CN117545971A

CN117545971A - Refrigerant distributor, heat exchanger and refrigeration cycle device

Info

Publication number: CN117545971A
Application number: CN202180099717.4A
Authority: CN
Inventors: 高桥笃史; 前田刚志; 梁池悟
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2021-06-28
Filing date: 2021-06-28
Publication date: 2024-02-09
Also published as: WO2023275936A1; JP7486671B2; EP4365511A1; JPWO2023275936A1

Abstract

The refrigerant distributor is connected to the refrigerant piping and the plurality of heat transfer tubes, and distributes the refrigerant flowing from the refrigerant piping to the plurality of heat transfer tubes by flowing through a flow path formed in the refrigerant distributor, wherein the refrigerant distributor has a 1 st plate-like member, a 2 nd plate-like member, and a 3 rd plate-like member arranged side by side in the 1 st direction, the refrigerant piping is connected to the 1 st plate-like member, the plurality of heat transfer tubes are connected to the 3 rd plate-like member, and the 1 st plate-like member has: an inflow path formed so as to penetrate in the 1 st direction, through which the refrigerant flows from the refrigerant pipe; and a plurality of return flow paths for returning the refrigerant flowing from the side of the plate-like member 2 to flow, wherein the plate-like member 2 has a plurality of through-passages formed so as to pass through in the 1 st direction, the plate-like member 3 has a plurality of protruding portions protruding in a direction opposite to the plate-like member 2, the plurality of through-passages communicate with the inflow path or one of the plurality of return flow paths, and a space communicating with the plurality of through-passages is formed in each of the plurality of protruding portions.

Description

Refrigerant distributor, heat exchanger and refrigeration cycle device

Technical Field

The present disclosure relates to a refrigerant distributor that distributes refrigerant to a plurality of heat transfer tubes, a heat exchanger having the refrigerant distributor, and a refrigeration cycle apparatus having the heat exchanger.

Background

In recent years, in order to reduce the amount of refrigerant and to improve the performance of heat exchangers, the diameter of heat transfer tubes in heat exchangers used in air conditioning apparatuses has been reduced. In the case of reducing the diameter of the heat transfer pipe, it is necessary to suppress an increase in pressure loss when the refrigerant passes through the heat transfer pipe. Therefore, the number of branches of the heat exchanger, that is, the number of passages is increased.

In general, in order to increase the number of channels, a multi-branched refrigerant distributor is provided for distributing the refrigerant flowing from 1 inlet channel to a plurality of channels and supplying the refrigerant. In this case, in the heat exchanger, a compact refrigerant distributor capable of suppressing the flow deviation of the refrigerant to each passage is required in order to maintain the heat exchange performance. For example, patent document 1 discloses a refrigerant distributor in which a plate-like member having a through groove for branching a refrigerant into two parts and a plate-like member having a through hole for allowing a refrigerant to flow through the through groove are laminated as such a refrigerant distributor.

Prior art literature

Patent literature

Patent document 1: japanese patent No. 6782792

Disclosure of Invention

Problems to be solved by the invention

In the refrigerant distributor of patent document 1, in order to establish a through groove formed in a plate-like member as a flow path, the plate-like member in which the through groove is formed is sandwiched by other plate-like members. In the refrigerant distributor of patent document 1, there are 2 plate-like members in which only openings into which flat tubes are inserted are formed in order to ensure an insertion space for the flat tubes. As described above, in the refrigerant distributor of patent document 1, the number of plate-like members having no function of distributing refrigerant is large, resulting in an increase in size.

The present disclosure has been made to solve the above-described problems, and provides a small-sized refrigerant distributor, a heat exchanger, and a refrigeration cycle apparatus having the heat exchanger.

Means for solving the problems

The refrigerant distributor of the present disclosure is connected to a refrigerant pipe and a plurality of heat transfer pipes, and distributes a refrigerant flowing in from the refrigerant pipe to the plurality of heat transfer pipes by flowing through a flow path formed inside the refrigerant distributor, wherein the refrigerant distributor has a 1 st plate-like member, a 2 nd plate-like member, and a 3 rd plate-like member arranged side by side in a 1 st direction, the refrigerant pipe is connected to the 1 st plate-like member, the plurality of heat transfer pipes are connected to the 3 rd plate-like member, and the 1 st plate-like member has: an inflow path formed so as to penetrate in the 1 st direction, through which the refrigerant flows from the refrigerant pipe; and a plurality of return flow paths for returning the refrigerant flowing from the side of the plate-like member 2 to flow, wherein the plate-like member 2 has a plurality of through-passages formed so as to pass through in the 1 st direction, the plate-like member 3 has a plurality of protruding portions protruding in a direction opposite to the plate-like member 2, the plurality of through-passages communicate with the inflow path or one of the plurality of return flow paths, and a space communicating with the plurality of through-passages is formed in each of the plurality of protruding portions.

Effects of the invention

In the present disclosure, a part of the flow path is formed in a protruding portion of the 3 rd plate member connected to the flat tube. Thus, in the refrigerant distributor of the present disclosure, the plate-like member required to form a part of the flow path is reduced, and miniaturization is achieved.

Drawings

Fig. 1 is a circuit diagram showing a refrigeration cycle apparatus 1 according to embodiment 1.

Fig. 2 is a perspective view showing the indoor heat exchanger 7 according to embodiment 1.

Fig. 3 is a schematic diagram showing the refrigerant distributor 7b according to embodiment 1.

Fig. 4 is a perspective view showing the 1 st plate-like member 10 of embodiment 1.

Fig. 5 is a rear view showing the 3 rd plate member 30 of embodiment 1.

Fig. 6 is a perspective view showing the 3 rd plate member 30 of embodiment 1.

Fig. 7 is a cross-sectional view showing the 3 rd plate member 30 of embodiment 1.

Fig. 8 is a diagram for explaining a flow channel in embodiment 1.

Fig. 9 is a diagram for explaining a flow channel in embodiment 1.

Fig. 10 is a cross-sectional view showing a 3 rd plate member 30A according to modification 1 of embodiment 1.

Fig. 11 is a cross-sectional view showing a 3 rd plate member 30B according to modification 2 of embodiment 1.

Fig. 12 is a schematic diagram showing the refrigerant distributor 7Ab according to embodiment 2.

Fig. 13 is a perspective view showing the 3 rd plate member 30 according to embodiment 2.

Fig. 14 is a cross-sectional view showing the 3 rd plate member 30 of embodiment 2.

Fig. 15 is a diagram for explaining a flow channel in embodiment 2.

Fig. 16 is a schematic diagram showing the refrigerant distributor 7Bb of embodiment 3.

Fig. 17 is a perspective view showing the 3 rd plate member 30 according to embodiment 3.

Fig. 18 is a cross-sectional view showing the 3 rd plate member 30 of embodiment 3.

Fig. 19 is a diagram for explaining a flow channel in embodiment 3.

Fig. 20 is a schematic view showing the refrigerant distributor 7Cb according to embodiment 4.

Fig. 21 is a perspective view showing the 3 rd plate member 30 according to embodiment 4.

Fig. 22 is a cross-sectional view showing the 3 rd plate member 30 of embodiment 4.

Fig. 23 is a diagram for explaining a flow channel in embodiment 4.

