JPWO2019087235A1 - Refrigerant distributor and refrigeration cycle equipment - Google Patents

Abstract

The refrigerant distributor is a refrigerant distributor having a flow path inlet and a plurality of flow path outlets, and is provided with a flow path having a plurality of branch portions hierarchically for distributing the refrigerant flowing in from the flow path inlet in a plurality of directions. It has a first flow path plate and a second flow path plate which is overlapped with the first flow path plate and provided with a flow path inlet.

Description

The present invention relates to a refrigerant distributor that distributes and flows out refrigerant into a plurality of flow paths, and a refrigeration cycle device including a refrigerant distributor.

In the heat exchanger provided in the refrigeration cycle apparatus, by reducing the diameter of the heat transfer tube through which the refrigerant flows, it is possible to improve the heat exchanger performance and reduce the amount of the refrigerant. If the diameter of the conventional heat transfer tube (for example, outer diameter 7 mm) is made smaller and the number of heat exchanger passes is increased, the heat exchanger performance can be improved, but the pressure loss increases. Therefore, the distributor provided in the heat exchanger is required to be a high-performance multi-branch distributor in which the refrigerant evenly flows out to a plurality of heat transfer tubes. Further, in order to reduce the amount of refrigerant, it is desirable that the distributor is compact.

As a conventional heat exchanger, a heat exchanger having a cylindrical hollow header for storing the refrigerant in order to evenly distribute the refrigerant to a plurality of heat transfer tubes is known (see, for example, Patent Document 1). In the heat exchanger disclosed in Patent Document 1, since the distributor has a hollow header structure, the amount of refrigerant retained in the distributor increases. In order to reduce the amount of refrigerant, it is necessary to reduce the volume of the branch flow path of the distributor as well.

As a distributor that does not use a hollow header structure, a distributor having a configuration in which a plurality of aluminum plates are laminated is known (see, for example, Patent Document 2). In the distributor disclosed in Patent Document 2, a branch portion for distributing the refrigerant to the two branch flow paths is provided for each aluminum plate.

Japanese Unexamined Patent Publication No. 2016-125748 International Publication No. 2016/071946

The distributor disclosed in Patent Document 2 has a configuration in which a number of aluminum plates corresponding to the number of branches of the refrigerant are laminated. Therefore, if the number of branches is increased, the number of aluminum plates to be laminated increases. In this case, the number of parts of the distributor increases, the assembleability of the distributor is poor, and the manufacturing cost becomes high.

The present invention has been made to solve the above problems, and provides a refrigerant distributor and a refrigeration cycle device capable of reducing manufacturing costs.

The refrigerant distributor according to the present invention is a refrigerant distributor having a flow path inlet and a plurality of flow path outlets, and has a plurality of branching portions for distributing the refrigerant flowing in from the flow path inlet in a plurality of directions. It has a first flow path plate provided with a flow path having the flow path, and a second flow path plate overlapped with the first flow path plate and provided with the flow path inlet.

According to the present invention, since a plurality of branch portions for distributing the refrigerant in a plurality of directions are provided hierarchically on one first flow path plate, the number of parts can be reduced and the manufacturing cost can be reduced.

It is an external view which shows the mounting configuration example of the refrigerant distributor which concerns on Embodiment 1 of this invention. It is an external perspective view which shows the structural example of the refrigerant distributor which concerns on Embodiment 1 of this invention. It is a top view of the flow path plate shown in FIG. It is sectional drawing of the flow path plate shown in FIG. It is an external perspective view which shows the structural example of the refrigerant distributor which concerns on Embodiment 2 of this invention. It is an external perspective view which shows the structural example of the refrigerant distributor which concerns on Embodiment 3 of this invention. It is sectional drawing of the flow path plate shown in FIG. It is an external perspective view which shows the structural example of the refrigerant distributor which concerns on Embodiment 4 of this invention. It is an external perspective view which shows the structural example of the refrigerant distributor which concerns on Embodiment 5 of this invention. It is an external perspective view which shows the structural example of the refrigerant distributor which concerns on Embodiment 6 of this invention. It is a refrigerant circuit diagram which shows the structural example of the refrigeration cycle apparatus which concerns on Embodiment 7 of this invention.

Embodiment 1.
The configuration of the refrigerant distributor of the first embodiment will be described. FIG. 1 is an external view showing an example of mounting configuration of the refrigerant distributor according to the first embodiment of the present invention. As shown in FIG. 1, the refrigerant distributor 1 is attached to a heat exchanger 5 of a refrigeration cycle device (not shown). The refrigerant distributor 1 has a flow path inlet 21 for the refrigerant and a plurality of flow path outlets 23. The flow path inlet 21 is connected to a refrigerant pipe (not shown in the figure). The plurality of flow path outlets 23 are connected to heat transfer tubes (not shown). The refrigerant flowing into the refrigerant distributor 1 from the flow path inlet 21 is distributed into a plurality of parts inside the refrigerant distributor 1 and then flows into the heat transfer tubes of the heat exchanger 5 from the plurality of flow path outlets 23. The heat transfer tube of the heat exchanger 5 may be a flat tube.

FIG. 2 is an external perspective view showing a configuration example of the refrigerant distributor according to the first embodiment of the present invention. As shown in FIG. 2, the refrigerant distributor 1 has a first flow path plate 11 provided with a flow path 30 through which the refrigerant flows, and a second flow path provided with a flow path inlet 21 and a flow path outlets 23a to 23h. It has a road plate 12. The refrigerant distributor 1 has a configuration in which the first flow path plate 11 and the second flow path plate 12 are superposed. In FIG. 2, for the sake of explanation, the first flow path plate 11 and the second flow path plate 12 are shown separately.

The flow path 30 has a first branch 41, second branches 42a and 42b, and third branches 43a to 43d as branch portions for distributing the refrigerant. The first branch 41 is provided at a position corresponding to the flow path inlet 21 of the second flow path plate 12. The first branch 41 distributes the refrigerant flowing in from the flow path inlet 21 to the two branch flow paths. The second branch 42a distributes one of the two refrigerants distributed in the first branch 41 to the two branch flow paths. The second branch 42b distributes the other refrigerant out of the two refrigerants distributed in the first branch 41 to the two branch flow paths.

The third branch 43a distributes one of the two refrigerants distributed in the second branch 42a to the two branch flow paths and distributes them to the flow path outlets 23a and 23b. The third branch 43b distributes the other refrigerant out of the two refrigerants distributed in the second branch 42a to the two branch flow paths and distributes them to the flow path outlets 23c and 23d. The third branch 43c distributes one of the two refrigerants distributed by the second branch 42b to the two branch flow paths and distributes them to the flow path outlets 23e and 23f. The third branch 43d distributes the other refrigerant among the two refrigerants distributed in the second branch 42b to the two branch flow paths and distributes them to the flow path outlets 23g and 23h.

