JP7313557B2 - Refrigerant distributors, heat exchangers and air conditioners - Google Patents

Description

TECHNICAL FIELD The present disclosure relates to refrigerant distributors, heat exchangers, and air conditioners that branch out incoming refrigerant.

In recent years, the diameter of heat transfer tubes in heat exchangers used in air conditioners has been reduced in order to reduce the amount of refrigerant and improve the performance of heat exchangers. When the diameter of the heat transfer tube is reduced, it is necessary to suppress an increase in pressure loss when the refrigerant passes through the heat transfer tube. Therefore, in the heat exchanger, the number of paths, which is the number of branches when the refrigerant flows inside, is increased.

In general, a heat exchanger is provided with a multi-branched refrigerant distributor that distributes and supplies refrigerant flowing from one inlet channel to a plurality of paths in order to increase the number of paths. For example, Patent Document 1 discloses a refrigerant distributor in which a plurality of heat transfer tubes extending in the horizontal direction are arranged vertically side by side, and a header-shaped refrigerant distributor connected to the plurality of heat transfer tubes is arranged to extend in the vertical direction. When the heat exchanger functions as an evaporator, the refrigerant distributor has an inflow pipe into which a gas-liquid two-phase refrigerant flows, a mixing chamber in which the inflowing gas-liquid two-phase refrigerant is mixed and homogenized, a communication chamber to which a plurality of heat transfer tubes are connected, and a distribution passage for distributing the gas-liquid two-phase refrigerant to the plurality of communication chambers.

Japanese Patent No. 5376010

However, since the refrigerant distributor described in Patent Document 1 is large, the mounting area of the heat exchanger is reduced. Therefore, this refrigerant distributor has a problem that the heat exchanger performance is deteriorated.

The present disclosure has been made in view of the problems in the conventional technology described above, and aims to provide a refrigerant distributor, a heat exchanger, and an air conditioner that can improve the performance of the heat exchanger by suppressing an increase in size and a decrease in the mounting area of the heat exchanger.

本開示の冷媒分配器は、複数の板状体で構成され、１または複数の流入口から流入する冷媒を複数に分岐し、第１の方向に互いに間隔をあけて配列された複数の流出口から前記冷媒を流出させる冷媒分配器であって、前記複数の板状体は、前記流入口が形成された流入板と、前記流入板に形成された前記流入口に連通する矩形状の連通室を有する連通板と、前記流出口に連通する伝熱管が挿通され、前記連通室に対して複数の前記伝熱管が連通するように形成された伝熱管差し込み空間を有する伝熱管差し込み板とを備え、前記流入口から気液二相状態の前記冷媒が流入する場合において、前記連通室は、前記流入口の高さよりも下側に、側面から前記第１の方向と異なる第２の方向に突出し、液冷媒の下降を抑制する下降抑制部が形成されているものである。
A heat exchanger according to the present disclosure includes a refrigerant distributor according to the present disclosure and a plurality of heat transfer tubes connected to each of the plurality of outlets.
An air conditioner of the present disclosure includes the heat exchanger of the present disclosure.

According to the present disclosure, by forming a communication chamber in which a plurality of heat transfer tubes communicate, it is possible to reduce the thickness of the refrigerant distributor. Therefore, it is possible to suppress an increase in the size of the refrigerant distributor, suppress a decrease in the mounting area of the heat exchanger, and improve the performance of the heat exchanger.

1 is a perspective view showing an example of a configuration of a heat exchanger according to Embodiment 1; FIG. 1 is an exploded perspective view showing an example of a configuration of a refrigerant distributor according to Embodiment 1; FIG. FIG. 3 is a schematic diagram for explaining the relationship between channels when the refrigerant distributor of FIG. 2 is viewed from above; FIG. 3 is a schematic diagram showing an example of a positional relationship between flow paths when the refrigerant distributor of FIG. 2 is viewed from the front; 1 is a schematic diagram showing an example of a configuration of an air conditioner to which a heat exchanger according to Embodiment 1 is applied; FIG. FIG. 8 is an exploded perspective view showing an example of the configuration of a refrigerant distributor according to Embodiment 2; FIG. 7 is a schematic diagram for explaining the relationship between flow paths when the refrigerant distributor of FIG. 6 is viewed from above; FIG. 7 is a schematic diagram showing an example of a positional relationship between flow paths when the refrigerant distributor of FIG. 6 is viewed from the front; FIG. 11 is an exploded perspective view showing an example of the configuration of a refrigerant distributor according to Embodiment 3; FIG. 10 is a schematic diagram for explaining the relationship between flow paths when the refrigerant distributor of FIG. 9 is viewed from above; FIG. 10 is a schematic diagram showing an example of the positional relationship of each flow path when the refrigerant distributor of FIG. 9 is viewed from the front; FIG. 11 is an exploded perspective view showing an example of the configuration of a refrigerant distributor according to Embodiment 4; FIG. 11 is an exploded perspective view showing an example of the configuration of a refrigerant distributor according to Embodiment 5; FIG. 12 is an exploded perspective view showing an example of the configuration of a refrigerant distributor according to Embodiment 6;

Embodiment 1.
A refrigerant distributor according to Embodiment 1 will be described below with reference to the drawings and the like. In the following description, the refrigerant distributor according to Embodiment 1 distributes the refrigerant flowing into the heat exchanger. However, the present invention is not limited to this, and the refrigerant distributor may distribute the refrigerant flowing into other devices. Also, in the following description, the same reference numerals denote the same or equivalent parts, and are common throughout the embodiments described below. Furthermore, in the drawings, the size relationship of each component may differ from the actual size. In addition, detailed structures are simplified or omitted as appropriate. The forms of the constituent elements shown in the entire specification are merely examples, and are not limited to the forms described in the specification.

[Configuration of heat exchanger 1]
The configuration of the heat exchanger 1 according to Embodiment 1 will be described. FIG. 1 is a perspective view showing an example of the configuration of a heat exchanger according to Embodiment 1. FIG. As shown in FIG. 1 , the heat exchanger 1 includes a refrigerant distributor 2 , a gas header 3 , multiple heat transfer tubes 4 and multiple fins 5 . The refrigerant distributor 2 is provided with one or a plurality of refrigerant inflow portions 2A, which are refrigerant inflow ports, and a plurality of refrigerant outflow portions 2B, which are refrigerant outflow ports. A plurality of refrigerant outflow parts 2B are arranged in the height direction. The gas header 3 is provided with a plurality of refrigerant inflow portions 3A and one refrigerant outflow portion 3B. Refrigerant pipes of a refrigeration cycle device such as an air conditioner are connected to the refrigerant inlet portion 2A of the refrigerant distributor 2 and the refrigerant outlet portion 3B of the gas header 3 . A heat transfer tube 4 is connected between the refrigerant outflow portion 2B of the refrigerant distributor 2 and the refrigerant inflow portion 3A of the gas header 3 .

