JP7387074B1 - Refrigerant distributors, heat exchangers, and refrigeration cycle equipment - Google Patents

Abstract

One aspect of the refrigerant distributor according to the present disclosure is a refrigerant distributor that distributes refrigerant, and includes a first piping section and a second piping section connected to the first piping section, the second piping section being , a pair of parallel pipe sections extending in the first direction and spaced apart in a second direction intersecting the first direction; and a connecting pipe section connecting the ends of the pair of parallel pipe sections in the first direction. The first piping part has a first elongated pipe part extending in the second direction, a second elongated pipe part bent from the first elongated pipe part, and a second elongated pipe part bent from the second elongated pipe part. a third extending tube section extending in two directions and connected to one of the pair of parallel tube sections, and the second extending tube section extends in the first direction and the second direction with respect to the first extending tube section. It is bent to one side in a direction perpendicular to both.

Description

The present disclosure relates to refrigerant distributors, heat exchangers, and refrigeration cycle devices.

A structure is known in which a refrigerant is distributed and supplied to a plurality of heat exchanger tubes in a heat exchanger. For example, Patent Document 1 describes an air conditioner having such a structure.

International Publication No. 2014/199501

In the structure for distributing refrigerant as described above, a bent portion may be provided in the piping section upstream of the portion where the refrigerant branches to avoid other members such as piping. In this case, the refrigerant after flowing through the bent portion is likely to become uneven within the pipe due to inertia. Therefore, the amount of refrigerant distributed to the plurality of heat exchanger tubes may be uneven, and the heat exchange efficiency of the heat exchanger may be reduced.

In view of the above circumstances, the present disclosure provides a refrigerant distributor having a structure that can suppress unevenness in the amount of refrigerant distributed, a heat exchanger equipped with such a refrigerant distributor, and such a refrigerant distributor. One of the objects is to provide a refrigeration cycle device including a heat exchanger.

One aspect of the refrigerant distributor according to the present disclosure is a refrigerant distributor that is installed in a heat exchanger having a plurality of heat transfer tubes and distributes refrigerant, and is connected to a first piping section and the first piping section. a second piping section, the second piping section extending in the first direction, and a pair of parallel piping sections spaced apart in a second direction intersecting the first direction; a connecting pipe section that connects one ends of the parallel pipe sections in the first direction, and the first pipe section includes a first extending pipe section extending in the second direction; a second elongated tube portion that is bent and extends from the second elongated tube portion, and a third elongated tube portion that is bent from the second elongated tube portion, extends in the second direction, and is connected to one of the pair of parallel tube portions. , the second elongated tube portion is bent to one side in a direction orthogonal to both the first direction and the second direction with respect to the first elongated tube portion, and The other end in the first direction is connected to two different heat transfer tubes, and the refrigerant distributor divides the refrigerant that has flowed into the first piping into two flows in the second piping. It is branched and distributed into the two heat exchanger tubes .

One aspect of the refrigerant distributor according to the present disclosure is a refrigerant distributor that distributes a refrigerant, and includes a first piping section and a second piping section connected to the first piping section, the second piping section being connected to the second piping section. The section includes a pair of parallel pipe sections extending in a first direction and spaced apart in a second direction intersecting the first direction, and connecting ends of the pair of parallel pipe sections in the first direction to each other. The first piping part has a first extending pipe part, a second extending pipe part bent and extending from the first extending pipe part, and a connecting pipe part bent from the second extending pipe part. and a third extending tube section extending in the second direction and connected to one of the pair of parallel tube sections, the length of the third extending tube section being equal to the inner diameter of the third extending tube section. This is more than 10 times as large.

One aspect of the heat exchanger according to the present disclosure includes the above-mentioned refrigerant distributor, a plurality of heat exchanger tubes, and a plurality of fins connected to the plurality of heat exchanger tubes.

One aspect of the refrigeration cycle device according to the present disclosure includes the above-described heat exchanger.

According to the present disclosure, it is possible to suppress unevenness in the amount of refrigerant distributed by the refrigerant distributor.

1 is a schematic diagram showing a schematic configuration of a refrigeration cycle device in Embodiment 1. FIG. FIG. 3 is a schematic diagram showing a heat exchanger of the outdoor unit in Embodiment 1. FIG. FIG. 3 is a view of a part of the heat exchanger of the outdoor unit in the first embodiment, viewed in the front-rear direction. It is a perspective view showing a part of heat exchanger of the outdoor unit in Embodiment 1. FIG. 3 is a view of a part of the refrigerant distributor in the first embodiment, viewed in the left-right direction. FIG. 7 is a view of a part of the refrigerant distributor in Embodiment 2, seen in the left-right direction. FIG. 7 is a view of a part of the refrigerant distributor in Embodiment 3, seen in the left-right direction. FIG. 7 is a diagram of a part of the refrigerant distributor in Embodiment 4, seen in the front-rear direction. FIG. 7 is a view of a part of the refrigerant distributor in Embodiment 4, seen in the left-right direction. It is a sectional view showing a part of a refrigerant distributor of a comparative example.

Embodiments of the present disclosure will be described below with reference to the drawings. Note that the scope of the present disclosure is not limited to the following embodiments, and can be arbitrarily modified within the scope of the technical idea of the present disclosure. Further, in the following drawings, in order to make each structure easier to understand, the scale and number of each structure may be different from the scale and number of the actual structure.

Further, in the drawings, an X axis, a Y axis, and a Z axis are shown as appropriate. The X-axis indicates one of the horizontal directions. The Y axis indicates the other horizontal direction. The Z axis indicates the vertical direction. In the following explanation, the horizontal direction along the X-axis will be referred to as the "back-and-forth direction ”. The front-rear direction X, the left-right direction Y, and the vertical direction Z are directions that are orthogonal to each other. In the following explanation, the side of the vertical direction Z that the Z-axis arrow points to (+Z side) is referred to as the upper side, and the side of the vertical direction Z that is opposite to the side that the Z-axis arrow points to (-Z side) is referred to as the lower side. do. Further, in the front-rear direction X, the side toward which the X-axis arrow points (+X side) is the front side, and in the front-rear direction X, the side opposite to the side toward which the X-axis arrow points (-X side) is the rear side. Moreover, the left-right direction Y is the left-right direction when the outdoor unit of the following embodiment is viewed from the front (+X direction). In other words, the side of the left-right direction Y that the Y-axis arrow points to (+Y side) is the right side, and the side of the left-right direction Y that is opposite to the side that the Y-axis arrow points to (-Y side) is the left side.