Note that FIG. 2 shows a case where each branch portion of the first branch 41, the second branches 42a and 42b, and the third branch 43a to 43d distributes the refrigerant in two directions. The number of is not limited to two, and may be three or more. Further, FIG. 2 shows a case where the branch hierarchy is three layers of the first branch to the third branch, but the branch hierarchy may be four or more layers.

FIG. 3 is a plan view of the flow path plate shown in FIG. The flow path 30 includes a first connection flow path 31a provided with a first branch 41, a second connection flow path 31b provided with a second branch 42a, and a second connection flow path provided with a second branch 42b. It has 31c and. Further, the flow path 30 includes a third connection flow path 31d provided with the third branch 43a, a third connection flow path 31e provided with the third branch 43b, and a third connection flow path provided with the third branch 43c. It has a third connection flow path 31g provided with 31f and a third branch 43d.

The flow path 30 is provided with a first linear flow path 32a that connects one end of both ends of the first connection flow path 31a and the second branch 42a. A second linear flow path 33a that connects one end of the second connection flow path 31b and the third branch 43a is provided. A second linear flow path 33b that connects the other end of the second connection flow path 31b and the third branch 43b is provided.

Further, the flow path 30 is provided with a first linear flow path 32b that connects the other end of the first connection flow path 31a and the second branch 42b. A second linear flow path 33c that connects one end of the second connection flow path 31c and the third branch 43c is provided. A second linear flow path 33d that connects the other end of the second connection flow path 31b and the third branch 43d is provided.

The first connecting flow path 31a has two linear flow paths 36a and 37a and a curved flow path 35a connecting the two linear flow paths 36a and 37a. The first branch 41 is provided in the linear flow path 36a. FIG. 3 shows a case where the linear flow paths 36a and 37a are parallel to the horizontal direction (X-axis arrow direction) perpendicular to the gravity direction (Z-axis arrow direction), but the linear flow paths 36a and 37a does not have to be parallel. Further, the linear flow path 36a provided with the first branch 41 is preferably parallel to the horizontal direction, but the linear flow path 36a may be inclined with respect to the horizontal direction. In this case, the inclination may be an angle within a certain range with respect to the horizontal direction. The angle in a certain range may be an angle that can evenly distribute the refrigerant flowing in from the first branch 41, and is, for example, an angle of ± 10 ° or less in the Z-axis direction with reference to the X-axis shown in FIG. Is desirable.

Like the first connection flow path 31a, the second connection flow path 31b has two linear flow paths 36b and 37b and a curved flow path 35b. A second branch 42a is provided in the linear flow path 37b. Like the first connection flow path 31a, the second connection flow path 31c has two linear flow paths 36c and 37c and a curved flow path 35c. A second branch 42b is provided in the linear flow path 36c. The linear flow paths 37b and 36c are preferably parallel to the horizontal direction, but the inclination of these flow paths with respect to the horizontal direction may be an angle within a certain range with respect to the horizontal direction.

Like the first connection flow path 31a, the third connection flow path 31d has two linear flow paths 36d and 37d and a curved flow path 35d. A third branch 43a is provided in the linear flow path 37d. The ends of the linear flow paths 36d and 37d opposite to the X-axis arrow are located at the flow path outlets 23a and 23b shown in FIG. Like the first connection flow path 31a, the third connection flow path 31e has two linear flow paths 36e and 37e and a curved flow path 35e. A third branch 43b is provided in the linear flow path 36e. The ends of the linear flow paths 36e and 37e opposite to the X-axis arrow are located at the flow path outlets 23c and 23d shown in FIG. The linear flow paths 37d and 36e are preferably parallel to the horizontal direction, but the inclination of these flow paths with respect to the horizontal direction may be an angle within a certain range with respect to the horizontal direction.

Like the first connection flow path 31a, the third connection flow path 31f has two linear flow paths 36f and 37f and a curved flow path 35f. A third branch 43c is provided in the linear flow path 37f. The ends of the linear flow paths 36f and 37f on the opposite side of the X-axis arrow are located at the flow path outlets 23e and 23f shown in FIG. The third connection flow path 31g has two linear flow paths 36g and 37g and a curved flow path 35g, similarly to the first connection flow path 31a. A third branch 43d is provided in the linear flow path 36g. The ends of the linear flow paths 36g and 37g opposite to the X-axis arrow are located at the flow path outlets 23g and 23h shown in FIG. The linear flow paths 37f and 36g are preferably parallel to the horizontal direction, but the inclination of these flow paths with respect to the horizontal direction may be an angle within a certain range with respect to the horizontal direction.

FIG. 4 is a cross-sectional view of the flow path plate shown in FIG. FIG. 4 is a cross-sectional view of the line segment AA shown in FIG. The first flow path plate 11 is, for example, an aluminum plate having a thickness of 3 to 5 mm. The flow path 30 is provided in a groove shape on the first flow path plate 11. In the configuration example shown in FIG. 4, the cross-sectional shape of the flow path 30 is a semicircle. The groove of the flow path 30 is formed by cutting. As shown in FIG. 4, the linear flow paths 36d to 36g and 37d to 37g have the same cross-sectional area.

In the first embodiment, the flow path outlets 23a to 23h shown in FIG. 2 are provided on the side surface of the first flow path plate 11 in the Y-axis arrow direction instead of the second flow path plate 12. May be good. The orientation of the flow path outlets 23a to 23h can be selected according to the position of the heat transfer tube provided in the heat exchanger 5 shown in FIG.

Next, the flow of the refrigerant in the refrigerant distributor 1 will be described with reference to FIGS. 2 to 4. When the refrigerant flows into the second flow path plate 12 of the refrigerant distributor 1 from the flow path inlet 21, it reaches the first branch 41 of the first flow path plate 11. In the first branch 41, the refrigerant collides with the wall of the linear flow path 36a vertically (Y-axis arrow direction) and is distributed in two in the horizontal direction (X-axis arrow direction). In the first branch 41, since the linear flow path 36a that distributes the refrigerant into two in the direction equivalent to the horizontal direction is linear, the liquid refrigerant can be used regardless of whether the refrigerant is in the liquid phase or the gas-liquid two-phase state. The effect of gravity is evenly applied, and the refrigerant is evenly distributed to the left and right.

