HK1217531B

HK1217531B - Laminated header, heat exchanger, and air conditioner

Info

Publication number: HK1217531B
Application number: HK16105432.7A
Authority: HK
Inventors: 松田拓也; 石桥晃; 冈崎多佳志; 松井繁佳; 东井上真哉; 伊东大辅; 望月厚志
Original assignee: 三菱电机株式会社
Priority date: 2013-05-15
Filing date: 2014-05-13
Publication date: 2018-04-20

Description

Laminated header, heat exchanger, and air conditioner

Technical Field

The invention relates to a laminated header, a heat exchanger and an air conditioner.

Background

As a conventional laminated header, there is a structure including: a first plate-like body having a plurality of outlet flow paths formed therein; and a second plate-shaped body laminated on the first plate-shaped body, having a distribution flow channel formed therein, and distributing the refrigerant flowing in from the inlet flow channel to a plurality of outlet flow channels formed in the first plate-shaped body through the distribution flow channel to flow out. The distribution flow path includes a branch flow path having a plurality of grooves perpendicular to the inflow direction of the refrigerant. The refrigerant flowing from the inlet channel into the branch channel is branched into a plurality of branches by passing through the plurality of grooves, and the branches flow out by passing through a plurality of outlet channels formed in the first plate-like member (see, for example, patent document 1).

Patent document 1: japanese patent laid-open No. 2000-161818 (paragraphs [0012] to [0020], FIG. 1 and FIG. 2)

In such a laminated header, if the laminated header is used in a state where the inflow direction of the refrigerant flowing into the branch flow path is not parallel to the direction of gravity, the refrigerant may be insufficient or excessive in a certain branch direction due to the influence of gravity. That is, the conventional laminated header has a problem that the uniformity of refrigerant distribution is low.

Disclosure of Invention

The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a laminated header in which uniformity of refrigerant distribution is improved. In addition, the invention aims to obtain a heat exchanger with improved uniformity of refrigerant distribution. In addition, the invention aims to obtain an air conditioner with improved uniformity of refrigerant distribution.

The laminated header according to the present invention includes: a first plate-like body having a plurality of first outlet flow paths formed therein; and a second plate-like body attached to the first plate-like body, the second plate-like body having a distribution flow path that distributes the refrigerant flowing in from the first inlet flow path to the plurality of first outlet flow paths and flows out, the distribution flow path including a branch flow path, the branch flow path including: an opening part; a first straight portion parallel to the direction of gravity, a lower end of the first straight portion communicating with the opening portion via a first connection portion; and a second straight portion parallel to a direction of gravity, an upper end of the second straight portion communicating with the opening portion via a second connection portion, at least a part of the first connection portion and at least a part of the second connection portion not being parallel to the direction of gravity, wherein in the branch flow path, the refrigerant flows in from the opening portion to a lower end of the first straight portion and an upper end of the second straight portion via the first connection portion and the second connection portion, and flows out from an upper end of the first straight portion and a lower end of the second straight portion.

In the laminated header according to the present invention, the distribution flow path includes a branch flow path having: an opening part; a first straight line portion parallel to the direction of gravity, a lower end of which communicates with the opening portion via a first connection portion; and a second straight portion parallel to the direction of gravity, an upper end of the second straight portion communicating with the opening portion via a second connection portion, at least a part of the first connection portion and at least a part of the second connection portion not being parallel to the direction of gravity, wherein in the branch flow path, the refrigerant flows from the opening portion to a lower end of the first straight portion and an upper end of the second straight portion via the first connection portion and the second connection portion, and flows out from an upper end of the first straight portion and a lower end of the second straight portion. Therefore, after the uneven flow of the refrigerant in the direction perpendicular to the direction of gravity is made uniform in the first and second straight portions parallel to the direction of gravity, the refrigerant is made to flow out from the branch flow passage, and the refrigerant distribution is improved in uniformity because the refrigerant is less affected by the gravity.