Fig. 24 is a diagram for explaining a flow channel in embodiment 4.

Detailed Description

Embodiment 1

Next, a refrigeration cycle apparatus 1 having a refrigerant distributor according to embodiment 1 will be described with reference to the drawings. In the following description, the same reference numerals are used to designate the same or corresponding parts, and the embodiments described below are the same throughout. In the drawings, the relationship between the sizes of the respective components may be different from the actual ones. Further, the fine structure is appropriately simplified or omitted. The modes of the structural elements shown throughout the specification are merely examples, and are not limited to the modes described in the specification.

Fig. 1 is a circuit diagram showing a refrigeration cycle apparatus 1 according to embodiment 1. As shown in fig. 1, the refrigeration cycle apparatus 1 includes an outdoor unit 2, an indoor unit 3, and a refrigerant pipe 4. The outdoor unit 2 includes a compressor 5, a flow path switching valve 6, an expansion valve 8, an outdoor heat exchanger 9, and an outdoor blower 9a. The indoor unit 3 has an indoor heat exchanger 7 and an indoor blower 7a. The refrigerant pipe 4 is a pipe that connects the compressor 5, the flow path switching valve 6, the indoor heat exchanger 7, the expansion valve 8, and the outdoor heat exchanger 9, and through which the refrigerant flows. The refrigerant pipe 4 and each device connected to the refrigerant pipe 4 constitute a refrigerant circuit.

The compressor 5 sucks the low-temperature and low-pressure refrigerant, compresses the sucked refrigerant, and discharges the refrigerant into the high-temperature and high-pressure refrigerant. The flow path switching valve 6 switches the flow direction of the refrigerant in the refrigerant circuit, and is, for example, a four-way valve. The expansion valve 8 decompresses and expands the refrigerant, and is an electronic expansion valve, for example. The outdoor heat exchanger 9 exchanges heat between the refrigerant and the outdoor air, and is, for example, a fin-tube heat exchanger. The outdoor heat exchanger 9 functions as a condenser in the cooling operation and functions as an evaporator in the heating operation. The outdoor blower 9a is a device that sends outdoor air to the outdoor heat exchanger 9.

The indoor heat exchanger 7 exchanges heat between indoor air and a refrigerant. The indoor heat exchanger 7 functions as an evaporator in the cooling operation and functions as a condenser in the heating operation. The indoor blower 7a is a device that sends indoor air to the indoor heat exchanger 7, and is, for example, a cross flow fan.

The indoor heat exchanger 7 has a refrigerant distributor 7b. The refrigerant distributor 7b is provided on the inflow side of the flow of the refrigerant in the rich liquid phase state when the indoor heat exchanger 7 functions as an evaporator. The outdoor heat exchanger 9 has a refrigerant distributor 9b. The refrigerant distributor 9b is provided on the inflow side in the case where the outdoor heat exchanger 9 functions as an evaporator. The description of the refrigerant distributor 7b and the refrigerant distributor 9b will be described later.

(cooling operation)

Here, the operation of the refrigeration cycle apparatus 1 will be described. First, the cooling operation will be described. The refrigeration cycle device 1 performs a cooling operation by switching the flow path switching valve 6 to connect the discharge side of the compressor 5 to the outdoor heat exchanger 9. In the cooling operation, the refrigerant sucked into the compressor 5 is compressed by the compressor 5 and discharged in a high-temperature and high-pressure gas state. The high-temperature and high-pressure gas-state refrigerant discharged from the compressor 5 flows into the outdoor heat exchanger 9 functioning as a condenser through the flow path switching valve 6. The refrigerant flowing into the outdoor heat exchanger 9 exchanges heat with the outdoor air sent by the outdoor fan 9a, and condenses and liquefies. The liquid-state refrigerant flows into the expansion valve 8, is depressurized and expanded, and becomes a low-temperature and low-pressure refrigerant in a gas-liquid two-phase state. The refrigerant in the gas-liquid two-phase state flows into the indoor heat exchanger 7 functioning as an evaporator. The refrigerant flowing into the indoor heat exchanger 7 exchanges heat with the indoor air sent by the indoor blower 7a, and evaporates and gasifies. At this time, the indoor air is cooled, and indoor cooling is performed. The evaporated low-temperature low-pressure gas-state refrigerant is then sucked into the compressor 5 through the flow path switching valve 6.

(heating operation)

Next, the heating operation will be described. The refrigeration cycle device 1 performs a heating operation by switching the flow path switching valve 6 to connect the discharge side of the compressor 5 to the indoor heat exchanger 7. In the heating operation, the refrigerant sucked into the compressor 5 is compressed by the compressor 5 and discharged in a high-temperature and high-pressure gas state. The high-temperature and high-pressure gas-state refrigerant discharged from the compressor 5 flows into the indoor heat exchanger 7 functioning as a condenser through the flow path switching valve 6. The refrigerant flowing into the indoor heat exchanger 7 exchanges heat with the indoor air sent by the indoor blower 7a, and condenses and liquefies. At this time, the indoor air is heated, and heating of the room is performed. The liquid-state refrigerant flows into the expansion valve 8, is depressurized and expanded, and becomes a low-temperature and low-pressure refrigerant in a gas-liquid two-phase state. The refrigerant in the gas-liquid two-phase state flows into the outdoor heat exchanger 9 functioning as an evaporator. The refrigerant flowing into the outdoor heat exchanger 9 exchanges heat with the outdoor air sent by the outdoor fan 9a, and evaporates and gasifies. The evaporated low-temperature low-pressure gas-state refrigerant is then sucked into the compressor 5 through the flow path switching valve 6.

(indoor Heat exchanger 7)

Next, the structure of the heat exchanger will be described by taking the indoor heat exchanger 7 as an example. The outdoor heat exchanger 9 and the refrigerant distributor 9b of the outdoor heat exchanger 9 have the same configuration as the indoor heat exchanger 7 and the refrigerant distributor 9b of the indoor heat exchanger 7, and therefore, the description thereof is omitted. In addition, the present disclosure may be applied to only any one of the indoor heat exchanger 7 and the refrigerant distributor 9b and the outdoor heat exchanger 9 and the refrigerant distributor 9 b. Fig. 2 is a perspective view showing the indoor heat exchanger 7 according to embodiment 1. In fig. 2, the refrigerant distributor 7b side of the indoor heat exchanger 7 is shown enlarged. The indoor heat exchanger 7 has a refrigerant distributor 7b, a plurality of heat transfer tubes 50, and a gas header (not shown). As shown in fig. 2, the refrigerant piping 4 and the plurality of heat transfer pipes 50 of the refrigeration cycle apparatus 1 are connected to the refrigerant distributor 7 b. The refrigerant distributor 7b distributes the refrigerant flowing in from the refrigerant pipe 4 to the plurality of heat transfer pipes 50 by flowing through a flow path formed inside.

The heat transfer pipe 50 is, for example, a flat pipe or a round pipe in which a plurality of flow paths are formed. The heat transfer pipe 50 is formed of copper or aluminum, for example. The end of the heat transfer pipe 50 on the side of the refrigerant distributor 7b is inserted into the refrigerant distributor 7 b. In fig. 2, 8 heat transfer tubes 50 are shown, but the present invention is not limited to this.