The heat transfer tube 4 is a flat tube or circular tube in which a plurality of flow paths are formed. The heat transfer tubes 4 are made of copper or aluminum, for example. The end portion of the heat transfer tube 4 on the side of the refrigerant distributor 2 is connected to the refrigerant outlet portion 2B of the refrigerant distributor 2 . A plurality of fins 5 are joined to the heat transfer tube 4 . The fins 5 are made of aluminum, for example. Although the example of FIG. 1 shows the case where the number of heat transfer tubes 4 is eight, the present invention is not limited to this, and any number may be used as long as the number of heat transfer tubes is plural.

[Refrigerant flow in heat exchanger 1]
The flow of refrigerant in the heat exchanger 1 according to Embodiment 1 will be described. For example, when the heat exchanger 1 functions as an evaporator, the refrigerant flowing through the refrigerant pipe flows into the refrigerant distributor 2 through the refrigerant inflow portion 2A, is distributed, and flows out to the plurality of heat transfer tubes 4 through the plurality of refrigerant outflow portions 2B. The refrigerant exchanges heat with, for example, air supplied by a blower (not shown) in the plurality of heat transfer tubes 4 . The refrigerant flowing through the plurality of heat transfer tubes 4 flows into the gas header 3 via the plurality of refrigerant inflow portions 3A, merges, and flows out to the refrigerant pipes via the refrigerant outflow portion 3B. In addition, when the heat exchanger 1 functions as a condenser, the refrigerant flows in a direction opposite to this flow.

[Configuration of Refrigerant Distributor 2]
The configuration of the refrigerant distributor 2 according to Embodiment 1 will be described. FIG. 2 is an exploded perspective view showing an example of the configuration of the refrigerant distributor according to Embodiment 1. FIG. FIG. 3 is a schematic diagram for explaining the relationship between the flow paths when the refrigerant distributor of FIG. 2 is viewed from above. In FIG. 3, each channel is indicated by a dashed line so as to facilitate the relationship between the channels formed in each plate-like body. FIG. 4 is a schematic diagram showing an example of the positional relationship of each flow path when the refrigerant distributor of FIG. 2 is viewed from the front.

As shown in FIGS. 2 to 4, the refrigerant distributor 2 is formed by stacking a plurality of rectangular plate-like bodies 10, for example. The plate-like body 10 is formed by alternately stacking first plate-like bodies 101, 102 and 103 and second plate-like bodies 111 and 112. As shown in FIG. The first plate-like bodies 101, 102 and 103 and the second plate-like bodies 111 and 112 have the same outer shape in plan view. The second plate-shaped bodies 111 and 112 are partition plates for partitioning the first plate-shaped bodies 101, 102 and 103, and are coated with brazing material on both sides, for example. Each of the first plate-like bodies 101, 102 and 103 is laminated via each of the second plate-like bodies 111 and 112 and integrally joined by brazing. Each plate-like body is processed by press work, cutting work, or the like.

In the first plate-like body 101, one or a plurality of first flow paths 10A, which are through-holes, are formed at substantially the center of the first plate-like body 101 in the width direction. A refrigerant pipe or a capillary tube of a refrigeration cycle device is connected to the first flow path 10A. The first flow path 10A corresponds to the coolant inlet portion 2A in FIG. The first plate-like body 101 is an inflow plate formed with one or a plurality of first flow paths 10A, which are the coolant inflow portions 2A as inlets.

The example shown in FIG. 2 shows a case where a capillary tube is connected to the first plate-like body 101. In this case, the first plate-like body 101 is provided with a plurality of first flow paths 10A. When a refrigerant pipe is connected to the first plate-like body 101, the first plate-like body 101 may be provided with one first flow path 10A.

In the second plate-like body 111, one or a plurality of second flow paths 10B, which are through-holes, are formed at substantially the central position of the second plate-like body 111 in the lateral direction. The second flow path 10B is formed at a position corresponding to the first flow path 10A of the first plate-shaped body 101, and communicates the first flow path 10A with a communication chamber 11 of the first plate-shaped body 102, which will be described later.

A plurality of communication chambers 11 are formed in the first plate-like body 102 . The communication chamber 11 is formed corresponding to the second flow path 10B of the second plate-shaped body 111, and communicates the second flow path 10B with a third flow path 10C of the second plate-shaped body 112, which will be described later. The communication chamber 11 is formed so that the plurality of third flow paths 10C communicate with each other. In this example, each communication chamber 11 is formed to communicate with two third flow paths 10C. The first plate-like body 102 is a communication plate formed with a communication chamber 11 as a communication channel communicating with the coolant inflow portion 2A as an inlet.

A plurality of third flow paths 10</b>C having the same shape as the outer shape of the heat transfer tubes 4 are formed in the second plate-like body 112 . The third flow path 10C holds the end portion of the heat transfer tube 4 inserted via the fourth flow path 10D of the first plate-like body 103, which will be described later.

The first plate-like body 103 is formed with a plurality of fourth flow paths 10</b>D, which are heat transfer tube insertion spaces having the same shape as the outer shape of the heat transfer tubes 4 . The fourth channel 10D is formed corresponding to the third channel 10C of the second plate-like body 112. As shown in FIG. The heat transfer tube 4 is inserted through the fourth flow path 10D. The heat transfer tube 4 is brazed to the first plate 103, and the heat transfer tube 4 is connected to the third flow path 10C of the second plate 112 by stacking the first plate 103 and the second plate 112. The first plate-like body 103 is a heat-transfer-tube insertion plate in which a fourth flow path 10D, which is a heat-transfer-tube insertion space through which the heat-transfer tubes 4 are inserted, is formed.

Thus, in the refrigerant distributor 2, the distribution channels 2a are formed by the channels formed in the first plate-shaped bodies 101, 102 and 103 and the second plate-shaped bodies 111 and 112, respectively. That is, the distribution channel 2a is composed of the first channel 10A, the second channel 10B, the third channel 10C, the fourth channel 10D, and the communication chamber 11. As shown in FIG.