Drawings

Fig. 1 is a diagram showing the structure of a heat exchanger according to embodiment 1.

Fig. 2 is a perspective view of the heat exchanger according to embodiment 1 in a state in which the laminated header is disassembled.

Fig. 3 is a development view of a laminated header of the heat exchanger according to embodiment 1.

Fig. 4 is a development view of a laminated header of the heat exchanger according to embodiment 1.

Fig. 5 is a diagram showing a modification of the flow path formed in the third plate member in the heat exchanger according to embodiment 1.

Fig. 6 is a diagram showing a modification of the flow path formed in the third plate member in the heat exchanger according to embodiment 1.

Fig. 7 is a perspective view of the heat exchanger according to embodiment 1 in a state in which the laminated header is disassembled.

Fig. 8 is a development view of a laminated header of the heat exchanger according to embodiment 1.

Fig. 9 is a diagram illustrating a flow passage formed in the third plate member in the heat exchanger according to embodiment 1.

Fig. 10 is a diagram illustrating a flow passage formed in the third plate member in the heat exchanger according to embodiment 1.

Fig. 11 is a diagram showing a relationship between a linear ratio of a first linear portion and a second linear portion formed in a flow passage of a third plate-like member and a distribution ratio in the heat exchanger according to embodiment 1.

Fig. 12 is a graph showing a relationship between the AK value of the heat exchanger and a linear ratio between a first linear portion and a second linear portion of a flow path formed in the third plate member in the heat exchanger according to embodiment 1.

Fig. 13 is a graph showing a relationship between the AK value of the heat exchanger and a linear ratio between the first linear portion and the second linear portion of the flow path formed in the third plate member in the heat exchanger according to embodiment 1.

Fig. 14 is a diagram showing a relationship between a distribution ratio and a linear ratio of the third linear portion formed in the flow passage of the third plate-like member in the heat exchanger according to embodiment 1.

Fig. 15 is a diagram showing a relationship between a bend angle and a distribution ratio of a connection portion formed in a flow path of a third plate member in the heat exchanger according to embodiment 1.

Fig. 16 is a diagram showing a configuration of an air conditioning apparatus to which the heat exchanger according to embodiment 1 is applied.

Fig. 17 is a perspective view of a heat exchanger according to variation-1 of embodiment 1, in which the laminated header is disassembled.

Fig. 18 is a perspective view of a heat exchanger according to variation-1 of embodiment 1, in which the laminated header is disassembled.

Fig. 19 is a perspective view of a heat exchanger according to variation-2 of embodiment 1, in which the laminated header is disassembled.

Fig. 20 is a perspective view of a heat exchanger according to variation-3 of embodiment 1, in which the laminated header is disassembled.

Fig. 21 is a development view of a laminated header according to modification-3 of the heat exchanger according to embodiment 1.

Fig. 22 is a perspective view of a heat exchanger according to variation-4 of embodiment 1, in which the laminated header is disassembled.

Fig. 23 is a perspective view of a main part of a heat exchanger according to variation-5 of embodiment 1 in a state where a laminated header is disassembled.

Fig. 24 is a sectional view of a main portion of a heat exchanger according to variation-5 of embodiment 1, in a state in which the laminated header is disassembled.

Fig. 25 is a perspective view of a main part of a heat exchanger according to variation-6 of embodiment 1 in a state where a laminated header is disassembled.

Fig. 26 is a sectional view of a main portion of a heat exchanger according to variation-6 of embodiment 1, in a state in which the laminated header is disassembled.

Fig. 27 is a perspective view of a heat exchanger according to variation-7 of embodiment 1, in which the laminated header is disassembled.

Fig. 28 is a diagram showing the structure of a heat exchanger according to embodiment 2.

Fig. 29 is a perspective view of the heat exchanger according to embodiment 2 in a state in which the laminated header is disassembled.

Fig. 30 is a development view of a laminated header of a heat exchanger according to embodiment 2.

Fig. 31 is a diagram showing a configuration of an air conditioning apparatus to which the heat exchanger according to embodiment 2 is applied.