The flow of the refrigerant in the indoor heat exchanger 7 according to embodiment 1 will be described. For example, when the indoor heat exchanger 7 functions as an evaporator, the refrigerant flowing through the refrigerant pipe 4 flows into the refrigerant distributor 7b, is distributed, and flows out to the plurality of heat transfer pipes 50. The refrigerant exchanges heat with the air or the like supplied by the indoor blower 7a in the plurality of heat transfer tubes 50. The refrigerant inflow gas headers flowing through the plurality of heat transfer tubes 50 are joined together and flow out to the refrigerant piping 4. When the indoor heat exchanger 7 functions as a condenser, the refrigerant flows in a direction opposite to the flow direction.

(refrigerant distributor 7 b)

Fig. 3 is a schematic diagram showing the refrigerant distributor 7b according to embodiment 1. In fig. 3, a state in which the refrigerant distributor 7b is deployed and arranged is shown. As shown in fig. 3, the refrigerant distributor 7b is formed by stacking, for example, a 1 st plate member 10, a 2 nd plate member 20, a 3 rd plate member 30, and a 4 th plate member 40, which are rectangular in shape. The 1 st plate member 10, the 2 nd plate member 20, the 4 th plate member 40, and the 3 rd plate member 30 are arranged side by side in this order in the X-axis direction of fig. 3. In the following description, the X-axis direction is referred to as the lamination direction. The lamination direction corresponds to the 1 st direction. The width direction of the refrigerant distributor 7b corresponding to the Y-axis direction in fig. 3 is simply referred to as the width direction. The arrangement direction of the plurality of heat transfer tubes 50 corresponding to the Z-axis direction of fig. 3 is simply referred to as an arrangement direction. The 1 st plate member 10, the 2 nd plate member 20, the 4 th plate member 40, and the 3 rd plate member 30 are integrally joined, for example, by brazing. The 1 st plate-like member 10, the 2 nd plate-like member 20, the 4 th plate-like member 40, and the 3 rd plate-like member 30 are processed by, for example, press working, cutting working, or the like.

Fig. 4 is a perspective view showing the 1 st plate-like member 10 of embodiment 1. The viewpoint of fig. 4 is located on the opposite side of fig. 3 in the stacking direction. As shown in fig. 3 and 4, the 1 st plate-like member 10 has 2 cross-layer protrusions 12a and 4 cross-layer protrusions 12b. The cross-layer protrusion 12a and the cross-layer protrusion 12b protrude in the direction opposite to the 2 nd plate-like member 20 in the stacking direction. The cross-layer protrusion 12a is formed so as to cross 2 heat transfer tubes 50 inserted into the refrigerant distributor 7b when viewed from the stacking direction. The cross-layer protrusion 12b is formed so as to cross 1 heat transfer pipe 50 inserted into the refrigerant distributor 7b when viewed from the stacking direction.

A return flow path 13a is formed inside each cross-layer protrusion 12 a. The return flow path 13a is a flow path for returning the refrigerant flowing from the through-passage 21b of the 2 nd plate member 20 to be described later to the through-passage 21c of the 2 nd plate member 20 to flow. A return flow path 13b is formed inside each cross-layer protrusion 12b. The return flow path 13b is a flow path for returning the refrigerant flowing from the through-passage 21d of the 2 nd plate member 20 to be described later to the through-passage 21e of the 2 nd plate member 20 to flow. The 1 st plate member 10 is formed with an inflow passage 11. The inflow path 11 is formed to penetrate the 1 st plate-like member 10 in the stacking direction. The 1 st plate member 10 is connected to the refrigerant pipe 4, and an internal space of the refrigerant pipe 4 communicates with the inflow path 11. The inflow path 11, the return path 13a, and the return path 13b constitute a path of the refrigerant distributor 7 b.

The 2 nd plate member 20 has a through-passage 21a, 2 through-passages 21b, 2 through-passages 21c, 4 through-passages 21d, and 4 through-passages 21e formed so as to pass through in the stacking direction. The through-passage 21a is substantially circular in shape when viewed from the stacking direction, and is formed substantially in the center of the 2 nd plate-like member 20. The through-passage 21a communicates with the inflow passage 11 of the 1 st plate member 10 and a 1 st communication passage 41a of a 4 th plate member 40 described later. Each through-passage 21b has a substantially circular shape when viewed from the stacking direction, and is formed adjacent to the through-passage 21a in the width direction. The through passages 21b communicate with the return flow passage 13a of the 1 st plate member 10 and a 1 st communication passage 41b of the 4 th plate member 40 described later. The through-passages 21c are formed in a substantially circular shape when viewed from the stacking direction, at positions substantially at the center in the width direction at equal intervals from the through-passages 21 a. The through-passages 21c communicate with the return flow passage 13a of the 1 st plate member 10 and a 1 st communication passage 41c of the 4 th plate member 40 described later.

Each through-passage 21d has a substantially circular shape when viewed from the stacking direction, and is formed adjacent to the through-passage 21c in the width direction. The through-passages 21d communicate with the return flow passage 13b of the 1 st plate member 10 and a 1 st communication passage 41d of the 4 th plate member 40 described later. Each of the through-passages 21e has a substantially circular shape when viewed from the stacking direction, and is formed alternately with the through-passages 21a and 2 through-passages 21c in the arrangement direction. The through-passages 21e are formed at equal intervals in the arrangement direction. Each through passage 21e communicates with the return passage 13b and a 2 nd communication passage 42 of a 4 nd plate member 40 described later. The through-passages 21a, 2 through-passages 21b, 2 through-passages 21c, 4 through-passages 21d, and 4 through-passages 21e constitute a flow path of the refrigerant distributor 7 b.

Fig. 5 is a rear view showing the 3 rd plate member 30 of embodiment 1. Fig. 6 is a perspective view showing the 3 rd plate member 30 of embodiment 1. The viewpoints of fig. 5 and 6 are located on the opposite side of fig. 3 in the stacking direction. As shown in fig. 3, 5 and 6, the 3 rd plate member 30 has 15 protruding portions 31 protruding in the opposite direction to the 2 nd plate member 20. Each of the protruding portions 31 protrudes substantially perpendicularly from the surface of the 3 rd plate member 30 on the opposite side from the 2 nd plate member 20. In which insertion openings 32 into which the heat transfer tubes 50 are inserted are formed at the end portions of the 8 protruding portions 31, respectively. As shown in fig. 3, a branch 34a is formed inside the other 1 protruding portion 31. A branch 34b is formed inside the other 2 protruding portions 31. A branched line 34c is formed inside the remaining 4 protruding portions 31. The protruding portions 31 formed with the insertion openings 32 are alternately provided with the protruding portions 31 formed with any one of the branch lines 34a, 34b, and 34c.

The protruding portion 31 having the branch line 34a formed therein is provided at substantially the center in the arrangement direction of the 3 rd plate member 30. The branch line 34a communicates the 1 st communication path 41a and the 1 st communication path 41b of the 4 th plate member 40. The respective protruding portions 31 formed with the branch lines 34b are disposed at equal intervals in the arrangement direction from the protruding portions 31 formed with the branch lines 34a. The branch line 34b communicates the 1 st communication passage 41c and the 1 st communication passage 41d of the 4 th plate member 40. Each of the protruding portions 31 formed with the branch lines 34c is alternately arranged with the protruding portion 31 formed with the branch line 34a and the 2 protruding portions 31 formed with the branch line 34b in the arrangement direction. The respective protruding portions 31 formed with the branch lines 34c are formed at equal intervals in the arrangement direction. Each branch 34c communicates a 1 st communication passage 41e and a 2 nd communication passage 42 of a 4 th plate member 40 described later.

