JPWO2020217271A1 - Refrigerant distributor, heat exchanger and refrigeration cycle equipment - Google Patents

Abstract

The present invention is a refrigerant distributor and heat exchange in which the flow rate of the refrigerant distributed to each heat transfer tube is made uniform by suppressing the drift in the distribution of the refrigerant in response to the change in the flow rate of the refrigerant depending on the operating state of the air conditioner. It is an object of the present invention to provide a vessel and a refrigeration cycle device.
The refrigerant distributor is a refrigerant distributor connected to a heat exchanger having a plurality of heat transfer tubes arranged in the first direction, and has a first refrigerant inlet and a second refrigerant inlet on one side surface side. Has a main body in which a plurality of insertion holes for inserting a plurality of heat transfer tubes are formed on the other side surface side, and the main body communicates with the first refrigerant inlet and extends in the first direction. A plurality of merging flow paths that communicate with the distribution flow path and the second refrigerant inflow port, and the refrigerants that have flowed through the first distribution flow path and the second distribution flow path merge, and each of the plurality of merging flow paths and the first. A first communication hole group composed of a plurality of communication holes for communicating with the distribution flow path, and a first communication hole group for communicating each of the plurality of confluence flow paths with the second distribution flow path. A group of two communication holes is formed, and the first refrigerant inlet and the second refrigerant inlet are formed on one end side of the main body in the first direction, and in the first distribution flow path, When the distance from one end of the main body to the other end is defined as the distance A, and the distance from one end of the main body to the other end in the second distribution flow path is defined as the distance B. At a position where the distance A and the distance B are equal, the flow path shape of the first distribution flow path and the second distribution flow path, and one of the plurality of communication hole portions constituting the first communication hole group and the second communication hole. Of the flow path shapes with one of the plurality of communication holes forming the group, at least one of the flow path shapes is different.

Description

The present invention relates to a refrigerant distributor, a heat exchanger provided with the refrigerant distributor, and a refrigeration cycle device provided with the heat exchanger.

In recent years, in order to reduce the amount of refrigerant and improve the performance of heat exchangers, the diameter of heat transfer tubes of heat exchangers for air conditioners has been reduced. Recently, flat perforated tubes have begun to be used as the structure of heat transfer tubes. When the diameter of the heat transfer tube is reduced, it is necessary to suppress the increase in the refrigerant pressure loss, and the number of passes (number of branches) of the heat exchanger is increased as compared with the conventional heat exchanger. Therefore, as the refrigerant distributor that distributes the refrigerant to the heat exchanger, a refrigerant distributor formed in multiple branches as compared with the conventional refrigerant distributor is used. In order to achieve both the performance of the heat exchanger and the reduction of the amount of refrigerant used, it is possible to suppress the drift of the refrigerant to each path, reduce the amount of refrigerant used by reducing the volume of the distribution flow path, and transfer heat. A compact refrigerant distributor that secures a large area but does not hinder the installation space of the heat exchanger is required.

Conventionally, a refrigerant distributor having a main body in which heat transfer tubes extending in the horizontal direction are arranged in the vertical direction and formed in a cylindrical shape so as to extend in the vertical direction has been disclosed (see, for example, Patent Document 1). In the refrigerant distributor of Patent Document 1, flat tubes are inserted into the main body with equal lengths, and the flow velocity of the refrigerant in the refrigerant distributor is set to an appropriate value so that the refrigerant is evenly distributed to each heat transfer tube. It will be adjusted. Then, in the refrigerant distributor of Patent Document 1, the amount of the flat tube inserted into the main body is adjusted so that the cross-sectional area of the effective flow path of the portion where the flat tube is inserted in the main body becomes a predetermined value. The flow velocity of the refrigerant in the refrigerant distributor is adjusted to an appropriate value.

Japanese Patent No. 5626254

However, in the refrigerant distributor of Patent Document 1, under the condition that the flow rate of the refrigerant decreases depending on the operating state of the air conditioner, the refrigerant does not reach the upper part of the refrigerant distributor, and the distribution of the refrigerant is biased in the vertical direction. There is.

The present invention is for solving the above-mentioned problems, and is distributed to each heat transfer tube in order to suppress the drift in the distribution of the refrigerant against the change in the refrigerant flow rate depending on the operating state of the air conditioner. It is an object of the present invention to provide a refrigerant distributor, a heat exchanger, and a refrigeration cycle device having a uniform refrigerant flow rate.

The refrigerant distributor according to the present invention is a refrigerant distributor which is arranged at intervals in the first direction and is connected to a heat exchanger provided with a plurality of heat transfer tubes for circulating the refrigerant inside. Has a plurality of insertion holes in which a first refrigerant inlet and a second refrigerant inlet are formed on one side surface side and a plurality of heat transfer tubes are inserted on the other side surface side in the extending direction of the plurality of heat transfer tubes. It has a formed main body, and the main body communicates with the first refrigerant inlet and extends in the first direction, and communicates with the second refrigerant inlet and is parallel to the first distribution flow path. The second distribution flow path extending in the first direction and the refrigerant flowing through the first distribution flow path and the second distribution flow path communicate with the plurality of heat transfer tubes when the plurality of heat transfer tubes are inserted into the main body. A first communication hole group composed of a plurality of merging flow paths to be merged, a plurality of communication holes formed along the first direction, and a plurality of communication holes for communicating each of the plurality of merging flow paths with the first distribution flow path. And a second communication hole group formed along the first direction and composed of a plurality of communication hole portions for communicating each of the plurality of merging flow paths and the second distribution flow path. , The first refrigerant inlet and the second refrigerant inlet are formed on one end side of the main body in the first direction, and in the first distribution flow path, one end to the other end of the main body. When the distance toward is defined as the distance A and the distance from one end of the main body to the other end is defined as the distance B in the second distribution flow path, the distance A and the distance B are equal to each other. The shape of the flow path between the first distribution flow path and the second distribution flow path, and one of the plurality of communication hole portions constituting the first communication hole group and one of the plurality of communication hole portions constituting the second communication hole group. Of the two flow path shapes, at least one of the flow path shapes is different.

The heat exchanger according to the present invention includes the refrigerant distributor according to the present invention.

The refrigeration cycle apparatus according to the present invention includes the heat exchanger according to the present invention.

According to the present invention, the refrigerant distributor forms a plurality of flow path shapes of the first distribution flow path and the second distribution flow path and the first communication hole group at positions where the distance A and the distance B are equal. Of the flow path shapes of one of the communication hole portions of the above and one of the plurality of communication hole portions constituting the second communication hole group, at least one of the flow path shapes is different. Therefore, in the refrigerant distributor according to the present invention, a biased flow with respect to the distance from the refrigerant inflow port is caused by the total flow rate of the flow rate of the refrigerant flowing through the first distribution flow path and the flow rate of the refrigerant flowing through the second distribution flow path. It can be suppressed and the flow rate of the refrigerant distributed to a plurality of heat transfer tubes can be made uniform.

It is a refrigerant circuit diagram which shows the structure of the refrigerating cycle apparatus provided with the refrigerant distributor which concerns on Embodiment 1. FIG. It is an exploded perspective view which shows the main part structure of the heat exchanger provided with the refrigerant distributor which concerns on Embodiment 1. FIG. It is a side view which shows the main part structure of the heat exchanger provided with the refrigerant distributor which concerns on Embodiment 1. FIG. It is sectional drawing which shows the structure of the heat transfer tube connected to the refrigerant distributor which concerns on Embodiment 1. FIG. It is sectional drawing which shows the structure of the refrigerant distributor which concerns on Embodiment 1. FIG. It is a conceptual diagram which shows the refrigerant distribution of the refrigerant distributor which concerns on Embodiment 1. FIG. It is an exploded perspective view which shows the main part structure of the heat exchanger provided with the refrigerant distributor which concerns on Embodiment 2. FIG. It is an upper sectional view which shows the structure of the refrigerant distributor which concerns on Embodiment 2. FIG. It is an exploded perspective view which shows the main part structure of the heat exchanger provided with the refrigerant distributor which concerns on Embodiment 3. FIG. It is sectional drawing which shows the structure of the refrigerant distributor which concerns on Embodiment 3. FIG. It is a conceptual diagram which shows the refrigerant distribution of the refrigerant distributor which concerns on Embodiment 3. FIG. It is an exploded perspective view which shows the main part structure of the heat exchanger provided with the refrigerant distributor which concerns on Embodiment 4. FIG. It is sectional drawing which shows the structure of the refrigerant distributor which concerns on Embodiment 4. FIG. FIG. 5 is an exploded perspective view showing a main configuration of a heat exchanger provided with a refrigerant distributor according to a fifth embodiment. It is sectional drawing which shows the structure of the refrigerant distributor which concerns on Embodiment 5. It is a perspective view of the refrigerant distributor which concerns on Embodiment 6. It is a perspective view which shows typically the internal structure of the refrigerant distributor which concerns on Embodiment 6. It is sectional drawing which shows the structure of the refrigerant distributor which concerns on Embodiment 6. It is a vertical sectional view which shows the structure of the refrigerant distributor which concerns on Embodiment 6. It is a perspective view which shows typically the internal structure of the modification of the refrigerant distributor which concerns on Embodiment 6. It is a conceptual diagram of the modification of the 1st wall part of the refrigerant distributor which concerns on Embodiment 6. FIG. 5 is a conceptual diagram of another modification of the first wall portion of the refrigerant distributor according to the sixth embodiment.

Hereinafter, the refrigerant distributor 50 according to the first embodiment will be described with reference to the drawings and the like. In the following drawings including FIG. 1, the relative dimensional relationships and shapes of the constituent members may differ from the actual ones. Further, in the following drawings, those having the same reference numerals are the same or equivalent thereof, and this shall be common to the entire text of the specification. In addition, terms that indicate directions (for example, "top", "bottom", "right", "left", "front", "rear", etc.) are used as appropriate for ease of understanding. For convenience of explanation, it is described as such, and does not limit the arrangement and orientation of the device or component. In the specification, the positional relationship between the constituent members, the extending direction of each constituent member, and the parallel direction of each constituent member are, in principle, those when the heat exchanger is installed in a usable state.

Embodiment 1.
FIG. 1 is a refrigerant circuit diagram showing a configuration of a refrigerating cycle device 100 provided with a refrigerant distributor 50 according to the first embodiment. First, the refrigeration cycle device 100 provided with the refrigerant distributor 50 will be described with reference to FIG. In FIG. 1, the arrow indicated by the dotted line indicates the direction in which the refrigerant flows in the refrigerant circuit 110 during the cooling operation, and the arrow indicated by the solid line indicates the direction in which the refrigerant flows during the heating operation. .. In the present embodiment, the air conditioner is exemplified as the refrigerating cycle device 100, but the refrigerating cycle device 100 is used for refrigerating, for example, a refrigerator or a freezer, a vending machine, an air conditioner, a refrigerating device, a water heater, or the like. Used for applications or air conditioning applications.

The refrigeration cycle device 100 has a refrigerant circuit 110 in which a compressor 101, a flow path switching device 102, an indoor heat exchanger 103, a decompression device 104, and an outdoor heat exchanger 105 are connected in a ring shape via a refrigerant pipe. .. Further, the refrigeration cycle device 100 has a refrigerant distributor 50 connected to either one or both of the indoor heat exchanger 103 and the outdoor heat exchanger 105. The refrigeration cycle device 100 includes an outdoor unit 106 and an indoor unit 107. The outdoor unit 106 includes a compressor 101, a flow path switching device 102, an outdoor heat exchanger 105, a refrigerant distributor 50 and a decompression device 104, and an outdoor blower 108 that supplies outdoor air to the outdoor heat exchanger 105. Has been done. The indoor unit 107 includes an indoor heat exchanger 103, a refrigerant distributor 50, and an indoor blower 109 that supplies air to the indoor heat exchanger 103. The outdoor unit 106 and the indoor unit 107 are connected via two extension pipes 111 and 112 which are a part of the refrigerant pipe.

The compressor 101 is a fluid machine that compresses and discharges the sucked refrigerant. The flow path switching device 102 is, for example, a four-way valve, and is a device that switches the flow path of the refrigerant between the cooling operation and the heating operation by controlling the control device (not shown). The indoor heat exchanger 103 is a heat exchanger that exchanges heat between the refrigerant circulating inside and the indoor air supplied by the indoor blower 109. The indoor heat exchanger 103 functions as a condenser during the heating operation and as an evaporator during the cooling operation. The pressure reducing device 104 is, for example, an expansion valve, which is a device for reducing the pressure of the refrigerant. As the pressure reducing device 104, an electronic expansion valve whose opening degree is adjusted by the control of the control device can be used. The outdoor heat exchanger 105 is a heat exchanger that exchanges heat between the refrigerant circulating inside and the air supplied by the outdoor blower 108. The outdoor heat exchanger 105 functions as an evaporator during the heating operation and as a condenser during the cooling operation.

A heat exchanger 80, which will be described later, is used for at least one of the outdoor heat exchanger 105 and the indoor heat exchanger 103. It is desirable that the refrigerant distributor 50 connected to the heat exchanger 80 is arranged at a position in the heat exchanger 80 where the amount of the liquid phase refrigerant is larger. Specifically, the refrigerant distributor 50 is arranged on the inlet side of the heat exchanger 80 that functions as an evaporator, that is, on the outlet side of the heat exchanger 80 that functions as a condenser in the flow of the refrigerant in the refrigerant circuit 110. Is desirable. The refrigerant distributor 50 is used in both the indoor heat exchanger 103 and the outdoor heat exchanger 105, but the heat of either the indoor heat exchanger 103 or the outdoor heat exchanger 105 is used. It may be used only in the exchanger.

FIG. 2 is an exploded perspective view showing a main configuration of the heat exchanger 80 provided with the refrigerant distributor 50 according to the first embodiment. FIG. 3 is a side view showing a main configuration of the heat exchanger 80 provided with the refrigerant distributor 50 according to the first embodiment. The refrigerant distributor 50 and the heat exchanger 80 according to the first embodiment will be described with reference to FIGS. 1 to 3. The arrow A shown in the figure represents an example of the distance A, and the distance A is the distance from one end 51a of the main body 51 toward the other end 51b in the first distribution flow path 15a described later. .. Further, the arrow B represents an example of the distance B, and the distance B is a distance from one end 51a of the main body 51 toward the other end 51b in the second distribution flow path 16a described later. Further, in FIGS. 2 and 3, the arrow F indicated by hatching indicates the direction of the refrigerant flowing through the first flow path portion 15 and the second flow path portion 16 of the refrigerant distributor 50. The refrigerant distributor 50 is connected to the inlet side of the heat transfer tube 70 when the heat exchanger 80 operates as an evaporator when applied to the refrigeration cycle device 100. The heat exchanger 80 to which the refrigerant distributor 50 is connected is an air heat exchanger that exchanges heat between air and the refrigerant, and functions at least as an evaporator of the refrigeration cycle device 100.