[Refrigerant Flow in Refrigerant Distributor 2]
Next, the distribution channel 2a in the refrigerant distributor 2 and the flow of the refrigerant will be described with reference to FIGS. 2 to 4. FIG. When the heat exchanger 1 functions as an evaporator, a gas-liquid two-phase refrigerant flows into the refrigerant distributor 2 from the first flow path 10A of the first plate-like body 101 . The refrigerant that has flowed into the refrigerant distributor 2 flows into the communication chamber 11 of the first plate-like body 102 via the second flow path 10B of the second plate-like body 111 . The coolant that has flowed into the communication chamber 11 flows into the plurality of third flow paths 10C of the second plate-like body 112 that communicates with the communication chamber 11 and is divided. The divided refrigerant flows into the fourth flow passages 10D, which are heat transfer tube insertion spaces of the second plate-like body 112, and is uniformly distributed to the heat transfer tubes 4 connected to the respective fourth flow passages 10D.

In this example, the case where two third flow paths 10C communicate with one communication chamber 11 has been described, but the present invention is not limited to this, and three or more third flow paths 10C may communicate with one communication chamber 11. Thus, by changing the number of the third flow paths 10C communicating with the communication chamber 11, the number of distributions can be changed.

[Usage mode of heat exchanger 1]
Next, an example of usage of the heat exchanger 1 according to Embodiment 1 will be described. In addition, although the case where the heat exchanger 1 is used in the air conditioner 80 is described below, the heat exchanger 1 is not limited to this, and may be used in other refrigeration cycle devices having a refrigerant circulation circuit, for example. Moreover, although the case where the air conditioner 80 switches between the cooling operation and the heating operation has been described, the present invention is not limited to this, and the air conditioner 80 may perform only the cooling operation or the heating operation.

FIG. 5 is a schematic diagram showing an example of the configuration of an air conditioner 80 to which the heat exchanger 1 according to Embodiment 1 is applied. In FIG. 5 , the flow of the refrigerant during the cooling operation is indicated by dashed arrows, and the flow of the refrigerant during the heating operation is indicated by solid arrows. As shown in FIG. 5 , the air conditioner 80 has a compressor 81 , a four-way valve 82 , an outdoor heat exchanger 83 , an expansion valve 84 , an indoor heat exchanger 85 , an outdoor fan 86 and an indoor fan 87 . A refrigerant circulation circuit is formed by connecting the compressor 81, the four-way valve 82, the outdoor heat exchanger 83, the expansion valve 84, and the indoor heat exchanger 85 with refrigerant piping.

The flow of refrigerant during cooling operation will be described. The high-pressure, high-temperature gaseous refrigerant discharged from the compressor 81 flows through the four-way valve 82 into the outdoor heat exchanger 83, exchanges heat with the air supplied by the outdoor fan 86, and condenses. The condensed refrigerant becomes a high-pressure liquid state, flows out from the outdoor heat exchanger 83 , and becomes a low-pressure gas-liquid two-phase state by the expansion valve 84 . The low-pressure gas-liquid two-phase refrigerant flows into the indoor heat exchanger 85 and evaporates through heat exchange with the air supplied by the indoor fan 87, thereby cooling the room. The evaporated refrigerant becomes a low-pressure gas state, flows out from the indoor heat exchanger 85 , and is sucked into the compressor 81 via the four-way valve 82 .

The flow of refrigerant during heating operation will be described. The high-pressure, high-temperature gaseous refrigerant discharged from the compressor 81 flows into the indoor heat exchanger 85 via the four-way valve 82, and is condensed by heat exchange with the air supplied by the indoor fan 87, thereby heating the room. The condensed refrigerant becomes a high-pressure liquid state, flows out from the indoor heat exchanger 85 , and becomes a low-pressure gas-liquid two-phase refrigerant by the expansion valve 84 . The low-pressure gas-liquid two-phase refrigerant flows into the outdoor heat exchanger 83, exchanges heat with the air supplied by the outdoor fan 86, and evaporates. The evaporated refrigerant becomes a low-pressure gas state, flows out from the outdoor heat exchanger 83 , and is sucked into the compressor 81 via the four-way valve 82 .

In Embodiment 1, heat exchanger 1 is used as at least one of outdoor heat exchanger 83 and indoor heat exchanger 85 . The heat exchanger 1 is connected such that the refrigerant flows in from the refrigerant distributor 2 when acting as an evaporator. In other words, when the heat exchanger 1 functions as an evaporator, a gas-liquid two-phase refrigerant flows from the refrigerant pipe into the refrigerant distributor 2 and branches to flow into the heat transfer tubes 4 of the heat exchanger 1 . Further, when the heat exchanger 1 acts as a condenser, the liquid refrigerant flows from each heat transfer tube 4 into the refrigerant distributor 2, merges, and flows out to the refrigerant pipe.

As described above, the refrigerant distributor 2 according to Embodiment 1 includes the first plate-shaped body 101 having the first flow path 10A, the first plate-shaped body 102 having the communication chamber 11 communicating with the first flow path 10A, and the first plate-shaped body 103 having the third flow path 10C formed so that the plurality of heat transfer tubes 4 communicate with the communication chamber 11. By forming the communication chambers 11 communicating with the plurality of heat transfer tubes 4 in this way, the thickness of the refrigerant distributor 2 can be reduced compared to the case where the refrigerant distributor is formed in a cylindrical shape. Therefore, the refrigerant distributor 2 can be downsized. In addition, in an air conditioner with the same housing size, the downsizing of the refrigerant distributor 2 increases the mounting area of the heat exchanger 1, so that the performance of the heat exchanger can be improved.

Embodiment 2.
Next, Embodiment 2 will be described. Refrigerant distributor 2 according to Embodiment 2 differs from Embodiment 1 in the arrangement positions of first flow path 10A of first plate-shaped body 101 and second flow path 10B of second plate-shaped body 111 . In the following description, the same reference numerals are given to the parts that are common to the first embodiment, and detailed description thereof will be omitted.

[Configuration of Refrigerant Distributor 2]
A configuration of the refrigerant distributor 2 according to the second embodiment will be described. FIG. 6 is an exploded perspective view showing an example of the configuration of a refrigerant distributor according to the second embodiment. FIG. 7 is a schematic diagram for explaining the relationship between the flow paths when the refrigerant distributor of FIG. 6 is viewed from above. In FIG. 7, each channel is indicated by a dashed line so as to facilitate the relationship between the channels formed in each plate-like body. FIG. 8 is a schematic diagram showing an example of the positional relationship of each flow path when the refrigerant distributor of FIG. 6 is viewed from the front.

