from the upper part of the main flow path 15a, so the flow rate of the refrigerant increases. Therefore, as indicated by the solid line B, the flow rate of the refrigerant flowing in the main flow path 15a with the sub flow path 25 is compared with the flow rate of the refrigerant flowing in the main flow path 15a without the auxiliary flow path 25. Approach the flow rate of the refrigerant shown by the one-point chain line C. Therefore, the refrigerant distributor 150 having the sub-flow path 25 can evenly distribute the refrigerant to each heat pipe 70 as compared with the refrigerant distributor having no sub-flow path 25 . [Effect of heat exchanger 100]

The refrigerant distributor 150 has the fourth plate-shaped member 40 and the fifth plate-shaped member 50 . Further, in the fourth plate-shaped member 40, a communication hole 45 is formed between the main flow channel 15a, which is the first flow channel, and both ends of the secondary flow channel 25, and a second distribution hole 46 is formed in the second distribution hole 46. It is between the main flow path 15 a of the first flow path and the distribution hole portion 26 . Further, in the fifth plate-shaped member 50 , a third distribution hole portion 51 is formed, and the third distribution hole portion 51 is located between the distribution hole portion 26 and the insertion hole 31 .

The main body 151 of the refrigerant distributor 150 is provided with the above-mentioned penetration of the fourth plate-shaped member 40 and the fifth plate-shaped member 50 so as not to hinder the flow of the refrigerant between the main flow channel 15a and the auxiliary flow channel 25, and the flow of the refrigerant from the main flow channel 15a. The passage 15a is for the circulation of the refrigerant to the heat transfer pipe 70. Furthermore, the main body 151 of the refrigerant distributor 150 can form the piping of the secondary 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 necessarily require the flat plate portion 11 of the first plate-like member 10 and the flat plate portion 34 of the third plate-like member 30 in order to form the piping of the sub-flow path 25 .

Therefore, when the second plate-shaped member 20 is viewed in the stacking direction of the respective plate-shaped members, the secondary flow can be formed such that the main flow path 15a of the first plate-shaped member 10 and the insertion hole 31 of the third plate-shaped member 30 overlap. Road 25. In other words, the main body 151 of the refrigerant distributor 150 is oriented in the third direction (Y-axis direction), so that the width of the auxiliary flow path 25 formed in the second plate-shaped member 20 can be increased, and the volume of the auxiliary flow path 25 can be increased. get bigger. Therefore, when the pressure loss of the refrigerant distributor 150 of the heat exchanger 100 on the side of the secondary flow path 25 is reduced and the circulation flow rate is high, a large amount of refrigerant remaining in the upper part can be circulated, and the drift of the refrigerant can be suppressed, and the heat exchange can be improved. performance of the device 100. Embodiment 3

FIG. 12 is an exploded perspective view schematically showing the configuration of the main part of the heat exchanger 100 according to the third embodiment. 13 is a cross-sectional view schematically showing a 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. 14 is a schematic diagram showing the flow of the refrigerant in the refrigerant distributor 150 constituting the heat exchanger 100 of the third embodiment. Here, the same reference numerals are attached to constituent elements having the same functions and actions as those of the first embodiment, and the description thereof will be omitted. The heat exchanger 100 of the third embodiment is different from the outlet portion 25c of the heat exchanger 100 of the first embodiment in the angle of the tube axis of the specific outlet portion 25c1.

As shown in FIG. 12 , the secondary flow path 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 part 25c1 is formed in the other end part 25a2 of the center part 25a in the 1st direction (Z-axis direction).

The pipe axis TA of the outlet part 25c1 is inclined so as to be close to the diagonal DL of the second plate-shaped member 20 with respect to the first direction (Z-axis direction) and the third direction (Y-axis direction). Therefore, the outlet portion 25c1 is indicated by arrows IF and UF in FIG. 14, and the flow direction of the refrigerant flowing out from the outlet portion 25c1 has a vector component of the flow direction of the refrigerant flowing out from the refrigerant inflow pipe 60. The form 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 along the flow direction of the refrigerant flowing in the main passage 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. 15 , 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 pipes 70 are arranged.