As shown in FIG. 2, the heat exchanger 80 includes a plurality of heat transfer tubes 70 for circulating a refrigerant, a refrigerant distributor 50 connected to one end of each of the plurality of heat transfer tubes 70 in the extending direction, and a refrigerant distributor 50. It has a refrigerant inflow pipe 60 attached to the lower part of the. In the following description, the heat transfer tube 70 is described as a flat tube, but a circular tube may be used for the heat transfer tube 70.

The plurality of heat transfer tubes 70 are flat tubes. Each of the plurality of heat transfer tubes 70 extends in the horizontal direction. The plurality of heat transfer tubes 70 are arranged in parallel in the vertical direction with each other. A gap 71 that serves as an air flow path is formed between two adjacent heat transfer tubes 70 among the plurality of heat transfer tubes 70. A heat transfer fin 75 may be provided between two adjacent heat transfer tubes 70. Although not shown, a refrigerant collecting pipe having a cylindrical shape, for example, is connected to the other end of each of the plurality of heat transfer tubes 70 in the extending direction. When the heat exchanger 80 functions as an evaporator of the refrigeration cycle device 100, the refrigerant flows from one end to the other end of each of the plurality of heat transfer tubes 70. When the heat exchanger 80 functions as a condenser of the refrigeration cycle device 100, the refrigerant flows from the other end to the one end in each of the plurality of heat transfer tubes 70.

FIG. 4 is a cross-sectional view showing a configuration of a heat transfer tube 70 connected to the refrigerant distributor 50 according to the first embodiment. FIG. 4 shows a cross section perpendicular to the extending direction of the heat transfer tube 70. As shown in FIG. 4, the heat transfer tube 70 has a unidirectionally flat cross-sectional shape such as an oval shape. The heat transfer tube 70 has a first side end portion 70a and a second side end portion 70b, and a pair of flat surfaces 70c and flat surfaces 70d. In the cross section shown in FIG. 3, the first side end portion 70a is connected to one end portion of the flat surface 70c and one end portion of the flat surface 70d. In the same cross section, the second side end 70b is connected to the other end of the flat surface 70c and the other end of the flat surface 70d. The first side end portion 70a is a side end portion arranged on the windward side, that is, on the front edge side in the flow of air passing through the heat exchanger. The second side end portion 70b is a side end portion arranged on the leeward side, that is, the trailing edge side in the flow of air passing through the heat exchanger. Hereinafter, the direction perpendicular to the extending direction of the heat transfer tube 70 and along the flat surface 70c and the flat surface 70d may be referred to as a major axis direction of the heat transfer tube 70. In FIG. 4, the long axis direction of the heat transfer tube 70 is the left-right direction. The major axis dimension of the heat transfer tube 70 in the major axis direction is LA1.

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

Returning to FIGS. 2 and 3, the refrigerant distributors 50 are arranged at intervals in the first direction and are connected to a heat exchanger 80 provided with a plurality of heat transfer tubes 70 for circulating the refrigerant inside. The first direction is the arrangement direction of the plurality of heat transfer tubes 70, and is the direction in which the plurality of heat transfer tubes 70 are lined up. The main body 51 of the refrigerant distributor 50 is formed so as to extend in the vertical direction along the arrangement direction of the plurality of heat transfer tubes 70. The main body 51 of the refrigerant distributor 50 has two refrigerant inlets 18 of a first refrigerant inlet 18a and a second refrigerant inlet 18b formed on one side surface side in the extending direction of the plurality of heat transfer tubes 70, and the other. A plurality of insertion holes 41 into which a plurality of heat transfer tubes 70 are inserted are formed on the side surface side of the above. The first refrigerant inlet 18a and the second refrigerant inlet 18b are formed on one end 51a side of the main body 51 in the first direction. For example, the first refrigerant inlet 18a and the second refrigerant inlet 18b are formed side by side in a direction perpendicular to the first direction, which is the arrangement direction of the plurality of heat transfer tubes 70. In this case, the center position of the first refrigerant inlet 18a and the center position of the second refrigerant inlet 18b may be at different distances from one end portion 51a. Further, the first refrigerant inflow port 18a and the second refrigerant inflow port 18b are formed, for example, in the first direction below the communication hole portion 25 formed at the lowermost side of the communication hole portions 25 described later. ing. However, the first refrigerant inflow port 18a and the second refrigerant inflow port 18b are not limited to those formed below the communication hole portion 25 formed on the lowermost side in the first direction.

The main body 51 of the refrigerant distributor 50 has a first plate-shaped member 10, a second plate-shaped member 20, a third plate-shaped member 30, and a fourth plate-shaped member 40. The first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, and the fourth plate-shaped member 40 are all formed by using a metal flat plate and have a long strip shape in one direction. There is. The contours of the outer edges of the first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, and the fourth plate-shaped member 40 have the same shape as each other. The first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, and the fourth plate-shaped member 40 have their respective plate thickness directions parallel to the extending direction of the heat transfer tube 70, that is, Each plate surface is arranged so as to be perpendicular to the extending direction of the heat transfer tube 70.

In the main body 51 of the refrigerant distributor 50, the first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, and the fourth plate-shaped member 40 are arranged in this order from the farthest distance from the heat transfer tube 70. It has a laminated structure. The farthest distance from the heat transfer tube 70 is the first plate-shaped member 10, and the closest distance from the heat transfer tube 70 is the fourth plate-shaped member 40. The second plate-shaped member 20 is arranged between the first plate-shaped member 10 and the heat transfer tube 70, and is adjacent to the first plate-shaped member 10. The third plate-shaped member 30 is arranged between the second plate-shaped member 20 and the heat transfer tube 70, and is adjacent to the second plate-shaped member 20. The fourth plate-shaped member 40 is arranged between the third plate-shaped member 30 and the heat transfer tube 70, and is adjacent to the third plate-shaped member 30. One end of each of the plurality of heat transfer tubes 70 is connected to the fourth plate-shaped member 40. Adjacent members of the first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, and the fourth plate-shaped member 40 are joined by brazing. The first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, and the fourth plate-shaped member 40 are arranged so that their longitudinal directions are along the vertical direction.

FIG. 5 is a cross-sectional view showing the configuration of the refrigerant distributor 50 according to the first embodiment. FIG. 5 shows a cross section of the refrigerant distributor 50 in the extending direction of the heat transfer tube 70 and the direction parallel to the major axis direction. The plate thickness directions of the first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, and the fourth plate-shaped member 40 are the left-right directions in FIG. 5, and are the extending directions of the heat transfer tube 70. be. The lateral direction of each of the first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, and the fourth plate-shaped member 40 is the vertical direction of FIG. 5, and the major axis direction of the heat transfer tube 70. Is.

As shown in FIGS. 2 and 5, the first plate-shaped member 10 has a first flow path portion 15 that bulges in a direction away from the heat transfer tube 70, and similarly, a first plate-shaped member 10 that bulges in a direction away from the heat transfer tube 70. It has two flow path portions 16. The first flow path portion 15 and the second flow path portion 16 are formed in parallel in the lateral direction of the first plate-shaped member 10. The first distribution flow path 15a formed in the first flow path portion 15 and the second distribution flow path 16a formed in the second flow path portion 16 are formed so as to have different flow path cross-sectional areas. Has been done. Here, in the first distribution flow path 15a, the distance from one end 51a of the main body 51 to the other end 51b is defined as a distance A, and in the second distribution flow path 16a, one end of the main body 51 is defined. The distance from 51a to the other end 51b is defined as the distance B. The refrigerant distributor 50 has a different flow path shape so that the flow path cross-sectional areas of the first distribution flow path 15a and the second distribution flow path 16a are different at positions where the distance A and the distance B are equal. Alternatively, the refrigerant distributor 50 may be connected to the first distribution flow path 15a at a position corresponding to the formation position of one of the communication hole portions 25, which will be described later, which is formed in plurality along the first direction. The flow path shape is different so that the flow path cross-sectional area of the second distribution flow path 16a is different.

The first flow path portion 15 extends from one end in the longitudinal direction to the other end in the longitudinal direction of the first plate-shaped member 10 along the longitudinal direction of the first plate-shaped member 10. The first flow path portion 15 is formed in a semi-cylindrical shape. Both ends of the first flow path portion 15 in the stretching direction are closed. The first flow path portion 15 has a semicircular, semi-elliptical or semi-oval cross-sectional shape. However, the cross-sectional shape of the first flow path portion 15 is not limited to a semicircular shape, a semi-elliptical shape, or a semi-elliptical shape, and may be, for example, a rectangular shape. Further, the first plate-shaped member 10 has a flat plate portion 11a and a flat plate portion 11b formed in a flat plate shape on both sides of the first flow path portion 15. Both the flat plate portion 11a and the flat plate portion 11b extend from one end in the longitudinal direction to the other end in the longitudinal direction of the first plate-shaped member 10 along the longitudinal direction of the first plate-shaped member 10.

The second flow path portion 16 extends from one end in the longitudinal direction to the other end in the longitudinal direction of the first plate-shaped member 10 along the longitudinal direction of the first plate-shaped member 10. The second flow path portion 16 is formed in a semi-cylindrical shape. Both ends of the second flow path portion 16 in the stretching direction are closed. The second flow path portion 16 has a semicircular, semi-elliptical or semi-oval cross-sectional shape. However, the cross-sectional shape of the second flow path portion 16 is not limited to a semicircular shape, a semi-elliptical shape, or a semi-elliptical shape, and may be, for example, a rectangular shape. Further, for example, the first flow path portion 15 may have a semicircular shape, and the second flow path portion 16 may have a different shape such as a rectangular shape. The first plate-shaped member 10 has a flat plate portion 11b and a flat plate portion 11c formed in a flat plate shape on both sides of the second flow path portion 16. Both the flat plate portion 11b and the flat plate portion 11c extend from one end in the longitudinal direction to the other end in the longitudinal direction of the first plate-shaped member 10 along the longitudinal direction of the first plate-shaped member 10. The first flow path portion 15 and the second flow path portion 16 are arranged side by side via the flat plate portion 11b.

Inside the first flow path portion 15, a first distribution flow path 15a extending in the vertical direction along the longitudinal direction of the first plate-shaped member 10 is formed. The first distribution flow path 15a is formed so as to communicate with the first refrigerant inflow port 18a, parallel to the second distribution flow path 16a, and extend in the first direction, which is the arrangement direction of the plurality of heat transfer tubes 70. .. The first distribution flow path 15a extends so as to intersect with each of the plurality of heat transfer tubes 70 when viewed in the plate thickness direction of the first plate-shaped member 10. The first distribution flow path 15a has a semicircular, semi-elliptical or semi-elliptical cross-sectional shape. That is, the first distribution flow path 15a is a space formed in a semi-cylindrical shape, a semi-elliptical cylinder shape, or a semi-long cylindrical shape. However, the cross-sectional shape of the first distribution flow path 15a is not limited to a semicircular shape, a semi-elliptical shape, or a semi-elliptical shape, and may be, for example, a rectangular shape.

The cross-sectional area of the first distribution flow path 15a is smaller than the cross-sectional area of the second distribution flow path 16a. The first distribution flow path 15a communicates with the refrigerant inflow pipe 60 at the end in the extending direction. The gas-liquid two-phase refrigerant flowing into the first distribution flow path 15a via the refrigerant inflow pipe 60 flows upward through the first distribution flow path 15a and is distributed to each heat transfer pipe 70 as shown by an arrow F. ..

The width direction of the first distribution flow path 15a is parallel to the lateral direction of the first plate-shaped member 10. The dimension of the first distribution flow path 15a in the width direction is smaller than the major axis dimension LA1 of the heat transfer tube 70. By making the shape of the first distribution flow path 15a semi-cylindrical, semi-elliptical cylinder, or semi-long cylinder, the internal volume of the first distribution flow path 15a is reduced as compared with the cylindrical distribution flow path. be able to. Therefore, the refrigerating cycle device 100 provided with the refrigerant distributor 50 according to the first embodiment can reduce the amount of refrigerant.

Inside the second flow path portion 16, a second distribution flow path 16a extending in the vertical direction along the longitudinal direction of the first plate-shaped member 10 is formed. The second distribution flow path 16a is formed so as to communicate with the second refrigerant inflow port 18b, parallel to the first distribution flow path 15a, and extend in the first direction, which is the arrangement direction of the plurality of heat transfer tubes 70. .. The second distribution flow path 16a extends so as to intersect with each of the plurality of heat transfer tubes 70 when viewed in the plate thickness direction of the first plate-shaped member 10. The second distribution flow path 16a has a semicircular, semi-elliptical or semi-oval cross-sectional shape. That is, the second distribution flow path 16a is a space formed in a semi-cylindrical shape, a semi-elliptical cylinder shape, or a semi-long cylindrical shape. However, the cross-sectional shape of the second distribution flow path 16a is not limited to a semicircular shape, a semi-elliptical shape, or a semi-elliptical shape, and may be, for example, a rectangular shape.

The cross-sectional area of the second distribution flow path 16a is larger than the cross-sectional area of the first distribution flow path 15a. The second distribution flow path 16a communicates with the refrigerant inflow pipe 60 at the end in the extending direction. The gas-liquid two-phase refrigerant flowing into the second distribution flow path 16a via the refrigerant inflow pipe 60 flows upward through the second distribution flow path 16a and is distributed to each heat transfer pipe 70 as shown by an arrow F. ..

The width direction of the second distribution flow path 16a is parallel to the lateral direction of the first plate-shaped member 10. The dimension of the second distribution flow path 16a in the width direction is smaller than the major axis dimension LA1 of the heat transfer tube 70. By making the shape of the second distribution flow path 16a semi-cylindrical, semi-elliptical cylinder, or semi-long cylindrical, the internal volume of the second distribution flow path 16a is reduced as compared with the cylindrical distribution flow path. be able to. Therefore, in the refrigerating cycle device 100 provided with the refrigerant distributor 50 according to the first embodiment, the amount of refrigerant can be reduced.