Note that in the following embodiments, the left-right direction Y corresponds to a "first direction." The vertical direction Z corresponds to a "second direction" that intersects the first direction. The front-rear direction X corresponds to a direction perpendicular to both the first direction and the second direction.

Embodiment 1.
FIG. 1 is a schematic diagram showing a schematic configuration of a refrigeration cycle device 100 in the first embodiment. The refrigeration cycle device 100 is a device that uses a refrigeration cycle in which refrigerant 19 circulates. In the first embodiment, refrigeration cycle device 100 is an air conditioner. As shown in FIG. 1, the refrigeration cycle device 100 includes an outdoor unit 10, an indoor unit 20, and a circulation path section 18. The outdoor unit 10 is placed outdoors. The indoor unit 20 is placed indoors. The outdoor unit 10 and the indoor unit 20 are connected to each other by a circulation path section 18 through which a refrigerant 19 circulates. The outdoor unit 10 and the indoor unit 20 are heat exchange units that exchange heat with air.

The refrigeration cycle device 100 can adjust the temperature of indoor air by exchanging heat between the refrigerant 19 flowing in the circulation path section 18 and the indoor air in which the indoor unit 20 is placed. Examples of the refrigerant 19 include a fluorine-based refrigerant or a hydrocarbon-based refrigerant that has a low global warming potential (GWP).

The outdoor unit 10 includes a housing 11 , a compressor 12 , a heat exchanger 13 , a flow rate adjustment valve 14 , a blower 15 , a four-way valve 16 , and a control section 17 . Inside the housing 11, a compressor 12, a heat exchanger 13, a flow rate regulating valve 14, an air blower 15, a four-way valve 16, and a control unit 17 are housed.

The compressor 12, the heat exchanger 13, the flow rate adjustment valve 14, and the four-way valve 16 are provided in a portion of the circulation path section 18 located inside the housing 11. The compressor 12, the heat exchanger 13, the flow rate adjustment valve 14, and the four-way valve 16 are connected by a portion of the circulation path portion 18 located inside the housing 11.

The four-way valve 16 is provided in a portion of the circulation path section 18 that is connected to the discharge side of the compressor 12. The four-way valve 16 can reverse the direction of the refrigerant 19 flowing within the circulation path section 18 by switching a part of the circulation path section 18 . When the path connected by the four-way valve 16 is the path shown by the solid line in the four-way valve 16 in FIG. 1, the refrigerant 19 flows in the circulation path section 18 in the direction shown by the solid line arrow in FIG. On the other hand, when the path connected by the four-way valve 16 is the path shown by the broken line in the four-way valve 16 in FIG. 1, the refrigerant 19 flows in the circulation path portion 18 in the direction shown by the broken line arrow in FIG.

The indoor unit 20 includes a housing 21, a heat exchanger 22, and a blower 23. The housing 21 houses a heat exchanger 22 and a blower 23 therein. The indoor unit 20 is capable of a cooling operation that cools the air in the room where the indoor unit 20 is placed, and a heating operation that warms the air in the room where the indoor unit 20 is placed.

When the indoor unit 20 is operated for cooling, the refrigerant 19 flowing within the circulation path portion 18 flows in the direction shown by the solid arrow in FIG. 1 . That is, when the indoor unit 20 is operated for cooling, the refrigerant 19 flowing in the circulation path section 18 is transferred to the compressor 12, the heat exchanger 13 of the outdoor unit 10, the flow rate adjustment valve 14, and the heat exchanger 22 of the indoor unit 20. are circulated in this order and returned to the compressor 12. In the cooling operation, the heat exchanger 13 in the outdoor unit 10 functions as a condenser, and the heat exchanger 22 in the indoor unit 20 functions as an evaporator.

On the other hand, when the indoor unit 20 is operated for heating, the refrigerant 19 flowing within the circulation path section 18 flows in the direction shown by the broken line in FIG. That is, when the indoor unit 20 is operated for heating, the refrigerant 19 flowing in the circulation path section 18 is transferred to the compressor 12, the heat exchanger 22 of the indoor unit 20, the flow rate adjustment valve 14, and the heat exchanger 13 of the outdoor unit 10. are circulated in this order and returned to the compressor 12. In heating operation, the heat exchanger 13 in the outdoor unit 10 functions as an evaporator, and the heat exchanger 22 in the indoor unit 20 functions as a condenser.

Next, the outdoor unit 10 will be explained in more detail. FIG. 2 is a schematic diagram showing the heat exchanger 13 of the outdoor unit 10. FIG. 3 is a diagram of a part of the heat exchanger 13 of the outdoor unit 10 as viewed in the front-rear direction X. FIG. 4 is a perspective view showing a part of the heat exchanger 13 of the outdoor unit 10.

As shown in FIGS. 2 to 4, the heat exchanger 13 of the outdoor unit 10 includes a heat exchanger main body 13c. The heat exchanger main body 13c includes a plurality of heat exchanger tubes 13a and a plurality of fins 13b. In the first embodiment, the plurality of heat exchanger tubes 13a extend in the left-right direction Y. The plurality of heat exchanger tubes 13a are, for example, cylindrical pipes. In the first embodiment, a plurality of rows of heat exchanger tubes 13a lined up at intervals in the vertical direction Z are arranged in two rows in the front-rear direction X. In addition, in FIG. 3 and FIG. 4, illustration of some heat exchanger tubes 13a is omitted.

The plurality of fins 13b are connected to the plurality of heat exchanger tubes 13a. In the first embodiment, the plurality of fins 13b are rectangular plates whose plate surfaces face in the left-right direction Y and are long in the vertical direction Z. The plurality of fins 13b are arranged side by side in the left-right direction Y. Although not shown, a slight gap is provided between adjacent fins 13b. Each fin 13b is formed with a plurality of through holes through which the plurality of heat exchanger tubes 13a are passed in the left-right direction Y. The outer peripheral surface of the heat exchanger tube 13a passed through the through hole is fixed to the inner edge of the through hole.

As shown in FIG. 2, the heat exchanger 13 includes bent portions 51 and 52 that connect the two heat exchanger tubes 13a. The bent portion 51 is a portion that connects the heat exchanger tubes 13a included in two rows adjacent to each other in the front-rear direction X. The bent portion 52 is a portion that connects the heat exchanger tubes 13a adjacent to each other in the vertical direction Z. A plurality of bent portions 51 and a plurality of bent portions 52 are provided. Each of the bent portions 51 and 52 is, for example, a U-shaped pipe. The bent portions 51 and 52 may be pipe joints separate from the heat exchanger tube 13a, or may be formed integrally with the heat exchanger tube 13a.