Fig. 7 is a cross-sectional view showing the 3 rd plate member 30 of embodiment 1. Fig. 7 shows 3 protruding portions 31 located at the end portion on the +side in the arrangement direction of the 3 rd plate member 30 in an enlarged manner from a cross section cut at the center in the width direction of the refrigerant distributor 7b in the arrangement direction, i.e., the A-A cross section of fig. 5. As shown in fig. 3 and 7, an insertion space 33 is formed inside each of the protruding portions 31 formed with the insertion openings 32. The insertion space 33 also includes a space corresponding to the plate thickness of the 3 rd plate member 30. In other words, the insertion space 33 extends from the surface of the 3 rd plate member 30 on the 2 nd plate member 20 side to the downstream end surface inside the protruding portion 31 in the stacking direction. The end portions of the corresponding heat transfer tubes 50 are positioned in the insertion spaces 33. The branch lines 34a, 34b, and 34c also include spaces corresponding to the plate thickness of the 3 rd plate member 30. In other words, the branch line 34a, the branch line 34b, and the branch line 34c extend from the surface of the 3 rd plate member 30 on the 2 nd plate member 20 side to the end surface on the downstream side of the inside of the protruding portion 31 in the stacking direction. The insertion space 33, the branched path 34a, the branched path 34b, and the branched path 34c constitute a flow path of the refrigerant distributor 7 b.

As shown in fig. 3, the 4 th plate member 40 has 1 st communication passages 41a, 21 st communication passages 41b, 21 st communication passages 41c, 41 st communication passages 41d, 41 st communication passages 41e, and 8 2 nd communication passages 42 formed so as to penetrate in the stacking direction. The 1 st communication path 41a is formed in a substantially circular shape when viewed from the stacking direction, and is formed in a substantially center of the 2 nd plate-like member 20. The 1 st communication path 41a communicates with the through path 21a of the 2 nd plate member 20 and the branch path 34a of the 3 rd plate member 30. That is, the through passage 21a of the 2 nd plate member 20 and the branch passage 34a of the 3 rd plate member 30 communicate via the 1 st communication passage 41 a.

Each 1 st communication path 41b has a substantially circular shape when viewed from the stacking direction, and is formed adjacent to the 1 st communication path 41a in the width direction. The 1 st communication path 41b communicates with the through path 21b of the 2 nd plate member 20 and the branch path 34a of the 3 rd plate member 30. That is, the through passage 21b of the 2 nd plate member 20 and the branch passage 34a of the 3 rd plate member 30 communicate via the 1 st communication passage 41 b. Each 1 st communication path 41c has a substantially circular shape when viewed from the stacking direction, and is formed at a substantially central position in the width direction at equal intervals from the 1 st communication path 41 a. The 1 st communication path 41c communicates with the through path 21c of the 2 nd plate member 20 and the branch path 34b of the 3 rd plate member 30. That is, the through passage 21c of the 2 nd plate member 20 and the branch passage 34b of the 3 rd plate member 30 communicate via the 1 st communication passage 41 c.

Each 1 st communication path 41d has a substantially circular shape when viewed from the stacking direction, and is formed adjacent to the 1 st communication path 41c in the width direction. The 1 st communication path 41d communicates with the through path 21d of the 2 nd plate member 20 and the branch path 34b of the 3 rd plate member 30. That is, the through passage 21d of the 2 nd plate member 20 and the branch passage 34b of the 3 rd plate member 30 communicate via the 1 st communication passage 41 d. Each 1 st communication passage 41e has a substantially circular shape when viewed from the stacking direction, and is formed alternately with the 1 st communication passage 41a and 21 st communication passages 41c in the arrangement direction. The 1 st communication passages 41e are formed at equal intervals in the arrangement direction. The 1 st communication path 41e communicates with the through path 21e of the 2 nd plate member 20 and the branch path 34c of the 3 rd plate member 30. That is, the through passage 21e of the 2 nd plate member 20 and the branch passage 34c of the 3 rd plate member 30 communicate via the 1 st communication passage 41e.

Each of the 2 nd communication passages 42 is formed in a substantially L-shape as viewed from the stacking direction so as to surround the 1 st communication passage 41e. Each of the 2 nd communication passages 42 communicates with the branch passage 34c of the 3 rd plate member 30 and the insertion space 33. That is, the branch line 34c of the 3 rd plate member 30 and the insertion space 33 of the 3 rd plate member 30 communicate via the 2 nd communication path 42. Accordingly, the through passage 21e of the 2 nd plate member 20 and the insertion space 33 of the 3 rd plate member 30 communicate via the 1 st communication passage 41e, the branch passage 34c of the 3 rd plate member 30, and the 2 nd communication passage 42. The 1 st communication path 41a, 21 st communication paths 41b, 21 st communication paths 41c, 41 st communication paths 41d, 41 st communication paths 41e, and 8 2 nd communication paths 42 constitute the flow paths of the refrigerant distributor 7 b.

(flow of refrigerant in refrigerant distributor 7 b)

Fig. 8 is a diagram for explaining a flow channel in embodiment 1. Fig. 9 is a diagram for explaining a flow channel in embodiment 1. The flow path shown in fig. 9 is subsequent to the flow path shown in fig. 8. The flow path according to embodiment 1 will be described with reference to fig. 8 and 9. Here, all the branches of the flow path are not described, and 1 branch of the plurality of branches of the flow path from which the refrigerant flowing in from the refrigerant pipe 4 flows out to 1 heat transfer pipe 50 is represented. First, as shown in fig. 8, the refrigerant flowing in from the refrigerant pipe 4 linearly advances through the inflow passage 11 of the 1 st plate member 10, the through passage 21a of the 2 nd plate member 20, and the 1 st communication passage 41a of the 4 th plate member 40, and reaches the branch passage 34a of the 3 rd plate member 30. The refrigerant reaching the branch line 34a of the 3 rd plate member 30 is branched and returned toward the 4 th plate member 40. The one of the branched refrigerants passes through the 1 st communication passage 41b of the 4 th plate member 40 and the through passage 21b of the 2 nd plate member 20, reaches the return passage 13a of the 1 st plate member 10, and returns toward the 2 nd plate member 20.

Next, as shown in fig. 9, the refrigerant after the folding-back passes through the through-passage 21c of the 2 nd plate member 20 and the 1 st communication passage 41c of the 4 th plate member 40, and reaches the branch 34b of the 3 rd plate member 30. The refrigerant reaching the branch line 34b of the 3 rd plate member 30 is branched and returned toward the 4 th plate member 40. The one of the branched refrigerants passes through the 1 st communication passage 41d of the 4 th plate member 40 and the through passage 21d of the 2 nd plate member 20, reaches the return passage 13b of the 1 st plate member 10, and returns toward the 2 nd plate member 20.