As described above, the refrigerant inflow pipe 60 communicates with the lower ends of the first distribution flow path 15a and the second distribution flow path 16a. When the heat exchanger 80 functions as an evaporator, the refrigerant inflow pipe 60 causes the gas-liquid two-phase refrigerant to flow into the first distribution flow path 15a and the second distribution flow path 16a. The refrigerant inflow pipe 60 has a base 61, a first branch pipe 62, and a second branch pipe 63. The first branch pipe 62 and the second branch pipe 63 are formed so as to be bifurcated at the end of the base portion 61. The first branch pipe 62 is connected to the first flow path portion 15 and communicates with the first distribution flow path 15a, and the second branch pipe 63 is connected to the second flow path portion 16 to communicate with the second distribution flow path 16a. Communicate with. The connection position between the refrigerant inflow pipe 60 and the first flow path portion 15 and the second flow path portion 16 is the refrigerant inflow port 18 through which the refrigerant flows into the refrigerant distributor 50. When the heat exchanger 80 functions as a condenser, the liquid refrigerant flows downward through the first distribution flow path 15a and the second distribution flow path 16a and flows out through the refrigerant inflow pipe 60.

The second plate-shaped member 20 has a plurality of communication holes 25 each having a circular opening shape. Each of the plurality of communication hole portions 25 forms a through hole penetrating the second plate-shaped member 20, and is provided corresponding to each of the plurality of heat transfer tubes 70. Each of the plurality of communication hole portions 25 penetrates the second plate-shaped member 20 in the plate thickness direction of the second plate-shaped member 20. The opening shape of the communication hole portion 25 is circular, but is not limited to a circular shape, and may be, for example, a semicircular shape, a semi-elliptical shape, a semi-elliptical shape, or a rectangular shape. The flow path cross-sectional areas of the plurality of communication hole portions 25 are the same size. However, the flow path cross-sectional areas of the plurality of communication hole portions 25 are not limited to those having the same size, and may be formed to have different sizes. The cross-sectional area of each flow path of the plurality of communication hole portions 25 is based on the cross-sectional area of each flow path of the plurality of heat transfer tubes 70, that is, the sum of the cross-sectional areas of the flow paths of the plurality of refrigerant passages 72 formed in each heat transfer tube 70. Is also getting smaller. Further, the cross-sectional area of each flow path of the plurality of communication hole portions 25 is smaller than the opening area of each of the plurality of through hole portions 31, which will be described later.

The plurality of communication hole portions 25 are arranged in the vertical direction along the longitudinal direction of the second plate-shaped member 20. Further, two communication hole portions 25 are formed side by side along the lateral direction of the second plate-shaped member 20. That is, two rows of communication hole portions 25 formed by the plurality of communication hole portions 25 arranged in the vertical direction are formed in the lateral direction of the second plate-shaped member 20. Here, a group of a plurality of communication hole portions 25 arranged in one row is referred to as a first communication hole group 125a. The first communication hole group 125a is formed along the first direction in which a plurality of heat transfer tubes 70 are arranged, and a plurality of communication hole portions that communicate each of the plurality of confluence flow paths 32 with the first distribution flow path 15a. It is composed of 25. Further, a group of a plurality of communication hole portions 25 arranged in the other row is referred to as a second communication hole group 125b. The second communication hole group 125b is formed along the first direction in which a plurality of heat transfer tubes 70 are arranged, and a plurality of communication hole portions that communicate each of the plurality of confluence flow paths 32 with the second distribution flow path 16a. It is composed of 25.

All of the plurality of communication hole portions 25 of the first communication hole group 125a are formed so as to overlap the first distribution flow path 15a of the first plate-shaped member 10 when viewed in the plate thickness direction of the second plate-shaped member 20. Has been done. Further, each of the plurality of communication hole portions 25 of the first communication hole group 125a has a plurality of merging flow paths 32 of the third plate-shaped member 30, which will be described later, when viewed in the plate thickness direction of the second plate-shaped member 20. It is formed so as to overlap each other. Further, each of the plurality of communication hole portions 25 of the first communication hole group 125a is formed so as to overlap each of the plurality of heat transfer tubes 70 when viewed in the plate thickness direction of the second plate-shaped member 20. Therefore, the first distribution flow path 15a of the first plate-shaped member 10 and each of the plurality of heat transfer tubes 70 communicate with each other through the plurality of communication hole portions 25 of the first communication hole group 125a.

All of the plurality of communication hole portions 25 of the second communication hole group 125b are formed so as to overlap the second distribution flow path 16a of the first plate-shaped member 10 when viewed in the plate thickness direction of the second plate-shaped member 20. Has been done. Further, each of the plurality of communication hole portions 25 of the second communication hole group 125b and each of the plurality of merging flow paths 32 of the third plate-shaped member 30 when viewed in the plate thickness direction of the second plate-shaped member 20. It is formed so as to overlap. Further, each of the plurality of communication hole portions 25 of the second communication hole group 125b is formed so as to overlap each of the plurality of heat transfer tubes 70 when viewed in the plate thickness direction of the second plate-shaped member 20. Therefore, the second distribution flow path 16a of the first plate-shaped member 10 and each of the plurality of heat transfer tubes 70 communicate with each other through the plurality of communication hole portions 25 of the second communication hole group 125b.

Further, the second plate-shaped member 20 has a flat plate-shaped closing portion 24. A part of the closing portion 24 overlaps the first distribution flow path 15a and the second distribution flow path 16a of the first plate-shaped member 10 when viewed in the plate thickness direction of the second plate-shaped member 20. The closing portion 24 has a function of preventing the first distribution flow path 15a and the second distribution flow path 16a and each of the plurality of heat transfer tubes 70 from directly communicating with each other without passing through the communication hole portion 25.

The third plate-shaped member 30 is arranged between the second plate-shaped member 20 and the fourth plate-shaped member 40. The third plate-shaped member 30 has a plurality of through-hole portions 31. Each of the plurality of through-hole portions 31 forms a through hole that penetrates the third plate-shaped member 30, and penetrates the third plate-shaped member 30 in the plate thickness direction of the third plate-shaped member 30. The plurality of through-hole portions 31 are provided independently of each other corresponding to each of the plurality of heat transfer tubes 70. The plurality of through-hole portions 31 are formed in parallel in the vertical direction along the longitudinal direction of the third plate-shaped member 30.

The through hole portion 31 has a flat opening shape similar to the outer peripheral shape of the heat transfer tube 70. The opening area of each through hole portion 31 is the same as or larger than the opening area of each insertion hole 41 of the fourth plate-shaped member 40. When viewed along the extending direction of the heat transfer tube 70, the open end of the through hole portion 31 overlaps with the outer peripheral surface of the heat transfer tube 70 or is located outside the outer peripheral surface.

Inside each through hole portion 31, a merging flow path 32 provided corresponding to each heat transfer tube 70 is formed. When a plurality of heat transfer tubes 70 are inserted into the main body 51, the merging flow path 32 communicates with the plurality of heat transfer tubes 70, and the refrigerant flowing through the first distribution flow path 15a and the second distribution flow path 16a merges. It is a space. One end of the heat transfer tube 70 penetrates the insertion hole 41 of the fourth plate-shaped member 40 and reaches the merging flow path 32. The open ends of the plurality of refrigerant passages 72 formed at one end of the heat transfer tube 70 all face the merging passage 32. Each of the plurality of refrigerant passages 72 of the heat transfer tube 70 communicates with the first distribution flow path 15a and the second distribution flow path 16a via the merging flow path 32 and the communication hole portion 25. The merging flow path 32 flows through the first distribution flow path 15a, the refrigerant that has passed through the communication hole portion 25 of the first communication hole group 125a, and the second distribution flow path 16a, and flows through the communication hole of the second communication hole group 125b. This is a space where the refrigerant that has passed through the portion 25 merges. The refrigerant flowing through the first distribution flow path 15a and the second distribution flow path 16a merges in the merging flow path 32, and then flows into the refrigerant passage 72 of the heat transfer tube 70.

The fourth plate-shaped member 40 is formed with a plurality of insertion holes 41 into which one ends of the plurality of heat transfer tubes 70 are inserted. Each of the plurality of insertion holes 41 penetrates the fourth plate-shaped member 40 in the plate thickness direction of the fourth plate-shaped member 40. The plurality of insertion holes 41 are arranged in parallel in the vertical direction along the longitudinal direction of the fourth plate-shaped member 40. The insertion hole 41 has a flat opening shape similar to the outer peripheral shape of the heat transfer tube 70. The open end of the insertion hole 41 is joined to the outer peripheral surface of the heat transfer tube 70 over the entire circumference by brazing.

Next, the operation of the refrigeration cycle device 100 will be described with reference to FIG. During the heating operation of the refrigeration cycle device 100, the high-pressure and high-temperature gas-state refrigerant discharged from the compressor 101 flows into the indoor heat exchanger 103 via the flow path switching device 102, and the air supplied by the indoor blower 109. Heat exchange with and condenses. The condensed refrigerant is in a high-pressure liquid state, flows out from the indoor heat exchanger 103, and is in a low-pressure gas-liquid two-phase state by the decompression device 104. The low-pressure gas-liquid two-phase state refrigerant is distributed to each heat transfer tube 70 of the outdoor heat exchanger 105 by the refrigerant distributor 50, and evaporates by heat exchange with the air supplied by the outdoor blower 108. The evaporated refrigerant becomes a low-pressure gas state and is sucked into the compressor 101.

During the cooling operation of the refrigerating cycle device 100, the refrigerant flowing through the refrigerant circuit 110 flows in the opposite direction to that during the heating operation. That is, during the cooling operation of the refrigeration cycle device 100, the high-pressure and high-temperature gas-state refrigerant discharged from the compressor 101 flows into the outdoor heat exchanger 105 via the flow path switching device 102 and is supplied by the outdoor blower 108. It exchanges heat with the air and condenses. The condensed refrigerant is in a high-pressure liquid state, flows out of the outdoor heat exchanger 105, and is in a low-pressure gas-liquid two-phase state by the decompression device 104. The low-pressure gas-liquid two-phase state refrigerant is distributed to each heat transfer tube 70 of the indoor heat exchanger 103 by the refrigerant distributor 50, and evaporates by heat exchange with the air supplied by the indoor blower 109. The evaporated refrigerant becomes a low-pressure gas state and is sucked into the compressor 101.

Next, the operation of the refrigerant distributor 50 according to the first embodiment will be described by exemplifying the operation when the heat exchanger 80 functions as the evaporator of the refrigeration cycle device 100. When the refrigeration cycle device 100 is in the heating operation, the refrigerant flowing from the decompression device 104 into the refrigerant distributor 50 of the heat exchanger 80 functioning as an evaporator is a gas-liquid two-phase refrigerant decompressed by the decompression device 104. This gas-liquid two-phase refrigerant flows into the refrigerant distributor 50 from the refrigerant inflow pipe 60, and has two distribution flow paths 15a and a second distribution flow path 16a provided in parallel with the first plate-shaped member 10. It flows upward in the distribution flow path.

The refrigerant flowing through the two distribution channels 15a and 16a has a height corresponding to each heat transfer tube 70 via the first communication hole group 125a and the second communication hole group 125b. It will be distributed. The first communication hole group 125a and the second communication hole group 125b are formed in the second plate-shaped member 20 so as to correspond to the respective heat transfer tubes 70, and are formed with the first distribution flow path 15a and the second distribution flow path 16a. It communicates with the merging flow path 32.

The refrigerant flowing through the first distribution flow path 15a, whose cross-sectional area is smaller than that of the second distribution flow path 16a, has a predetermined height in the first communication hole group 125a communicating with the first distribution flow path 15a. The refrigerant is distributed so as to maximize the flow rate of the refrigerant passing through the communication hole portion 25. Further, the refrigerant flowing through the second distribution flow path 16a whose cross-sectional area is larger than that of the first distribution flow path 15a is predetermined in the second communication hole group 125b communicating with the second distribution flow path 16a. The refrigerant is distributed so as to maximize the flow rate of the refrigerant passing through the communication hole portion 25 having a height of. At this time, the position of the communication hole portion 25 in which the refrigerant flow rate is maximum in the second communication hole group 125b is lower than the position of the communication hole portion 25 in which the refrigerant flow rate is maximum in the first communication hole group 125a, that is, The position is close to the connection position of the refrigerant inflow pipe 60.

FIG. 6 is a conceptual diagram showing the refrigerant distribution of the refrigerant distributor 50 according to the first embodiment. In FIG. 6, the horizontal axis represents the flow rate of the refrigerant liquid [kg / h], and the vertical axis represents the distance from the refrigerant inflow port 18 in the first direction in which the heat transfer tubes 70 are arranged. Further, in FIG. 6, the dotted line A shows the flow rate of the refrigerant flowing through the first distribution flow path 15a, and the broken line B shows the flow rate of the refrigerant flowing through the second distribution flow path 16a. Further, the solid line C shows the total flow rate of the flow rate of the refrigerant flowing through the first distribution flow path 15a and the flow rate of the refrigerant flowing through the second distribution flow path 16a. Further, the alternate long and short dash line D indicates a case where the total flow rate of the flow rate of the refrigerant flowing through the first distribution flow path 15a and the flow rate of the refrigerant flowing through the second distribution flow path 16a are equal in the distance from the refrigerant inlet 18. It is a dotted line. Further, the point M1 shown in FIG. 6 represents the maximum refrigerant flow rate and the distance thereof in the first distribution flow path 15a, and the point M2 shown in FIG. 6 represents the maximum refrigerant flow rate and the distance thereof in the second distribution flow path 16a. Represents.

As shown by the dotted line A in FIG. 6, the communication hole portion 25 that maximizes the flow rate of the refrigerant passing through the plurality of communication hole portions 25 constituting the first communication hole group 125a, and the first refrigerant inflow port 18a. The distance between them is the first distance L1. Then, as shown by the broken line B, the communication hole portion 25 in which the flow rate of the refrigerant passing through the plurality of communication hole portions 25 constituting the second communication hole group 125b is maximized, and the second refrigerant inflow port 18b. The distance is the second distance L2. In this case, the refrigerant distributor 50 has a different distance between the first distance L1 and the second distance L2.