Fig. 32 is a diagram showing the structure of a heat exchanger according to embodiment 3.

Fig. 33 is a perspective view of the heat exchanger according to embodiment 3, in a state in which the laminated header is disassembled.

Fig. 34 is a development view of a laminated header of a heat exchanger according to embodiment 3.

Fig. 35 is a diagram showing a configuration of an air conditioning apparatus to which the heat exchanger according to embodiment 3 is applied.

Detailed Description

The laminated header according to the present invention will be described below with reference to the drawings.

In the following description, the laminated header according to the present invention is described as a laminated header that distributes the refrigerant flowing into the heat exchanger, but the laminated header according to the present invention may be a laminated header that distributes the refrigerant flowing into another device. The following configurations, operations, and the like are merely examples, and are not limited to such configurations, operations, and the like. In the drawings, the same or similar components are denoted by the same reference numerals, or the reference numerals are omitted. In addition, the fine structure is appropriately simplified or omitted from the drawings. In addition, duplicate or similar descriptions are appropriately simplified or omitted.

Embodiment 1.

A heat exchanger according to embodiment 1 will be described.

< Structure of Heat exchanger >

The structure of the heat exchanger according to embodiment 1 will be described below.

As shown in fig. 1, the heat exchanger 1 has a laminated header 2, a header 3, a plurality of first heat transfer pipes 4, a holding member 5, and a plurality of fins 6.

The laminated header 2 has a refrigerant inflow portion 2A and a plurality of refrigerant outflow portions 2B. The header 3 has a refrigerant outflow portion 3B and a plurality of refrigerant inflow portions 3A. Refrigerant pipes are connected to the refrigerant inflow portion 2A of the laminated header 2 and the refrigerant outflow portion 3B of the header 3. A plurality of first heat transfer pipes 4 are connected between the plurality of refrigerant outflow portions 2B of the laminated header 2 and the plurality of refrigerant inflow portions 3A of the header 3.

The first heat transfer pipe 4 is a flat pipe in which a plurality of flow paths are formed. The first heat transfer pipe 4 is made of aluminum, for example. The ends of the plurality of first heat transfer pipes 4 on the laminated header 2 side are connected to the plurality of refrigerant outflow portions 2B of the laminated header 2 while being held by the plate-like holding member 5. The holding member 5 is made of aluminum, for example. A plurality of fins 6 are joined to the first heat transfer pipe 4. The fins 6 are made of aluminum, for example. The joining of the first heat transfer pipe 4 and the fin 6 may be brazing. In fig. 1, the case where the number of the first heat transfer pipes 4 is 8 is shown, but the present invention is not limited to this case.

< flow of refrigerant in Heat exchanger >

The flow of the refrigerant in the heat exchanger according to embodiment 1 will be described below.

The refrigerant flowing through the refrigerant pipe flows into the laminated header 2 through the refrigerant inflow portion 2A, is distributed, and further flows out to the plurality of first heat transfer tubes 4 through the plurality of refrigerant outflow portions 2B. The refrigerant exchanges heat with, for example, air supplied by a fan in the plurality of first heat transfer pipes 4. The refrigerant flowing through the plurality of first heat transfer tubes 4 flows into the header 3 through the plurality of refrigerant inflow portions 3A, is joined, and further flows out to the refrigerant piping through the refrigerant outflow portion 3B. The refrigerant can flow backwards.

< Structure of laminated header >

The structure of the laminated header of the heat exchanger according to embodiment 1 will be described below.

As shown in fig. 2, the laminated header 2 includes a first plate-like member 11 and a second plate-like member 12. The first plate-like body 11 and the second plate-like body 12 are laminated together.

The first plate-like body 11 is stacked on the refrigerant outflow side. The first plate-like body 11 has a first plate-like member 21. The first plate-like body 11 has a plurality of first outlet flow channels 11A formed therein. The plurality of first outlet channels 11A correspond to the plurality of refrigerant outflow portions 2B in fig. 1.