The heat exchanger 13 includes a first distributor 41 and a second distributor 42. The first distributor 41 has a plurality of piping sections 41a. In the example of FIG. 2, six piping portions 41a are provided. Each of the plurality of piping portions 41a is connected to the heat transfer tube 13a arranged above in the vertical direction Z among the plurality of heat transfer tubes 13a. A pipe 18a connecting the heat exchanger 13 and the four-way valve 16 is connected to the first distributor 41.

When the indoor unit 20 is operated for cooling, the refrigerant 19 that has flowed from the piping 18a to the first distributor 41 branches into a plurality of piping portions 41a and flows into each heat transfer tube 13a to which each piping portion 41a is connected. flows into. In the first embodiment, the refrigerant 19 that has flowed into each heat transfer tube 13a from each piping section 41a flows to another heat transfer tube 13a via one bent portion 52, and then flows to another heat transfer tube 13a via one bent portion 51. It flows into the heat pipe 13a, and then flows through another bend 52 and further into the other heat exchanger pipe 13a. The refrigerant 19 that has flowed to the other heat transfer tube 13a flows into a refrigerant distributor 30, which will be described later.

The second distributor 42 has a plurality of piping sections 42a. In the example of FIG. 2, three piping portions 42a are provided. Each of the plurality of piping portions 42a is connected to a heat transfer tube 13a arranged on the lower side in the vertical direction Z among the plurality of heat transfer tubes 13a. A pipe 18b connecting the heat exchanger 13 and the flow rate regulating valve 14 is connected to the second distributor 42.

When the indoor unit 20 is operated for heating, the refrigerant 19 that has flowed from the piping 18b to the second distributor 42 branches into a plurality of piping sections 42a and flows into each heat transfer tube 13a to which each piping section 42a is connected. flows into. In Embodiment 1, the refrigerant 19 that has flowed into each heat transfer tube 13a from each piping portion 42a flows to another heat transfer tube 13a via one bent portion 52, and then flows to another heat transfer tube 13a via one bent portion 51. It flows into the heat pipe 13a, and then flows through another bend 52 and further into the other heat exchanger pipe 13a. The refrigerant 19 that has flowed to the other heat transfer tube 13a flows into a refrigerant distributor 30, which will be described later.

The heat exchanger 13 includes a refrigerant distributor 30 that distributes the refrigerant 19. In the first embodiment, the refrigerant distributor 30 connects the first distributor 41 and the second distributor 42 via a plurality of heat transfer tubes 13a, respectively. The refrigerant 19 that has flowed from the first distributor 41 to the plurality of heat transfer tubes 13a flows to the second distributor 42 via the refrigerant distributor 30. The refrigerant 19 that has flowed from the second distributor 42 to the plurality of heat transfer tubes 13a flows to the first distributor 41 via the refrigerant distributor 30. In the first embodiment, a plurality of refrigerant distributors 30 are provided. In the example of FIG. 2, three refrigerant distributors 30 are provided.

As shown in FIGS. 3 and 4, in the first embodiment, the refrigerant distributor 30 is located on the right side (+Y side) of the heat exchanger main body 13c. FIG. 5 is a diagram of a part of the refrigerant distributor 30 viewed in the left-right direction Y. As shown in FIGS. 3 to 5, the refrigerant distributor 30 includes a first piping section 31 and a second piping section 32 connected to the first piping section 31.

In the first embodiment, the first piping section 31 is a piping that connects one heat exchanger tube 13a and the second piping section 32. The first piping section 31 is, for example, a cylindrical piping. As shown in FIG. 3, the first piping section 31 includes a connecting tube section 31a, a first extending tube section 31b, a second extending tube section 31c, and a third extending tube section 31d.

The connecting pipe portion 31a extends in the left-right direction Y. The connecting tube portion 31a is connected to an end in the left-right direction Y of a heat exchanger tube 13a that is disposed at a relatively lower side among the plurality of heat exchanger tubes 13a. That is, in the first embodiment, the other member to which the connecting tube portion 31a is connected is the heat exchanger tube 13a. The end portion of the connecting pipe portion 31a that is connected to the heat exchanger tube 13a is the end portion of the first piping portion 31 that is opposite to the end portion of the first piping portion 31 that is connected to the second piping portion 32. The connecting tube portion 31a extends linearly to the right from the right (+Y side) end of the heat exchanger tube 13a. In the first embodiment, the connecting pipe portion 31a extends in a direction parallel to the left-right direction Y.

The first extending pipe portion 31b extends in the vertical direction Z. In the first embodiment, the first extending tube section 31b extends linearly upward from the right end of the connecting tube section 31a. Note that another tube section may be provided between the connecting tube section 31a and the first extension tube section 31b, and the another tube section may have any shape. For example, the other tube portion may extend upward from the right end of the connecting tube portion 31a obliquely in a direction horizontally inclined with respect to the vertical direction Z. When the other tube section is provided, the first extending tube section 31b extends upward from the end of the other tube section on the opposite side to the side connected to the connecting tube section 31a.

The first extending tube portion 31b extends upwardly from the connecting tube portion 31a. That is, a bent portion 33a is formed between the connecting tube portion 31a and the first extending tube portion 31b. In the first embodiment, the bent portion 33a is a connecting portion between the connecting tube portion 31a and the first extending tube portion 31b. In the first embodiment, the bending angle θ3 at the bending portion 33a is 90°. The bending angle θ3 is the bending angle of the first extending tube portion 31b with respect to the connecting tube portion 31a. The bending angle θ3 is not particularly limited, and may be an angle other than 90°.

In addition, in this specification, "the bending angle of another pipe part with respect to a certain pipe part" refers to the degree to which another pipe part connected to a certain pipe part is bent with respect to a certain pipe part. This is the angle shown. In other words, the greater the bending angle, the more the other tube sections are bent relative to a certain tube section. In addition, when a certain pipe part is not bent with respect to another pipe part, and the other pipe part continues to the certain pipe part and extends in the direction in which the certain pipe part extends, the bending angle is This is a state where the angle is 0°.

The second stretched tube section 31c is connected to the upper end of the first stretched tube section 31b. As shown in FIGS. 4 and 5, the second elongated tube section 31c extends in a bent manner from the first elongated tube section 31b. The second elongated tube section 31c is bent to one side in the front-rear direction X, which is orthogonal to both the left-right direction Y and the vertical direction Z, that is, to the rear side (-X side) with respect to the first elongated tube section 31b. . In the first embodiment, the second elongated tube portion 31c is obliquely inclined with respect to the vertical direction Z and the front-rear direction X and extends linearly. The second elongated tube section 31c is located on the rear side upward from the upper end of the first elongated tube section 31b.