As in the first embodiment, when the main body 151 is provided with the secondary flow path 25 serving as the second flow path, the liquid refrigerant accumulated in the upper portion of the main flow path 15a is returned to the lower portion of the main flow path 15a via the secondary flow path 25 . Therefore, as indicated by the arrow MU between the dotted line A and the solid line B, the flow rate of the refrigerant decreases because the refrigerant returns to the lower part of the main flow path 15a in the upper part of the main flow passage 15a. In addition, as indicated by the arrow MD between the dotted line A and the solid line B, in the lower part of the main flow path 15a, the refrigerant flows back from the upper part of the main flow path 15a, so the flow rate of the refrigerant increases. Therefore, as indicated by the solid line B, the flow rate of the refrigerant flowing in the main flow path 15a with the sub flow path 25 is compared with the flow rate of the refrigerant flowing in the main flow path 15a without the auxiliary flow path 25. Approach the flow rate of the refrigerant shown by the one-point chain line C. Therefore, the refrigerant distributor 150 having the sub-flow path 25 can evenly distribute the refrigerant to each heat pipe 70 as compared with the refrigerant distributor having no sub-flow path 25 . [Effect of heat exchanger 100]

The outlet portion 25c1 is indicated by arrows IF and UF in FIG. 14, and is configured such that the flow direction of the refrigerant flowing out of the outlet portion 25c1 has a vector component of the flow direction of the refrigerant flowing 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 secondary flow path 25 formed by the second plate-shaped member 20 is the vertical upward direction, and since the flow vector of the refrigerant when converging from the secondary flow path 25 to the main flow path 15a faces upward, the refrigerant above the The inertial force of the direction increases. Therefore, the refrigerant distributor 150 of the heat exchanger 100 promotes the circulation of the refrigerant in the main flow passage 15a and the secondary flow passage 25 . Furthermore, the refrigerant distributor 150 of the heat exchanger 100 can circulate a large amount of refrigerant retained in the upper portion of the main flow passage 15a, thereby suppressing uneven flow of the refrigerant. Embodiment 4

FIG. 16 is an exploded perspective view schematically showing the configuration of the main part of the heat exchanger 100 according to the fourth embodiment. 17 is a cross-sectional view schematically showing a 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. 18 is a schematic diagram showing the flow of the refrigerant in the refrigerant distributor 150 constituting the heat exchanger 100 of the fourth embodiment. In addition, the same code|symbol is attached|subjected to the structural element which has the same function and effect as Embodiment 1, and the description is abbreviate|omitted. The heat exchanger 100 of the fourth embodiment is different from the heat exchanger 100 of the first embodiment in that the configuration of the main flow channel 15a of the first flow channel is further specified.

The first flow path portion 15 is, as described above, formed inside the main flow path 15a which is the first flow path. In the heat exchanger 100 of the fourth embodiment, the main flow path 15a of the first flow path is such that the cross-sectional area of the flow path becomes smaller from the lower end portion 15a2 on the one side that communicates with the refrigerant inflow pipe 60 to the upper end portion 15a1 on the other side. way formed. When specifying the first direction (Z-axis direction) as the vertical direction, the main flow channel 15a is formed so that the flow channel cross-sectional area becomes smaller as it goes upward. The first flow path portion 15 has a rectangular cross-sectional shape as shown in FIG. 17 . However, the cross-sectional shape of the first flow path portion 15 is not limited to a rectangle, and may be, for example, a semicircle, a semiellipse, or a half racetrack shape.