The first plate-like member 21 has a plurality of flow passages 21A formed therein. The plurality of flow paths 21A are through holes whose inner peripheral surfaces are shaped to follow the outer peripheral surface of the first heat transfer pipe 4. When the first plate-like member 21 is laminated, the plurality of flow passages 21A function as the plurality of first outlet flow passages 11A. The first plate-like member 21 is made of aluminum, for example, and has a thickness of about 1mm to 10 mm. When the plurality of flow paths 21A are formed by press working or the like, the working can be simplified and the manufacturing cost can be reduced.

The end of the first heat transfer pipe 4 protrudes from the surface of the holding member 5, the first plate-like body 11 is laminated on the holding member 5, and the inner peripheral surface of the first outlet channel 11A is fitted to the outer peripheral surface of the end of the first heat transfer pipe 4, whereby the first heat transfer pipe 4 and the first outlet channel 11A are connected. The first outlet channel 11A and the first heat transfer pipe 4 may be positioned by, for example, fitting a convex portion formed in the holding member 5 into a concave portion formed in the first plate-like member 11, and in this case, the end portion of the first heat transfer pipe 4 may not protrude from the surface of the holding member 5. The first heat transfer pipe 4 may be directly connected to the first outlet flow path 11A without providing the holding member 5. In this case, the component cost and the like can be reduced.

The second plate-like body 12 is laminated on the inflow side of the refrigerant. The second plate-like body 12 has a second plate-like member 22 and a plurality of third plate-like members 23 _ 1 to 23 _ 3. The second plate-like body 12 is formed with a distribution flow channel 12A. The distribution channel 12A has a first inlet channel 12A and a plurality of branch channels 12b. The first inlet channel 12A corresponds to the refrigerant inflow portion 2A in fig. 1.

The second plate-like member 22 has a flow passage 22A formed therein. The flow path 22A is a circular through hole. When the second plate-like member 22 is laminated, the flow passage 22A functions as the first inlet flow passage 12A. The second plate-like member 22 is, for example, about 1mm to 10mm thick and is made of aluminum. When the flow path 22A is formed by press working or the like, the working can be simplified and the manufacturing cost can be reduced.

For example, a joint or the like is provided on the surface of the second plate-like member 22 on the side where the refrigerant flows, and the refrigerant pipe is connected to the first inlet channel 12a via the joint or the like. The inner peripheral surface of the first inlet passage 12a is shaped to fit the outer peripheral surface of the refrigerant pipe, and the refrigerant pipe may be directly connected to the first inlet passage 12a without using a joint or the like. In this case, the component cost and the like can be reduced.

A plurality of flow passages 23A _ 1 to 23A _ 3 are formed in the plurality of third plate members 23 _ 1 to 23 _ 3. The flow paths 23A _ 1 to 23A _ 3 are through grooves. The shape of the through-groove will be described in detail later. When the plurality of third plate members 23 _ 1 to 23 _ 3 are laminated, the plurality of flow passages 23A _ 1 to 23A _ 3 function as branch flow passages 12b, respectively. The third plate members 23 _ 1 to 23 _ 3 are made of aluminum and have a thickness of, for example, about 1mm to 10 mm. When the plurality of flow paths 23A _ 1 to 23A _ 3 are formed by press working or the like, the working can be simplified and the manufacturing cost can be reduced.

Hereinafter, the plurality of third plate members 23 _ 1 to 23 _ 3 may be collectively referred to as a third plate member 23. Hereinafter, the plurality of channels 23A _ 1 to 23A _ 3 may be collectively referred to as a channel 23A. Hereinafter, the holding member 5, the first plate-like member 21, the second plate-like member 22, and the third plate-like member 23 may be collectively referred to as a plate-like member.