A connecting portion between the first stretched tube section 31b and the second stretched tube section 31c is a bent section 33b. In the first embodiment, the bending angle θ1a at the bending portion 33b is an acute angle. The bending angle θ1a is the bending angle of the second elongated tube portion 31c with respect to the first elongated tube portion 31b.

The third elongated tube section 31d is connected to the upper and rear (-X side) end of the second elongated tube section 31c. The third elongated tube portion 31d extends linearly upward from the upper and rear end of the second elongated tube portion 31c. That is, the third elongated tube section 31d is bent from the second elongated tube section 31c and extends in the vertical direction Z. The third elongated tube section 31d is bent upward with respect to the second elongated tube section 31c. The upper end of the third extended tube section 31d is the upper end of the first piping section 31 and is connected to the second piping section 32. The third elongated tube section 31d is disposed at a position shifted from the first elongated tube section 31b when viewed in the vertical direction Z. In the first embodiment, the third elongated tube section 31d is disposed at a position shifted in the front-rear direction X with respect to the first elongated tube section 31b. The third elongated tube section 31d is located further back (in the -X direction) than the first elongated tube section 31b.

A connecting portion between the second stretched tube portion 31c and the third stretched tube portion 31d is a bent portion 33c. In the first embodiment, the bending angle θ2a at the bending portion 33c is an acute angle. The bending angle θ2a is the bending angle of the third elongated tube portion 31d with respect to the second elongated tube portion 31c. In the first embodiment, the bending angle θ1a and the bending angle θ2a are the same angle. Note that the bending angle θ1a and the bending angle θ2a may be different angles from each other.

In the first embodiment, the length L1b of the first stretched tube section 31b is longer than the length L1d of the second stretched tube section 31c and the third stretched tube section 31d. The length L1b of the first stretched tube portion 31b is 10 times or more the inner diameter Db of the first stretched tube portion 31b. The length L1d of the third stretched tube section 31d is larger than the length of the second stretched tube section 31c. The length L1d of the third stretched tube portion 31d is 10 times or more the inner diameter Dd of the third stretched tube portion 31d. The length of each stretched tube section is the dimension of each stretched tube section in the direction in which each stretched tube section extends. That is, the length L1b of the first stretched tube section 31b is the dimension of the first stretched tube section 31b in the vertical direction Z, and the length L1d of the third stretched tube section 31d is the dimension of the third stretched tube section 31d in the vertical direction. This is the Z dimension. Note that the length L1b of the first stretched tube section 31b may be the same as the length L1d of the third stretched tube section 31d, or may be smaller than the length L1d of the third stretched tube section 31d.

As shown in FIG. 3, a portion of the first piping section 31 including the first elongated tube section 31b, the second elongated tube section 31c, and the third elongated tube section 31d extends in both the left-right direction Y and the vertical direction Z. It has a shape that extends linearly in the vertical direction Z when viewed in the front-rear direction X perpendicular to the front-back direction. In the first embodiment, the portion of the first piping section 31 that includes the first elongated tube section 31b, the second elongated tube section 31c, and the third elongated tube section 31d refers to the first This is a portion between the lower end of the stretched tube section 31b and the upper end of the third stretched tube section 31d. That is, in the first embodiment, when viewed in the front-rear direction It has an elongated shape.

The second piping section 32 is connected to the upper end of the first piping section 31 . The second piping section 32 includes a pair of parallel tube sections 32a and 32b and a connecting tube section 32c. The pair of parallel pipe portions 32a and 32b extend in the left-right direction Y. The pair of parallel pipe portions 32a and 32b are arranged at intervals in the vertical direction Z intersecting the left-right direction Y. In the first embodiment, the pair of parallel pipe sections 32a and 32b are straight pipe sections that extend parallel to each other.

One end portions of the pair of parallel tube portions 32a and 32b in the left-right direction Y are connected to each other by a connecting tube portion 32c. In the first embodiment, the right end portions of the parallel tube portions 32a and 32b are connected to each other by a connecting tube portion 32c. The pair of parallel tube portions 32a, 32b are connected to different heat exchanger tubes 13a, respectively. In the first embodiment, the left end of each parallel tube section 32a, 32b is connected to the right end of each heat exchanger tube 13a. The heat exchanger tube 13a to which the pair of parallel tube parts 32a and 32b are connected is the heat exchanger tube 13a located relatively above among the plurality of heat exchanger tubes 13a.

The parallel tube portion 32b is arranged below the parallel tube portion 32a with a space therebetween. A cylindrical portion 32d that protrudes downward is formed on the lower wall portion of the right side portion of the parallel tube portion 32b. The cylindrical portion 32d has a cylindrical shape that opens downward. The upper end portion of the first piping portion 31, that is, the upper end portion of the third extending tube portion 31d is fitted into the cylindrical portion 32d. The third elongated tube portion 31d and the cylindrical portion 32d are fixed to each other by, for example, welding. Thereby, the third extended tube section 31d is connected to one of the pair of parallel tube sections 32a and 32b, that is, the parallel tube section 32b. In the first embodiment, the third extended tube section 31d is connected from below to the right end of the parallel tube section 32b, which is located on the lower side in the vertical direction Z, of the pair of parallel tube sections 32a and 32b.

The connecting pipe section 32c is located on the right side of the pair of parallel pipe sections 32a and 32b. The connecting pipe portion 32c connects the ends of the pair of parallel pipe portions 32a, 32b in the left-right direction Y. In the first embodiment, the connecting pipe portion 32c extends in a curved shape. More specifically, the connecting pipe portion 32c extends in a semicircular arc shape convex to the right side when viewed in the front-rear direction X. The upper end of the connecting pipe section 32c is connected to the right end of the parallel pipe section 32a. The lower end of the connecting pipe section 32c is connected to the right end of the parallel pipe section 32b. The pair of parallel pipe parts 32a and 32b are connected to each other by the semicircular arc-shaped connecting pipe part 32c when viewed in the front-back direction In other words, in the first embodiment, it has a U-shape that opens to the left (-Y side).