The refrigerant after the return passes through the through-passage 21e of the 2 nd plate member 20 and the 1 st communication passage 41e of the 4 th plate member 40, and reaches the branch 34c of the 3 rd plate member 30. The refrigerant reaching the branch line 34c of the 3 rd plate member 30 is branched and returned toward the 4 th plate member 40. The one of the branched refrigerants passes through the 2 nd communication passage 42 of the 4 rd plate member 40, and is folded back toward the 3 rd plate member 30. The refrigerant after the return reaches the insertion space 33 of the 3 rd plate member 30, and flows out to 1 heat transfer pipe 50.

In embodiment 1, the insertion space 33, the branch line 34a, the branch line 34b, and the branch line 34c, that is, a part of the flow path, are formed in the protruding portion 31 of the 3 rd plate member 30 connected to the heat transfer pipe 50. As a result, the refrigerant distributor 7b according to embodiment 1 reduces the number of plate-like members required to form a part of the flow path, thereby achieving downsizing.

In general, in order to smoothly flow the refrigerant into the heat transfer pipe 50 in the insertion space 33, a predetermined width is required to prevent the refrigerant from remaining. When the insertion space 33 is formed in the plate-like member, the thickness, width, and the like of the entire plate-like member need to be increased in order to satisfy the required width. Here, in embodiment 1, an insertion space 33 is formed in the protruding portion 31 of the 3 rd plate member. Therefore, when securing the width of the insertion space 33, it is not necessary to increase the portion that does not contribute to the formation of the insertion space 33. Therefore, the refrigerant distributor 7b according to embodiment 1 can be miniaturized.

Similarly, the branches 34a, 34b, and 34c are required to have a predetermined width so that the refrigerant is not retained in order to smoothly branch the flow. In embodiment 1, the branch line 34a, the branch line 34b, and the branch line 34c are formed in the protruding portion 31 of the 3 rd plate member. Therefore, when the widths of the branch lines 34a, 34b, and 34c are ensured, it is not necessary to increase the portion that does not contribute to the formation of the insertion space 33. Therefore, the refrigerant distributor 7b according to embodiment 1 can be miniaturized.

Further, the refrigerant distributor 7b is miniaturized, and thus, in the indoor heat exchanger 7, the installation area of the heat transfer pipe 50 is ensured, and the heat exchange performance can be improved. Further, the refrigerant distributor 7b and the indoor heat exchanger 7 can be made lightweight.

In the refrigerant distributor 7b, the number of plate-like members required to form a part of the flow path is reduced, thereby simplifying the manufacturing process and reducing the manufacturing cost.

In embodiment 1, the folded-back flow path 13a and the folded-back flow path 13b, that is, part of the flow path, are formed in the cross-layer protruding portion 12a and the cross-layer protruding portion 12b of the 1 st plate-like member 10. As a result, the refrigerant distributor 7b according to embodiment 1 reduces the number of plate-like members required to form a part of the flow path, thereby achieving downsizing.

Further, by forming the return flow path 13a or the return flow path 13b in the 1 st plate member 10, the refrigerant reciprocating between the 1 st plate member 10 and the 3 rd plate member 30 can be circulated again to the 3 rd plate member 30 side. This allows the flow to be performed multiple times through the same plate-like member, thereby reducing the number of plate-like members required.

Modification 1

Fig. 10 is a cross-sectional view showing a 3 rd plate member 30A according to modification 1 of embodiment 1. Fig. 10 shows, in an enlarged manner, 3 protruding portions 31 located at the end portion on the +side in the arrangement direction of the 3 rd plate member 30A from a section corresponding to the section A-A of fig. 5 in the 3 rd plate member 30A. As shown in fig. 10, the downstream side of the inside of each protruding portion 31 is formed in an arc shape. The protruding portions 31 are formed such that the dimension in the arrangement direction decreases toward the distal end portion. In addition, as in embodiment 1, the protruding portion 31 may protrude substantially perpendicularly from the surface of the 3 rd plate member 30A on the opposite side from the 2 nd plate member 20.

By forming the downstream side of the inside of the protruding portion 31 in the circular arc shape, it is possible to avoid the refrigerant flowing through the flow path of the refrigerant distributor 7b from concentrating at one point on the downstream side of the inside of the protruding portion 31. Accordingly, the pressure resistance of the 3 rd plate member 30A is improved, and therefore, the thickness of the thin plate can be reduced, and the manufacturing cost can be reduced.

Modification 2

Fig. 11 is a cross-sectional view showing a 3 rd plate member 30B according to modification 2 of embodiment 1. Fig. 11 shows, in an enlarged manner, 3 protruding portions 31 located at the end portion on the +side in the arrangement direction of the 3 rd plate member 30B from a section corresponding to the section A-A of fig. 5 in the 3 rd plate member 30B. As shown in fig. 11, the portion of the 3 rd plate member 30B facing the protruding portion 31 on the 2 nd plate member 20 side is formed in a wedge shape. The protruding portions 31 are formed such that the dimension in the arrangement direction decreases toward the distal end portion.

The 3 rd plate member 30B has a wedge shape, and thus, rapid expansion of the flow path is suppressed immediately before flowing into the heat transfer pipe 50. This reduces the pressure loss, and improves the heat exchange performance of the indoor heat exchanger 7.

Embodiment 2

Fig. 12 is a schematic diagram showing the refrigerant distributor 7Ab according to embodiment 2. Embodiment 2 differs from embodiment 1 in that the 4 th plate member 40 is omitted, and the insertion space 33 of the 3 rd plate member 30 and the branch line 34c are formed to communicate with each other. The 1 st plate-like member 10 and the 2 nd plate-like member 20 have the same shape as the 1 st plate-like member 10 and the 2 nd plate-like member 20 of embodiment 1. In the following description, the same reference numerals are given to the portions common to embodiment 1, and detailed description thereof is omitted.

The flow path of the refrigerant distributor 7Ab will be mainly described with respect to the differences from embodiment 1. The through passages 21a communicate with the inflow passage 11 of the 1 st plate member 10 and the branch passage 34a of the 3 rd plate member 30. Each through passage 21b communicates with the return passage 13a of the 1 st plate member 10 and the branch passage 34a of the 3 rd plate member 30. Each through passage 21c communicates with the return passage 13a of the 1 st plate member 10 and the branch passage 34b of the 3 rd plate member 30. Each through passage 21d communicates with the return flow path 13b of the 1 st plate member 10 and the branch path 34b of the 3 rd plate member 30. Each through passage 21e communicates with the return passage 13b of the 1 st plate member 10 and the branch passage 34c of the 3 rd plate member 30.

Fig. 13 is a perspective view showing the 3 rd plate member 30 according to embodiment 2. The viewpoint of fig. 13 is located on the opposite side of fig. 12 in the stacking direction. As shown in fig. 12 and 13, in the 3 rd plate member 30, 2 protruding portions 31 formed with the insertion space 33 and the protruding portion 31 formed with the branched line 34c are integrally formed. Further, 2 insertion spaces 33 communicate with the branched path 34 c.