The branch flow path 12b branches the refrigerant flowing in into two and flows out. Therefore, in the case where 8 first heat transfer pipes 4 are connected, a minimum of 3 third plate members 23 are required. In the case of 16 connected first heat transfer pipes 4, a minimum of 4 third plate parts 23 are required. The number of first heat transfer pipes 4 connected is not limited to the power of 2. In this case, the branched flow path 12b and the flow path not branched may be combined. In addition, the number of the first heat transfer pipes 4 connected may be 2.

As shown in fig. 3, the flow passage 23A formed in the third plate-like member 23 has a shape in which the lower end 23c of the first linear portion 23A and the upper end 23f of the second linear portion 23d are connected to each other via the third linear portion 23g. The first straight portion 23a and the second straight portion 23d are parallel to the direction of gravity. The third straight portion 23g is perpendicular to the direction of gravity. The third straight portion 23g may be inclined from a state perpendicular to the direction of gravity. In the flow path 23A, a region of the third straight portion 23g other than a partial region 23j (hereinafter, referred to as an opening 23j) between the end portion 23h and the end portion 23i is blocked by a member stacked adjacently on the inflow side of the refrigerant, and a region other than the upper end 23b of the first straight portion 23A and the lower end 23e of the second straight portion 23d is blocked by a member stacked adjacently on the outflow side of the refrigerant, thereby forming the branch flow path 12b.

In order to cause the inflowing refrigerant to branch at positions of different heights and flow out, the upper end 23b of the first straight portion 23a is positioned above the opening 23j, and the lower end 23e of the second straight portion 23d is positioned below the opening 23j. In particular, when the length of the first straight portion 23A is almost equal to the length of the second straight portion 23d and the opening 23j is positioned approximately in the middle between the lower end 23c of the first straight portion 23A and the upper end 23f of the second straight portion 23d, it is possible to reduce the variation in the distances from the opening 23j to the upper end 23b of the first straight portion 23A and the lower end 23e of the second straight portion 23d along the flow path 23A, and to avoid complicating the shape. The straight line connecting the upper end 23b of the first straight portion 23a and the lower end 23e of the second straight portion 23d is parallel to the longitudinal direction of the third plate-like member 23, so that the dimension of the third plate-like member 23 in the short direction can be reduced, and the member cost, the weight, and the like can be reduced. Further, the straight line connecting the upper end 23b of the first straight portion 23a and the lower end 23e of the second straight portion 23d is parallel to the arrangement direction of the first heat transfer pipes 4, thereby saving space of the heat exchanger 1.

As shown in fig. 4, when the arrangement direction of the first heat transfer pipes 4 is not parallel to the direction of gravity, that is, intersects the direction of gravity, the longitudinal direction of the third plate-like member 23 is not perpendicular to the third straight portion 23g. That is, the laminated header 2 is not limited to the case where the plurality of first outlet flow paths 11A are arranged in the direction of gravity, and may be used when the heat exchanger 1 is arranged obliquely, such as a heat exchanger of a wall-mounted indoor air conditioner indoor unit, an air conditioner outdoor unit, or a cooling device outdoor unit. In fig. 4, the longitudinal direction of the cross section of the flow channel 21A formed in the first plate-like member 21, that is, the longitudinal direction of the cross section of the first outlet flow channel 11A is perpendicular to the longitudinal direction of the first plate-like member 21, but the longitudinal direction of the cross section of the first outlet flow channel 11A may be perpendicular to the direction of gravity.

The flow path 23A has connecting portions 23k and 23l that connect an end portion 23h and an end portion 23i of the third linear portion 23g to a lower end 23c of the first linear portion 23A and an upper end 23f of the second linear portion 23d, respectively. The connecting portions 23k and 23l may be linear or curved. At least a part of the connecting portion 23k and at least a part of the connecting portion 23l are not parallel to the direction of gravity. The connecting portion 23k connecting the end portion 23h of the third linear portion 23g and the lower end 23c of the first linear portion 23a corresponds to a "first connecting portion" in the present invention. The connecting portion 23l connecting the end portion 23i of the third straight portion 23g and the upper end 23f of the second straight portion 23d corresponds to a "second connecting portion" in the present invention.