In the first embodiment, the refrigerant distributor 30 functions as a distributor that distributes the refrigerant 19 when the indoor unit 20 is operated for heating. When the indoor unit 20 is operated for heating, the refrigerant 19 flows into the connecting pipe part 31a from the heat transfer tube 13a connected to the connecting pipe part 31a, as shown by the broken line arrow in FIG. Here, the refrigerant 19 flowing into the connecting pipe portion 31a is in a gas-liquid two-phase state. The refrigerant 19 that has flowed into the connecting pipe section 31a flows to the right through the connecting pipe section 31a, and flows into the first extending pipe section 31b. The refrigerant 19 that has flowed into the first stretched tube section 31b flows upward through the first stretched tube section 31b, the second stretched tube section 31c, and the third stretched tube section 31d in this order. The water flows into the parallel pipe section 32b from the upper end of the pipe. The refrigerant 19 that has flowed into the parallel pipe section 32b collides with a portion of the inner wall of the parallel pipe section 32b that faces above the third extending pipe section 31d, and branches into two streams that flow in opposite directions in the left-right direction Y. do. A part of the refrigerant 19 that has flowed into the parallel pipe section 32b flows to the left through the parallel pipe section 32b, and flows into the heat exchanger tube 13a to which the parallel pipe section 32b is connected. The remainder of the refrigerant 19 that has flowed into the parallel pipe section 32b flows to the right and flows into the connecting pipe section 32c. The refrigerant 19 that has flowed into the connecting pipe portion 32c flows into the parallel pipe portion 32a, flows to the left within the parallel pipe portion 32a, and flows into the heat exchanger tube 13a to which the parallel pipe portion 32a is connected. In this way, the refrigerant distributor 30 branches the refrigerant 19 that has flowed into the first piping section 31 into two flows at the second piping section 32, and distributes them into the two heat exchanger tubes 13a.

Next, a refrigerant distributor 530 as a comparative example will be described. FIG. 10 is a sectional view showing a part of a refrigerant distributor 530 of a comparative example. As shown in FIG. 10, the refrigerant distributor 530 differs from the first embodiment in a first piping section 531. In the following description of the refrigerant distributor 530, the same components as the refrigerant distributor 30 of Embodiment 1 may be given the same reference numerals and the description thereof may be omitted.

The first piping section 531 includes a first elongated tube section 31b, a second elongated tube section 531c, and a third elongated tube section 531d. The second elongated tube portion 531c is bent toward one side (−Y side) in the left-right direction Y, in which the pair of parallel tube portions 32a and 32b extend, with respect to the first elongated tube portion 31b. A connecting portion between the first stretched tube portion 31b and the second stretched tube portion 531c is a bent portion 533b. The bent portion 533b is the same as the bent portion 33b of Embodiment 1, except that the bent portion 533b is bent in a different direction with respect to the first extending tube portion 31b. The second elongated tube portion 531c is located at the upper side as it goes to the left from the upper end of the first elongated tube portion 31b.

The third elongated tube section 531d is bent from the second elongated tube section 531c, extends in the vertical direction Z, and is connected to the parallel tube section 32b. The third elongated tube portion 531d is disposed at a position shifted in the left-right direction Y with respect to the first elongated tube portion 31b. The third stretched tube section 531d is located on the left side (-Y side) of the first stretched tube section 31b. The length L2d of the third stretched tube portion 531d is smaller than 10 times the inner diameter Dd of the third stretched tube portion 531d. In the example of FIG. 10, the length L2d of the third stretched tube portion 531d is smaller than five times the inner diameter Dd of the third stretched tube portion 531d. A connecting portion between the second stretched tube portion 531c and the third stretched tube portion 531d is a bent portion 533c. The bent portion 533c is the same as the bent portion 33c of the first embodiment, except that the relative positional relationship between the second stretched tube portion 531c and the third stretched tube portion 531d is different.

In the refrigerant distributor 530 of the comparative example, when the refrigerant 19 flows from the first elongated tube section 31b into the second elongated tube section 531c, the liquid refrigerant LR of the refrigerant 19 in the gas-liquid two-phase state flows into the first elongated tube section 531c. The inertia flowing upward through the stretched tube section 31b presses it against the upper inner wall section 531e of the inner wall of the second stretched tube section 531c. The liquid refrigerant LR pressed against the inner wall portion 531e by inertia flows inside the second extending tube portion 531c along the inner wall portion 531e, and flows into the third extending tube portion 531d. The liquid refrigerant LR that has flowed into the third elongated tube section 531d is caused by the inertia generated when flowing inside the first elongated tube section 31b and the second elongated tube section 531c to the inner wall of the third elongated tube section 531d. It flows within the third extension tube portion 531d along the inner wall portion 531f that is connected to the inner wall portion 531e. The inner wall portion 531f is a portion located on the right side (+Y side) of the inner wall of the third extension tube portion 531d. The liquid refrigerant LR that has flowed upward along the inner wall portion 531f flows into the second piping portion 32 from the parallel pipe portion 32b.

Since the liquid refrigerant LR flows along the inner wall portion 531f due to inertia, the refrigerant 19 in the third extended tube portion 531d is in a state where the liquid refrigerant LR is closer to the right side and the gaseous refrigerant GR is closer to the left side. When the refrigerant 19 in this state collides with the part of the inner wall of the parallel pipe section 32b that faces the third extending pipe section 531d, the liquid refrigerant LR, which is closer to the right side, flows to the right side and is connected to the parallel pipe section 32c via the connecting pipe section 32c. The gaseous refrigerant GR that easily flows to the pipe portion 32a and is closer to the left side tends to flow to the left side in the parallel pipe portion 32b. Therefore, the amount of refrigerant 19 flowing from parallel tube section 32b to heat exchanger tubes 13a is smaller than the amount of refrigerant 19 flowing from parallel tube section 32a to heat exchanger tubes 13a. In this way, in the refrigerant distributor 530 of the comparative example, since the bent portions 533b and 533c are provided, the liquid refrigerant LR may be biased due to inertia, and the amount of the refrigerant 19 to be distributed may be biased. there were. Therefore, the amount of refrigerant 19 flowing in each heat exchanger tube 13a may be uneven, and the heat exchange efficiency of the heat exchanger 13 may be reduced.