The first flow path portion 15 extends from one end portion 151 a of the main body 151 to the other end portion 151 b along the longitudinal direction of the first plate-shaped member 10 . Both ends in the extending direction of the first flow path portion 15 are closed. In FIG. 16, the 1st flow-path part 15 has the side wall 15b formed in the trapezoid shape when seeing in the lamination direction of the 1st plate-shaped member 10, the 2nd plate-shaped member 20, and the 3rd plate-shaped member 30. The first flow path portion 15 is formed in a quadrangular columnar shape having a side wall 15b. The first flow path portion 15 is formed to taper gradually from the lower end portion 15a2 on the side of the refrigerant inflow port 18 to the upper end portion 15a1 on the other side in the longitudinal direction of the first plate-shaped member 10 . In addition, the 1st flow-path part 15 is not limited to being formed in the quadrangular column shape which has the side wall 15b, For example, other shapes, such as a truncated cone shape or a truncated polygonal pyramid, may be sufficient. [Effect of heat exchanger 100]

The main flow path 15a of the first flow path is formed so that the cross-sectional area of the flow path becomes smaller from the lower end portion 15a2 of the one side communicating with the refrigerant inflow pipe 60 toward the upper end portion 15a1 of the other side. When the first direction (Z-axis direction) is taken as the vertical direction, since the flow path cross-sectional area of the main flow path 15a is formed so as to become smaller toward the vertical upper part, the refrigerant distributor 150 of the heat exchanger 100 can be The flow rate of the refrigerant in the main flow path 15a is increased. Therefore, according to the operating state of the air conditioner, when the circulating amount of the refrigerant is small, the refrigerant distributor 150 of the heat exchanger 100 can make the refrigerant reach the uppermost part of the main flow passage 15a, thereby suppressing the uneven flow of the refrigerant. Embodiment 5

FIG. 19 is an exploded perspective view schematically showing the configuration of the main part of the heat exchanger 100 according to the fifth embodiment. FIG. 20 is a side view schematically showing the inside of the refrigerant distributor 150 shown in FIG. 19 . 21 is a cross-sectional view schematically showing a 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. In addition, the same code|symbol is attached|subjected to the structural element which has the same function and effect as Embodiment 1, and the description is abbreviate|omitted. The refrigerant distributors 150 according to Embodiments 1 to 4 are configured such that the first plate-shaped member 10 to the fifth plate-shaped member 50 are stacked in layers. On the other hand, the main body 151 of the refrigerant distributor 150 of the fifth embodiment is constituted by using a cylindrical member.

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

The main body 151 of the refrigerant distributor 150 has a cylindrical portion 90 extending in the first direction (Z-axis direction) that is the direction in which the plurality of heat transfer pipes 70 are arranged. In addition, the main body 151 of the refrigerant distributor 150 has a wall portion 91 in the hollow portion 95 in the cylindrical portion 90, and the wall portion 91 separates the main flow passage 15a and the secondary flow passage 25 in the third direction, and is in the first Both end portions in the direction form an inlet portion 92a and an outlet portion 92b that are through holes. Furthermore, the main body 151 of the refrigerant distributor 150 has a cover portion 94 , and the cover portion 94 closes both ends of the cylindrical portion 90 , respectively.

The cylindrical portion 90 is formed in a hollow cylindrical shape extending in the arrangement direction of the plurality of heat transfer pipes 70 . However, the cylindrical portion 90 is not limited to a cylindrical shape, but may be formed in a cylindrical shape, for example, a rectangular parallelepiped box shape. Moreover, in FIG. 19, the cylindrical part 90 has the 1st cylindrical part 90a connected with the refrigerant|coolant inflow pipe 60, and the 2nd cylindrical part 90b connected with the heat transfer pipe 70. The first cylindrical portion 90a and the second cylindrical portion 90b have a cross section perpendicular to the first direction (Z-axis direction), and are formed in a semicircular arc shape. In addition, the cylindrical part 90 may not have the structure which divided the 1st cylindrical part 90a and the 2nd cylindrical part 90b, but the structure which formed the 1st cylindrical part 90a and the 2nd cylindrical part 90b integrally and compactly may be sufficient.