In the first branch 41, the refrigerant distributed in the direction of the X-axis arrow reaches the second branch 42a via the linear flow path 36a and the first linear flow path 32a. In the second branch 42a, the refrigerant hits the wall of the linear flow path 37b vertically (in the direction of the Z-axis arrow) and is distributed in two in the horizontal direction (in the direction of the X-axis arrow). Also in the second branch 42a, since the linear flow path 37b is linear in the same direction as the horizontal direction, the refrigerant is evenly distributed to the left and right as in the first branch 41.

In the second branch 42a, the refrigerant distributed in the direction of the X-axis arrow reaches the third branch 43a via the linear flow path 37b, the curved flow path 35b, the linear flow path 36b, and the second linear flow path 33a. To do. At the third branch 43a, the refrigerant hits the wall of the linear flow path 37d vertically (Z-axis arrow direction) and is distributed in two in the horizontal direction (X-axis arrow direction). In the second branch 42a, the refrigerant distributed in the direction opposite to the X-axis arrow reaches the third branch 43b via the linear flow path 37b and the second linear flow path 33b. At the third branch 43b, the refrigerant collides with the wall of the linear flow path 36e in the direction of gravity (direction opposite to the Z-axis arrow) and is distributed in two in the horizontal direction (direction of the X-axis arrow). Also in the third branches 43a and 43b, since the linear flow paths 37d and 36e are linear in the same direction as the horizontal direction, the refrigerant is evenly distributed to the left and right as in the first branch 41.

On the other hand, in the first branch 41, the refrigerant distributed in the direction opposite to the X-axis arrow reaches the second branch 42b via the linear flow path 36a, the curved flow path 35a, and the first linear flow path 32b. At the second branch 42b, the refrigerant collides with the wall of the linear flow path 36c in the direction of gravity and is distributed in two in the horizontal direction (direction of the X-axis arrow). Also in the second branch 42b, since the linear flow path 36c is linear in the same direction as the horizontal direction, the refrigerant is evenly distributed to the left and right as in the first branch 41.

In the second branch 42b, the refrigerant distributed in the direction opposite to the X-axis arrow reaches the third branch 43c via the linear flow path 36c and the second linear flow path 33c. In the third branch 43c, the refrigerant hits the wall of the linear flow path 37f vertically (Z-axis arrow direction) and is distributed in two in the horizontal direction (X-axis arrow direction). In the second branch 42b, the refrigerant distributed in the direction of the X-axis arrow reaches the third branch 43d via the linear flow path 36c, the curved flow path 35c, the linear flow path 37c, and the second linear flow path 33d. To do. At the third branch 43d, the refrigerant collides with the wall of the linear flow path 36g in the direction of gravity and is distributed in two in the horizontal direction (direction of the X-axis arrow). Also in the third branches 43c and 43d, since the linear flow paths 37f and 36g are linear in the same direction as the horizontal direction, the refrigerant is evenly distributed to the left and right as in the first branch 41.

As described above, the refrigerant flows in a plurality of layers from the first layer of the first branch 41 to the third layer of the third branches 43a to 43d, so that the refrigerant flowing in from the flow path inlet 21 becomes eight. It is evenly distributed and evenly flows into the heat transfer tubes connected to the flow path outlets 23a to 23h.

Next, a method of manufacturing the refrigerant distributor 1 will be described with reference to FIG. The flow path 30 is formed on an aluminum plate by cutting, and the first flow path plate 11 shown in FIG. 2 is manufactured. The formation of the flow path 30 is not limited to cutting, but may be performed by drawing, forging, or the like. Further, the flow path inlet 21 and the flow path outlets 23a to 23h are formed on an aluminum plate by press working, and the second flow path plate 12 shown in FIG. 2 is manufactured. Subsequently, of the two side surfaces of the second flow path plate 12, the brazing material is applied to the side surface facing the first flow path plate 11. The second flow path plate 12 coated with the brazing material and the first flow path plate 11 are overlapped with each other. After that, the laminated second flow path plate 12 and the first flow path plate 11 are brazed.

The refrigerant distributor 1 of the first embodiment includes a first flow path plate 11 provided with a flow path 30 having a plurality of branch portions hierarchically for distributing the refrigerant flowing in from the flow path inlet 21 in a plurality of directions. It has a second flow path plate 12 that is superposed on the first flow path plate 11.

According to the first embodiment, a plurality of branch portions for distributing the refrigerant in a plurality of directions are hierarchically provided on one first flow path plate 11. As a specific example, the flow path 30 has a configuration having a first branch 41 of the first layer, a plurality of second branches 42a and 42b of the second layer, and a plurality of third branches 43a to 43d of the third layer. is there. In this case, in the first flow path plate 11, the refrigerant is distributed to two flow paths in the first layer, to four flow paths in the second layer, and to eight flow paths in the third layer. Therefore, in the first embodiment, the number of parts can be reduced, the assembling property can be improved, and the manufacturing cost can be reduced as compared with the distributor disclosed in Patent Document 2.

Further, in the first embodiment, in the branch system from the first branch 41 to the third connection flow path 31d, the first branch 41 is provided in the linear flow path 36a, and the second branch 42a is provided in the linear flow path 37b. Is provided, and a third branch 43a is provided in the linear flow path 37d. This configuration is the same for other branch systems. Each branch portion of the first branch to the third branch is provided in a linear flow path parallel to the direction equivalent to the horizontal direction. Therefore, regardless of whether the refrigerant is in the liquid phase or the gas-liquid two-phase state, the liquid refrigerant is evenly affected by gravity, and the refrigerant is evenly distributed to the two branch flow paths.

Further, since the flow path inlet 21 and the flow path outlets 23a to 23h of the second flow path plate 12 have a structure penetrating the plate, these flow paths can be formed by press working, and the manufacturing process becomes easy. ..

Embodiment 2.
The refrigerant distributor of the second embodiment has a configuration in which the flow path described in the first embodiment is also formed on the second flow path plate. In the second embodiment, detailed description of the configuration similar to that of the first embodiment will be omitted.

FIG. 5 is an external perspective view showing a configuration example of the refrigerant distributor according to the second embodiment of the present invention. As shown in FIG. 2, the refrigerant distributor 1a has a first flow path plate 11a and a second flow path plate 12a. The refrigerant distributor 1a has a configuration in which the first flow path plate 11a and the second flow path plate 12a are superposed. In FIG. 5, for the sake of explanation, the first flow path plate 11a and the second flow path plate 12a are shown separately.