On the other hand, according to the first embodiment, the second elongated tube portion 31c extends in the left-right direction Y and the left-right direction Y in which the pair of parallel tube portions 32a and 32b extend with respect to the first elongated tube portion 31b. It is bent to one side in the front-rear direction X that is orthogonal to both of the intersecting vertical directions Z. Therefore, even if the liquid refrigerant LR flowing through the third extending pipe portion 31d is biased due to the inertia generated in the refrigerant 19, the direction in which the liquid refrigerant LR is biased is not in the left-right direction Y in which the pair of parallel pipe portions 32a and 32b extend. Not in the front-back direction. As a result, when the refrigerant 19 flowing into the parallel pipe part 32b from the third extending pipe part 31d collides with the inner wall part in the parallel pipe part 32b, the amount of the refrigerant 19 branching and flowing in the left-right direction Y becomes uneven. Hateful. Therefore, it is possible to suppress unevenness in the amount of refrigerant 19 distributed to each of the pair of parallel pipe portions 32a, 32b. Therefore, the amount of refrigerant 19 flowing into the plurality of heat exchanger tubes 13a is less likely to be uneven, and it is possible to suppress a decrease in the heat exchange efficiency of the heat exchanger 13. Therefore, the performance of the refrigeration cycle device 100 including the heat exchanger 13 can be improved.

Furthermore, by bending a part of the first piping section 31, it is possible to suppress the first piping section 31 from coming into contact with other members such as other piping, and to avoid the first piping section 31 from other members. It can be easily arranged appropriately. In the refrigerant distributor 530 of the comparative example described above, as a result of bending the first piping section 531 to avoid other members such as other piping, the amount of refrigerant 19 distributed as described above is uneven. There was a case. In contrast, according to the first embodiment, as described above, even though a portion of the first piping section 31 is bent, it is possible to suppress unevenness in the amount of refrigerant 19 distributed by the refrigerant distributor 30. . Therefore, it is possible to prevent the refrigerant 19 distributed by the refrigerant distributor 30 from being unevenly distributed while the refrigerant distributor 30 is suitably arranged inside the outdoor unit 10 while avoiding other members such as other pipes.

According to the first embodiment, the portion of the first piping section 31 including the first elongated tube section 31b, the second elongated tube section 31c, and the third elongated tube section 31d is arranged in the left-right direction Y and the vertical direction. It has a shape that extends linearly in the vertical direction Z when viewed in the front-rear direction X that is perpendicular to both directions. Therefore, it is possible to further suppress the liquid refrigerant LR in the refrigerant 19 flowing from the first elongated tube section 31b through the second elongated tube section 31c and into the third elongated tube section 31d from being biased in the left-right direction Y. Therefore, it is possible to further suppress the occurrence of unevenness in the amount of distributed refrigerant 19, and it is possible to further suppress a decrease in the heat exchange efficiency of the heat exchanger 13.

Further, according to the first embodiment, the length L1d of the third elongated tube portion 31d is 10 times or more the inner diameter Dd of the third elongated tube portion 31d. Therefore, the length L1d of the third stretched tube portion 31d can be suitably increased. As a result, even if the liquid refrigerant LR is biased in the left-right direction Y when flowing into the third extending tube portion 31d due to the refrigerant 19 flowing within the bent portion 33a, While the liquid refrigerant LR flows through the relatively long third elongated pipe portion 31d, it is easy to eliminate the deviation of the liquid refrigerant LR in the left-right direction Y within the third elongated pipe portion 31d. Specifically, since the frictional force that the liquid refrigerant LR receives when flowing along the inner wall portion is relatively large, the liquid refrigerant LR tries to flow toward the gaseous refrigerant GR with less frictional resistance, and gradually the gas The liquid refrigerant LR mixes with the liquid refrigerant GR again, and the imbalance of the liquid refrigerant LR is eliminated. Thereby, it is possible to suppress the refrigerant 19 from flowing into the second piping section 32 in a state where the liquid refrigerant LR and the gaseous refrigerant GR are separated in the left-right direction Y, and the refrigerant 19 distributed in the second piping section 32 can be suppressed. It is possible to more preferably suppress the occurrence of bias in the amount of . Therefore, it is possible to more preferably suppress a decrease in the heat exchange efficiency of the heat exchanger 13.

Note that in the refrigerant distributor 530 of the comparative example, the length L2d of the third elongated pipe portion 531d is smaller than ten times the inner diameter Dd of the third elongated pipe portion 531d, so the third elongated pipe portion 531d is short. Therefore, while the liquid refrigerant LR is flowing inside the third extended pipe portion 531d, it is difficult to eliminate the deviation of the liquid refrigerant LR in the left-right direction Y.

Further, according to the first embodiment, the first elongated tube portion 31b extends in the vertical direction Z. Therefore, the first elongated tube section 31b and the third elongated tube section 31d extend in the same direction. In the case of such a structure, the refrigerant 19 flowing into the third elongated tube section 31d from the inside of the first elongated tube section 31b through the inside of the second elongated tube section 31c is more susceptible to Therefore, when the liquid refrigerant LR is biased in the left-right direction Y due to inertia, the liquid refrigerant LR is more likely to be biased. On the other hand, according to the first embodiment, as described above, it is possible to suppress the liquid refrigerant LR from flowing into the second piping section 32 in a state where it is biased in the left-right direction Y. Even if the structure is such that the third elongated tube portion 31b and the third elongated tube portion 31d extend in the same direction, it is possible to suitably suppress the occurrence of unevenness in the amount of the refrigerant 19 to be distributed. Moreover, by having a structure in which the first elongated pipe portion 31b and the third elongated pipe portion 31d extend in the same direction, the structure of the refrigerant distributor 30 can be simplified and the manufacturing cost of the refrigerant distributor 30 can be reduced.

Further, according to the first embodiment, the bending angle θ1a of the second drawing tube portion 31c with respect to the first drawing tube portion 31b and the bending angle θ2a of the third drawing tube portion 31d with respect to the second drawing tube portion 31c are smaller than 0°. It is a large, acute angle less than 90°. Therefore, when the refrigerant 19 flows from the first elongated tube section 31b into the second elongated tube section 31c, and when the refrigerant 19 flows from the second elongated tube section 31c into the third elongated tube section 31d, the refrigerant 19 It is possible to suppress large changes in the direction of flow. Thereby, the loss that occurs when the refrigerant 19 flows through the first piping section 31 can be reduced, and the refrigerant 19 can be made to flow more easily into the refrigerant distributor 30.

Further, according to the first embodiment, the second direction intersecting the first direction in which the pair of parallel pipe portions 32a and 32b extend is the vertical direction Z. The third extended tube portion 31d is connected from below to a parallel tube portion 32b located on the lower side in the vertical direction Z of the pair of parallel tube portions 32a and 32b. Therefore, it is possible to prevent the amount of refrigerant 19 that branches and flows into each of the pair of parallel pipe portions 32a and 32b from becoming uneven due to gravity. Therefore, it is possible to more preferably suppress the occurrence of imbalance in the amount of the refrigerant 19 to be distributed, and it is possible to more preferably suppress the heat exchange efficiency of the heat exchanger 13 from decreasing.