The wall portion 91 has a belt-like shape long in one direction. The wall portion 91 is a plate-shaped portion extending in the arrangement direction of the plurality of heat pipes 70 , and the longitudinal direction of the wall portion 91 is the first direction (Z-axis direction) serving as the arrangement direction of the plurality of heat pipes 70 . Moreover, the short-side direction of the wall part 91 is a 2nd direction (X-axis direction), and is the extension direction of the duct of the heat transfer pipe 70. FIG. In addition, the plate thickness direction of the wall portion 91 is the long axis direction of the heat transfer pipe 70 . The wall portion 91 is formed as 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 portion 91b connected to the side of the refrigerant inflow pipe 60 . In addition, the wall portion 91 forms an inlet portion 92a at the other end portion 91a. The inlet portion 92 a and the outlet portion 92 b are through holes that penetrate the wall portion 91 in the thickness direction of the wall portion 91 . in the body 151 . The direction of the flow path formed by the inlet part 92a and the outlet part 92b is a 3rd direction.

In the wall portion 91, a plurality of insertion holes 93 are further formed, and the plurality of insertion holes 93 are respectively inserted into one end of the plurality of heat transfer pipes 70. As shown in FIG. Each of the plurality of insertion holes 93 is a through hole penetrating the wall portion 91 in the thickness direction of the wall portion 91 . In addition, each of the plurality of insertion holes 93 is also a cutout portion, and the cutout portion is cut away from the edge portion 91e extending in the first direction (Z-axis direction) to the edge portion 91d on the opposite side.

The plurality of insertion holes 93 are juxtaposed 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 so as to correspond to each of the plurality of heat pipes 70 . The insertion hole 93 has a flat opening shape like the outer peripheral shape of the heat transfer pipe 70 . The opening end of the insertion hole 93 is joined to the outer peripheral surface of the heat transfer pipe 70 over the entire circumference by welding. By joining the plurality of heat transfer pipes 70 to the wall portion 91, the plurality of heat transfer pipes 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 secondary flow path 25 which is the second flow path.

The cover portion 94 closes both ends of the cylindrical portion 90 in the extending direction. The cover portion 94 may be a plate-shaped member or a member covering the end portion of the cylindrical portion 90 as long as it closes both ends of the cylindrical portion 90 in the extending direction.

The hollow part 95 in the cylindrical part 90 is formed by the cylindrical part 90 and the cover part 94 which closes the both ends of the cylindrical part 90. Moreover, as shown in FIG. 21, the hollow part 95 in the cylindrical part 90 is partitioned into two spaces of the 1st space S1 and the 2nd space S2 by the wall part 91. The 1st space S1 and the 2nd space S2 communicate via the inlet part 92a and the outlet part 92b.

The main body 151 of the refrigerant distributor 150 constitutes the first space S1 as the main flow path 15a. The main flow path 15a is a flow path through which the refrigerant flows from one end 151a to the other end 151b on the side of the main body 151 connected to the refrigerant inflow pipe 60 . When the first direction (Z-axis direction) is regarded as an up-down direction, the main flow passage 15a is a flow passage in which the refrigerant ascends. The main flow path 15a of the first flow path is formed so as to extend in the first direction, communicates with the plurality of heat pipes 70, and at the lower end portion 15a2 in the first direction, communicates with the refrigerant that flows the refrigerant into the refrigerant distributor 150. Inflow pipe 60 is connected.

The main body 151 of the refrigerant distributor 150 includes the second space S2 , the inlet portion 92 a, and the outlet portion 92 b as the secondary flow path 25 . The secondary flow path 25 is a flow path through which the refrigerant flows from the other end portion 151b to the one end portion 151a of the main body 151 connected to the side of the refrigerant inflow pipe 60 . When the first direction (Z-axis direction) is regarded as an up-down direction, the secondary flow path 25 is a flow path through which the refrigerant descends. The secondary 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 secondary flow path 25 of the second flow path is formed so as to be located in the third direction with respect to the main flow path 15a of the first flow path. That is, the main flow path 15a and the secondary flow path 25 are formed so that the ventilation directions of the wind generated by the outdoor fan 108 or the indoor fan 109 shown in FIG. 1 are located on the upstream side and the downstream side.

The main body 151 of the refrigerant distributor 150 internally forms the main flow path 15a, which is the first flow path, and the secondary flow path 25, which is the second flow path, through which the refrigerant flows. 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 auxiliary flow path 25 .