As shown in FIGS. 6 to 8, the refrigerant distributor 2 is formed by stacking a plurality of rectangular plate-like bodies 20, for example. The plate-like body 20 is formed by alternately stacking first plate-like bodies 101, 102 and 103 and second plate-like bodies 111 and 112. As shown in FIG. First plate-shaped bodies 102 and 103 and second plate-shaped body 112 are the same as those in the first embodiment.

In the refrigerant distributor 2, a distribution channel 2a is formed by the channels formed in the first plate-like bodies 101, 102 and 103 and the second plate-like bodies 111 and 112, respectively. That is, the distribution channel 2a is composed of the first channel 10A, the second channel 10B, the third channel 10C, the fourth channel 10D, and the communication chamber 11, as in the first embodiment.

The first plate-like body 101 is formed with one or a plurality of first flow paths 10A to which refrigerant pipes or capillary tubes of a refrigeration cycle device are connected. The example shown in FIG. 6 shows a case where a capillary tube is connected to the first plate-like body 101 . One or a plurality of second flow paths 10B are formed in the second plate-shaped body 111 at positions corresponding to the first flow paths 10A of the first plate-shaped body 101 .

Here, when a fluid such as air flows generally in one direction through the heat exchanger 1, the heat transfer performance of the heat exchanger 1 is higher on the upstream side of the fluid flow than on the downstream side. Therefore, in the second embodiment, the first flow path 10A of the first plate-like body 101 and the second flow path 10B of the second plate-like body 111 are arranged such that more refrigerant flows upstream of the flow of fluid with high heat transfer performance.

The first flow path 10A and the second flow path 10B are provided on the upstream side of the fluid flow relative to the central position of the plate-like body 10 in the transverse direction. As a result, when the heat exchanger 1 including the refrigerant distributor 2 functions as an evaporator into which a gas-liquid two-phase refrigerant flows, more gas-liquid two-phase refrigerant flows upstream where the amount of heat exchange is higher than that on the downstream side of the fluid flow. Therefore, the heat transfer performance on the upstream side of the fluid flow in the heat exchanger 1 is improved, and the heat exchanger performance can be improved.

As described above, in the refrigerant distributor 2 according to Embodiment 2, the first flow path 10A is formed in the first plate-like body 101 so as to be positioned upstream of the flow of fluid flowing outside the heat transfer tubes 4. As a result, more refrigerant flows on the upstream side of the fluid, so the heat transfer performance on the upstream side where the amount of heat exchange is large improves, and the performance of the heat exchanger can be improved.

Embodiment 3.
Next, the third embodiment will be described. A refrigerant distributor 2 according to Embodiment 3 differs from Embodiments 1 and 2 in the shape of communication chamber 11 of first plate-like body 102 . In the following description, parts common to those in Embodiments 1 and 2 are denoted by the same reference numerals, and detailed description thereof is omitted.

[Configuration of Refrigerant Distributor 2]
The configuration of the refrigerant distributor 2 according to Embodiment 3 will be described. FIG. 9 is an exploded perspective view showing an example of the configuration of a refrigerant distributor according to the third embodiment. FIG. 10 is a schematic diagram for explaining the relationship between the flow paths when the refrigerant distributor of FIG. 9 is viewed from above. In FIG. 10, each channel is indicated by a dashed line so as to facilitate the relationship between the channels formed in each plate-like body. FIG. 11 is a schematic diagram showing an example of the positional relationship of each flow path when the refrigerant distributor of FIG. 9 is viewed from the front.

As shown in FIGS. 9 to 11, the refrigerant distributor 2 is formed by stacking a plurality of rectangular plate-like bodies 30, for example. Plate-shaped body 30 is formed by alternately stacking first plate-shaped bodies 101, 102 and 103 and second plate-shaped bodies 111 and 112. As shown in FIG. First plate-shaped bodies 101 and 103 and second plate-shaped bodies 111 and 112 are the same as those in the first embodiment.

In the refrigerant distributor 2, a distribution channel 2a is formed by the channels formed in the first plate-like bodies 101, 102 and 103 and the second plate-like bodies 111 and 112, respectively. That is, the distribution channel 2a is composed of the first channel 10A, the second channel 10B, the third channel 10C, the fourth channel 10D, and the communication chamber 11, as in the first and second embodiments.

A plurality of communication chambers 11 corresponding to the second flow paths 10B of the second plate-like body 111 are formed in the first plate-like body 102 . In the third embodiment, the communication chamber 11 is provided with a descent suppressing portion 11a.

As shown in FIG. 10, the descent suppressing portion 11a is provided so as to be unevenly distributed on the downstream side of the fluid flow. Further, as shown in FIG. 11, the descent suppressing portion 11a is provided so as to be below the position of the second flow path 10B.

Normally, in the communication chamber 11, the downward flow resistance in the direction of gravity for the inflowing refrigerant is large. Since the descent suppressing portion 11a is provided below the refrigerant inflow position, the flow resistance on the lower side of the communication chamber 11 is greater than that on the upper side. Therefore, the liquid refrigerant of the gas-liquid two-phase refrigerant is suppressed from flowing biased downward due to gravity. As a result, the liquid refrigerant flows evenly through the communication chamber 11, so that when the liquid refrigerant flows out of the communication chamber 11, the liquid refrigerant can be evenly distributed to the plurality of communicating heat transfer tubes 4, and the performance of the heat exchanger 1 can be improved.

In addition, since the descent suppressing portion 11a is provided so as to be unevenly distributed on the downstream side of the fluid flow, the gas-liquid two-phase refrigerant flowing from the second flow path 10B of the second plate-shaped body 111 flows more upstream than on the downstream side of the fluid flow. As a result, the heat transfer performance on the upstream side of the fluid flow in the heat exchanger 1 is improved, so the heat exchanger performance can be improved.

As described above, in the refrigerant distributor 2 according to Embodiment 3, the communication chamber 11 has the descent suppressing portion 11a formed below the height of the first flow path 10A. As a result, of the gas-liquid two-phase refrigerant that has flowed into the communication chamber 11, the liquid refrigerant is suppressed from being biased downward due to gravity, and the liquid refrigerant is evenly distributed to the plurality of heat transfer tubes 4, so that the heat exchanger performance can be improved.

In the refrigerant distributor 2, the descent suppressing portion 11a is formed so as to be located on the downstream side of the fluid flow. As a result, more refrigerant flows on the upstream side of the fluid, so the heat transfer performance on the upstream side where the amount of heat exchange is large improves, and the performance of the heat exchanger can be improved.