The flow path 23A may be a through groove having a shape in which the connection portions 23k and 23l are branched, and the other flow path may be communicated with the branch flow path 12b. When the other flow path is not communicated with the branch flow path 12b, the uniformity of refrigerant distribution can be reliably improved.

Fig. 5 and 6 are views showing modifications of the flow path formed in the third plate member in the heat exchanger according to embodiment 1.

As shown in fig. 5, the flow path 23A may not have the third straight portion 23g. That is, the end of the connecting portion 23k on the side not connected to the lower end 23c of the first straight portion 23a and the end of the connecting portion 23l on the side not connected to the upper end 23f of the second straight portion 23d may be directly connected to the opening 23j. The end of the connecting portion 23k on the side connected to the opening 23j and the end of the connecting portion 23l on the side connected to the opening 23j may not be perpendicular to the direction of gravity. Even when the third straight portion 23g is not provided, the first straight portion 23a and the second straight portion 23d are provided, so that the uniformity of refrigerant distribution can be improved. In the case of having the third straight portion 23g, the uniformity of refrigerant distribution can be further improved.

As shown in fig. 6, for example, when the arrangement direction of the first heat transfer pipes 4 intersects the direction of gravity, the flow path 23A may be configured such that: the lower end 23c of the first linear portion 23a is close to the end 23h of the third linear portion 23g, and the upper end 23f of the second linear portion 23d is close to the end 23i of the third linear portion 23g.

< flow of refrigerant in laminated header >

The flow of the refrigerant in the laminated header of the heat exchanger according to embodiment 1 will be described below.

As shown in fig. 3 and 4, the refrigerant passing through the flow passage 22A of the second plate-like member 22 flows into the opening 23j of the flow passage 23A formed in the third plate-like member 23 _ 1. The refrigerant that has flowed into the opening 23j contacts the surfaces of the adjacently stacked members, and is divided into two streams toward the end 23h and the end 23i of the third linear portion 23g. The branched refrigerant flows into the lower end 23c of the first straight portion 23A and the upper end 23f of the second straight portion 23d of the flow passage 23A via the connection portions 23k and 23l of the flow passage 23A, reaches the upper end 23b of the first straight portion 23A and the lower end 23e of the second straight portion 23d of the flow passage 23A, and further flows into the opening 23j of the flow passage 23A formed in the third plate-like member 23 _ 2.

Similarly, the refrigerant flowing into the opening 23j of the flow path 23A formed in the third plate-like member 23 _ 2 contacts the surfaces of the adjacently stacked members, and is divided into two flows toward the end 23h and the end 23i of the third linear portion 23g. The branched refrigerant flows into the lower end 23c of the first straight portion 23A and the upper end 23f of the second straight portion 23d of the flow passage 23A via the connection portions 23k and 23l of the flow passage 23A, reaches the upper end 23b of the first straight portion 23A and the lower end 23e of the second straight portion 23d of the flow passage 23A, and further flows into the opening 23j of the flow passage 23A formed in the third plate-like member 23 _ 3.

Similarly, the refrigerant flowing into the opening 23j of the flow path 23A formed in the third plate-like member 23 _ 3 contacts the surfaces of the adjacently stacked members, and is divided into two flows toward the end 23h and the end 23i of the third linear portion 23g. The branched refrigerant flows into the lower end 23c of the first straight portion 23A and the upper end 23f of the second straight portion 23d of the flow passage 23A via the connecting portions 23k and 23l of the flow passage 23A, reaches the upper end 23b of the first straight portion 23A and the lower end 23e of the second straight portion 23d of the flow passage 23A, and further flows into the first heat transfer pipe 4 through the flow passage 21A of the first plate-like member 21.

< method for laminating plate-like Member >

A method of laminating the plate-like members of the laminated header of the heat exchanger according to embodiment 1 will be described below.