As shown by the dotted line A and the broken line B in FIG. 6, the position of the communication hole portion 25 in which the refrigerant flow rate is maximum in the first communication hole group 125a is the communication hole portion in which the refrigerant flow rate is maximum in the second communication hole group 125b. The position is farther from the refrigerant inflow port 18 than the position of 25. In other words, as shown by the dotted line A and the broken line B in FIG. 6, the position of the communication hole portion 25 where the refrigerant flow rate is maximum in the second communication hole group 125b is such that the refrigerant flow rate is maximum in the first communication hole group 125a. The position is closer to the refrigerant inflow port 18 than the position of the communication hole portion 25.

The first distribution flow path 15a has a smaller cross-sectional area than the second distribution flow path 16a. Therefore, the flow velocity of the refrigerant flowing through the first distribution flow path 15a is higher than the flow velocity of the refrigerant flowing through the second distribution flow path 16a. Therefore, the refrigerant flowing through the first distribution flow path 15a can flow to a position farther from the refrigerant inflow port 18 than the refrigerant flowing through the second distribution flow path 16a while maintaining the flow velocity. For example, when the extension direction of the first distribution flow path 15a and the second distribution flow path 16a is the vertical direction, the refrigerant flowing through the first distribution flow path 15a is larger than the refrigerant flowing through the second distribution flow path 16a. It is possible to reach a high position from the refrigerant inlet 18 while maintaining the flow velocity. That is, the refrigerant distributor 50 controls the flow velocity of the refrigerant flowing through the first distribution flow path 15a and the flow velocity of the refrigerant flowing through the second distribution flow path 16a by the difference in the size of the flow path cross-sectional area.

The refrigerant that flows through the two distribution flow paths of the first distribution flow path 15a and the second distribution flow path 16a and is distributed so as to maximize the refrigerant flow rate at different distances from the refrigerant inflow port 18 is a third plate-shaped member. 30 joins each heat transfer tube 70 at the height of each heat transfer tube 70. As shown by the solid line C in FIG. 6, the total flow rate of the refrigerant flowing through the first distribution flow path 15a and the flow rate of the refrigerant flowing through the second distribution flow path 16a approaches the alternate long and short dash line D. That is, the total flow rate of the flow rate of the refrigerant flowing through the first distribution flow path 15a and the flow rate of the refrigerant flowing through the second distribution flow path 16a suppresses the drift with respect to the distance from the refrigerant inflow port 18, and a plurality of transmissions. The flow rate of the refrigerant distributed to the heat pipe 70 can be made uniform.

Generally, in a refrigerant distributor, the higher the refrigerant flow rate in the distribution flow path through which the gas-liquid two-phase refrigerant flows upward, the larger the refrigerant flow rate is distributed to the upper heat transfer tube far from the refrigerant inlet. As described above, the refrigerant distributor 50 is formed so that the flow path cross-sectional area of the first distribution flow path 15a and the flow path cross-sectional area of the second distribution flow path 16a are different. In the refrigerant distributor 50, a large amount of refrigerant is distributed to the lower heat transfer tube 70 by the second distribution flow path 16a having a large flow path cross-sectional area, and the upper heat transfer tube 70 is distributed by the first distribution flow path 15a having a small flow path cross-sectional area. A large amount of refrigerant is distributed to. Then, the refrigerant distributor 50 merges the refrigerant flowing through the second distribution flow path 16a and the refrigerant flowing through the first distribution flow path 15a at the merging flow path 32 and flows them through the heat transfer tubes 70. Therefore, the refrigerant distributor 50 can equalize the distribution of the refrigerant flowing into each heat transfer tube 70 and improve the performance of the heat exchanger 80.

Further, in the main body 51 of the refrigerant distributor 50, the first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, and the fourth plate-shaped member 40 having the above configuration are laminated. Is formed. The refrigerant distributor 50 separates the holding member into which the heat transfer tube 70 is directly inserted and the first distribution flow path 15a and the second distribution flow path 16a into separate parts, whereby the first distribution flow path 15a and the second distribution flow path 15a and the second distribution flow path 16a are separated. The length of the distribution flow path 16a in the long axis direction of the flat tube can be made smaller than the long axis of the flat tube. Therefore, the refrigerant distributor 50 can reduce the volume inside the main body 51, and can reduce the amount of the required refrigerant sealed in the air conditioner. When a flat pipe with a longer major axis length than a circular pipe is inserted into the refrigerant distributor, the diameter of the main body is larger than when a circular pipe is used, so the volume of the distribution flow path is expanded and the amount of refrigerant is increased. May increase. On the other hand, with the above configuration, the refrigerant distributor 50 can reduce the volume inside the main body 51 and reduce the amount of refrigerant required to be sealed in the air conditioner.

Embodiment 2.
FIG. 7 is an exploded perspective view showing a main configuration of the heat exchanger 80 provided with the refrigerant distributor 50A according to the second embodiment. FIG. 8 is an upper cross-sectional view showing the configuration of the refrigerant distributor 50A according to the second embodiment. The components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

In the refrigerant distributor 50A according to the second embodiment, the configuration of the first plate-shaped member 10A is different from that of the first plate-shaped member 10 of the refrigerant distributor 50 of the first embodiment. As shown in FIGS. 7 and 8, the first plate-shaped member 10A has a first flow path portion 115 forming a first distribution flow path 115a inside and a second distribution flow path 116a forming a second distribution flow path 116a inside. It has a flow path portion 116. In the refrigerant distributor 50A, the flow path cross-sectional area of the first distribution flow path 115a decreases as it goes upward, and the flow path cross-sectional area of the second distribution flow path 116a increases as it goes upward. That is, in the first direction, which is the arrangement direction of the heat transfer tubes 70, the flow path cross-sectional area of the first distribution flow path 115a decreases as the distance from the first refrigerant inflow port 18a increases, and the second distribution flow path 116a becomes the second distribution flow path 116a. The cross-sectional area of the flow path increases as the distance from the refrigerant inlet 18b increases. Here, in the first distribution flow path 115a, the distance from one end 51a of the main body 51 to the other end 51b is defined as a distance A, and in the second distribution flow path 116a, one end of the main body 51 is defined. The distance from 51a to the other end 51b is defined as the distance B. The refrigerant distributor 50A has a different flow path shape so that the flow path cross-sectional areas of the first distribution flow path 115a and the second distribution flow path 116a are different at positions where the distance A and the distance B are equal. Alternatively, the refrigerant distributor 50A has the first distribution flow path 115a and the second distribution flow path 115a at a position corresponding to the formation position of a certain communication hole portion 25 among the plurality of communication hole portions 25 formed along the first direction. The flow path shape is different so that the flow path cross-sectional area of the distribution flow path 116a is different. Hereinafter, the first flow path portion 115 and the second flow path portion 116 will be described with a focus on the differences from the refrigerant distributor 50 of the first embodiment.

The first flow path portion 115 extends from one end in the longitudinal direction to the other end in the longitudinal direction of the first plate-shaped member 10A along the longitudinal direction of the first plate-shaped member 10A. Both ends of the first flow path portion 115 in the stretching direction are closed. The first flow path portion 115 is formed in a square columnar shape in which one surface is inclined with respect to the major axis direction. The first flow path portion 115 is formed so as to taper from one end to the other end on the first refrigerant inflow port 18a side in the longitudinal direction of the first plate-shaped member 10A. The first flow path portion 115 has a rectangular cross-sectional shape. However, the cross-sectional shape of the first flow path portion 115 is not limited to a rectangle, and may be, for example, a semicircular shape, a semi-elliptical shape, or a semi-elliptical shape.

The second flow path portion 116 extends from one end in the longitudinal direction to the other end in the longitudinal direction of the first plate-shaped member 10A along the longitudinal direction of the first plate-shaped member 10A. Both ends of the second flow path portion 116 in the stretching direction are closed. The second flow path portion 116 is formed in a square columnar shape whose one surface is inclined with respect to the major axis direction. In the second flow path portion 116, the second refrigerant inflow port 18b is formed from one end on the side opposite to the side on which the second refrigerant inflow port 18b is formed in the longitudinal direction of the first plate-shaped member 10A. It is formed so as to taper toward the other end of the side. The second flow path portion 116 has a rectangular cross-sectional shape. However, the cross-sectional shape of the second flow path portion 116 is not limited to a rectangle, and may be, for example, a semicircular shape, a semi-elliptical shape, or a semi-elliptical shape.

The first flow path portion 115 and the second flow path portion 116 are not limited to a square columnar whose surface is inclined with respect to the major axis direction, and are, for example, a truncated cone shape or a polygonal pyramid stand. Other shapes such as a shape may be used. Further, the first flow path portion 115 and the second flow path portion 116 may be, for example, a square columnar whose one surface is inclined with respect to the extending direction of the heat transfer tube 70. That is, the first flow path portion 115 and the second flow path portion 116 may change the amount of protrusion of the wall in the extending direction of the heat transfer tube 70 in the longitudinal direction of the first plate-shaped member 10A.

Inside the first flow path portion 115, a first distribution flow path 115a extending in the vertical direction along the longitudinal direction of the first plate-shaped member 10A is formed. Further, inside the second flow path portion 116, a second distribution flow path 116a extending in the vertical direction along the longitudinal direction of the first plate-shaped member 10A is formed. The first distribution flow path 115a and the second distribution flow path 116a extend so as to intersect with each of the plurality of heat transfer tubes 70 when viewed in the plate thickness direction of the first plate-shaped member 10A. The first distribution flow path 115a and the second distribution flow path 116a have a rectangular cross-sectional shape. That is, the first distribution flow path 115a and the second distribution flow path 116a are spaces formed in a rectangular parallelepiped shape. However, the cross-sectional shapes of the first distribution flow path 115a and the second distribution flow path 116a are not limited to a rectangular shape, and may be, for example, a semicircular shape, a semi-elliptical shape, or a semi-long circular shape.

The cross-sectional area of the first distribution flow path 115a decreases from one end to the other end where the first refrigerant inflow port 18a is formed in the extending direction of the first flow path portion 115. On the other hand, the cross-sectional area of the second distribution flow path 116a increases from one end to the other end where the second refrigerant inflow port 18b is formed in the stretching direction of the first flow path portion 115. In the refrigerant distributor 50A shown in FIG. 7, the change in the cross-sectional area of the first distribution flow path 115a and the second distribution flow path 116a in the extension direction is the same as that of the first distribution flow path 115a in the major axis direction of the heat transfer tube 70. It depends on the change in the size of the second distribution flow path 116a. However, the change in the cross-sectional area of the first distribution flow path 115a and the second distribution flow path 116a in the extension direction is not limited to the configuration, and for example, the first distribution flow path 115a in the extension direction of the heat transfer tube 70. And may depend on the change in size of the second distribution channel 116a.

The first distribution flow path 115a and the second distribution flow path 116a communicate with the refrigerant inflow pipe 60 at the end in the extending direction. The gas-liquid two-phase refrigerant flowing into the first distribution flow path 115a and the second distribution flow path 116a via the refrigerant inflow pipe 60 is the first distribution flow path 115a and the second distribution flow path 116a as shown by an arrow F. Flows upward and is distributed to each heat transfer tube 70. The first branch pipe 62 is connected to the first flow path portion 115 and communicates with the first distribution flow path 115a, and the second branch pipe 63 is connected to the second flow path portion 116 and is connected to the second distribution flow path 116a. Communicate with.

The relationship between the first distribution flow path 115a and the second plate-shaped member 20, the third plate-shaped member 30, the fourth plate-shaped member 40, and the heat transfer tube 70 is the relationship between the first distribution flow path 15a and the second plate described above. Since the relationship is the same as that of the shape member 20, the third plate-shaped member 30, the fourth plate-shaped member 40, and the heat transfer tube 70, the description thereof will be omitted. Similarly, the relationship between the second distribution flow path 116a and the second plate-shaped member 20, the third plate-shaped member 30, the fourth plate-shaped member 40, and the heat transfer tube 70 is the second distribution flow path 16a and the second. Since the relationship is the same as that of the plate-shaped member 20, the third plate-shaped member 30, the fourth plate-shaped member 40, and the heat transfer tube 70, the description thereof will be omitted.

Next, the flow of the refrigerant in the refrigerant distributor 50 will be described. As described above, the first distribution flow path 115a is formed so that the cross-sectional area of the flow path decreases as the distance from the first refrigerant inflow port 18a increases in the stretching direction of the first flow path portion 115. Therefore, the flow velocity of the refrigerant flowing through the first distribution flow path 115a increases as the distance from the first refrigerant inflow port 18a, that is, toward the upward direction, increases. As a result, the refrigerant flowing through the first distribution flow path 115a has a predetermined height located above the first communication hole group 125a communicating with the first distribution flow path 115a, away from the first refrigerant inflow port 18a. It is distributed to each heat transfer tube 70 so that the flow rate of the refrigerant passing through the communication hole 25 is maximized.

On the other hand, the second distribution flow path 116a is formed so that the cross-sectional area of the flow path increases as the distance from the second refrigerant inflow port 18b increases in the extending direction of the second flow path portion 116. Therefore, the flow velocity of the refrigerant flowing through the second distribution flow path 116a decreases as the refrigerant flows away from the second refrigerant inflow port 18b, that is, as it goes upward. As a result, the refrigerant flowing through the second distribution flow path 116a communicates with a predetermined height located below the second refrigerant inflow port 18b in the second communication hole group 125b communicating with the second distribution flow path 116a. It is distributed to each heat transfer tube 70 so that the flow rate of the refrigerant passing through the hole 25 is maximized.

The refrigerant distributor 50A controls the flow velocity of the refrigerant flowing through the first distribution flow path 115a and the flow velocity of the refrigerant flowing through the second distribution flow path 116a by the difference in the size of the flow path cross-sectional area. Therefore, as shown by the dotted line A and the broken line B in FIG. 6, the position of the communication hole portion 25 where the refrigerant flow rate is maximum in the first communication hole group 125a is the communication where the refrigerant flow rate is maximum in the second communication hole group 125b. The position is farther from the refrigerant inflow port 18 than the position of the hole 25. In other words, as shown by the dotted line A and the broken line B in FIG. 6, the position of the communication hole portion 25 where the refrigerant flow rate is maximum in the second communication hole group 125b is such that the refrigerant flow rate is maximum in the first communication hole group 125a. The position is closer to the refrigerant inflow port 18 than the position of the communication hole portion 25.