The first flow path plate 11a has a flow path 30a through which the refrigerant flows. The first flow path plate 11a has the same configuration as the first flow path plate 11 described in the first embodiment. The flow path 30a corresponds to the flow path 30 described with reference to FIGS. 2 to 4. In addition to the flow path inlet 21 and the flow path outlets 23a to 23h shown in FIG. 2, the second flow path plate 12a has a flow path 30b that faces the flow path 30a of the first flow path plate 11a symmetrically. In the refrigerant distributor 1a, since the refrigerant flows through the flow path 30a and the flow path 30b, the flow path cross-sectional area is twice the flow path cross-sectional area of the refrigerant distributor 1 described in the first embodiment.

The flow path outlets 23a to 23h shown in FIG. 5 may be provided on the side surface of the first flow path plate 11a in the direction of the Y-axis arrow instead of the second flow path plate 12a. Also in the second embodiment, the directions of the flow path outlets 23a to 23h can be selected according to the position of the heat transfer tube provided in the heat exchanger 5 shown in FIG.

Regarding the flow of the refrigerant in the refrigerant distributor 1a of the second embodiment, the cross-sectional area of the flow path is double that of the first embodiment, so that the refrigerant flowing in from the flow path inlet 21 flows from the flow path outlets 23a to 23h. The pressure loss from to the outflow is reduced as compared with the first embodiment. Further, also in the second embodiment, the refrigerant is evenly distributed at each branch portion of the first branch to the third branch.

Next, a method of manufacturing the refrigerant distributor 1a will be described with reference to FIG. The flow path 30a is formed on an aluminum plate by cutting, and the first flow path plate 11a shown in FIG. 5 is manufactured. Further, the flow path 30b is formed by cutting on an aluminum plate in which the flow path inlet 21 and the flow path outlets 23a to 23h are formed by press working. As a result, the second flow path plate 12a shown in FIG. 5 is produced. The flow path 30a and the flow path 30b are not limited to cutting, but may be drawn or forged. Subsequently, of the two side surfaces of the second flow path plate 12a, the brazing material is applied to the side surface facing the first flow path plate 11a. The second flow path plate 12a coated with the brazing material and the first flow path plate 11a are overlapped with each other. After that, the laminated second flow path plate 12a and the first flow path plate 11a are brazed.

According to the second embodiment, the same effect as that of the first embodiment can be obtained. Further, in the refrigerant distributor 1a of the second embodiment, the first flow path plate 11a and the second flow path plate 12a are overlapped with each other, and the flow path 30a and the second flow path plate 12a of the first flow path plate 11a are overlapped with each other. The configuration is such that the flow path 30b has a plane-symmetrical positional relationship. In the second embodiment, the cross-sectional area of the flow path is doubled as compared with the first embodiment, so that the pressure loss of the refrigerant flowing through the refrigerant distributor 1a is reduced as compared with the first embodiment.

Embodiment 3.
The refrigerant distributor of the third embodiment is configured such that the flow path described in the first embodiment penetrates the flow path plate. In the third embodiment, detailed description of the configuration similar to that of the first embodiment will be omitted.

FIG. 6 is an external perspective view showing a configuration example of the refrigerant distributor according to the third embodiment of the present invention. As shown in FIG. 6, the refrigerant distributor 1b has a first flow path plate 11b provided with a flow path 30c through which the refrigerant flows, and a second flow path provided with a flow path inlet 21 and a flow path outlets 23a to 23h. It has a road plate 12b and a side plate 13. The refrigerant distributor 1b has a configuration in which a side plate 13, a first flow path plate 11b, and a second flow path plate 12b are superposed.

The side plate 13 is superposed on the side surface of the first flow path plate 11b that is opposite to the side surface facing the second flow path plate 12b. In FIG. 6, the three plates are shown separated from each other for the sake of explanation. The second flow path plate 12b has the same configuration as the second flow path plate 12 described with reference to FIG. 2, and the layout of the flow path 30c is the same as that of the flow path 30 described in the first embodiment. Detailed description will be omitted.

FIG. 7 is a cross-sectional view of the flow path plate shown in FIG. FIG. 7 is a cross-sectional view of the line segment BB shown in FIG. The first flow path plate 11b is, for example, an aluminum plate having a thickness of 3 to 5 mm. The flow path 30c is provided so as to penetrate the first flow path plate 11b. The flow path 30c is formed by press working. As shown in FIG. 7, the flow path cross-sectional areas of the linear flow paths 36d to 36 g and 37d to 37 g can be obtained by multiplying the length of each flow path in the Z-axis direction and the thickness of the first flow path plate 11c. The thickness of the first flow path plate 11b is uniform throughout the plate, and assuming that the lengths of the linear flow paths 36d to 36g and 37d to 37g in the Z-axis direction are the same, the linear flow paths 36d to 36d of each flow path The cross-sectional areas of 36 g and 37d-37 g are equivalent. The cross-sectional area of the flow path 30c is larger than the cross-sectional area of the flow path 30 of the first embodiment.

The flow path outlets 23a to 23h shown in FIG. 6 may be provided on the side surface of the side plate 13 in the Y-axis arrow direction instead of the second flow path plate 12b. Also in the third embodiment, the directions of the flow path outlets 23a to 23h can be selected according to the position of the heat transfer tube provided in the heat exchanger 5 shown in FIG.

Regarding the flow of the refrigerant in the refrigerant distributor 1b of the third embodiment, since the flow path cross-sectional area is larger than that of the first embodiment, the refrigerant flowing in from the flow path inlet 21 flows from the flow path outlets 23a to 23h. The pressure loss until the outflow is reduced as compared with the first embodiment. Further, also in the third embodiment, the refrigerant is evenly distributed at each branch portion of the first branch to the third branch.

Next, a method of manufacturing the refrigerant distributor 1b will be described with reference to FIG. The flow path 30c is formed on an aluminum plate by press working, and the first flow path plate 11b shown in FIG. 6 is manufactured. Further, the flow path inlet 21 and the flow path outlets 23a to 23h are formed on an aluminum plate by press working, and the second flow path plate 12b shown in FIG. 6 is manufactured. Subsequently, of the two side surfaces of the second flow path plate 12b, the brazing material is applied to the side surface facing the first flow path plate 11b. Further, of the two side surfaces of the side plate 13, the brazing material is applied to the side surface facing the first flow path plate 11b. Then, the three plates are overlapped so that the side plate 13 and the second flow path plate 12b sandwich the first flow path plate 11b. After that, a brazing process is performed on the three stacked boards.