22 is a cross-sectional view schematically showing a communication position between a first flow path and a second flow path of a refrigerant distributor constituting a modification of the heat exchanger 100 of the fifth embodiment. The cylindrical portion 90 is not limited to the cylindrical shape as shown in FIG. 21 . The cylindrical portion 90 may be formed in a semi-cylindrical shape as shown in FIG. 22, for example.

FIG. 23 is a schematic diagram showing the flow of the refrigerant in the refrigerant distributor 150 constituting the heat exchanger 100 according to the fifth embodiment. As in the first embodiment, the refrigerant remaining in the upper portion of the main flow passage 15a flows into the inlet portion 92a provided in the second plate member 20, and the inlet portion 92a communicates with the upper end portion 15a1 of the main flow passage 15a. At this time, the refrigerant system flows in the third direction from the main flow path 15a which is the first flow path to the secondary flow path 25 which is the second flow path, as indicated by the arrow OF. And the refrigerant|coolant which flows in from the inlet part 92a of the auxiliary|assistant flow path 25 flows downward in the direction of gravity in the auxiliary flow path 25 formed in the 2nd plate-shaped member 20, as shown by the arrow DF.

The refrigerant that has reached the lower end of the secondary flow passage 25 flows out to the main passage 15a from the outlet portion 92b, and the outlet portion 92b communicates with the lower end portion 15a2 of the main passage 15a. At this time, the refrigerant system flows in the third direction from the secondary flow path 25 which is the second flow path to the main flow path 15a which is the first flow path, as indicated by the arrow IF. Then, the refrigerant flowing out from the outlet portion 92b to the main flow passage 15a vertically ascends in the main flow passage 15a together with the refrigerant flowing from the refrigerant inflow pipe 60 into the main body 151, and is distributed to each heat transfer pipe 70. [Effect of heat exchanger 100]

The refrigerant distributor 150 has a cylindrical portion 90, a lid portion 94, and a wall portion 91, and partitions the main flow path 15a, which is the first flow path, and the secondary flow path 25, which is the second flow path, in the third direction. An inlet portion 92a and an outlet portion 92b which are through holes are formed at both ends in the first direction. Furthermore, the plurality of heat transfer pipes 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 secondary flow path 25 which is the second flow path. The main body 151 of the heat exchanger 100 adopts a cylindrical body such as a circular tube, which can suppress the enlargement of the refrigerant distributor 150 in the second direction for circulating the refrigerant, and can make the heat exchanger 100 within the scope of structural limitations. The length increases in the second direction in which the pipes of the heat pipes 70 extend. Therefore, the heat exchanger 100 can ensure a wide heat transfer area of the heat transfer pipe 70, and the refrigerant distributor 150 can be formed in the extending direction of the heat transfer pipe 70 without becoming large and compact.

Moreover, the refrigeration cycle apparatus 200 has the heat exchanger 100 of any one of Embodiments 1-5. Therefore, the refrigeration cycle apparatus 200 can obtain the same effect as any one of Embodiments 1-5.

The above-mentioned Embodiments 1 to 5 can be implemented in combination with each other. In addition, the structure shown in the above embodiment is an example, and may be combined with another well-known technique, and a part of a structure may be abbreviate|omitted or changed in the range which does not deviate from the summary. For example, the refrigerant distributors 150 and the like in Embodiments 1 to 5 may be 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. Moreover, the system body 151, such as the refrigerant|coolant distributor 150 of Embodiments 1-5, can also implement the structure which inclines with respect to a vertical direction.