The refrigerant that flows through the two distribution channels 115a and the second distribution flow path 116a and is distributed so as to maximize the refrigerant flow rate at different distances from the refrigerant inlet 18 is a third plate-shaped member. 30 joins each heat transfer tube 70 at the height of each heat transfer tube 70. As shown by the solid line C in FIG. 6, the total flow rate of the refrigerant flowing through the first distribution flow path 115a and the flow rate of the refrigerant flowing through the second distribution flow path 116a is approaching the alternate long and short dash line D. That is, the total flow rate of the flow rate of the refrigerant flowing through the first distribution flow path 115a and the flow rate of the refrigerant flowing through the second distribution flow path 116a suppresses the drift with respect to the distance from the refrigerant inflow port 18, and a plurality of transmissions. The flow rate of the refrigerant distributed to the heat pipe 70 can be made uniform.

Generally, in a refrigerant distributor, the higher the refrigerant flow rate in the distribution flow path through which the gas-liquid two-phase refrigerant flows upward, the larger the refrigerant flow rate is distributed to the upper heat transfer tube far from the refrigerant inlet. As described above, in the refrigerant distributor 50A, the flow path cross-sectional area decreases as the first distribution flow path 115a moves away from the first refrigerant inflow port 18a in the arrangement direction of the heat transfer tubes 70, and the second distribution flow path 116a becomes The flow path cross-sectional area is formed so as to increase as the distance from the second refrigerant inflow port 18b increases. The refrigerant distributor 50 is largely distributed to the lower heat transfer tube 70 by the second distribution flow path 16a, and is largely distributed to the upper heat transfer tube 70 by the first distribution flow path 15a. Then, the refrigerant distributor 50 merges the refrigerant flowing through the second distribution flow path 16a and the refrigerant flowing through the first distribution flow path 15a at the merging flow path 32 and flows them through the heat transfer tubes 70. Therefore, the refrigerant distributor 50 can equalize the distribution of the refrigerant flowing into each heat transfer tube 70 and improve the performance of the heat exchanger 80.

Embodiment 3.
FIG. 9 is an exploded perspective view showing a main configuration of the heat exchanger 80 provided with the refrigerant distributor 50B according to the third embodiment. FIG. 10 is a cross-sectional view showing the configuration of the refrigerant distributor 50B according to the third embodiment. The components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

In the refrigerant distributor 50B according to the third embodiment, the configuration of the first plate-shaped member 10B and the second plate-shaped member 20B is the first plate-shaped member 10 and the second plate-shaped member 10 of the refrigerant distributor 50 of the first embodiment. Different from member 20. Hereinafter, the first plate-shaped member 10B and the second plate-shaped member 20B will be described with a focus on the differences between the refrigerant distributors 50 of the first embodiment.

The first flow path portion 215 and the second flow path portion 216 extend from one end in the longitudinal direction to the other end in the longitudinal direction of the first plate-shaped member 10 along the longitudinal direction of the first plate-shaped member 10. The first flow path portion 215 and the second flow path portion 216 are formed in a semi-cylindrical shape. Both ends of the first flow path portion 215 and the second flow path portion 216 in the stretching direction are closed. The first flow path portion 215 and the second flow path portion 216 have a semicircular, semi-elliptical or semi-elliptical cross-sectional shape. However, the cross-sectional shapes of the first flow path portion 215 and the second flow path portion 216 are not limited to a semicircular shape, a semi-elliptical shape, or a semi-elliptical shape, and may be, for example, a rectangular shape.

Inside the first flow path portion 215, a first distribution flow path 215a extending in the vertical direction along the longitudinal direction of the first plate-shaped member 10B is formed. Similarly, inside the second flow path portion 216, a second distribution flow path 216a extending in the vertical direction along the longitudinal direction of the first plate-shaped member 10B is formed. The first distribution flow path 215a and the second distribution flow path 216a extend so as to intersect with each of the plurality of heat transfer tubes 70 when viewed in the plate thickness direction of the first plate-shaped member 10B.

The first distribution flow path 215a and the second distribution flow path 216a have a semicircular, semi-elliptical or semi-elliptical cross-sectional shape. That is, the first distribution flow path 215a and the second distribution flow path 216a are spaces formed in a semi-cylindrical shape, a semi-elliptical cylinder shape, or a semi-long cylindrical shape. However, the cross-sectional shapes of the first distribution flow path 215a and the second distribution flow path 216a are not limited to a semicircular shape, a semi-elliptical shape, or a semi-elliptical shape, and may be, for example, a rectangular shape.

The cross-sectional area of the first distribution flow path 215a is the same as the cross-sectional area of the second distribution flow path 216a. It should be noted that the same size includes a size that is completely equal and a size that has a slight error from each other. The first distribution flow path 215a and the second distribution flow path 216a communicate with the refrigerant inflow pipe 60 at the end in the extending direction. The gas-liquid two-phase refrigerant flowing into the first distribution flow path 215a and the second distribution flow path 216a via the refrigerant inflow pipe 60 is the first distribution flow path 215a and the second distribution flow path 216a as shown by an arrow F. Flows upward and is distributed to each heat transfer tube 70.

A refrigerant inflow pipe 60 communicates with the lower ends of the first distribution flow path 215a and the second distribution flow path 216a. The first branch pipe 62 is connected to the first flow path portion 215 and communicates with the first distribution flow path 215a, and the second branch pipe 63 is connected to the second flow path portion 216 to communicate with the second distribution flow path 216a. Communicate with.

A plurality of communication hole portions 25 are formed in the second plate-shaped member 20B. The plurality of communication hole portions 25 are composed of a first communication hole portion 25a and a second communication hole portion 25b. The opening diameter of the first communication hole portion 25a is smaller than that of the second communication hole portion 25b, and the flow path cross-sectional area is smaller. The second communication hole portion 25b has a larger opening diameter and a larger flow path cross-sectional area than the first communication hole portion 25a.

In the first communication hole group 125a, the second plate-shaped member 20 has the first communication hole portion 25a arranged above the second plate-shaped member 20B in the longitudinal direction and the second communication hole portion 25b arranged below. There is. That is, in the first communication hole group 125a, the second communication hole portion 25b is formed on the side of the first refrigerant inflow port 18a from the intermediate position in the longitudinal direction of the second plate-shaped member 20B, and the first refrigerant inflow port is formed from the intermediate position. The first communication hole portion 25a is formed on the side opposite to the 18a. Therefore, in the first communication hole group 125a, the cross-sectional area of the communication hole portion 25 provided below the second plate-shaped member 20 is larger than the cross-sectional area of the communication hole portion 25 provided above. That is, in the first communication hole group 125a, in the first direction which is the arrangement direction of the heat transfer tubes 70, the flow path cross-sectional area of the plurality of communication holes 25 on the side close to the first refrigerant inflow port 18a is the first refrigerant flow. It is formed larger than the flow path cross-sectional area of the plurality of communication hole portions 25 on the far side of the inlet 18a.

In the second communication hole group 125b, the second plate-shaped member 20 has the second communication hole portion 25b arranged above the second plate-shaped member 20B in the longitudinal direction and the first communication hole portion 25a arranged below. There is. That is, in the second communication hole group 125b, the first communication hole portion 25a is formed from the intermediate position to the second refrigerant inflow port 18b side in the longitudinal direction of the second plate-shaped member 20B, and the second refrigerant inflow port is formed from the intermediate position. A second communication hole portion 25b is formed on the side opposite to 18b. Therefore, in the second communication hole group 125b, the cross-sectional area of the communication hole portion 25 provided above the second plate-shaped member 20 is larger than the cross-sectional area of the communication hole portion 25 provided below. That is, in the second communication hole group 125b, in the first direction which is the arrangement direction of the heat transfer tubes 70, the flow path cross-sectional area of the plurality of communication holes 25 on the side far from the second refrigerant inflow port 18b is the second refrigerant flow. It is formed larger than the flow path cross-sectional area of the plurality of communication hole portions 25 on the side close to the inlet 18b. Here, in the first distribution flow path 215a, the distance from one end 51a of the main body 51 to the other end 51b is defined as a distance A, and in the second distribution flow path 216a, one end of the main body 51 is defined. The distance from 51a to the other end 51b is defined as the distance B. In the refrigerant distributor 50B, at a position where the distance A and the distance B are equal to each other, one of the plurality of communication hole portions 25 constituting the first communication hole group 125a and the plurality of communication hole portions 25 constituting the second communication hole group 125b are provided. The shape of the flow path is different so that the cross-sectional area of one flow path is different. Alternatively, the refrigerant distributor 50B constitutes the first communication hole group 125a at a position corresponding to the formation position of one communication hole portion 25 among the plurality of communication hole portions 25 formed along the first direction. The flow path shape is different so that one of the plurality of communication hole portions 25 and one of the plurality of communication hole portions 25 constituting the second communication hole group 125b have different flow path cross-sectional areas.

Next, the flow of the refrigerant in the refrigerant distributor 50B will be described. As described above, in the first communication hole group 125a, the cross-sectional area of the communication hole portion 25 provided below the second plate-shaped member 20 is larger than the cross-sectional area of the communication hole portion 25 provided above. Therefore, the refrigerant passing through the communication hole portion 25 has a small resistance when passing through the communication hole portion 25 at the lower part of the second plate-shaped member 20, and passes through the communication hole portion 25 at the upper part of the second plate-shaped member 20. There is a lot of resistance. Therefore, in the first communication hole group 125a, the refrigerant tends to flow to the lower communication hole 25 closer to the first refrigerant inlet 18a than to the upper communication hole 25 far from the first refrigerant inlet 18a.

On the other hand, in the second communication hole group 125b, the cross-sectional area of the communication hole portion 25 provided above the second plate-shaped member 20 is larger than the cross-sectional area of the communication hole portion 25 provided below. Therefore, the refrigerant passing through the communication hole portion 25 has a large resistance when passing through the communication hole portion 25 at the lower part of the second plate-shaped member 20, and passes through the communication hole portion 25 at the upper part of the second plate-shaped member 20. The resistance is small. Therefore, in the second communication hole group 125b, the refrigerant is more likely to flow to the upper communication hole 25 far from the second refrigerant inlet 18b than the lower communication hole 25 near the second refrigerant inlet 18b.

FIG. 11 is a conceptual diagram showing the refrigerant distribution of the refrigerant distributor 50B according to the third embodiment. In FIG. 11, the dotted line A shows the flow rate of the refrigerant flowing through the first distribution flow path 215a, and the broken line B shows the flow rate of the refrigerant flowing through the second distribution flow path 216a. Further, the solid line C shows the total flow rate of the flow rate of the refrigerant flowing through the first distribution flow path 215a and the flow rate of the refrigerant flowing through the second distribution flow path 216a. Further, the alternate long and short dash line D is a case where the total flow rate of the refrigerant flowing through the first distribution flow path 215a and the flow rate of the refrigerant flowing through the second distribution flow path 216a is equal to the distance from the refrigerant inlet 18. It is a line showing.

As shown by the dotted line A in FIG. 11, the communication hole portion 25 that maximizes the flow rate of the refrigerant passing through the plurality of communication hole portions 25 constituting the first communication hole group 125a, and the first refrigerant inflow port 18a. The distance between them is the first distance L1. Then, as shown by the broken line B, the communication hole portion 25 in which the flow rate of the refrigerant passing through the plurality of communication hole portions 25 constituting the second communication hole group 125b is maximized, and the second refrigerant inflow port 18b. The distance is the second distance L2. In this case, in the refrigerant distributor 50B, the first distance L1 and the second distance L2 are different distances.

The refrigerant distributor 50B according to the third embodiment has the same cross-sectional area as the first distribution flow path 215a and the second distribution flow path 216a. Then, in the first communication hole group 125a, the refrigerant tends to flow to the lower communication hole portion 25 closer to the first refrigerant inflow port 18a than the upper communication hole portion 25 far from the first refrigerant inflow port 18a. Therefore, as shown by the dotted line A in FIG. 11, the refrigerant flowing through the first distribution flow path 215a communicates below the first refrigerant inlet 18a with respect to the upper communication hole 25 far from the first refrigerant inlet 18a. The flow rate of the refrigerant passing through the hole 25 increases.

Similarly, the refrigerant distributor 50B has the same cross-sectional area as the first distribution flow path 215a and the second distribution flow path 216a. Then, in the second communication hole group 125b, the refrigerant tends to flow to the upper communication hole portion 25 far from the second refrigerant inflow port 18b than the lower communication hole portion 25 near the second refrigerant inflow port 18b. Therefore, as shown by the broken line B in FIG. 11, the refrigerant flowing through the second distribution flow path 216a communicates with the second refrigerant inflow port 18b far from the lower communication hole 25 near the second refrigerant inflow port 18b. The flow rate of the refrigerant passing through the hole 25 increases.

The refrigerant that flows through the two distribution channels 215a and the second distribution channel 216a and is distributed so as to maximize the refrigerant flow rate at different distances from the refrigerant inlet 18 is a third plate-shaped member. 30 joins each heat transfer tube 70 at the height of each heat transfer tube 70. As shown by the solid line C in FIG. 11, the total flow rate of the refrigerant flowing through the first distribution flow path 215a and the flow rate of the refrigerant flowing through the second distribution flow path 216a is approaching the alternate long and short dash line D. That is, the total flow rate of the flow rate of the refrigerant flowing through the first distribution flow path 215a and the flow rate of the refrigerant flowing through the second distribution flow path 216a suppresses the drift with respect to the distance from the refrigerant inflow port 18, and a plurality of transmissions. The flow rate of the refrigerant distributed to the heat pipe 70 can be made uniform.

It is said that the plurality of communication hole portions 25 of the refrigerant distributor 50B according to the third embodiment are composed of a first communication hole portion 25a and a second communication hole portion 25b. However, the plurality of communication hole portions 25 are not limited to two types, that is, the first communication hole portion 25a having a different flow path cross-sectional area and the second communication hole portion 25b. For example, the plurality of communication hole portions 25 constituting the first communication hole group 125a have a flow path cross-sectional area depending on the position where the communication hole portion 25 is formed from the upper side to the lower side in the longitudinal direction of the second plate-shaped member 20B. May be formed so that Further, the plurality of communication hole portions 25 constituting the second flow path hole group 126a cut the flow path from the lower side to the upper side depending on the position where the communication hole portion 25 is formed in the longitudinal direction of the second plate-shaped member 20B. It may be formed so that the area is large.