According to the third embodiment, the same effect as that of the first embodiment can be obtained. Further, the refrigerant distributor 1b of the third embodiment has a configuration in which the flow path 30c is provided so as to penetrate the first flow path plate 11b. In the third embodiment, since the flow path cross-sectional area is larger than that in the first embodiment, the pressure loss of the refrigerant flowing through the refrigerant distributor 1b is reduced as compared with the first embodiment.

Further, since the flow path 30c of the first flow path plate 11b and the flow path inlet 21 and the flow path outlets 23a to 23h of the second flow path plate 12b penetrate the plate, these flow paths are pressed. Can be formed with, which facilitates the manufacturing process. As a result, the manufacturing cost can be suppressed.

Embodiment 4.
The refrigerant distributor of the fourth embodiment uses a brazing material coating sheet for brazing the three plates described in the third embodiment. In the fourth embodiment, the difference from the third embodiment will be described based on the refrigerant distributor described in the third embodiment, and detailed description of the configuration similar to the third embodiment will be omitted.

FIG. 8 is an external perspective view showing a configuration example of the refrigerant distributor according to the fourth embodiment of the present invention. As shown in FIG. 8, the refrigerant distributor 1c has a first flow path plate 11c, a second flow path plate 12c, and a side plate 13. In the fourth embodiment, the first wax material coating sheet 14 is provided between the first flow path plate 11c and the second flow path plate 12c. Further, a second wax material coating sheet 15 is provided between the first flow path plate 11c and the side plate 13. The refrigerant distributor 1c has a configuration in which a side plate 13, a second wax material coating sheet 15, a first flow path plate 11c, a first brazing material coating sheet 14, and a second flow path plate 12c are superposed. In FIG. 8, the five plates are shown separated from each other for illustration purposes.

Since the first flow path plate 11c has the same configuration as the first flow path plate 11b shown in FIG. 6 and the second flow path plate 12c has the same configuration as the second flow path plate 12b, these details are detailed. The explanation is omitted. The first brazing material coating sheet 14 and the second brazing material coating sheet 15 are sheets to which the brazing material is pre-coated, and are, for example, brazing sheets. The first brazing material coating sheet 14 is formed with a plurality of openings corresponding to the positions of the flow path inlet 21 and the flow path outlets 23a to 23h provided on the second flow path plate 12c.

The flow path outlets 23a to 23h shown in FIG. 8 may be provided on the surface of the side plate 13 in the direction of the Y-axis arrow instead of the second flow path plate 12c. In this case, the second brazing material coating sheet 15 is formed with a plurality of openings corresponding to the positions of the flow path inlet 21 and the flow path outlets 23a to 23h provided on the side plate 13. Also in the fourth embodiment, the directions of the flow path outlets 23a to 23h can be selected according to the position of the heat transfer tube provided in the heat exchanger 5 shown in FIG.

Since the flow of the refrigerant in the refrigerant distributor 1c of the fourth embodiment is the same as that of the third embodiment, detailed description thereof will be omitted. Also in the fourth embodiment, the refrigerant is evenly distributed at each branch portion of the first branch to the third branch.

Next, a method of manufacturing the refrigerant distributor 1c will be described with reference to FIG. The flow path 30c is formed on an aluminum plate by press working, and the first flow path plate 11c shown in FIG. 8 is manufactured. Further, the flow path inlet 21 and the flow path outlets 23a to 23h are formed on an aluminum plate by press working, and the second flow path plate 12c shown in FIG. 8 is manufactured. The first wax material coating sheet 14 and the second wax material coating sheet 15 shown in FIG. 8 are prepared. Subsequently, the second wax material coating sheet 15 and the side plate 13 are sequentially overlapped in the direction of the Y-axis arrow of the first flow path plate 11c, and the first brazing material is applied in the direction opposite to the Y-axis arrow of the first flow path plate 11c. The sheet 14 and the second flow path plate 12c are laminated in this order. After that, brazing treatment is performed on the five stacked boards.

According to the fourth embodiment, the same effect as that of the first embodiment can be obtained. Further, the refrigerant distributor 1c of the fourth embodiment has a first wax material coating sheet 14 provided between the second flow path plate 12c and the first flow path plate 11c, and the first flow path plate 11c. It has a second brazing material coating sheet 15 provided between the side plate 13 and the side plate 13. In the fourth embodiment, since the brazing material coating sheet is used for brazing the three plates, the brazing material coating step becomes unnecessary, and the working time at the time of assembling the refrigerant distributor 1c can be shortened.

Embodiment 5.
The refrigerant distributor of the fifth embodiment is the refrigerant distributor described in any one of the first to fourth embodiments, in which the cross-sectional area of the flow path is different before and after the branch portion. In the fifth embodiment, the difference from the second embodiment will be described based on the refrigerant distributor described in the second embodiment, and detailed description of the configuration similar to the second embodiment will be omitted.

FIG. 9 is an external perspective view showing a configuration example of the refrigerant distributor according to the fifth embodiment of the present invention. As shown in FIG. 9, the refrigerant distributor 1d has a first flow path plate 11d and a second flow path plate 12d. The refrigerant distributor 1d has a configuration in which the first flow path plate 11d and the second flow path plate 12d are superposed. In FIG. 9, for the sake of explanation, the first flow path plate 11d and the second flow path plate 12d are shown separately.

The first flow path plate 11d has a flow path 30d through which the refrigerant flows. The layout of the flow path 30d is the same as the layout of the flow path 30 described in the first embodiment, but the flow path cross-sectional area of the flow path 30d is different from the flow path cross-sectional area of the flow path 30. The second flow path plate 12d has a flow path 30e that is plane-symmetrically opposed to the flow path 30d provided on the first flow path plate 11d. The second flow path plate 12d has a flow path inlet 21 and a flow path outlets 23a to 23h shown in FIG.

The flow path outlets 23a to 23h shown in FIG. 9 may be provided on the side surface of the first flow path plate 11d in the direction of the Y-axis arrow instead of the second flow path plate 12d. Also in the fifth embodiment, the directions of the flow path outlets 23a to 23h can be selected according to the position of the heat transfer tube provided in the heat exchanger 5 shown in FIG.

As shown in FIG. 9, the flow path 30d has a first flow path 51a and 51b, a second flow path 52a to 52d, and a third flow path 53a to 53h. The first flow path 51a is a branch flow path from the first branch 41 to the second branch 42a. The first flow path 51b is a branch flow path from the first branch 41 to the second branch 42b.

The second flow path 52a is a branch flow path from the second branch 42a to the third branch 43a. The second flow path 52b is a branch flow path from the second branch 42a to the third branch 43b. The second flow path 52c is a branch flow path from the second branch 42b to the third branch 43c. The second flow path 52d is a branch flow path from the second branch 42b to the third branch 43d.