Embodiment 4.
Next, the fourth embodiment will be described. Embodiment 4 is different from Embodiments 1 to 3 in that a plate-like body provided with a branch flow path for branching the refrigerant into a plurality is provided between the first plate-like body 101 and the first plate-like body 102. In the following description, parts common to those in Embodiments 1 to 3 are denoted by the same reference numerals, and detailed description thereof will be omitted.

[Configuration of Refrigerant Distributor 2]
The configuration of the refrigerant distributor 2 according to Embodiment 4 will be described. FIG. 12 is an exploded perspective view showing an example of the configuration of a refrigerant distributor according to the fourth embodiment.

As shown in FIG. 12, the refrigerant distributor 2 is formed by stacking a plurality of rectangular plate-like bodies 40, for example. Plate-like body 40 is formed by stacking first plate-like bodies 101, 102 and 103, second plate-like bodies 112, 113 and 114, and third plate-like bodies 121 and 122. As shown in FIG. The first plate-shaped bodies 101, 102 and 103, the second plate-shaped bodies 112, 113 and 114, and the third plate-shaped bodies 121 and 122 have the same outer shape in plan view.

In the refrigerant distributor 2, a distribution channel 2a is formed by channels formed in the first plate-shaped bodies 101, 102 and 103, the second plate-shaped bodies 112, 113 and 114, and the third plate-shaped bodies 121 and 122. The distribution channel 2a includes a first channel 10A, a fifth channel 10E, a sixth channel 10F, a seventh channel 10G, an eighth channel 10H, a ninth channel 10I, a tenth channel 10J and an eleventh channel 10K, a communication chamber 11, a first branch channel 12A, a second branch channel 12B and a third branch channel 12C, and a first stepping channel 13A and a second stepping channel 13B.

In the first plate-like body 101, one or a plurality of first flow paths 10A, which are through-holes, are formed at substantially the center of the first plate-like body 101 in the width direction. The example shown in FIG. 12 shows a case where a refrigerant pipe is connected to the first plate-like body 101. In this case, one first flow path 10A is provided substantially in the center of the first plate-like body 101.

A fifth flow path 10E, which is a through hole, is formed in the third plate-like body 121 at a substantially central position of the third plate-like body 121 . The fifth flow path 10E is formed at a position corresponding to the first flow path 10A of the first plate-like body 101, and communicates the first flow path 10A with a sixth flow path 10F, which will be described later.

In the second plate-shaped body 113, a pair of seventh flow paths 10G, which are circular through holes, are opened at positions in the horizontal direction with respect to the sixth flow path 10F, and a pair of eighth flow paths 10H, which are circular through holes, are opened at positions symmetrical in the height direction with respect to the sixth flow path 10F. In the second plate-like body 113, a pair of ninth flow paths 10I, which are circular through holes, are opened at positions in the horizontal direction with respect to the respective eighth flow paths 10H, and a pair of tenth flow paths 10J, which are circular through holes, are opened at positions symmetrical with respect to the eighth flow paths 10H. The second plate-like body 113 is a through channel plate in which sixth through tenth channels 10F to 10J are formed as through channels.

In the third plate-shaped body 122, a first branch flow channel 12A, which is a straight through groove extending in the horizontal direction, is formed so that the sixth flow channel 10F and the seventh flow channel 10G of the second plate-shaped body 113 communicate with each other in the stacked state. Further, in the third plate-shaped body 122, a second branch channel 12B, which is a linear through-groove extending in the horizontal direction, is formed at a position symmetrical in the height direction with respect to the first branch channel 12A so that the eighth channel 10H and the ninth channel 10I communicate with each other.

Furthermore, the third plate-like body 122 is formed with a third branch flow path 12C, which is a through groove. 12 C of 3rd branched flow paths are formed so that both ends of a linear part may extend in a mutually different height direction while extending in a horizontal direction linearly. Both ends of the third branch channel 12C are formed so as to be connected to the eleventh channel 10K of the second plate-like body 114, which will be described later. The third plate-like body 122 is a branch channel plate in which a first branch channel 12A to a third branch channel 12C are formed as branch channels.

In the third plate-like body 121, a first step-over flow channel 13A, which is a pair of through grooves extending in the height direction, is formed so that the seventh flow channel 10G and the eighth flow channel 10H of the second plate-shaped body 113 communicate with each other in the stacked state. Further, in the third plate-like body 121, a second step-over flow channel 13B, which is a pair of through grooves extending in the height direction, is formed so that the ninth flow channel 10I and the tenth flow channel 10J of the second plate-shaped body 113 communicate with each other in the stacked state. Each of the first-step bridging passage 13A and the second-step bridging passage 13B is formed so as to straddle the heat transfer tube 4 connected to the refrigerant outlet 2B, which is the outlet, so that the two passages communicate with each other. The third plate-shaped body 121 is a step-spanning channel plate in which a first step-spanning channel 13A and a second step-spanning channel 13B are formed as step-spanning channels.

An eleventh channel 10K, which is a through hole, is formed in the second plate-like body 114 . The eleventh channel 10K is formed at a position corresponding to the end of the third branched channel 12C of the third plate-shaped body 122, and communicates the third branched channel 12C and the communication chamber 11 of the first plate-shaped body 102 with each other.

When the plate-like bodies are stacked, the first branched flow path 12A is connected to the sixth flow path 10F and the seventh flow path 10G. Further, the seventh flow path 10G and the eighth flow path 10H are connected to both end portions of the first step bridging flow path 13A. The eighth channel 10H and the ninth channel 10I are connected to the second branch channel 12B. A ninth channel 10I and a tenth channel 10J are connected to both end portions of the second-step bridging channel 13B. The eleventh channel 10K is connected to both ends of the third branch channel 12C.

[Refrigerant Flow in Refrigerant Distributor 2]
Next, the distribution channel 2a in the refrigerant distributor 2 and the flow of the refrigerant will be described with reference to FIG. When the heat exchanger 1 functions as an evaporator, a gas-liquid two-phase refrigerant flows into the refrigerant distributor 2 from the first flow path 10A of the first plate-like body 101 .

The refrigerant flowing into the refrigerant distributor 2 goes straight through the fifth flow path 10E of the third plate-shaped body 121 and the sixth flow path 10F of the second plate-shaped body 113, collides with the surface of the second plate-shaped body 114 in the first branched flow path 12A of the third plate-shaped body 122, and splits in the horizontal direction. The branched coolant advances to both end portions of the first branch flow path 12A and flows into the pair of seventh flow paths 10G.