As described above, in the refrigerant distributor 50B, the first communication hole group 125a has the flow path cross-sectional area of the plurality of communication holes 25 on the side close to the first refrigerant inflow port 18a in the arrangement direction of the heat transfer tubes 70. The first refrigerant inflow port 18a is formed to be larger than the flow path cross-sectional area of the plurality of communication holes 25 on the far side. Further, in the refrigerant distributor 50B, the second refrigerant group 125b has a flow path cross-sectional area of a plurality of communication holes 25 on the side farther from the second refrigerant inlet 18b in the arrangement direction of the heat transfer tubes 70. It is formed larger than the flow path cross-sectional area of the plurality of communication hole portions 25 on the side close to the inflow port 18b. In the refrigerant distributor 50, a large amount of refrigerant is distributed to the lower heat transfer tube 70 by the flow path resistance of the first communication hole group 125a, and the refrigerant is distributed to the upper heat transfer tube 70 by the flow path resistance of the second communication hole group 125b. Is distributed a lot. Then, the refrigerant distributor 50 merges the refrigerant flowing through the second distribution flow path 216a and the refrigerant flowing through the first distribution flow path 215a at the merging flow path 32 and flows them through the heat transfer tubes 70. Therefore, the refrigerant distributor 50 can equalize the distribution of the refrigerant flowing into each heat transfer tube 70 and improve the performance of the heat exchanger 80.

Embodiment 4.
FIG. 12 is an exploded perspective view showing a main configuration of the heat exchanger 80 provided with the refrigerant distributor 50C according to the fourth embodiment. FIG. 13 is a cross-sectional view showing the configuration of the refrigerant distributor 50C according to the fourth embodiment. The components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

In the refrigerant distributor 50C according to the fourth embodiment, the configuration of the second plate-shaped member 20C is different from that of the second plate-shaped member 20 of the refrigerant distributor 50 of the first embodiment. Hereinafter, the refrigerant distributor 50C according to the fourth embodiment will be described focusing on the differences between the refrigerant distributor 50 of the first embodiment.

The second plate-shaped member 20C of the refrigerant distributor 50C according to the fourth embodiment has the same configuration as the second plate-shaped member 20B of the third embodiment. That is, a plurality of communication hole portions 25 are formed in the second plate-shaped member 20C. The plurality of communication hole portions 25 are composed of a first communication hole portion 25a and a second communication hole portion 25b. The opening diameter of the first communication hole portion 25a is smaller than that of the second communication hole portion 25b, and the flow path cross-sectional area is smaller. The second communication hole portion 25b has a larger opening diameter and a larger flow path cross-sectional area than the first communication hole portion 25a. Therefore, the refrigerant passing through the second plate-shaped member 20C has the characteristics shown in FIG. 11 described above, and in the first communication hole group 125a, the refrigerant is from the upper communication hole portion 25 far from the first communication inlet 18a. Also easily flows into the lower communication hole 25 near the first refrigerant inflow port 18a. Further, in the second communication hole group 125b, the refrigerant tends to flow to the upper communication hole 25 far from the second refrigerant inlet 18b than the lower communication hole 25 near the second refrigerant inlet 18b.

Further, the first plate-shaped member 10 of the refrigerant distributor 50C has a first distribution flow path 15a formed in the first flow path portion 15 and a second distribution flow path formed in the second flow path portion 16. 16a and 16a are formed so as to have different flow path cross-sectional areas from each other. Specifically, the flow path cross-sectional area of the second distribution flow path 16a is larger than the flow path cross-sectional area of the first distribution flow path 15a, and the flow path cross-sectional area of the first distribution flow path 15a is the second distribution flow flow. It is smaller than the flow path cross-sectional area of the road 16a. Therefore, the first plate-shaped member 10 has the characteristics shown in FIG. 6 described above, and the position of the communication hole portion 25 where the refrigerant flow rate is maximum in the first communication hole group 125a is the refrigerant flow rate in the second communication hole group 125b. Is a position farther from the first refrigerant inflow port 18a than the position of the communication hole portion 25 having the maximum value. The position of the communication hole portion 25 in which the refrigerant flow rate is maximum in the second communication hole group 125b is larger than the position of the communication hole portion 25 in which the refrigerant flow rate is maximum in the first communication hole group 125a. It will be close to.

The refrigerant distributor 50C has the following configuration from the first plate-shaped member 10 and the second plate-shaped member 20C described above. In the refrigerant distributor 50C, the first distribution flow path 15a has a smaller flow path cross-sectional area than the second distribution flow path 16a. Further, in the first communication hole group 125a communicating with the first distribution flow path 15a, the communication hole portion 25 having the cross-sectional area of the communication hole portion 25 provided at the lower portion of the second plate-shaped member 20C is cut off. Larger than the area. The first communication hole group 125a communicating with the first distribution flow path 15a breaks the flow paths of the plurality of communication hole portions 25 on the side close to the first refrigerant inflow port 18a in the first direction which is the arrangement direction of the heat transfer tubes 70. The area is formed larger than the flow path cross-sectional area of the plurality of communication holes 25 on the side far from the first refrigerant inflow port 18a. Further, in the refrigerant distributor 50C, a second communication hole group 125b communicating with the second distribution flow path 16a having a larger flow path cross-sectional area than the first distribution flow path 15a is provided above the second plate-shaped member 20C. The cross-sectional area of the communication hole portion 25 provided is larger than the cross-sectional area of the communication hole portion 25 provided at the lower part. The second communication hole group 125b communicating with the second distribution flow path 16a breaks the flow paths of the plurality of communication hole portions 25 on the side far from the second refrigerant inflow port 18b in the first direction, which is the arrangement direction of the heat transfer tubes 70. The area is formed larger than the flow path cross-sectional area of the plurality of communication holes 25 on the side close to the second refrigerant inflow port 18b. Here, in the first distribution flow path 15a, the distance from one end 51a of the main body 51 to the other end 51b is defined as a distance A, and in the second distribution flow path 16a, one end of the main body 51 is defined. The distance from 51a to the other end 51b is defined as the distance B. The refrigerant distributor 50C has a flow path shape of the first distribution flow path 15a and the second distribution flow path 16a at a position where the distance A and the distance B are equal, and a plurality of communication holes constituting the first communication hole group 125a. The flow path shapes of one of the portions 25 and one of the plurality of communication hole portions 25 constituting the second communication hole group 125b are different so that the flow path cross-sectional areas are different. Alternatively, the refrigerant distributor 50C has the first distribution flow path 15a and the second at a position corresponding to the formation position of one communication hole portion 25 among the plurality of communication hole portions 25 formed along the first direction. The flow path shape of the distribution flow path 16a, and the flow path shape of one of the plurality of communication hole portions 25 constituting the first communication hole group 125a and one of the plurality of communication hole portions 25 constituting the second communication hole group 125b. Are different so that the cross-sectional areas of the flow paths are different.

Next, the flow of the refrigerant in the refrigerant distributor 50C will be described. In the refrigerant distributor 50 of the first embodiment, when the refrigerant flow rate is large, a large amount of refrigerant is likely to be distributed to the upper heat transfer tube 70 in the first distribution flow path 15a having a small flow path cross-sectional area. Therefore, if the flow rate of the refrigerant flowing through the refrigerant distributor 50 becomes too large, an excessively large amount of refrigerant may flow through the upper heat transfer tube 70, and the refrigerant flowing through the refrigerant distributor 50 may flow unevenly.

The refrigerant distributor 50C is a communication hole portion located below the cross-sectional area of the communication hole portion 25 located at the upper part of the second plate-shaped member 20C in the first communication hole group 125a communicating with the first distribution flow path 15a. It is made smaller than the cross-sectional area of 25 to increase the flow path resistance of the communication hole portion 25 located at the upper part. Therefore, when the refrigerant flow rate is large, the refrigerant distributor 50C suppresses the refrigerant flow rate from becoming excessively large at a predetermined distance from the refrigerant inflow port 18 due to the flow path resistance formed by the second plate-shaped member 20C. be able to.

Similarly, in the refrigerant distributor 50C, in the second distribution flow path 16a having a large flow path cross-sectional area, a large amount of refrigerant is likely to be distributed to the lower heat transfer tube 70, and if the flow rate becomes too small, the lower heat transfer tube 70 Excessive amount of refrigerant may flow into the refrigerant, and the refrigerant flowing through the refrigerant distributor 50 may flow unevenly.

The refrigerant distributor 50C is a communication hole portion located above the cross-sectional area of the communication hole portion 25 located at the lower part of the second plate-shaped member 20C in the second communication hole group 125b communicating with the second distribution flow path 16a. It is made smaller than the cross-sectional area of 25 to increase the flow path resistance of the communication hole portion 25 located at the lower part. Therefore, when the refrigerant flow rate is small, the refrigerant distributor 50C suppresses the refrigerant flow rate from becoming excessively large at a predetermined distance from the refrigerant inflow port 18 due to the flow path resistance formed by the second plate-shaped member 20C. be able to.

As described above, in the refrigerant distributor 50C, the flow path cross-sectional area of the second distribution flow path 16a is larger than the flow path cross-sectional area of the first distribution flow path 15a, and the flow path cross-sectional area of the first distribution flow path 15a. However, it is smaller than the flow path cross-sectional area of the second distribution flow path 16a. Further, in the first communication hole group 125a communicating with the first distribution flow path 15a, the flow path cross-sectional area of the plurality of communication hole portions 25 on the side close to the first refrigerant inflow port 18a in the first direction is the first refrigerant. It is formed larger than the flow path cross-sectional area of the plurality of communication holes 25 on the far side of the inflow port 18a. Further, in the second communication hole group 125b communicating with the second distribution flow path 16a, the flow path cross-sectional area of the plurality of communication hole portions 25 on the side far from the second refrigerant inflow port 18b in the first direction is the second refrigerant. It is formed larger than the flow path cross-sectional area of the plurality of communication hole portions 25 on the side close to the inflow port 18b.

The refrigerant distributor 50C has an excessively large amount of refrigerant in the upper heat transfer tube 70 in the first distribution flow path 15a in which the flow path cross-sectional area is small and a large amount of refrigerant is easily distributed to the upper heat transfer tube 70 when the refrigerant flow rate becomes large. Suppresses the uneven flow. Further, the refrigerant distributor 50C is provided to the lower heat transfer tube 70 in the second distribution flow path 16a, which has a large flow path cross-sectional area and tends to distribute a large amount of refrigerant to the lower heat transfer tube 70 when the refrigerant flow rate becomes small. It is possible to prevent an excessively large amount of refrigerant from flowing unevenly. Therefore, the refrigerant distributor 50C can improve the distribution robustness with respect to the refrigerant flow rate, and can expand the operating range of the air conditioner equipped with the refrigerant distributor 50C. Further, for example, in a conventional refrigerant distributor, the distribution characteristics to each heat transfer tube largely depend on the flow velocity of the refrigerant in the refrigerant distributor, so that the distribution robustness with respect to the flow rate of the refrigerant that changes depending on the operating state of the air conditioner. Is low. The distribution robustness is a flow rate that can be approached to even distribution to heat transfer tubes when the flow rate of the refrigerant used in an air conditioner or the like is not a specific flow rate of the refrigerant but a range of the flow rate. The ability to expand the range. Compared to this conventional refrigerant distributor, the refrigerant distributor 50C according to the fourth embodiment can improve the distribution robustness with respect to the refrigerant flow rate as described above.

Embodiment 5.
FIG. 14 is an exploded perspective view showing a main configuration of the heat exchanger 80 provided with the refrigerant distributor 50D according to the fifth embodiment. FIG. 15 is a cross-sectional view showing the configuration of the refrigerant distributor 50D according to the fifth embodiment. The white arrow AF shown in FIGS. 14 and 15 indicates the flow of wind. The air flow toward the refrigerant distributor 50D is formed by, for example, the indoor blower 109 of the refrigeration cycle device 100 shown in FIG. 1 or the outdoor blower 108. In FIG. 15, the arrows F1 and F2 shown by hatching indicate the flow of the refrigerant passing through the second plate-shaped member 20D and flowing into the merging flow path 32 formed in the third plate-shaped member 30. .. The components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

The configuration of the second plate-shaped member 20D of the refrigerant distributor 50D according to the fifth embodiment is different from that of the second plate-shaped member 20 of the refrigerant distributor 50 of the first embodiment. Hereinafter, the refrigerant distributor 50D according to the fifth embodiment will be described focusing on the differences between the refrigerant distributor 50 of the first embodiment.

A plurality of communication hole portions 25 are formed in the second plate-shaped member 20D of the refrigerant distributor 50D according to the fifth embodiment. The plurality of communication hole portions 25 are composed of a first communication hole portion 25a and a second communication hole portion 25b. The opening diameter of the first communication hole portion 25a is smaller than that of the second communication hole portion 25b, and the flow path cross-sectional area is smaller. The second communication hole portion 25b has a larger opening diameter and a larger flow path cross-sectional area than the first communication hole portion 25a. In the second plate-shaped member 20D, the first communication hole group 125a is composed of the first communication hole portion 25a. Further, in the second plate-shaped member 20D, the second communication hole group 125b is composed of the second communication hole portion 25b.

The refrigerant distributor 50D according to the fifth embodiment is configured such that the first communication hole group 125a and the first flow path portion 15 are arranged on the side where the indoor blower 109 or the outdoor blower 108 is arranged. Has been done. That is, in the refrigerant distributor 50D according to the fifth embodiment, the first communication hole group 125a and the first flow path portion 15 are located on the upstream side of the wind flow in the flow direction of the wind passing through the refrigerant distributor 50D. It is configured to be placed. The refrigerant distributor 50D is configured such that the second communication hole group 125b and the second flow path portion 16 are arranged on the downstream side of the wind flow in the flow direction of the wind passing through the refrigerant distributor 50D. Has been done.