10: 1st plate member 11: Flat panel 11a: Flat panel 11b: Flat plate 15: 1st channel part 15a: Main Street 15a1: Upper end 15a2: lower end 15b: Sidewall 18: Refrigerant flow inlet 20: Second plate member 24: Closed Department 25: Secondary flow path 25a: Central Section 25a1: End 25a2: End 25b: Entrance section 25c: Export Department 25c1: Export Department 26: Distribution hole 30: 3rd plate member 31: Insertion hole 34: Flat panel 40: Fourth plate member 44: Closed Department 45: Connecting holes 46: Second distribution hole 50: Fifth plate member 51: The third distribution hole 53: Closed Department 60: Refrigerant inflow pipe 70: heat pipe 70a: 1st side end 70b: 2nd side end 70c: flat surface 70d: flat surface 71: Gap 72: Refrigerant passage 75: Thermal heat sink 90: Cylindrical part 90a: 1st cylindrical part 90b: Second cylindrical part 91: Wall 91a: end 91b: end 91d: edge 91e: edge 92a: Entrance 92b: Export Department 93: Insertion hole 94: Cover 95: hollow part 100: heat exchanger 101: Compressor 102: Flow switching device 103: Indoor heat exchanger 104: Pressure reducing device 105: Outdoor heat exchanger 106: Outdoor unit 107: Indoor unit 108: Outdoor blower 109: Indoor blower 110: Refrigerant circuit 111: Extension piping 112:Extended piping 115: Flow Path Section 150: Refrigerant distributor 151: Ontology 151a: End 151b: end 200: Refrigeration cycle device

FIG. 1 is a refrigerant circuit diagram showing the configuration of a refrigeration cycle apparatus having a heat exchanger according to Embodiment 1. FIG. 2 is a side view schematically showing the configuration of the main part of the heat exchanger according to the first embodiment. [ Fig. 3] Fig. 3 is an exploded perspective view schematically showing the configuration of a main part of the heat exchanger according to the first embodiment. [ Fig. 4] Fig. 4 is a cross-sectional view showing a configuration of a heat transfer pipe constituting the heat exchanger according to Embodiment 1. [Fig. [ Fig. 5] Fig. 5 is a cross-sectional view schematically showing a communication position between a first flow path and a second flow path of the refrigerant distributor constituting the heat exchanger according to Embodiment 1. [Fig. 6] It is a schematic diagram which shows the flow of the refrigerant|coolant in the refrigerant|coolant distributor which comprises the heat exchanger of Embodiment 1. [FIG. 7] It is a figure which shows the flow distribution of the refrigerant|coolant in the refrigerant|coolant distributor which comprises the heat exchanger of Embodiment 1. [FIG. [ Fig. 8] Fig. 8 is an exploded perspective view schematically showing the configuration of the main part of the heat exchanger according to the second embodiment. [ Fig. 9] Fig. 9 is a cross-sectional view schematically showing a communication position between a first flow path and a second flow path of the refrigerant distributor constituting the heat exchanger according to Embodiment 2. [Fig. 10 is a schematic diagram showing the flow of the refrigerant in the refrigerant distributor constituting the heat exchanger according to the second embodiment. Fig. 11 is a diagram showing the flow rate distribution of the refrigerant in the refrigerant distributor constituting the heat exchanger according to the second embodiment. 12 is an exploded perspective view schematically showing the configuration of the main part of the heat exchanger according to the third embodiment. 13 is a cross-sectional view schematically 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. 14 is a schematic diagram showing the flow of the refrigerant in the refrigerant distributor constituting the heat exchanger according to the third embodiment. 15 is a diagram showing the flow rate distribution of the refrigerant in the refrigerant distributor constituting the heat exchanger according to the third embodiment. 16 is an exploded perspective view schematically showing the configuration of the main part of the heat exchanger according to the fourth embodiment. 17 is a cross-sectional view schematically 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. 18 is a schematic diagram showing the flow of the refrigerant in the refrigerant distributor constituting the heat exchanger according to the fourth embodiment. 19 is an exploded perspective view schematically showing the configuration of the main part of the heat exchanger according to the fifth embodiment. [Fig. 20] is a side view schematically showing the inside of the refrigerant distributor shown in Fig. 19. [Fig. 21 is a cross-sectional view schematically 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. 22 is a cross-sectional view schematically showing a communication position between a first flow path and a second flow path of a refrigerant distributor constituting a modification of the heat exchanger of the fifth embodiment. 23 is a schematic diagram showing the flow of the refrigerant in the refrigerant distributor constituting the heat exchanger according to the fifth embodiment.