Fig. 14 is a cross-sectional view showing the 3 rd plate member 30 of embodiment 2. Fig. 14 shows 3 protruding portions 31 located at the end portions on the +side in the arrangement direction of the 3 rd plate member 30 in an enlarged manner from a cross section cut at the center in the width direction of the refrigerant distributor 7Ab in the arrangement direction, that is, a cross section corresponding to the A-A cross section in fig. 5 in the refrigerant distributor 7 Ab. As shown in fig. 14, as in embodiment 1, the insertion space 33 and the branch line 34c extend in the stacking direction from the surface of the 3 rd plate member 30 on the 2 nd plate member 20 side to the end surface on the downstream side of the inside of the protruding portion 31. In embodiment 2, the insertion space 33, the branch line 34a, the branch line 34b, and the branch line 34c also constitute a flow path of the refrigerant distributor 7 Ab.

(flow of refrigerant in refrigerant Dispenser 7 Ab)

Fig. 15 is a diagram for explaining a flow channel in embodiment 2. The flow path according to embodiment 2 will be described with reference to fig. 15. Here, all the branches of the flow path are not described, and 1 branch of the plurality of branches of the flow path from which the refrigerant flowing in from the refrigerant pipe 4 flows out to 1 heat transfer pipe 50 is represented. First, as shown in fig. 15, the refrigerant flowing in from the refrigerant pipe 4 passes through the inflow passage 11 of the 1 st plate member 10 and the through passage 21a of the 2 nd plate member 20, and reaches the branch passage 34a of the 3 rd plate member 30. The refrigerant reaching the branch line 34a of the 3 rd plate member 30 is branched and returned toward the 2 nd plate member 20. The one of the branched refrigerants passes through the through-passage 21b of the 2 nd plate member 20, reaches the return flow path 13a of the 1 st plate member 10, and returns toward the 2 nd plate member 20.

Then, the refrigerant after the return passes through the through-passage 21c of the 2 nd plate member 20, and reaches the branch line 34b of the 3 rd plate member 30. The refrigerant reaching the branch line 34b of the 3 rd plate member 30 is branched and returned toward the 2 nd plate member 20. The one of the branched refrigerants passes through the through-passage 21d of the 2 nd plate member 20, reaches the return flow path 13b of the 1 st plate member 10, and returns toward the 2 nd plate member 20.

Then, the refrigerant after the return passes through the through-passage 21e of the 2 nd plate member 20, and reaches the branch line 34c of the 3 rd plate member 30. The refrigerant reaching the branch line 34c of the 3 rd plate member 30 is branched into the insertion space 33 of the 3 rd plate member 30. The split refrigerant flows out to 1 heat transfer pipe 50.

In embodiment 2, the insertion space 33, the branch line 34a, the branch line 34b, and the branch line 34c, that is, a part of the flow path, are formed in the protruding portion 31 of the 3 rd plate member 30 connected to the heat transfer pipe 50. As a result, the refrigerant distributor 7Ab according to embodiment 2 reduces the number of plate-like members required to form a part of the flow path, thereby achieving downsizing.

In embodiment 2, in the 3 rd plate member 30, 2 protruding portions 31 in which the insertion space 33 is formed and the protruding portion 31 in which the branched path 34c is formed are integrally formed. Thereby, the function of dividing the refrigerant is concentrated on the 3 rd plate member 30. As a result, the refrigerant distributor 7Ab can omit another plate-like member for diverting the refrigerant, thereby further achieving downsizing.

Embodiment 3

Fig. 16 is a schematic diagram showing the refrigerant distributor 7Bb of embodiment 3. As shown in fig. 16, embodiment 3 is different from embodiment 1 in that the protruding portion 31 in which the branch line 34a, the branch line 34b, or the branch line 34c is formed is omitted, and the insertion space 33 is formed in the entire protruding portion 31. The 1 st plate-like member 10 and the 2 nd plate-like member 20 have the same shape as the 1 st plate-like member 10 and the 2 nd plate-like member 20 of embodiment 1. In the following description, the same reference numerals are given to the portions common to embodiment 1, and detailed description thereof is omitted.

The flow path of the refrigerant distributor 7Bb will be mainly described with respect to the differences from embodiment 1. The through passages 21a communicate with the inflow passage 11 of the 1 st plate member 10 and a 1 st sub-branch passage 43a of the 4 th plate member 40 described later. The through passages 21b communicate with the return flow path 13a of the 1 st plate member 10 and the 1 st sub-branch path 43a of the 4 th plate member 40. The through passages 21c communicate with the return flow passage 13a of the 1 st plate member 10 and a 1 st sub-branch passage 43b of the 4 th plate member 40 described later. The through-passages 21d communicate with the return flow path 13b of the 1 st plate member 10 and the 1 st sub-branch path 43b of the 4 th plate member 40. The through passages 21e communicate with the return flow path 13b of the 1 st plate member 10 and a 2 nd sub-branch 44 of the 4 th plate member 40 described later.

Fig. 17 is a perspective view showing the 3 rd plate member 30 according to embodiment 3. The viewpoint of fig. 17 is located on the opposite side of fig. 16 in the stacking direction. As shown in fig. 16 and 17, the 3 rd plate member 30 has 8 protruding portions 31 protruding in the opposite direction to the 2 nd plate member 20. An insertion opening 32 into which the heat transfer pipe 50 is inserted is formed at the end portions of the 8 protruding portions 31.

Fig. 18 is a cross-sectional view showing the 3 rd plate member 30 of embodiment 3. Fig. 18 shows 2 protruding portions 31 located at the end portion on the +side in the arrangement direction of the 3 rd plate member 30 in an enlarged manner from a cross section cut at the center in the width direction of the refrigerant distributor 7Bb in the arrangement direction, that is, a cross section corresponding to the A-A cross section in fig. 5 in the refrigerant distributor 7 Bb. As shown in fig. 16 and 18, an insertion space 33 is formed inside each of the protruding portions 31 in which the insertion opening 32 is formed. The insertion space 33 also includes a space corresponding to the plate thickness of the 3 rd plate member 30. In other words, the insertion space 33 extends from the surface of the 3 rd plate member 30 on the 2 nd plate member 20 side to the downstream end surface inside the protruding portion 31 in the stacking direction. The end portions of the corresponding heat transfer tubes 50 are positioned in the insertion spaces 33. Further, the downstream side of the inside of the protruding portion 31 is formed in an arc shape. The protruding portions 31 are formed such that the size in the arrangement direction becomes smaller toward the end portions. In embodiment 3, the insertion space 33 also constitutes a flow path of the refrigerant distributor 7 Bb.

As shown in fig. 16, the 4 th plate member 40 has a 1 st sub-branch 43a, 2 nd sub-branches 44, and 4 nd sub-branches 44 formed so as to penetrate in the stacking direction. The 1 st sub-branch 43a is formed in a straight line shape when viewed from the stacking direction, and is formed in the substantially center of the 2 nd plate-like member 20. The 1 st sub branch line 43a communicates with the through passage 21a of the 2 nd plate member 20 and the 2 nd through passages 21b of the 2 nd plate member 20. Each 1 st sub-branch 43b has a linear shape when viewed from the stacking direction, and is formed at a position equally spaced from the 1 st sub-branch 43 a. Each 1 st sub-branch 43b communicates with the through passage 21c of the 2 nd plate member 20 and the 2 nd through passages 21d of the 2 nd plate member 20.