The refrigerant that has flowed into the seventh flow path 10G advances straight through the seventh flow path 10G in the opposite direction to the refrigerant that advances through the fifth flow path 10E and the sixth flow path 10F. This coolant flows into one end side of the first stepping flow channel 13A of the third plate-shaped body 121, collides with the surface of the first plate-shaped body 101 in the first stepping flow channel 13A, and advances to the other end side of the first stepping flow channel 13A. The coolant that has reached the other end of the first step bridging flow path 13A flows into the eighth flow path 10H of the second plate-like body 113 .

The refrigerant that has flowed into the eighth flow path 10H advances straight through the eighth flow path 10H in the opposite direction to the refrigerant that advances through the seventh flow path 10G. This coolant collides with the surface of the second plate-like body 114 in the second branch flow path 12B of the third plate-like body 122 and splits in the horizontal direction. The branched coolant advances to both end portions of the second branch flow path 12B and flows into the pair of ninth flow paths 10I.

The refrigerant that has flowed into the ninth flow path 10I advances straight through the ninth flow path 10I in the opposite direction to the refrigerant that advances through the eighth flow path 10H. This coolant flows into one end side of the second stepping flow channel 13B of the third plate-shaped body 121, collides with the surface of the first plate-shaped body 101 in the second stepping flow channel 13B, and advances to the other end side of the second stepping flow channel 13B. The coolant that has reached the other end of the second-step bridging flow path 13B flows into the tenth flow path 10J.

The refrigerant that has flowed into the tenth flow path 10J advances straight through the tenth flow path 10J in the opposite direction to the refrigerant that advances through the ninth flow path 10I. This coolant collides with the surface of the second plate-like body 114 in the third branch flow path 12C of the third plate-like body 122 and splits in the horizontal direction. The branched coolant advances to both ends of the third branch channel 12</b>C and flows into the eleventh channel 10</b>K of the second plate-like body 114 . Then, the coolant flows out from the eleventh channel 10K and flows into the communication chamber 11 of the first plate-like body 102 .

The coolant that has flowed into the communication chamber 11 flows into the plurality of third flow paths 10C of the second plate-like body 112 that communicates with the communication chamber 11 and is divided. The divided refrigerant flows into the fourth flow passages 10D of the second plate-like body 112, and is uniformly distributed to the heat transfer tubes 4 connected to the respective fourth flow passages 10D.

In this example, the refrigerant distributor 2 is divided into eight branches by passing the refrigerant through three branched flow paths. However, the number of branches can be changed by changing the number of branched flow paths.

As described above, in the refrigerant distributor 2 according to Embodiment 4, the third plate-shaped body 122 is arranged between the first plate-shaped body 101 and the first plate-shaped body 102. The third plate-shaped body 122 is formed with a branch flow path for branching and circulating the refrigerant flowing in from the first flow path 10A. As a result, multi-branching is achieved without increasing the size of the refrigerant distributor 2, and the length of the heat transfer tubes 4 in the heat exchanger 1 can be increased, so that the performance of the heat exchanger can be improved.

Embodiment 5.
Next, Embodiment 5 will be described. A refrigerant distributor 2 according to the fifth embodiment differs from that of the fourth embodiment in the shape of the communication chamber 11 of the first plate-like body 102 . In the following description, parts common to those in Embodiments 1 to 4 are denoted by the same reference numerals, and detailed description thereof will be omitted.

[Configuration of Refrigerant Distributor 2]
The configuration of the refrigerant distributor 2 according to Embodiment 5 will be described. FIG. 13 is an exploded perspective view showing an example of the configuration of a refrigerant distributor according to the fifth embodiment.

As shown in FIG. 13, the refrigerant distributor 2 is formed by stacking a plurality of rectangular plate-like bodies 50, for example. Plate-like body 40 is formed by stacking first plate-like bodies 101, 102 and 103, second plate-like bodies 112, 113 and 114, and third plate-like bodies 121 and 122. As shown in FIG. First plate-shaped bodies 101 and 103, second plate-shaped bodies 112, 113 and 114, and third plate-shaped body 121 are the same as those in the fourth embodiment.

In the refrigerant distributor 2, a distribution channel 2a is formed by channels formed in the first plate-shaped bodies 101, 102 and 103, the second plate-shaped bodies 112, 113 and 114, and the third plate-shaped bodies 121 and 122. The distribution channel 2a includes a first channel 10A, a fifth channel 10E, a sixth channel 10F, a seventh channel 10G, an eighth channel 10H, a ninth channel 10I, a tenth channel 10J and an eleventh channel 10K, a communication chamber 11, a first branch channel 12A, a second branch channel 12B and a third branch channel 12C, and a first stepping channel 13A and a second stepping channel 13B.

A plurality of communication chambers 11 corresponding to the second flow paths 10B of the second plate-like body 111 are formed in the first plate-like body 102 . In the fifth embodiment, the communication chamber 11 is provided with a descent suppressing portion 11a as in the third embodiment.

By providing the lowering suppressing portion 11a in the communication chamber 11 in this manner, the flow resistance on the lower side of the communication chamber 11 is greater than that on the upper side, as in the third embodiment. Therefore, the liquid refrigerant of the gas-liquid two-phase refrigerant is suppressed from flowing biased downward due to gravity. As a result, the liquid refrigerant flows evenly through the communication chamber 11, so that when the liquid refrigerant flows out of the communication chamber 11, the liquid refrigerant can be evenly distributed to the plurality of communicating heat transfer tubes 4, and the performance of the heat exchanger 1 can be improved.

In addition, since the descent suppressing portion 11a is provided so as to be unevenly distributed on the downstream side of the fluid flow, the gas-liquid two-phase refrigerant flowing from the second flow path 10B of the second plate-shaped body 111 flows more upstream than on the downstream side of the fluid flow. As a result, the heat transfer performance on the upstream side of the fluid flow in the heat exchanger 1 is improved, so the heat exchanger performance can be improved.

As described above, in the refrigerant distributor 2 according to the fifth embodiment, the communication chamber 11 has the descent suppressing portion 11a formed below the height of the first flow path 10A. As a result, of the gas-liquid two-phase refrigerant that has flowed into the communication chamber 11, the liquid refrigerant is suppressed from being biased downward due to gravity, and the liquid refrigerant is evenly distributed to the plurality of heat transfer tubes 4, so that the heat exchanger performance can be improved.