In the refrigerant distributor 50D according to the fifth embodiment, the total cross-sectional area of the first communication hole group 125a located on the windward side of the air among the two communication hole groups communicating with each of the two distribution flow paths is leeward. It is smaller than the total cross-sectional area of the second communication hole group 125b located on the side. Therefore, the flow velocity of the refrigerant in the flow of the refrigerant (arrow F1) that passes through the first communication hole group 125a and flows into the merging flow path 32 is the flow rate of the refrigerant that passes through the second communication hole group 125b and flows into the merging flow path 32. It is larger than the flow velocity of the refrigerant in (arrow F2). That is, the flow velocity of the refrigerant in the flow of the refrigerant (arrow F2) that passes through the second communication hole group 125b and flows into the merging flow path 32 is the flow rate of the refrigerant that passes through the first communication hole group 125a and flows into the merging flow path 32. It is smaller than the flow velocity of the refrigerant in (arrow F1). The total cross-sectional area of the first communication hole group 125a is the sum of the cross-sectional areas of the first communication hole portions 25a constituting the first communication hole group 125a. Similarly, the total cross-sectional area of the second communication hole group 125b is the sum of the cross-sectional areas of the second communication hole portions 25b constituting the second communication hole group 125b.

The first plate-shaped member 10 of the refrigerant distributor 50D includes a first distribution flow path 15a formed in the first flow path portion 15 and a second distribution flow path 16a formed in the second flow path portion 16. Are formed so as to have different flow path cross-sectional areas from each other. Specifically, the cross-sectional area of the second distribution flow path 16a is larger than the cross-sectional area of the first distribution flow path 15a, and the cross-sectional area of the first distribution flow path 15a is larger than the cross-sectional area of the second distribution flow path 16a. Is also small. Therefore, the first plate-shaped member 10 has the characteristics shown in FIG. 6 described above, and the position of the communication hole portion 25 where the refrigerant flow rate is maximum in the first communication hole group 125a is the refrigerant flow rate in the second communication hole group 125b. Is a position farther from the refrigerant inflow port 18 than the position of the communication hole portion 25 having the maximum value. The position of the communication hole portion 25 in which the refrigerant flow rate is maximum in the second communication hole group 125b is closer to the refrigerant inflow port 18 than the position of the communication hole portion 25 in which the refrigerant flow rate is maximum in the first communication hole group 125a. It becomes the position. Then, the total flow rate of the flow rate of the refrigerant flowing through the first distribution flow path 15a and the flow rate of the refrigerant flowing through the second distribution flow path 16a is suppressed from being drifted with respect to the distance from the refrigerant inflow port 18, and a plurality of transmissions are performed. The flow rate of the refrigerant distributed to the heat pipe 70 can be made uniform. Here, in the first distribution flow path 15a, the distance from one end 51a of the main body 51 to the other end 51b is defined as a distance A, and in the second distribution flow path 16a, one end of the main body 51 is defined. The distance from 51a to the other end 51b is defined as the distance B. The refrigerant distributor 50D has a flow path shape of the first distribution flow path 15a and the second distribution flow path 16a at a position where the distance A and the distance B are equal, and a plurality of communication holes constituting the first communication hole group 125a. The flow path shapes of one of the portions 25 and one of the plurality of communication hole portions 25 constituting the second communication hole group 125b are different so that the flow path cross-sectional areas are different. Alternatively, the refrigerant distributor 50D has the first distribution flow path 15a and the second at a position corresponding to the formation position of one communication hole portion 25 among the plurality of communication hole portions 25 formed along the first direction. The flow path shape of the distribution flow path 16a, and the flow path shape of one of the plurality of communication hole portions 25 constituting the first communication hole group 125a and one of the plurality of communication hole portions 25 constituting the second communication hole group 125b. Are different so that the cross-sectional areas of the flow paths are different.

The refrigerant distributor 50D according to the fifth embodiment is connected to the heat exchanger 80. The heat transfer tube 70 constituting the heat exchanger 80 to which the refrigerant distributor 50D is connected is a flat perforated tube having a plurality of refrigerant passages 72. In general, in a heat exchanger, the amount of heat conversion between the refrigerant and air is larger on the windward side of air.

Next, the flow and action of the refrigerant in the refrigerant distributor 50D will be described. As described above, the flow velocity of the refrigerant in the flow of the refrigerant (arrow F1) that passes through the first communication hole group 125a and flows into the merging flow path 32 flows into the merging flow path 32 through the second communication hole group 125b. It is larger than the flow velocity of the refrigerant in the flow of the refrigerant (arrow F2). That is, the refrigerant distributor 50D has a communication hole portion 25 located on the windward side in the merging flow path 32 in which the refrigerant merges through the communication hole portion 25 communicating with the first distribution flow path 15a and the second distribution flow path 16a. The flow velocity of the refrigerant in the vicinity is increased. By having the above configuration, the refrigerant distributor 50D has a large inertial force of the refrigerant, and in the heat transfer pipe 70 which is a flat pipe, a larger amount of the refrigerant can flow through the refrigerant passage 72 on the windward side where the heat load is large. Since the refrigerant distributor 50D can distribute the refrigerant to the heat transfer tube 70 of the heat exchanger 80 according to the heat conversion, the heat conversion capacity of the heat exchanger 80 can be improved.

As described above, the refrigerant distributor 50D according to the fifth embodiment is the total of the first communication hole group 125a located on the windward side of the air among the two communication hole groups communicating with each of the two distribution channels. The cross-sectional area is smaller than the total cross-sectional area of the second communication hole group 125b located on the leeward side. The refrigerant distributor 50D has a communication hole portion 25 located on the windward side in the merging flow path 32 where the refrigerants distributed by the two distribution flow paths 15a and the second distribution flow path 16a merge. The flow velocity of the refrigerant flowing into the merging flow path 32 via the merging flow path 32 is made larger than that on the leeward side. Therefore, in the refrigerant distributor 50D, the refrigerant easily flows in the flow path on the wind side of the heat transfer tube 70 having a large heat load, and the heat exchange performance of the heat exchanger 80 can be improved.

Embodiment 6.
FIG. 16 is a perspective view of the refrigerant distributor 50E according to the sixth embodiment. FIG. 17 is a perspective view schematically showing the internal configuration of the refrigerant distributor 50E according to the sixth embodiment. FIG. 18 is a cross-sectional view showing the configuration of the refrigerant distributor 50E according to the sixth embodiment. FIG. 19 is a vertical cross-sectional view showing the configuration of the refrigerant distributor 50E according to the sixth embodiment. The refrigerant distributor 50E according to the sixth embodiment will be described with reference to FIGS. 16 to 19. The components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

The main body 51 of the refrigerant distributors 50 to 50D of the first to fifth embodiments is configured by laminating the first plate-shaped members 10 to the fourth plate-shaped members 40. On the other hand, the main body 52 of the refrigerant distributor 50E of the sixth embodiment is configured by using a tubular member.

The refrigerant distributor 50E has a main body 52 extending in the arrangement direction of the heat transfer tubes 70. The main body 52 of the refrigerant distributor 50E includes a tubular portion 90 extending in the arrangement direction of the heat transfer pipe 70, a first space S1 connected to the refrigerant inflow pipe 60 in the hollow portion of the tubular portion 90, and a plurality of heat transfer tubes 70. It has a first wall portion 91 that partitions the second space S2 connected to the second space S2. Further, the main body 52 of the refrigerant distributor 50E has a second wall portion 92 for partitioning the first space S1 into the first distribution flow path 315a and the second distribution flow path 316a, and the heat transfer tube 70 for the second space S2. It has a third wall portion 93 that is partitioned in the arrangement direction to form a merging flow path 32. Further, the main body 52 of the refrigerant distributor 50E has a lid portion 94 that closes both ends of the tubular portion 90, respectively.

The tubular portion 90 is formed in a hollow cylindrical shape extending in the arrangement direction of the heat transfer tubes 70. However, the tubular portion 90 is not limited to a cylindrical shape, and may be a cylindrical shape, for example, a rectangular parallelepiped box shape may be formed.

The first wall portion 91 has a strip-like shape that is long in one direction. The first wall portion 91 is a plate-shaped portion extending in the arrangement direction of the plurality of heat transfer tubes 70, and the longitudinal direction of the first wall portion 91 is the arrangement direction of the plurality of heat transfer tubes 70. Further, the lateral direction of the first wall portion 91 is the major axis direction of the heat transfer tube 70, and the plate thickness direction of the first wall portion 91 is the extension direction of the heat transfer tube 70.

The first wall portion 91 has a communication hole portion 25. Therefore, the first wall portion 91 exhibits the same function as any one of the second plate-shaped member 20, the second plate-shaped member 20B, the second plate-shaped member 20C, and the second plate-shaped member 20D described above. The communication hole portion 25 of the first wall portion 91 constitutes the first communication hole group 125a and the second communication hole group 125b in the same manner as the second plate-shaped member 20 and the like. The first wall portion 91 divides the hollow portion of the tubular portion 90 into the first space S1 and the second space S2. The first space S1 and the second space S2 communicate with each other through the communication hole portion 25.

The second wall portion 92 has a strip-like shape that is long in one direction. The second wall portion 92 is a plate-shaped portion extending in the arrangement direction of the plurality of heat transfer tubes 70, and the longitudinal direction of the second wall portion 92 is the arrangement direction of the plurality of heat transfer tubes 70. Further, the lateral direction of the second wall portion 92 is the extending direction of the heat transfer tube 70, and the plate thickness direction of the second wall portion 92 is the major axis direction of the heat transfer tube 70.

The second wall portion 92 divides the first space S1 into a first distribution flow path 315a and a second distribution flow path 316a. The first distribution flow path 315a is formed in the first flow path portion 315 composed of the cylindrical portion 90, the first wall portion 91, the second wall portion 92, and the lid portion 94. Similarly, the second distribution flow path 316a is formed in the second flow path portion 316 composed of the cylindrical portion 90, the first wall portion 91, the second wall portion 92, and the lid portion 94. There is.

The first distribution flow path 315a and the second distribution flow path 316a have the same configuration as the first distribution flow path 15a and the second distribution flow path 16a described above, and exhibit the same functions. That is, the flow path cross-sectional area of the first distribution flow path 315a and the flow path cross-sectional area of the second distribution flow path 316a are formed so as to be different. Further, the first flow path portion 315 and the second flow path portion 316 have the same configurations as those of the first flow path portion 15 and the second flow path portion 16 described above, and exhibit the same functions. A refrigerant inflow pipe 60 is connected to the first flow path portion 315 and the second flow path portion 316. Here, in the first distribution flow path 315a, the distance from one end 51a of the main body 51 to the other end 51b is defined as a distance A, and in the second distribution flow path 316a, one end of the main body 51 is defined. The distance from 51a to the other end 51b is defined as the distance B. The refrigerant distributor 50E has a different flow path shape so that the flow path cross-sectional areas of the first distribution flow path 315a and the second distribution flow path 316a are different at positions where the distance A and the distance B are equal. Alternatively, the refrigerant distributor 50E has the first distribution flow path 315a and the second distribution flow path 315a at a position corresponding to the formation position of one communication hole portion 25 among the plurality of communication hole portions 25 formed along the first direction. The flow path shape is different so that the flow path cross-sectional area of the distribution flow path 316a is different. In the refrigerant distributor 50E, the formation position of the second wall portion 92 is moved in the major axis direction of the heat transfer tube 70, and the flow path cross-sectional areas of the first distribution flow path 315a and the second distribution flow path 316a are the same size. It may be formed in the air.

The third wall portion 93 is a plate-shaped member. The third wall portion 93 is the extending direction of the heat transfer tube 70 and the major axis direction of the heat transfer tube 70. A plurality of the third wall portions 93 are provided in the hollow portion of the tubular portion 90, and the plurality of third wall portions 93 are arranged in the arrangement direction of the plurality of heat transfer tubes 70. The plurality of third wall portions 93 partition the second space S2 in the arrangement direction of the heat transfer tubes 70, and form a confluence flow path 32. More specifically, the merging flow path 32 is formed by a cylindrical portion 90, a first wall portion 91, and a third wall portion 93. Alternatively, the merging flow path 32 is formed by a cylindrical portion 90, a first wall portion 91, a third wall portion 93, and a lid portion 94.

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

The refrigerant distributor 50E has the same basic configurations and functions as the refrigerant distributor 50 and the like, such as the first distribution flow path 15a and the second distribution flow path 16a, the communication hole portion 25, and the merging flow path 32. The refrigerant distributor 50E exerts the same function as the refrigerant distributor 50 and the like, and exerts the same action and effect.

FIG. 20 is a perspective view schematically showing an internal configuration of a modified example of the refrigerant distributor 50E according to the sixth embodiment. In the modified example refrigerant distributor 50E, the second wall portion 92a is tilted in the major axis direction of the heat transfer tube 70. Therefore, the first distribution flow path 315a and the second distribution flow path 316a have the same configuration as the first distribution flow path 115a and the second distribution flow path 116a of the refrigerant distributor 50A according to the second embodiment. That is, the flow path cross-sectional area of the first distribution flow path 315a of the refrigerant distributor 50E decreases as it goes upward, and the flow path cross-sectional area of the second distribution flow path 316a increases as it goes upward. Therefore, the refrigerant distributor 50E of the modified example exhibits the same functions and effects as the refrigerant distributor 50A of the second embodiment. In the first distribution flow path 315a, the distance from one end 51a of the main body 51 to the other end 51b is defined as a distance A in the first distribution flow path 315a, and in the second distribution flow path 316a, as in the second embodiment. The distance from one end 51a of the main body 51 toward the other end 51b is defined as the distance B. The refrigerant distributor 50E has a different flow path shape so that the flow path cross-sectional areas of the first distribution flow path 315a and the second distribution flow path 316a are different at positions where the distance A and the distance B are equal. Alternatively, the refrigerant distributor 50E has the first distribution flow path 315a and the second distribution flow path 315a at a position corresponding to the formation position of one communication hole portion 25 among the plurality of communication hole portions 25 formed along the first direction. The flow path shape is different so that the flow path cross-sectional area of the distribution flow path 316a is different.

FIG. 21 is a conceptual diagram of a modified example of the first wall portion 91 of the refrigerant distributor 50E according to the sixth embodiment. The first wall portion 91a is a modified example of the first wall portion 91, and has the same configuration as the second plate-shaped member 20B. That is, the first wall portion 91a has different formation positions of the first communication hole portion 25a and the second communication hole portion 25b in the first communication hole group 125a and the second communication hole group 125b.