The plate-shaped members may be stacked by brazing. The brazing material for joining may be supplied by using the both-side clad material obtained by rolling the brazing material on both sides for all the plate-shaped members or for the plate-shaped members with one plate-shaped member interposed therebetween. The brazing material for joining may be supplied by using a single-side clad material obtained by rolling the brazing material on one side for all the plate-shaped members. The brazing material may be supplied by laminating brazing material sheets between the plate-shaped members. The brazing material may be supplied by applying a paste-like brazing material between the plate-like members. The brazing material may be supplied by laminating both side cladding members, which are obtained by rolling the brazing material on both sides, between the plate-shaped members.

The plate-like members are stacked by brazing so that there is no gap between the plate-like members, thereby suppressing leakage of the refrigerant and ensuring pressure resistance. When brazing is performed while pressing the plate-like members, the occurrence of brazing defects is further suppressed. When a treatment such as formation of a rib or the like to promote formation of a fillet is performed at a portion where leakage of the refrigerant is likely to occur, occurrence of a brazing defect is further suppressed.

In addition, when all the members to be brazed and joined, including the first heat transfer pipe 4, the fins 6, and the like, are made of the same material (for example, aluminum), the brazing and joining can be performed uniformly, and the productivity can be improved. The brazing of the first heat transfer tubes 4 and the fins 6 may be performed after the brazing of the laminated header 2. Alternatively, only the first plate-like body 11 may be brazed to the holding member 5, and then the second plate-like body 12 may be brazed.

Fig. 7 is a perspective view of the heat exchanger according to embodiment 1 in a state in which the laminated header is disassembled. Fig. 8 is a development view of a laminated header of the heat exchanger according to embodiment 1.

In particular, the brazing material can be supplied by laminating both side cladding members, which are plate-shaped members obtained by rolling the brazing material on both sides, between the plate-shaped members. As shown in FIGS. 7 and 8, a plurality of both-side covers 24 _ 1 to 24 _ 5 are laminated between the plate-like members. Hereinafter, the plurality of bilateral coating members 24 _ 1 to 24 _ 5 may be collectively referred to as the bilateral coating member 24. Further, the both-side covers 24 may be stacked between some of the plate-shaped members, and the brazing material may be supplied between the other plate-shaped members by another method.

The flow passage 24A through which the side cover 24 penetrates is formed in the side cover 24 in a region facing a region where the refrigerant flows out of the flow passage formed by the plate-like members stacked adjacent to the side where the refrigerant flows in. The flow passages 24A formed in the covers 24 on both sides of the second plate-like member 22 and the third plate-like member 23 are circular through holes. The flow path 24A formed by the both-side covers 24 _ 5 stacked between the first plate-like member 21 and the holding member 5 is a through hole having an inner peripheral surface along the shape of the outer peripheral surface of the first heat transfer pipe 4.

When the both-side covers 24 are laminated, the flow path 24A functions as a refrigerant isolation flow path between the first outlet flow path 11A and the distribution flow path 12A. In a state where the both-side covers 24 _ 5 are stacked on the holding member 5, the end portion of the first heat transfer pipe 4 may or may not protrude from the surface of the both-side covers 24 _ 5. When the flow path 24A is formed by press working or the like, the working can be simplified and the manufacturing cost can be reduced. When all the members to be brazed, including the both-side wrapping members 24, are made of the same material (for example, aluminum), the brazing can be performed uniformly, and the productivity can be improved.

Since the refrigerant isolation flow path is formed by the both-side cover 24, the isolation of the refrigerants branched and flowing out from the branch flow path 12b from each other is particularly reliably achieved. In addition, a traveling distance until the refrigerant flows into the branch flow path 12b and the first outlet flow path 11A can be secured according to the thickness of each of the both-side covers 24, thereby improving the uniformity of refrigerant distribution. In addition, the degree of freedom in designing the branch flow path 12b is increased by reliably achieving isolation between the refrigerants.