In the refrigerant distributor 2, the descent suppressing portion 11a is formed so as to be located on the downstream side of the fluid flow. As a result, more refrigerant flows on the upstream side of the fluid, so the heat transfer performance on the upstream side where the amount of heat exchange is large improves, and the performance of the heat exchanger can be improved.

Embodiment 6.
Next, Embodiment 6 will be described. A refrigerant distributor 2 according to the sixth embodiment differs from that of the fifth embodiment in the shape of the branch flow path of the third plate-like body. In the following description, parts common to those in Embodiments 1 to 5 are denoted by the same reference numerals, and detailed description thereof will be omitted.

[Configuration of Refrigerant Distributor 2]
The configuration of the refrigerant distributor 2 according to Embodiment 6 will be described. FIG. 14 is an exploded perspective view showing an example of the configuration of a refrigerant distributor according to Embodiment 6. FIG.

As shown in FIG. 14, the refrigerant distributor 2 is formed by stacking a plurality of rectangular plate-like bodies 60, for example. Plate-like body 60 is formed by stacking first plate-like bodies 101, 102 and 103, second plate-like bodies 112 and 113, and third plate-like bodies 121 and 123. As shown in FIG. The first plate-shaped bodies 101, 102 and 103, the second plate-shaped bodies 112, 113 and 114, and the third plate-shaped bodies 121 and 122 have the same outer shape in plan view.

In the refrigerant distributor 2, a distribution channel 2a is formed by the channels formed in the first plate-shaped bodies 101, 102 and 103, the second plate-shaped bodies 112 and 113, and the third plate-shaped bodies 121 and 123. The distribution channel 2a includes a first channel 10A, a fifth channel 10E, a sixth channel 10F, a seventh channel 10G, an eighth channel 10H, a ninth channel 10I and a tenth channel 10J, a communication chamber 11, a first branch channel 12A, a second branch channel 12B and a fourth branch channel 12D, and a first stepping channel 13A and a second stepping channel 13B.

In the first plate-like body 101, one or a plurality of first flow paths 10A, which are through-holes, are formed at substantially the center of the first plate-like body 101 in the width direction. The example shown in FIG. 14 shows a case where a refrigerant pipe is connected to the first plate-like body 101. In this case, one first flow path 10A is provided substantially in the center of the first plate-like body 101.

A fifth flow path 10E, which is a through hole, is formed in the third plate-like body 121 at a substantially central position of the third plate-like body 121 . The fifth flow path 10E is formed at a position corresponding to the first flow path 10A of the first plate-like body 101, and communicates the first flow path 10A with a sixth flow path 10F, which will be described later.

In the second plate-shaped body 113, a pair of seventh flow paths 10G, which are circular through holes, are opened at positions in the horizontal direction with respect to the sixth flow path 10F, and a pair of eighth flow paths 10H, which are circular through holes, are opened at positions symmetrical in the height direction with respect to the sixth flow path 10F. In the second plate-like body 113, a pair of ninth flow paths 10I, which are circular through holes, are opened at positions in the horizontal direction with respect to the respective eighth flow paths 10H, and a pair of tenth flow paths 10J, which are circular through holes, are opened at positions symmetrical with respect to the eighth flow paths 10H. The second plate-like body 113 is a through channel plate in which sixth through tenth channels 10F to 10J are formed as through channels.

In the third plate-shaped body 123, a first branch flow channel 12A, which is a straight through groove extending in the horizontal direction, is formed so that the sixth flow channel 10F and the seventh flow channel 10G of the second plate-shaped body 113 communicate with each other in the stacked state. Further, in the third plate-shaped body 122, a second branch channel 12B, which is a linear through-groove extending in the horizontal direction, is formed at a position symmetrical in the height direction with respect to the first branch channel 12A so that the eighth channel 10H and the ninth channel 10I communicate with each other.

Further, the third plate-like body 123 is formed with a fourth branch flow path 12D, which is a through groove. The fourth branch channel 12D extends linearly in the horizontal direction, and of the two ends of the straight portion, the upstream end, which is the end located on the upstream side of the fluid flow, extends linearly upward and downward. That is, the fourth branch channel 12D is formed so that the upstream end extends in two different directions parallel to the height direction, that is, is formed in a T-shape that is laid down. The upstream end of the fourth branch channel 12</b>D is formed so as to be connected to the communication chamber 11 of the first plate-like body 102 . The third plate-like body 123 is a branch channel plate in which a first branch channel 12A, a second branch channel 12B, and a fourth branch channel 12D are formed as branch channels.

In the third plate-like body 121, a first step-over flow channel 13A, which is a pair of through grooves extending in the height direction, is formed so that the seventh flow channel 10G and the eighth flow channel 10H of the second plate-shaped body 113 communicate with each other in the stacked state. Further, in the third plate-like body 121, a second step-over flow channel 13B, which is a pair of through grooves extending in the height direction, is formed so that the ninth flow channel 10I and the tenth flow channel 10J of the second plate-shaped body 113 communicate with each other in the stacked state. Each of the first-step bridging passage 13A and the second-step bridging passage 13B is formed so as to straddle the heat transfer tube 4 connected to the refrigerant outlet 2B, which is the outlet, so that the two passages communicate with each other. The third plate-shaped body 121 is a step-spanning channel plate in which a first step-spanning channel 13A and a second step-spanning channel 13B are formed as step-spanning channels.

When the plate-like bodies are stacked, the first branched flow path 12A is connected to the sixth flow path 10F and the seventh flow path 10G. Further, the seventh flow path 10G and the eighth flow path 10H are connected to both end portions of the first step bridging flow path 13A. The eighth channel 10H and the ninth channel 10I are connected to the second branch channel 12B. A ninth channel 10I and a tenth channel 10J are connected to both end portions of the second-step bridging channel 13B. Different communication chambers 11 are connected to the ends extending linearly upward and downward of the fourth branch channel 12D.

[Refrigerant Flow in Refrigerant Distributor 2]
Next, the distribution channel 2a in the refrigerant distributor 2 and the flow of the refrigerant will be described with reference to FIG. When the heat exchanger 1 functions as an evaporator, a gas-liquid two-phase refrigerant flows into the refrigerant distributor 2 from the first flow path 10A of the first plate-like body 101 .

The refrigerant that has flowed into the refrigerant distributor 2 travels straight through the fifth flow path 10E of the third plate-shaped body 121 and the sixth flow path 10F of the second plate-shaped body 113, collides with the surface of the first plate-shaped body 102 in the first branch flow path 12A of the third plate-shaped body 123, and splits in the horizontal direction. The branched coolant advances to both end portions of the first branch flow path 12A and flows into the pair of seventh flow paths 10G.