FIG. 22 is a conceptual diagram of another modification of the first wall portion 91 of the refrigerant distributor 50E according to the sixth embodiment. The first wall portion 91b is a modified example of the first wall portion 91, and has the same configuration as the second plate-shaped member 20D of the refrigerant distributor 50D according to the fifth embodiment. That is, the first wall portion 91a has a first communication hole portion 25a in the first communication hole group 125a and a second communication hole portion 25b in the second communication hole group 125b.

The refrigerant distributor 50E has a position where the second wall portion 92 is formed, an inclination of the second wall portion 92, and a communication hole forming the first communication hole group 125a and the second communication hole group 125b formed in the first wall portion 91. By combining the types of the parts 25 and the like, the same function as the refrigerant distributor 50 is exhibited. Similarly, the refrigerant distributor 50E exerts the same functions as the refrigerant distributor 50A to the refrigerant distributor 50D by combining the second wall portion 92 and the communication hole portion 25 of the first wall portion 91. Therefore, the refrigerant distributor 50E can exert the same effect as the refrigerant distributor 50D from the refrigerant distributor 50 of the first to fifth embodiments described above.

The configurations of the refrigerant distributor 50, the refrigerant distributor 50A, the refrigerant distributor 50B, the refrigerant distributor 50C, the refrigerant distributor 50D, and the refrigerant distributor 50E described above have the following features. The refrigerant distributor 50 or the like has at least one flow path having a flow path shape between the first distribution flow path 15a and the second distribution flow path 16a and a flow path shape between the first communication hole group 125a and the second communication hole group 125b. It is formed so that the shape is different. Then, in the refrigerant distributor 50 and the like, the communication hole portion 25 and the refrigerant inflow port 18 where the flow rate of the refrigerant passing through the plurality of communication hole portions 25 in the first direction, which is the arrangement direction of the heat transfer tubes 70, is maximized. The distance between them is different between the first communication hole group 125a and the second communication hole group 125b. Here, in the first distribution flow path, the distance from one end 51a of the main body 51 to the other end 51b is defined as a distance A, and in the second distribution flow path, from one end 51a of the main body 51. The distance toward the other end 51b is defined as the distance B. The refrigerant distributor 50, the refrigerant distributor 50A, the refrigerant distributor 50B, the refrigerant distributor 50C, the refrigerant distributor 50D and the refrigerant distributor 50E are the first distribution flow path and the second distribution flow path at positions where the distance A and the distance B are equal. The shape of the flow path with the distribution flow path, and the flow path between one of the plurality of communication hole portions 25 constituting the first communication hole group 125a and one of the plurality of communication hole portions 25 constituting the second communication hole group 125b. Of the shapes, at least one of the flow paths is different. Alternatively, the refrigerant distributor has a first distribution flow path and a second distribution flow at a position corresponding to the formation position of a certain communication hole portion 25 among the plurality of communication hole portions 25 formed along the first direction. The shape of the flow path with the road, and the shape of the flow path between one of the plurality of communication hole portions 25 constituting the first communication hole group 125a and one of the plurality of communication hole portions 25 constituting the second communication hole group 125b. Of these, at least one of them has a different flow path shape. Therefore, the refrigerant distributor 50, the refrigerant distributor 50A, the refrigerant distributor 50B, the refrigerant distributor 50C, the refrigerant distributor 50D, and the refrigerant distributor 50E have different distances from the first distance L1 and the second distance L2 described above. It is configured as follows. As a result, the total flow rate of the flow rate of the refrigerant flowing through the first distribution flow path 15a and the flow rate of the refrigerant flowing through the second distribution flow path 16a suppresses the drift with respect to the distance from the refrigerant inflow port 18, and a plurality of flow rates are suppressed. The flow rate of the refrigerant distributed to the heat transfer tube 70 can be made uniform.

Further, in the refrigerant distributor 50 or the like, when the refrigerant distributor is applied over a plurality of heat exchangers through which refrigerants in different flow rate ranges flow, the first plate-shaped member 10 or the communication hole portion 25 constituting the distribution flow path is formed. It can be dealt with by replacing any of the second plate-shaped members 20. That is, in the refrigerant distributor 50 and the like, the manufacturing cost can be reduced because the flow rate range for uniform refrigerant distribution can be changed by replacing the first plate-shaped member 10 or the second plate-shaped member 20.

The heat exchanger 80 includes the refrigerant distributor according to any one of the first to sixth embodiments. Therefore, the heat exchanger 80 has the same effect as that of any of the first to sixth embodiments. Further, the refrigeration cycle device 100 includes the refrigerant distributor according to any one of the first to sixth embodiments. Therefore, the refrigeration cycle device 100 can obtain the same effect as that of any one of the first to sixth embodiments.

Each of the above embodiments 1 to 6 can be carried out in combination with each other. Further, the configuration shown in the above embodiment is an example, and can be combined with another known technique, and a part of the configuration is omitted or changed without departing from the gist. It is also possible. For example, in the refrigerant distributors 50 and the like according to the first to sixth embodiments, the arrangement direction of the heat transfer tubes 70 is described as the vertical direction in the vertical direction, but the arrangement direction of the heat transfer tubes 70 is the horizontal direction. May be good. Further, the arrangement direction of the heat transfer tubes 70 may be inclined with respect to the vertical direction. Therefore, the refrigerant distributor 50 and the like according to the first to sixth embodiments may be a vertical type in which the main body 51 extends in the vertical direction or a horizontal type in which the main body 51 extends in the horizontal direction. Further, the refrigerant distributor 50 and the like according to the first to sixth embodiments may have a configuration in which the main body 51 is tilted with respect to the vertical direction.

10 1st plate-shaped member, 10A 1st plate-shaped member, 10B 1st plate-shaped member, 11a flat plate portion, 11b flat plate portion, 11c flat plate portion, 15 1st flow path portion, 15a 1st distribution flow path, 16 2nd Channel part, 16a 2nd distribution flow path, 18 refrigerant inflow port, 18a 1st refrigerant inflow port, 18b 2nd refrigerant inflow port, 20 2nd plate-shaped member, 20B 2nd plate-shaped member, 20C second plate-shaped member , 20D 2nd plate-shaped member, 24 closed part, 25 communication hole part, 25a 1st communication hole part, 25b 2nd communication hole part, 30 3rd plate-shaped member, 31 through hole part, 32 confluence flow path, 40th 4 plate-shaped member, 41 insertion hole, 50 refrigerant distributor, 50A refrigerant distributor, 50B refrigerant distributor, 50C refrigerant distributor, 50D refrigerant distributor, 50E refrigerant distributor, 51 main body, 51a one end, 51b the other End, 52 body, 60 refrigerant inflow pipe, 61 base, 62 1st branch pipe, 63 2nd branch pipe, 70 heat transfer tube, 70a 1st side end, 70b 2nd side end, 70c flat surface, 70d Flat surface, 71 gap, 72 refrigerant passage, 75 heat transfer fin, 80 heat exchanger, 90 tubular part, 91 first wall part, 91a first wall part, 91b first wall part, 92 second wall part, 92a 2nd wall, 93 3rd wall, 94 lid, 100 refrigeration cycle device, 101 compressor, 102 flow path switching device, 103 indoor heat exchanger, 104 decompression device, 105 outdoor heat exchanger, 106 outdoor unit, 107 Indoor unit, 108 Outdoor blower, 109 Indoor blower, 110 Refrigerant circuit, 111 Extension pipe, 112 Extension pipe, 115 1st flow path, 115a 1st distribution flow path, 116 2nd flow path, 116a 2nd distribution flow Road, 125a 1st communication hole group, 125b 2nd communication hole group, 126a 2nd flow path hole group, 215 1st flow path part, 215a 1st distribution flow path, 216 2nd flow path part, 216a 2nd distribution flow Road, 315 first flow path portion, 315a first distribution flow path, 316 second flow path section, 316a second distribution flow path.

The refrigerant distributor according to the present invention is a refrigerant distributor which is arranged at intervals in the first direction and is connected to a heat exchanger provided with a plurality of heat transfer tubes for circulating the refrigerant inside. Has a plurality of insertion holes in which a first refrigerant inlet and a second refrigerant inlet are formed on one side surface side and a plurality of heat transfer tubes are inserted on the other side surface side in the extending direction of the plurality of heat transfer tubes. It has a formed main body, and the main body communicates with the first refrigerant inlet and extends in the first direction, and communicates with the second refrigerant inlet and is parallel to the first distribution flow path. The second distribution flow path extending in the first direction and the refrigerant flowing through the first distribution flow path and the second distribution flow path communicate with the plurality of heat transfer tubes when the plurality of heat transfer tubes are inserted into the main body. A first communication hole group composed of a plurality of merging flow paths to be merged, a plurality of communication holes formed along the first direction, and a plurality of communication holes for communicating each of the plurality of merging flow paths with the first distribution flow path. And a second communication hole group formed along the first direction and composed of a plurality of communication hole portions for communicating each of the plurality of merging flow paths and the second distribution flow path. the first coolant inlet and the second refrigerant inlet is formed at one end of the body in a first direction, the first distribution passage, from one end of the body in the first direction When the distance toward the other end is defined as the distance A and the distance from one end of the main body in the first direction to the other end in the second distribution flow path is defined as the distance B, the distance A is defined as the distance A. At a position where the distance B is equal, the flow path shape of the first distribution flow path and the second distribution flow path, and one of the plurality of communication hole portions constituting the first communication hole group and the second communication hole group are formed. Of the flow path shapes with one of the plurality of communication holes, at least one of the flow path shapes is different.

Claims (10)

A refrigerant distributor that is arranged at intervals in the first direction and is connected to a heat exchanger having a plurality of heat transfer tubes for circulating the refrigerant inside.
The refrigerant distributor is
In the extending direction of the plurality of heat transfer tubes, a first refrigerant inlet and a second refrigerant inlet are formed on one side surface side, and a plurality of insertion holes into which the plurality of heat transfer tubes are inserted are formed on the other side surface side. Has a formed body,
The main body
A first distribution flow path that communicates with the first refrigerant inlet and extends in the first direction.
A second distribution flow path that communicates with the second refrigerant inlet and extends in the first direction in parallel with the first distribution flow path.
When the plurality of heat transfer tubes are inserted into the main body, the plurality of confluence channels communicate with the plurality of heat transfer tubes and the refrigerants flowing through the first distribution flow path and the second distribution flow path merge. ,
A first communication hole group formed along the first direction and composed of a plurality of communication hole portions that communicate each of the plurality of merging flow paths and the first distribution flow path.
A second communication hole group formed along the first direction and composed of a plurality of communication hole portions that communicate each of the plurality of merging flow paths and the second distribution flow path.
Is formed,
The first refrigerant inlet and the second refrigerant inlet are formed on one end side of the main body in the first direction.
In the first distribution flow path, the distance from the one end of the main body to the other end is defined as a distance A, and in the second distribution flow path, the distance from the one end of the main body to the other. When the distance toward the end of is defined as the distance B,
At a position where the distance A and the distance B are equal, the shape of the flow path between the first distribution flow path and the second distribution flow path, and one of the plurality of communication hole portions constituting the first communication hole group. A refrigerant distributor in which at least one of the flow path shapes with one of the plurality of communication hole portions constituting the second communication hole group is different. The refrigerant distributor according to claim 1, wherein the flow path cross-sectional area of the first distribution flow path and the flow path cross-sectional area of the second distribution flow path are different. In the first direction, the flow path cross-sectional area of the first distribution flow path decreases as the distance from the first refrigerant inflow port increases, and the flow path of the second distribution flow path decreases as the distance from the second refrigerant inflow port increases. The refrigerant distributor according to claim 1 or 2, wherein the cross-sectional area is expanded. The first communication hole group is
In the first direction, the flow path cross-sectional area of the plurality of communication holes on the side close to the first refrigerant inflow port is the flow path cross-sectional area of the plurality of communication holes on the side far from the first refrigerant inflow port. Is formed larger than
The second communication hole group is
In the first direction, the flow path cross-sectional area of the plurality of communication holes on the side far from the second refrigerant inflow port is the flow path cross-sectional area of the plurality of communication holes on the side close to the second refrigerant inflow port. The refrigerant distributor according to any one of claims 1 to 3, which is formed larger than the above. The first distribution flow path is formed to have a smaller flow path cross-sectional area than the second distribution flow path.
The first communication hole group communicating with the first distribution flow path is
In the first direction, the flow path cross-sectional area of the plurality of communication holes on the side close to the first refrigerant inflow port is the flow path cross-sectional area of the plurality of communication holes on the side far from the first refrigerant inflow port. Is formed larger than
The second distribution flow path has a larger flow path cross-sectional area than the first distribution flow path.
The second communication hole group communicating with the second distribution flow path is
In the first direction, the flow path cross-sectional area of the plurality of communication holes on the side far from the second refrigerant inflow port is the flow path cross-sectional area of the plurality of communication holes on the side close to the second refrigerant inflow port. The refrigerant distributor according to claim 4, which is formed larger than the above. When each of the plurality of heat transfer tubes inserted into the main body is a flat perforated tube in which a plurality of flow paths through which the refrigerant flows are arranged in the air flow direction, the first communication is arranged on the windward side of the air. 1. The total cross-sectional area of the plurality of communication holes forming the hole group is smaller than the total cross-sectional area of the plurality of communication holes forming the second communication hole group arranged on the leeward side of the air. The refrigerant distributor according to any one of 5 to 5. The main body
A first plate-shaped member in which the first distribution flow path and the second distribution flow path are formed,
The second plate-shaped member on which the plurality of communication holes are formed, and
With the third plate-shaped member in which the plurality of merging flow paths are formed,
A fourth plate-shaped member into which the plurality of heat transfer tubes are inserted, and
Any of claims 1 to 6, wherein the first plate-shaped member, the second plate-shaped member, the third plate-shaped member, and the fourth plate-shaped member are laminated. The refrigerant distributor according to claim 1. The main body
The tubular portion extending in the first direction and
A lid that closes both ends of the tubular portion and
A first wall portion that divides the hollow portion of the cylindrical portion into a first space connected to the refrigerant inflow pipe and a second space connected to the plurality of heat transfer pipes.
A second wall portion that divides the first space into the first distribution flow path and the second distribution flow path, and
A third wall portion that partitions the second space in the first direction to form the merging flow path, and
The refrigerant distributor according to any one of claims 1 to 6. A heat exchanger comprising the refrigerant distributor according to any one of claims 1 to 8. A refrigeration cycle apparatus including the heat exchanger according to claim 9.

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