The third flow path 53a is a branch flow path from the third branch 43a to the flow path outlet 23a. The third flow path 53b is a branch flow path from the third branch 43a to the flow path outlet 23b. The third flow path 53c is a branch flow path from the third branch 43b to the flow path outlet 23c. The third flow path 53d is a branch flow path from the third branch 43b to the flow path outlet 23d.

The third flow path 53e is a branch flow path from the third branch 43c to the flow path outlet 23e. The third flow path 53f is a branch flow path from the third branch 43c to the flow path outlet 23f. The third flow path 53g is a branch flow path from the third branch 43d to the flow path outlet 23g. The third flow path 53h is a branch flow path from the third branch 43d to the flow path outlet 23h.

Attention is paid to the branch system from the first branch 41 to the flow path outlet 23a via the first flow path 51a, the second branch 42a, the second flow path 52a, the third branch 43a, and the third flow path 53a. Then, the flow path cross-sectional area of the first flow path 51a is S1, the flow path cross-sectional area of the second flow path 52a is S2, and the flow path cross-sectional area of the third flow path 53a is S3. In this case, the size of the flow path cross-sectional area has a relationship of S1> S2> S3. The relationship between the sizes of the flow path cross-sectional area S1 of the first flow path, the flow path cross-sectional area S2 of the second flow path, and the flow path cross-sectional area S3 of the third flow path is the same for other branch systems.

Regarding the flow of the refrigerant in the refrigerant distributor 1d of the fifth embodiment, since the flow path cross-sectional area is reduced in the order of the first flow path, the second flow path, and the third flow path, after passing through the branch portion. The flow velocity of the refrigerant is maintained by inertial force, and the flow velocity of the refrigerant is maintained before and after each branch. In this case, for example, in the first linear flow paths 32a and 32b and the second linear flow paths 33a to 33d, the refrigerant flowing in the direction of the Z-axis arrow flows vigorously against the direction of gravity. At each branch, the flow of the split refrigerant is suppressed from being biased between the branch channels. In the fifth embodiment, the refrigerant is more evenly distributed at each branch portion of the first branch to the third branch.

The method for manufacturing the refrigerant distributor 1d according to the fifth embodiment is carried out except that the cutting step is performed so that the cross-sectional area is different for each branch flow path of the first flow path to the third flow path. Since the method is the same as that described in the second embodiment, the detailed description thereof will be omitted. The formation of the first flow path to the third flow path is not limited to cutting, and may be performed by drawing or forging. Further, although the present embodiment 5 has been described based on the refrigerant distributor of the second embodiment, the refrigerant distributor described in another embodiment may be applied to the fifth embodiment.

According to the fifth embodiment, the same effect as that of the first embodiment can be obtained. Further, in the refrigerant distributor 1d of the fifth embodiment, the flow path 30d has a first flow path from the first branch to the second branch, a second flow path from the second branch to the third branch, and a third flow path. It has a third flow path from the branch to the flow path outlet, and the flow path cross-sectional area becomes smaller in the order of the first flow path, the second flow path, and the third flow path. In the fifth embodiment, in each branch system from the flow path inlet 21 to the flow path outlets 23a to 23h, the flow path cross-sectional area is reduced each time it passes through the branch portion, so that the flow path cross-sectional area is reduced before and after each branch portion. The flow rate of the refrigerant is maintained. As a result, in each branch portion, the flow of the divided refrigerant is suppressed from being biased between the branch flow paths, and the refrigerant can be evenly flowed by the plurality of heat transfer tubes of the heat exchanger 5 shown in FIG.

Embodiment 6.
The refrigerant distributor of the sixth embodiment has a configuration in which an unnecessary portion of the flow path plate is cut in the refrigerant distributor described in any one of the first to fifth embodiments. In the sixth embodiment, the difference from the second embodiment will be described based on the refrigerant distributor described in the second embodiment, and detailed description of the configuration similar to the second embodiment will be omitted.

FIG. 10 is an external perspective view showing a configuration example of the refrigerant distributor according to the sixth embodiment of the present invention. As shown in FIG. 10, the refrigerant distributor 1e has a first flow path plate 11e and a second flow path plate 12e. The refrigerant distributor 1e has a configuration in which the first flow path plate 11e and the second flow path plate 12e are superposed. In FIG. 10, for the sake of explanation, the first flow path plate 11e and the second flow path plate 12e are shown separately.

The first flow path plate 11e has a configuration in which the portions 61a to 66a are cut from the first flow path plate 11a shown in FIG. The portions 61a to 66a are a part of the region where the flow path 30a is not provided in the first flow path plate 11e. The second flow path plate 12e has a configuration in which the portions 61b and 63b to 66b are cut from the second flow path plate 12a shown in FIG. The portions 61b and 63b to 66b are parts of the second flow path plate 12e where the flow path 30b, the flow path inlet 21 and the flow path outlets 23a to 23h are not provided.

Since a part of the plate is cut in each of the first flow path plate 11e and the second flow path plate 12e, the weight of the refrigerant distributor 1e is reduced as compared with the case of the second embodiment. Further, since the area where the first flow path plate 11e and the second flow path plate 12e are overlapped is small, the amount of brazing material applied to braze the two plates can be reduced.

The configuration shown in FIG. 10 is an example, and the portion to be cut is not limited to the case shown in FIG. The larger the total area of the cut portions, the lighter the weight of the refrigerant distributor 1e can be. Further, FIG. 10 shows a case where a part of the plate is cut for both the first flow path plate 11e and the second flow path plate 12e, but of the two flow path plates, The plate to be cut may be either one. Even in this case, the weight of the refrigerant distributor 1e can be reduced. Further, although the present embodiment 6 has been described based on the refrigerant distributor of the second embodiment, the refrigerant distributor described in the other embodiments may be applied to the sixth embodiment.

Since the flow of the refrigerant in the refrigerant distributor 1e of the sixth embodiment is the same as that of the second embodiment, detailed description thereof will be omitted. Also in the sixth embodiment, the refrigerant is evenly divided at each branch of the first branch to the third branch.

Next, a method of manufacturing the refrigerant distributor 1e will be described with reference to FIG. After the portions 61a to 66a are cut off from the rectangular aluminum plate by press working, the flow path 30a is formed on the aluminum plate by cutting, and the first flow path plate 11e shown in FIG. 10 is produced. The formation of the flow path 30a is not limited to cutting, and may be performed by drawing, forging, or the like. Further, by pressing the rectangular aluminum plate, the portions 61b and 63b to 66b are cut off from the aluminum plate, and the flow path inlet 21 and the flow path outlets 23a to 23h are formed on the aluminum plate. Subsequently, the flow path 30b is formed on the aluminum plate by cutting, and the second flow path plate 12e shown in FIG. 10 is manufactured. Since the subsequent steps are the same as those in the second embodiment, detailed description thereof will be omitted.