Further, according to the first embodiment, the second piping section 32 has a U-shape that opens to one side in the left-right direction Y when viewed in the front-back direction X that is orthogonal to both the left-right direction Y and the vertical direction Z. Therefore, the connecting pipe portion 32c can be formed into an arc shape, and the refrigerant 19 can easily flow into the connecting pipe portion 32c. As a result, the refrigerant 19 that has collided with the inner wall of the parallel pipe section 32b and branched out, which has flowed into the connecting pipe section 32c, can suitably flow into the parallel pipe section 32a.

Further, according to the first embodiment, the first piping section 31 has a connecting tube section 31a that is connected to another member. The end of the connecting pipe portion 31 a that is connected to another member is the end of the first piping portion 31 that is opposite to the end that is connected to the second piping portion 32 . At least one bent portion 33a is formed between the connecting tube portion 31a and the first extending tube portion 31b. Therefore, the first piping section 31 can be easily extended and arranged in a desired direction while suitably connecting the connecting tube section 31a to other members.

Further, according to the first embodiment, the length L1b of the first elongated tube portion 31b is 10 times or more the inner diameter Db of the first elongated tube portion 31b. Therefore, even if the liquid refrigerant LR is biased in the left-right direction Y when flowing into the first elongated tube portion 31b due to the refrigerant 19 flowing within the bent portion 33a, the relatively long While the liquid refrigerant LR flows through the first elongated tube portion 31b, it is easy to eliminate the deviation of the liquid refrigerant LR in the left-right direction Y within the first elongated tube portion 31b.

In the first embodiment, when the length L1b of the first stretched tube section 31b is 10 times or more the inner diameter Db of the first stretched tube section 31b, the length L1d of the third stretched tube section 31d is the third stretched tube section 31b. It may be smaller than 10 times the inner diameter Dd of the tube portion 31d. Even in this case, even if the refrigerant 19 flows through the bent portions 33b and 33c after the imbalance of the liquid refrigerant LR caused by the bent portion 33a in the first extending tube portion 31b is eliminated, the liquid refrigerant LR remains Since the liquid refrigerant LR is less likely to be biased in the left-right direction Y, it is possible to suppress the liquid refrigerant LR from being biased in the left-right direction Y within the third extending pipe portion 31d. As described above, in the first embodiment, even if the length L1d of the third elongated tube section 31d cannot be sufficiently secured due to the arrangement relationship with other components, the length L1b of the first elongated tube section 31b is By making 10 times or more the inner diameter Db of the first stretched tube part 31b, the same effect as when the length L1d of the third stretched tube part 31d is made 10 times or more the inner diameter Dd of the third stretched tube part 31d can be obtained. can be obtained.

Embodiment 2.
FIG. 6 is a diagram showing a part of the refrigerant distributor 230 in the second embodiment as viewed in the left-right direction Y. Note that, in the following description, the same components as those in the embodiment described above may be given the same reference numerals as appropriate, and the description thereof may be omitted.

As shown in FIG. 6, in the first piping section 231 of the refrigerant distributor 230, the second extending tube section 231c extends rearward (in the -X direction) from the upper end of the first extending tube section 31b. In the second embodiment, the second elongated tube portion 231c extends linearly in a direction parallel to the front-rear direction X. The bending angle θ1b of the second drawing tube portion 231c with respect to the first drawing tube portion 31b and the bending angle θ2b of the third drawing tube portion 31d with respect to the second drawing tube portion 231c are 90°. The other configurations of refrigerant distributor 230 are similar to the other configurations of refrigerant distributor 30 of Embodiment 1.

Even when, as in the second embodiment, the bending angle θ1b of the second drawn tube portion 231c with respect to the first drawn tube portion 31b and the bending angle θ2b of the third drawn tube portion 31d with respect to the second drawn tube portion 231c are 90°, Loss that occurs when the refrigerant 19 flows inside the first piping section 231 can be reduced.

Embodiment 3.
FIG. 7 is a diagram showing a part of the refrigerant distributor 330 in the third embodiment as viewed in the left-right direction Y. Note that, in the following description, the same components as those in the embodiment described above may be given the same reference numerals as appropriate, and the description thereof may be omitted.

As shown in FIG. 7, in the first piping section 331 of the refrigerant distributor 330, the second extending tube section 331c extends rearward (-X side) and below from the upper end of the first extending tube section 31b. It is extending. The second elongated tube section 331c is located at the lower side as it goes toward the rear side from the upper end of the first elongated tube section 31b. The bending angle θ1c of the second drawing tube portion 331c with respect to the first drawing tube portion 31b and the bending angle θ2c of the third drawing tube portion 31d with respect to the second drawing tube portion 331c are obtuse angles larger than 90°. The other configurations of refrigerant distributor 330 are similar to the other configurations of refrigerant distributor 30 of the first embodiment.

Embodiment 4.
FIG. 8 is a diagram of a part of the refrigerant distributor 430 in the fourth embodiment as viewed in the front-rear direction X. FIG. 9 is a diagram of a part of the refrigerant distributor 430 in the fourth embodiment as viewed in the left-right direction Y. Note that, in the following description, the same components as those in the embodiment described above may be given the same reference numerals as appropriate, and the description thereof may be omitted.

As shown in FIG. 8, the first pipe section 431 in the refrigerant distributor 430 includes a first extended pipe section 31b, a second extended pipe section 431c, and a third extended pipe section 31d. The second elongated tube portion 431c is bent toward one side (−Y side) in the left-right direction Y, in which the pair of parallel tube portions 32a and 32b extend, with respect to the first elongated tube portion 31b. The second elongated tube section 431c is located at the upper side toward the left side from the upper end of the first elongated tube section 31b. The second elongated tube section 431c is similar to the second elongated tube section 31c of Embodiment 1, except that the direction of bending is different from the first elongated tube section 31b.

As shown in FIG. 9, a portion of the first piping section 431 including the first elongated tube section 31b, the second elongated tube section 431c, and the third elongated tube section 31d has a pair of parallel tube sections 32a and 32b. It has a shape that extends linearly in the vertical direction Z when viewed in the extending left-right direction Y. In the fourth embodiment, the portion of the first piping section 431 that includes the first elongated tube section 31b, the second elongated tube section 431c, and the third elongated tube section 31d refers to the first This is a portion between the lower end of the stretched tube section 31b and the upper end of the third stretched tube section 31d. The other configurations of refrigerant distributor 430 are similar to the other configurations of refrigerant distributor 30 of Embodiment 1.