Each of the 2 nd sub-branches 44 has a substantially S-shape when viewed from the-side direction and the +side in the stacking direction, and is formed alternately with the 1 st sub-branch 43a and the 21 st sub-branches 43b in the arrangement direction. The respective 2 nd subsidiary branch lines 44 are formed at equal intervals in the arrangement direction. Each of the 2 nd sub-branches 44 communicates with the through passage 21e of the 2 nd plate member 20 and the 2 nd insertion spaces 33 of the 3 rd plate member 30. The 1 st sub-branch 43a, 2 nd sub-branches 44, and 4 nd sub-branches 44 constitute flow paths of the refrigerant distributor 7 Bb.

(flow of refrigerant in refrigerant distributor 7 Bb)

Fig. 19 is a diagram for explaining a flow channel in embodiment 3. Here, all the branches of the flow path are not described, and 1 branch of the plurality of branches of the flow path from which the refrigerant flowing in from the refrigerant pipe 4 flows out to 1 heat transfer pipe 50 is represented. First, as shown in fig. 19, the refrigerant flowing in from the refrigerant pipe 4 passes through the inflow passage 11 of the 1 st plate member 10 and the through passage 21a of the 2 nd plate member 20, and reaches the 1 st sub-branching passage 43a of the 4 th plate member 40. The refrigerant reaching the 1 st sub-branch 43a of the 4 th plate member 40 is branched and returned toward the 2 nd plate member 20. The one of the branched refrigerants passes through the through-passage 21b of the 2 nd plate member 20, reaches the return flow path 13a of the 1 st plate member 10, and returns toward the 2 nd plate member 20.

Then, the refrigerant after the return passes through the through-passage 21c of the 2 nd plate member 20, and reaches the 1 st sub-branch 43b of the 4 th plate member 40. The refrigerant reaching the 1 st sub-branch 43b of the 4 th plate member 40 is branched and returned toward the 2 nd plate member 20. The one of the branched refrigerants passes through the through-passage 21d of the 2 nd plate member 20, reaches the return flow path 13b of the 1 st plate member 10, and returns toward the 2 nd plate member 20.

Then, the refrigerant after the return passes through the through-passage 21e of the 2 nd plate member 20, and reaches the 2 nd sub-branch 44 of the 4 th plate member 40. The refrigerant reaching the 2 nd sub-branch 44 of the 4 th plate member 40 is branched to the 2 nd insertion spaces 33 of the 3 rd plate member 30. The split refrigerant flows out to 1 heat transfer pipe 50.

In embodiment 3, the insertion space 33, that is, a part of the flow path is formed in the protruding portion 31 of the 3 rd plate member 30 connected to the heat transfer pipe 50. As a result, in embodiment 3, the plate-like member required to form a part of the flow path is also reduced in the refrigerant distributor 7Bb, and miniaturization is achieved.

Embodiment 4

Fig. 20 is a schematic view showing the refrigerant distributor 7Cb according to embodiment 4. As shown in fig. 20, embodiment 4 is different from embodiment 1 in that the protruding portion 31 in which the insertion space 33 is formed is omitted, and any one of the branch lines 34a, 34b, and 34c is formed in the entire protruding portion 31. The 1 st plate-like member 10, the 2 nd plate-like member 20, and the 4 th plate-like member 40 are the same shape as the 1 st plate-like member 10, the 2 nd plate-like member 20, and the 4 th plate-like member 40 of embodiment 1. In the following description, the same reference numerals are given to the portions common to embodiment 1, and detailed description thereof is omitted.

The flow path of the refrigerant distributor 7Cb will be mainly described with respect to the differences from embodiment 1. Fig. 21 is a perspective view showing the 3 rd plate member 30 according to embodiment 4. The viewpoint of fig. 21 is located on the opposite side of fig. 20 in the stacking direction. As shown in fig. 20 and 21, the 3 rd plate member 30 has 7 protruding portions 31 protruding in the opposite direction to the 2 nd plate member 20. A branched path 34a is formed inside the 1 protruding portion 31. A branch 34b is formed inside the other 2 protruding portions 31. A branched line 34c is formed inside the remaining 4 protruding portions 31. Further, 8 insertion openings 32 are formed alternately with the protruding portion 31 in which any one of the branch lines 34a, 34b, and 34c is formed.

The formation position of the protruding portion 31 formed with the branch 34a, the branch 34b, or the branch 34c is the same as that of embodiment 1. The flow path from the inflow path 11 of the 1 st plate member 10 to the 2 nd communication path 42 of the 4 th plate member 40 is also the same as in embodiment 1. In embodiment 4, the branch line 34a, the branch line 34b, and the branch line 34c also constitute a flow path of the refrigerant distributor 7 Cb.

In embodiment 4, the insertion opening 32 is formed in the planar portion of the 3 rd plate member 30. Accordingly, the 2 nd communication passage 42 of the 4 th plate member 40 communicates with the branch passage 34c of the 3 rd plate member 30 and the insertion opening 32 of the 3 rd plate member 30.

Fig. 22 is a cross-sectional view showing the 3 rd plate member 30 of embodiment 4. Fig. 22 shows 3 protruding portions 31 located at the end portions on the +side in the arrangement direction of the 3 rd plate member 30 in an enlarged manner from a cross section cut at the center in the width direction of the refrigerant distributor 7Cb in the arrangement direction, that is, a cross section corresponding to the A-A cross section in fig. 5 in the refrigerant distributor 7 Cb. As shown in fig. 22, the downstream side of the inside of the protruding portion 31 is formed in an arc shape. The protruding portions 31 are formed such that the size in the arrangement direction becomes smaller toward the end portions. In fig. 22, the 4 th plate member 40 is omitted, but the end of the heat transfer tube 50 inserted into the refrigerant distributor 7Cb is located in the 2 nd communication path 42 through the insertion opening 32.

(flow of refrigerant in refrigerant Dispenser 7 Cb)

Fig. 23 is a diagram for explaining a flow channel in embodiment 4. Fig. 24 is a diagram for explaining a flow channel in embodiment 1. The flow path shown in fig. 24 is subsequent to the flow path shown in fig. 23. The flow path according to embodiment 4 will be described with reference to fig. 23 and 24. As described above, the flow path from the inflow path 11 of the 1 st plate-like member 10 to the 2 nd communication path 42 of the 4 th plate-like member 40 is the same as that of embodiment 1, and therefore omitted. As shown in fig. 24, the refrigerant passing through the 2 nd communication passage 42 of the 4 th plate member 40 flows out to 1 heat transfer tube 50 inserted into the insertion opening 32.

In embodiment 4, the branch line 34a, the branch line 34b, and the branch line 34c, that is, a part of the flow path, are formed in the protruding portion 31 of the 3 rd plate member 30 connected to the heat transfer pipe 50. As a result, in embodiment 4, the plate-like members required to form a part of the flow path are also reduced in the refrigerant distributor 7Cb, and the size is reduced.

Although embodiments 1 to 4 have been described above, the present disclosure is not limited to embodiments 1 to 4 described above, and various modifications and applications can be made without departing from the gist of the present disclosure. For example, the indoor heat exchanger 7 or the outdoor heat exchanger 9 may have a plurality of fins joined to the heat transfer pipe 50. The fins are formed of, for example, aluminum.