According to the sixth embodiment, the same effect as that of the first embodiment can be obtained. Further, the refrigerant distributor 1e of the sixth embodiment has a configuration in which at least a part of the region where the flow path 30a is not provided is cut off in at least the first flow path plate 11e. Therefore, the weight of the refrigerant distributor can be reduced. Further, the total amount of brazing material used for brazing the first flow path plate 11e and the second flow path plate 12e can be reduced. Further, by reducing the total amount of the brazing material to be applied, it is possible to prevent the remainder of the brazing material from flowing into the refrigerant flow path, and it is possible to improve the reliability of the distributor.

Embodiment 7.
The refrigerating cycle device of the seventh embodiment is configured to include any of the refrigerant distributors 1 and 1a to 1e described in the first to sixth embodiments. In the seventh embodiment, the case where the refrigerant distributor 1 described in the first embodiment is provided in the refrigeration cycle apparatus will be described.

FIG. 11 is a refrigerant circuit diagram showing a configuration example of the refrigeration cycle device according to the seventh embodiment of the present invention. The refrigeration cycle device 100 has a heat source side unit 110 and a load side unit 120. The load side unit 120 is installed in a room that is a space to be air-conditioned. The heat source side unit 110 includes a compressor 2, a flow path switching device 4, a heat source side heat exchanger 5a, a fan 6a, an expansion valve 3, and a control unit 7. The load-side unit 120 has a load-side heat exchanger 5b and a fan 6b. The compressor 2, the heat source side heat exchanger 5a, the load side heat exchanger 5b, and the expansion valve 3 are connected by a refrigerant pipe to form a refrigerant circuit 130 in which the refrigerant circulates.

In the heat source side unit 110, the refrigerant distributor 1 is provided in the heat source side heat exchanger 5a. The refrigerant distributor 1 is arranged on the heat source side heat exchanger 5a on the side where the heat source side heat exchanger 5a is connected to the expansion valve 3. In the load-side unit 120, the refrigerant distributor 1 is provided in the load-side heat exchanger 5b. The refrigerant distributor 1 is arranged on the load side heat exchanger 5b on the side where the load side heat exchanger 5b is connected to the expansion valve 3.

The compressor 2 compresses and discharges the refrigerant. An inverter circuit (not shown) may be connected to the compressor 2. The flow path switching device 4 switches the flow path of the refrigerant according to the operating state of the refrigeration cycle device 100. The flow path switching device 4 is, for example, a four-way valve. The heat source side heat exchanger 5a is a heat exchanger that exchanges heat between the refrigerant and the outdoor air. The fan 6a supplies outdoor air to the heat source side heat exchanger 5a. The expansion valve 3 decompresses the refrigerant and expands it. The load side heat exchanger 5b is a heat exchanger that exchanges heat between the refrigerant and the indoor air. The fan 6b supplies indoor air to the load side heat exchanger 5b. The control unit 7 is, for example, a microcomputer. The control unit 7 controls the operating frequency of the compressor 2, the flow path switching of the flow path switching device 4, the opening degree of the expansion valve 3, and the rotation frequencies of the fans 6a and 6b.

The refrigeration cycle device 100 may be a device that performs either a heating operation or a cooling operation. In this case, the refrigeration cycle device 100 may not be provided with the flow path switching device 4. Further, FIG. 11 shows a case where the refrigerant distributor 1 is provided in both the heat source side heat exchanger 5a and the load side heat exchanger 5b, and one of these heat exchangers is provided. A refrigerant distributor 1 may be provided in the heat exchanger. Further, the control unit 7 and the expansion valve 3 may be provided in the load side unit 120 instead of the heat source side unit 110.

Next, the flow of the refrigerant when the refrigeration cycle device 100 performs the cooling operation will be described. The control unit 7 sets the flow path of the flow path switching device 4 so that the refrigerant discharged from the compressor 2 flows to the heat source side heat exchanger 5a. The high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the heat source side heat exchanger 5a. In the heat source side heat exchanger 5a, the gas refrigerant exchanges heat with the outdoor air to become a liquid phase. The liquid refrigerant flows through the expansion valve 3 to reduce the pressure, and when it expands, it becomes a gas-liquid two-phase state. The gas-liquid two-phase state refrigerant flows into the load side heat exchanger 5b via the refrigerant distributor 1. When the refrigerant passes through the refrigerant distributor 1, it is evenly distributed to a plurality of heat transfer tubes (not shown in the figure) as described in the first embodiment. In the load side heat exchanger 5b, the refrigerant efficiently exchanges heat with the indoor air and evaporates. As a result, the indoor air is cooled. The gas refrigerant flowing out from the load side heat exchanger 5b returns to the compressor 2.

Subsequently, the flow of the refrigerant when the refrigeration cycle device 100 performs the heating operation will be described. The control unit 7 switches the flow path of the flow path switching device 4 so that the refrigerant discharged from the compressor 2 flows to the load side heat exchanger 5b. The high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the load-side heat exchanger 5b. In the load side heat exchanger 5b, the gas refrigerant exchanges heat with the indoor air to become a liquid phase. This warms the room air. The liquid refrigerant flows through the expansion valve 3 to reduce the pressure, and when it expands, it becomes a gas-liquid two-phase state. The gas-liquid two-phase state refrigerant flows into the heat source side heat exchanger 5a via the refrigerant distributor 1. When the refrigerant passes through the refrigerant distributor 1, it is evenly distributed to a plurality of heat transfer tubes (not shown in the figure) as described in the first embodiment. In the heat source side heat exchanger 5a, the refrigerant efficiently exchanges heat with the outdoor air and evaporates. The gas refrigerant flowing out of the heat source side heat exchanger 5a returns to the compressor 2.

In the seventh embodiment, the case where the refrigerant distributor of the first embodiment is applied to the refrigeration cycle apparatus has been described, but the refrigerant distribution described in any one of the first to sixth embodiments has been described. The vessel may be applied to the seventh embodiment.

In the refrigeration cycle device 100 of the seventh embodiment, the refrigerant distributor described in any one of the first to sixth embodiments is one of the heat source side heat exchanger 5a and the load side heat exchanger 5b. Or both are provided. In the heat exchanger, the above-mentioned refrigerant distributor is attached to the side of the liquid refrigerant or the side where the amount of liquid is large when the refrigerant is in a gas-liquid two-phase state. Therefore, the refrigerant is evenly distributed to the plurality of heat transfer tubes, and the heat exchanger performance can be improved.