10: 1st plate member

11: Flat panel

11a: Flat panel

11b: Flat plate

15: 1st channel part

15a: Main Street

15a1: Upper end

15a2: lower end

20: Second plate member

24: Closed Department

25: Secondary flow path

25a: Central Section

25a1: End

25a2: End

25b: Entrance section

25c: Export Department

26: Distribution hole

30: 3rd plate member

31: Insertion hole

34: Flat panel

60: Refrigerant inflow pipe

70: heat pipe

71: Gap

100: heat exchanger

150: Refrigerant distributor

151: Ontology

151a: End

151b: end

Z: 1st direction

X: 2nd direction

Y: 3rd direction

P: A plane parallel to the first and second directions

Claims (9)

A heat exchanger comprising: a plurality of heat-transfer pipes arranged at intervals in a first direction, the plurality of heat-transfer pipes allow a refrigerant to flow in a second direction intersecting with the first direction; and a refrigerant A distributor, which extends in the first direction, is connected to one end of each of the plurality of heat pipes, and distributes the refrigerant to the plurality of heat pipes; the refrigerant distributor is formed by laminating a plurality of plate-shaped members , a first flow path and a second flow path through which the refrigerant flows are formed inside; the first flow path is formed in a manner extending in the first direction, communicated with the plurality of heat pipes, and connected with the inflow pipe , the inflow pipe system makes the refrigerant flow into the inside of the refrigerant distributor; the second flow path system extends in the first direction, and is formed in a way that both ends are connected with the first flow path; When the direction intersecting the plane parallel to the first direction and the second direction is defined as the third direction, it is formed so as to be located in the third direction for the first flow path. The heat exchanger of claim 1, wherein the plurality of plate-shaped members of the refrigerant distributor include: a first plate-shaped member that forms the first flow path; and a second plate-shaped member that forms a distribution hole part, which is a through hole located between the plurality of heat pipes and the first flow path; and the second flow path; and a third plate-shaped member, which forms an insertion hole, and the insertion hole is the plurality of heat pipes The inserted through hole; the first plate-shaped member, the second plate-shaped member, and the third plate-shaped member are laminated; in the first plate-shaped member, the second plate-shaped member, and the third plate-shaped member the stacking direction of the One flow path overlaps with the both ends, and the first flow path, the distribution hole portion, and the insertion hole are formed so as to overlap. The heat exchanger of claim 2, wherein a plurality of the distribution holes are formed along the first direction. The heat exchanger of claim 2 or 3, wherein the second flow path is formed in the third direction on both sides of the distribution hole portion, respectively. The heat exchanger of claim 2 or 3, wherein the plurality of plate-shaped members of the refrigerant distributor have a fourth plate-shaped member between the first plate-shaped member and the second plate-shaped member; in A fifth plate-shaped member is provided between the second plate-shaped member and the third plate-shaped member, and a communication hole is formed in the fourth plate-shaped member, which is located between the first flow path and the both ends and a second distribution hole portion is a through hole located between the first flow path and the distribution hole portion; in the fifth plate-shaped member, a third distribution hole portion is formed, the third distribution hole The portion is a through hole located between the distribution hole portion and the insertion hole. The heat exchanger according to claim 2 or 3, wherein the two end portions are composed of an inlet portion and an outlet portion, the inlet portion is where the refrigerant flows into the first flow path, and the outlet portion is where the refrigerant flows into the first flow path. The inlet part and the outlet part are formed so as to extend in the third direction. The heat exchanger of claim 2 or 3, wherein the two end portions are composed of an inlet portion and an outlet portion, the inlet portion is where the refrigerant flows in from the first flow path, and the outlet portion is where the refrigerant flows to the first flow path. 1 flow path outflow; the outlet is formed so that the flow direction of the refrigerant flowing from the outlet has a vector component of the flow direction of the refrigerant flowing from the inflow pipe The third direction is inclined. The heat exchanger according to any one of claims 1 to 3, wherein the first flow path is such that the cross-sectional area of the flow path decreases from one end of the side connected to the inflow pipe to the other end. way formed. A refrigeration cycle apparatus having the heat exchanger according to any one of claims 1 to 8.

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