The refrigerant that has flowed into the seventh flow path 10G advances straight through the seventh flow path 10G in the opposite direction to the refrigerant that advances through the fifth flow path 10E and the sixth flow path 10F. This coolant flows into one end side of the first stepping flow channel 13A of the third plate-shaped body 121, collides with the surface of the first plate-shaped body 101 in the first stepping flow channel 13A, and advances to the other end side of the first stepping flow channel 13A. The coolant that has reached the other end of the first step bridging flow path 13A flows into the eighth flow path 10H of the second plate-like body 113 .

The refrigerant that has flowed into the eighth flow path 10H advances straight through the eighth flow path 10H in the opposite direction to the refrigerant that advances through the seventh flow path 10G. This coolant collides with the surface of the first plate-like body 102 in the second branch flow path 12B of the third plate-like body 123 and splits in the horizontal direction. The branched coolant advances to both end portions of the second branch flow path 12B and flows into the pair of ninth flow paths 10I.

The refrigerant that has flowed into the ninth flow path 10I advances straight through the ninth flow path 10I in the opposite direction to the refrigerant that advances through the eighth flow path 10H. This coolant flows into one end side of the second stepping flow channel 13B of the third plate-shaped body 121, collides with the surface of the first plate-shaped body 101 in the second stepping flow channel 13B, and advances to the other end side of the second stepping flow channel 13B. The coolant that has reached the other end of the second-step bridging flow path 13B flows into the tenth flow path 10J.

The refrigerant that has flowed into the tenth flow path 10J advances straight through the tenth flow path 10J in the opposite direction to the refrigerant that advances through the ninth flow path 10I. This coolant collides with the surface of the first plate-like body 102 in the fourth branch channel 12D of the third plate-like body 123, and flows at the upstream end of the fluid flow. The coolant that has flowed to the upstream end advances to both vertical ends of the upstream end and flows into the communication chamber 11 of the first plate-like body 102 .

The coolant that has flowed into the communication chamber 11 flows into the plurality of third flow paths 10C of the second plate-like body 112 that communicates with the communication chamber 11 and is divided. The divided refrigerant flows into the fourth flow passages 10D of the second plate-like body 112, and is uniformly distributed to the heat transfer tubes 4 connected to the respective fourth flow passages 10D.

As described above, in the refrigerant distributor 2 according to Embodiment 6, the fourth branch flow path 12D is formed such that, of the both ends of the horizontally extending linear portion, the upstream end located upstream of the fluid flow extends in two different directions parallel to the height direction. As a result, more refrigerant flows on the upstream side of the fluid, so the heat transfer performance on the upstream side where the amount of heat exchange is large improves, and the performance of the heat exchanger can be improved.

Although Embodiments 1 to 6 have been described above, the present disclosure is not limited to Embodiments 1 to 6 described above, and various modifications and applications are possible without departing from the gist of the present disclosure. For example, in Embodiments 1 to 6, the branch flow path and the step-spanning flow path were described as being entirely formed of through grooves penetrating through the front and rear surfaces of the plate-like body, but this is not limited to this example. A part of the branch channel and the step-spanning channel need only be in communication with each of the channels 10A to 10K.

REFERENCE SIGNS LIST 1 heat exchanger 2 refrigerant distributor 2A refrigerant inlet 2B refrigerant outlet 3 gas header 3A refrigerant inlet 3B refrigerant outlet 4 heat transfer tube 5 fins 10, 20, 30, 40, 50, 60 plate 10A first flow path 10B second flow path 10C third flow path 10D fourth flow path 10E fifth flow path 10F sixth flow path 10 G 7th flow path, 10H 8th flow path, 10I 9th flow path, 10J 10th flow path, 10K 11th flow path, 11 communication chamber, 11a descent suppressing portion, 12A first branch flow path, 12B second branch flow path, 12C third branch flow path, 12D fourth branch flow path, 13A first stage bridging flow path, 13B second step bridging flow path, 80 air conditioner, 81 compressor, 82 four-way valve, 8 3 outdoor heat exchanger 84 expansion valve 85 indoor heat exchanger 86 outdoor fan 87 indoor fan 101, 102, 103 first plate-shaped body 111, 112, 113, 114 second plate-shaped body 121, 122, 123 third plate-shaped body.

Claims (8)

A refrigerant distributor composed of a plurality of plate-shaped bodies, branching a refrigerant flowing in from one or more inlets into a plurality of outlets, and causing the refrigerant to flow out from a plurality of outlets arranged at intervals in a first direction,
The plurality of plate-like bodies are
an inflow plate in which the inflow port is formed;
a communication plate having a rectangular communication chamber communicating with the inlet formed in the inflow plate;
a heat-transfer-tube insertion plate having a heat-transfer-tube insertion space formed so that the heat-transfer tubes communicating with the outlet are inserted, and a plurality of the heat-transfer tubes communicates with the communication chamber ;
When the refrigerant in a gas-liquid two-phase state flows from the inlet,
The communication chamber is
Below the height of the inflow port, a descent suppressing portion that protrudes from the side surface in a second direction different from the first direction and suppresses descent of the liquid refrigerant is formed.
Refrigerant distributor. When the fluid flows in one direction outside the heat transfer tube,
The inlet is
2. A refrigerant distributor according to claim 1, wherein said inflow plate is formed so as to be positioned upstream of said fluid flow. The plurality of plate-like bodies are
3. The refrigerant distributor according to claim 1 or 2, further comprising a branch channel plate disposed between the inflow plate and the communication plate and having a branch channel for branching and circulating the refrigerant flowing from the inflow port in the second direction. The branch flow path is
4. The refrigerant distributor according to claim 3, wherein both ends of the linear portion linearly extending in the second direction are formed to extend in the first direction different from each other. When the fluid flows in one direction outside the heat transfer tube,
The branch flow path is
4. The refrigerant distributor according to claim 3, wherein, of both end portions of the linear portion linearly extending in the second direction, an upstream end portion located upstream of the flow of the fluid extends in two different directions parallel to the first direction. When the fluid flows in one direction outside the heat transfer tube,
The descent suppressing part is
2. A refrigerant distributor according to claim 1 , which is unevenly distributed downstream of said fluid flow. A refrigerant distributor according to any one of claims 1 to 6 ;
and a plurality of heat transfer tubes connected to each of the plurality of outlets. An air conditioner comprising the heat exchanger according to claim 7 .

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