As in Embodiment 4, the second elongated pipe portion 431c does not bend in the front-rear direction X with respect to the first elongated pipe portion 31b; Even in the case of bending in the direction Y, by making the length L1d of the third elongated pipe portion 31d at least 10 times the inner diameter Dd of the third elongated pipe portion 31d, the refrigerant 19 distributed by the refrigerant distributor 430 can be It is possible to suppress the amount of unevenness. Specifically, while the liquid refrigerant LR, which is biased in the left-right direction Y when flowing into the third elongated tube portion 31d by passing through the second elongated tube portion 531c, flows through the relatively long third elongated tube portion 31d. In addition, it mixes with the gaseous refrigerant GR, and the imbalance of the liquid refrigerant LR is easily eliminated. Therefore, unevenness in the amount of refrigerant 19 branched in the second piping section 32 is suppressed.

Although the embodiments of the present disclosure have been described above, the present disclosure is not limited to the configurations of each embodiment described above, and the following configurations and methods can also be adopted.

If the second stretched tube section is bent to one side in a direction perpendicular to both the first direction and the second direction, what is the length of the third stretched tube section? It may be of such length. As long as the length of the third stretched tube section is 10 times or more the inner diameter of the third stretched tube section, the first stretched tube section and the second stretched tube section may be bent in any way, and Each may extend in any way. The length of the first elongated tube section may be less than 10 times the inner diameter of the first elongated tube section.

In the present disclosure, "the second stretched tube part is bent to one side in a direction perpendicular to both the first direction and the second direction" means that the first stretched tube part As the second stretching tube part that extends bent from It may extend in a direction slightly inclined to the first direction with respect to a direction orthogonal to both the first direction and the second direction. Specifically, for example, in the above-described first embodiment, the second elongated tube section 31c is located upwardly from the upper end of the first elongated tube section 31b toward the rear side, and is located on either side of the left-right direction Y. It may extend in a direction that is located in either direction.

The bending angle of the second drawing tube section with respect to the first drawing tube section and the bending angle of the third drawing tube section with respect to the second drawing tube section are not particularly limited as long as they are larger than 0°. If the bending angle of the second drawn pipe part with respect to the first drawn pipe part and the bending angle of the third drawn pipe part with respect to the second drawn pipe part are greater than 0° and 90° or less, as described above, the refrigerant is It is possible to reduce the loss that occurs when flowing through the first piping section.

As long as the third extended pipe section is connected to one of the pair of parallel pipe sections in the second piping section, it may be connected to that one parallel pipe section in any way. The third extending pipe section may be connected to the parallel pipe section from above in the vertical direction Z. In the first piping part, two or more bent parts may be formed between the connecting pipe part and the first extension pipe part. The second piping part may have any shape as long as it has a pair of parallel pipe parts and a connecting pipe part that connects the ends of the pair of parallel pipe parts in the first direction.

The use of the refrigerant distributor according to the present disclosure is not particularly limited. A heat exchanger including a refrigerant distributor according to the present disclosure may be a heat exchanger of an indoor unit in a refrigeration cycle device. Both the indoor unit heat exchanger and the outdoor unit heat exchanger in the refrigeration cycle device may be heat exchangers equipped with the refrigerant distributor according to the present disclosure. The refrigeration cycle device equipped with the heat exchanger of the present disclosure may be any device that utilizes a refrigeration cycle in which a refrigerant circulates, and is not limited to an air conditioner. The refrigeration cycle device may be a heat pump water heater or the like.

The relative positional relationship and dimensions of each part described in each of the embodiments described above are merely examples, and the relative positional relationship and dimensions of each part in the present disclosure are not particularly limited as long as they are within the scope of the technical idea of the present disclosure. Not done. As mentioned above, each structure and each method explained in this specification can be combined as appropriate within a mutually consistent range.

13...Heat exchanger, 13a...Heat transfer tube (other members), 13b...Fin, 19...Refrigerant, 30,230,330,430,530...Refrigerant distributor, 31,231,331,431,531...First Piping section, 31a...Connection pipe section, 31b...First extension pipe section, 31c, 231c, 331c, 431c, 531c...Second extension pipe section, 31d, 531d...Third extension pipe section, 32...Second pipe section, 32a, 32b...Parallel pipe part, 32c...Connecting pipe part, 33a...Bending part, 100...Refrigerating cycle device, D...Inner diameter, L1b, L1d...Length, Y...Left-right direction (first direction), Z...Vertical direction (Second direction)

Claims (7)

A refrigerant distributor that is installed in a heat exchanger having a plurality of heat transfer tubes and distributes refrigerant,
a first piping section;
a second piping section connected to the first piping section;
Equipped with
The second piping section is
a pair of parallel pipe portions extending in a first direction and spaced apart in a second direction intersecting the first direction;
a connecting pipe section that connects one ends of the pair of parallel pipe sections in the first direction;
has
The first piping section is
a first elongated tube portion extending in the second direction;
a second elongated tube portion that extends in a bent manner from the first elongated tube portion;
a third extending tube portion that is bent from the second extending tube portion, extends in the second direction, and connects to one of the pair of parallel tube portions;
has
The second elongated tube portion is bent to one side in a direction perpendicular to both the first direction and the second direction, with respect to the first elongated tube portion,
The other end portions of the pair of parallel tube portions in the first direction are respectively connected to two different heat exchanger tubes,
The refrigerant distributor branches the refrigerant that has flowed into the first piping section into two flows in the second piping section, and distributes the refrigerant into the two heat transfer tubes. A portion of the first piping section including the first elongated pipe section, the second elongated pipe section, and the third elongated pipe section extends in a direction perpendicular to both the first direction and the second direction. The refrigerant distributor according to claim 1, having a shape extending linearly in the second direction when viewed. According to claim 1 , the bending angle of the second drawing tube section with respect to the first drawing tube section and the bending angle of the third drawing tube section with respect to the second drawing tube section are greater than 0° and less than or equal to 90°. Refrigerant distributor as described. The second direction is a vertical direction,
The refrigerant distributor according to claim 1 , wherein the third extending pipe section is connected from below to the parallel pipe section located on the lower side in the vertical direction of the pair of parallel pipe sections. The refrigerant distributor according to claim 1 , wherein the second piping section has a U-shape that opens to one side of the first direction when viewed in a direction perpendicular to both the first direction and the second direction. . A refrigerant distributor according to any one of claims 1 to 5 ,
multiple heat exchanger tubes;
a plurality of fins connected to the plurality of heat exchanger tubes;
A heat exchanger. A refrigeration cycle device comprising the heat exchanger according to claim 6 .

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