In embodiments 1 to 4, the refrigerant distributor 7b formed in 8 branches is described, but the present invention is not limited thereto, and the number of branches can be changed to other numbers by changing the number of branches.

In embodiments 1 to 4, the following will be described: in the 1 st plate-like member 10, the return flow path 13a is provided inside the cross-layer protruding portion 12a, and the return flow path 13b is provided inside the cross-layer protruding portion 12 b. However, the return flow paths 13a and 13b may be formed as grooves penetrating the 1 st plate-like member 10 and closed by other plate-like members, thereby establishing a flow path. The return flow paths 13a and 13b may be formed as grooves having a depth smaller than the plate thickness of the 1 st plate member 10. According to these cases, the refrigerant distributor 7b can be miniaturized by forming a part of the flow path in the protruding portion 31 of the 3 rd plate member 30.

In embodiment 2, modification 1 of embodiment 1 may be combined, and the inside of the protruding portion 31 may be formed in a circular arc shape on the downstream side. In addition, modification 2 of embodiment 1 may be combined, and in the 3 rd plate member 30, a wedge shape may be formed on the surface of the 2 nd plate member 20 side.

Description of the reference numerals

1: a refrigeration cycle device; 2: an outdoor unit; 3: an indoor unit; 4: refrigerant piping; 5: a compressor; 6: a flow path switching valve; 7: an indoor heat exchanger; 7b: a refrigerant distributor; 7Ab: a refrigerant distributor; 7Bb: a refrigerant distributor; 7Cb: a refrigerant distributor; 7a: an indoor blower; 8: an expansion valve; 9: an outdoor heat exchanger; 9a: an outdoor blower; 9b: a refrigerant distributor; 10: a 1 st plate-like member; 11: an inflow path; 12a: a cross-layer protrusion; 12b: a cross-layer protrusion; 13a: a return flow path; 13b: a return flow path; 20: a 2 nd plate-like member; 21a: a through passage; 21b: a through passage; 21c: a through passage; 21d: a through passage; 21e: a through passage; 30: 3 rd plate-like member; 30A: 3 rd plate-like member; 30B: 3 rd plate-like member; 31: a protruding portion; 32: an insertion opening; 33: an insertion space; 34a: branching; 34b: branching; 34c: branching; 40: a 4 th plate-like member; 41a: a 1 st communication path; 41b: a 1 st communication path; 41c: a 1 st communication path; 41d: a 1 st communication path; 41e: a 1 st communication path; 42: a 2 nd communication path; 43a: a 1 st sub-branch; 43b: a 1 st sub-branch; 44: a 2 nd branch circuit; 50: a heat transfer tube.

Claims

1. A refrigerant distributor connected to a refrigerant pipe and a plurality of heat transfer pipes, wherein the refrigerant flowing in from the refrigerant pipe flows through a flow path formed in the refrigerant distributor and is distributed to the plurality of heat transfer pipes,

the refrigerant distributor has a 1 st plate-like member, a 2 nd plate-like member, and a 3 rd plate-like member arranged side by side in the 1 st direction, the refrigerant piping is connected to the 1 st plate-like member, the plurality of heat transfer pipes are connected to the 3 rd plate-like member,

the 1 st plate-like member has:

an inflow path formed so as to penetrate in the 1 st direction, through which the refrigerant flows from the refrigerant pipe; and

a plurality of return flow paths for returning the refrigerant flowing from the side of the 2 nd plate-like member to flow,

the 2 nd plate-like member has a plurality of through-passages formed therethrough in the 1 st direction,

the 3 rd plate member has a plurality of protruding portions protruding in a direction opposite to the 2 nd plate member,

the plurality of through passages communicate with the inflow passage or one of the plurality of return passages,

spaces communicating with the plurality of through passages are formed in the respective protruding portions.

2. The refrigerant distributor according to claim 1, wherein,

the refrigerant distributor further has a 4 th plate-like member provided between the 2 nd plate-like member and the 3 rd plate-like member,

at least 2 of the plurality of protruding portions are respectively formed with insertion openings into which 1 of the plurality of heat transfer tubes is inserted,

the space formed in the inside of each of the at least 2 protruding portions in which the insertion opening is formed is an insertion space in which the tip end portion of 1 of the plurality of heat transfer tubes is located, the space formed in the inside of the protruding portion other than the at least 2 protruding portions in which the insertion space is formed is a branching path that branches off the refrigerant flowing in from 1 of the plurality of through-passages,

the 4 th plate-like member has a plurality of 1 st communication passages and a plurality of 2 nd communication passages formed therethrough in the 1 st direction,

the 1 st communication paths respectively communicate 1 through path among the through paths and 1 branch path among the branch paths,

the 2 nd communication paths respectively communicate 1 branch path of the branch paths with the insertion space.

3. The refrigerant distributor according to claim 1, wherein,

the at least 2 protrusions formed with the insertion space and the protrusions formed with the branched paths among the plurality of protrusions are integrally formed, and at least 2 of the insertion spaces communicate with the branched paths.

4. The refrigerant distributor according to claim 1, wherein,

Insertion openings into which 1 heat transfer tube of the plurality of heat transfer tubes is inserted are respectively formed in the plurality of protrusions,

the space formed inside each of the plurality of protruding portions is an insertion space in which the end portions of 1 heat transfer tube among the plurality of heat transfer tubes are located,

the 4 th plate-like member has a plurality of 1 st sub-branches and a plurality of 2 nd sub-branches formed so as to penetrate in the 1 st direction,

the 1 st sub-branch line communicates with 1 through-line of the plurality of through-lines and another 2 through-lines different from the through-line,

and the 2 nd sub-branches respectively communicate 1 through passage and 2 insertion spaces among the through passages.

5. The refrigerant distributor according to claim 1, wherein,

the space formed inside each of the plurality of protruding portions is a branch path for branching off the refrigerant flowing in from 1 through-path among the plurality of through-paths,

the 3 rd plate member has a plurality of insertion openings formed therethrough in the 1 st direction,

1 heat transfer tube among the plurality of heat transfer tubes is inserted into each of the plurality of insertion openings,

the 2 nd communication paths respectively communicate 1 branch path of the branch paths and 1 insertion opening of the insertion openings.

6. The refrigerant distributor according to any one of claims 1 to 5, wherein,

the downstream side of the inside of each of the plurality of protruding portions is formed in an arc shape.

7. The refrigerant distributor according to any one of claims 1 to 6, wherein,

the portion of the 3 rd plate member facing the plurality of protruding portions on the 2 nd plate member side surface is formed in a wedge shape.

8. The refrigerant distributor according to any one of claims 1 to 7, wherein,

the 1 st plate-like member has a plurality of cross-layer protrusions protruding in a direction opposite to the 2 nd plate-like member,

the plurality of cross-layer protrusions are formed so as to span at least 1 heat transfer tube of the plurality of heat transfer tubes when viewed from the 1 st direction, and the folded-back flow path is formed inside each of the plurality of cross-layer protrusions.

9. A heat exchanger, wherein the heat exchanger has:

the refrigerant distributor of any one of claims 1 to 8; and

a plurality of heat transfer tubes inserted into the refrigerant distributor.

10. A refrigeration cycle apparatus having the heat exchanger of claim 9.