Further, the refrigerant distributor provided in the refrigeration cycle device 100 of the seventh embodiment has a smaller internal volume than the hollow header structure type distributor. Therefore, the amount of refrigerant retained in the heat exchanger including the distributor can be reduced as compared with the hollow header structure type distributor. As a result, the operating cost of the refrigeration cycle device 100 can be reduced.

1, 1a to 1e Refrigerant distributor, 2 Compressor, 3 Expansion valve, 4 Flow path switching device, 5 Heat exchanger, 5a Heat source side heat exchanger, 5b Load side heat exchanger, 6a, 6b fan, 7 Control unit , 11, 11a to 11e 1st flow path plate, 12, 12a to 12e 2nd flow path plate, 13 side plate, 14 1st brazing material coating sheet, 15 2nd brazing material coating sheet, 21 flow path inlet, 23 , 23a to 23h flow path outlet, 30, 30a to 30e flow path, 31a first connection flow path, 31b, 31c second connection flow path, 31d to 31g third connection flow path, 32a, 32b first linear flow path. , 33a-33d 2nd linear flow path, 35a-35g curved flow path, 36a-36g, 37a-37g linear flow path, 41 1st branch, 42a, 42b 2nd branch, 43a-43d 3rd branch, 51a , 51b 1st flow path, 52a to 52d 2nd flow path, 53a to 53h 3rd flow path, 61a to 66a, 61b, 63b to 66b parts, 100 refrigeration cycle device, 110 heat source side unit, 120 load side unit, 130 Refrigerant circuit.

The refrigerant distributor according to the present invention is a refrigerant distributor having a flow path inlet and a plurality of flow path outlets, and has a plurality of branching portions for distributing the refrigerant flowing in from the flow path inlet in a plurality of directions. a first channel plate in which a flow path is provided with, superimposed with the first flow-path plate, have a, a second flow-path plate, wherein the flow path inlet is provided, the flow path, the flow A first connection flow path provided with a first branch that distributes the refrigerant flowing in from the passage inlet to a plurality of first branch flow paths, and a refrigerant distributed by the first branch is distributed to a plurality of second branch flow paths. A second connection flow path provided with a second branch is provided, and a third branch is provided to distribute the refrigerant distributed by the second branch to a plurality of third branch flow paths and distribute the refrigerant to the plurality of flow path outlets. The third connecting flow path, the first linear connecting flow path connecting one end of the first connecting flow path and the second branch, one end of the second connecting flow path, and the first branch. It has a second linear connecting flow path that connects the three branches, and at least one of the first linear connecting flow path and the second linear connecting flow path is along the direction of gravity. is there.

Claims (15)

A refrigerant distributor having a flow path inlet and a plurality of flow path outlets.
A first flow path plate provided with a flow path having a plurality of branch portions hierarchically for distributing the refrigerant flowing in from the flow path inlet in a plurality of directions.
A second flow path plate that is overlapped with the first flow path plate and is provided with the flow path inlet.
Refrigerant distributor with. The flow path serves as a plurality of the branch portions.
A first branch that distributes the refrigerant flowing in from the flow path inlet to a plurality of branch flow paths, and
A plurality of second branches that distribute the refrigerant distributed in the first branch to a plurality of branch flow paths, and
A plurality of third branches that distribute the refrigerant distributed by the plurality of second branches to the plurality of branch flow paths and distribute the refrigerant to the plurality of flow path outlets.
The refrigerant distributor according to claim 1. The flow path is
The first connection flow path provided with the first branch and
The second connection flow path provided with the second branch and
With the third connection flow path provided with the third branch
A first linear flow path connecting one end of the first connection flow path and the second branch,
A second linear flow path connecting one end of the second connection flow path and the third branch,
2. The refrigerant distributor according to claim 2. Each of the first connection flow path, the second connection flow path, and the third connection flow path
Two linear channels and
A curved flow path connecting the two linear flow paths and
The refrigerant distributor according to claim 3. Of the two linear flow paths of the first connection flow path, one linear flow path is provided with the first branch.
The second branch is provided in one of the two linear flow paths of the second connection flow path.
Of the two linear flow paths of the third connection flow path, one linear flow path is provided with the third branch.
The linear flow path provided with each of the first branch, the second branch, and the third branch has an inclination in a certain range with respect to the horizontal direction with respect to the horizontal direction perpendicular to the gravity direction. The refrigerant distributor according to claim 4. The flow path is
A plurality of first flow paths from the first branch to the plurality of second branches,
A plurality of second channels from the plurality of second branches to the plurality of third branches,
It has a plurality of third flow paths from the plurality of third branches to the plurality of flow path outlets.
The refrigerant distributor according to any one of claims 2 to 5, wherein the flow path cross-sectional area is reduced in the order of the first flow path, the second flow path, and the third flow path. The refrigerant distributor according to any one of claims 1 to 6, wherein the flow path is provided in a groove shape on the first flow path plate. The flow path is provided in a groove shape on the second flow path plate.
The refrigerant distributor according to claim 7, wherein the flow path of the first flow path plate and the flow path of the second flow path plate have a plane-symmetrical positional relationship. Of the two side surfaces of the first flow path plate, the side plate is further provided on the side surface opposite to the side surface facing the second flow path plate.
The refrigerant distributor according to any one of claims 1 to 6, wherein the flow path is provided through the first flow path plate. A first wax material coating sheet provided between the second flow path plate and the first flow path plate, and
A second wax material coating sheet provided between the first flow path plate and the side plate, and
The refrigerant distributor according to claim 9, further comprising. The refrigerant distributor according to claim 9 or 10, wherein the plurality of flow path outlets are provided on the side plate. The refrigerant distributor according to any one of claims 1 to 8, wherein the plurality of flow path outlets are provided on the first flow path plate. The refrigerant distributor according to any one of claims 1 to 10, wherein the plurality of flow path outlets are provided on the second flow path plate. The refrigerant distributor according to any one of claims 1 to 13, wherein a part of the region where the flow path is not provided is cut in the first flow path plate. A refrigerant circuit in which the compressor, heat source side heat exchanger, load side heat exchanger and expansion valve are connected by a refrigerant pipe and the refrigerant circulates.
The refrigerant distributor according to any one of claims 1 to 14, which is provided in one or both of the heat source side heat exchanger and the load side heat exchanger.
Refrigeration cycle equipment with.

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