< shape of flow passage of third plate-like member >

Fig. 9 and 10 are diagrams illustrating a flow passage formed in the third plate member in the heat exchanger according to embodiment 1. In fig. 9 and 10, a part of the flow path formed by the members stacked adjacent to each other is shown by a broken line. Fig. 9 shows the flow path 23A formed in the third plate-like member 23 in a state where the double-sided coating material 24 is not laminated (the state of fig. 2 and 3), and fig. 10 shows the flow path 23A formed in the third plate-like member 23 in a state where the double-sided coating material 24 is laminated (the state of fig. 7 and 8).

As shown in fig. 9 and 10, the center of the region of the flow path 23A where the refrigerant flows out of the first straight portion 23A is defined as the upper end 23b of the first straight portion 23A, and the distance between the upper end 23b and the lower end 23c of the first straight portion 23A is defined as the linear distance L1. The center of the region of the second straight portion 23d of the flow path 23A from which the refrigerant flows out is defined as the lower end 23e of the second straight portion 23d, and the distance between the lower end 23e and the upper end 23f of the second straight portion 23d is defined as a straight distance L2. Further, the hydraulic equivalent diameter of the first straight portion 23a is set to the hydraulic equivalent diameter De1, and the ratio of the straight distance L1 to the hydraulic equivalent diameter De1 is defined as a straight line ratio L1/De 1. Further, the hydraulic equivalent diameter of the second straight portion 23d is set to be the hydraulic equivalent diameter De2, and the ratio of the straight distance L2 to the hydraulic equivalent diameter De2 is defined as a straight ratio L2/De 2. The distribution ratio R is defined as a ratio of the flow rate of the refrigerant flowing out from the upper end 23b of the first straight portion 23A of the flow passage 23A to the sum of the flow rate of the refrigerant flowing out from the upper end 23b of the first straight portion 23A of the flow passage 23A and the flow rate of the refrigerant flowing out from the lower end 23e of the second straight portion 23d of the flow passage 23A.

Fig. 11 is a diagram showing a relationship between a linear ratio of the first linear portion and the second linear portion and the distribution ratio in the flow path formed in the third plate member in the heat exchanger according to embodiment 1. Fig. 11 shows a change in distribution ratio R in the next flow path 23A into which the refrigerant flowing out of the flow path 23A flows when the straight line ratio L1/De1 (L2/De 2) of the flow path 23A is changed in a state where the straight line ratio L1/De1 is equal to the straight line ratio L2/De 2.

As shown in fig. 11, the distribution ratio R is changed as follows: until the straight-line ratio L1/De1 and the straight-line ratio L2/De2 reach 10.0, the distribution ratio R increases, and the distribution ratio R becomes 0.5 when the straight-line ratio reaches 10.0 or more. If the linear ratio L1/De1 and the linear ratio L2/De2 are less than 10.0, the joints 23k and 23L are not parallel to the direction of gravity, and the refrigerant flows into the third linear portion 23g of the next flow path 23A in a state where a drift occurs, so that the distribution ratio R does not reach 0.5.

Fig. 12 and 13 are diagrams showing the relationship between the AK value of the heat exchanger and the ratio of the straight lines of the first straight line portion and the second straight line portion in the flow path formed in the third plate member in the heat exchanger according to embodiment 1. Fig. 12 shows changes in the AK values of the heat exchanger 1 when the straight-line ratio L1/De1 (L2/De 2) is changed. Fig. 13 shows the change in the effective AK value of the heat exchanger 1 when the straight-line ratio L1/De1 (L2/De 2) is changed. AK value is the heat transfer area A [ m ] of the heat exchanger 1²]Heat passing rate K [ J/(S.m) of heat exchanger 1²·K)]The effective AK value is a value defined by the product of the AK value and the above-mentioned distribution ratio R. The higher the effective AK value, the higher the performance of the heat exchanger 1.

On the other hand, as shown in fig. 12, the larger the straight line ratio L1/De1 and the straight line ratio L2/De2 are, the wider the arrangement interval of the first heat transfer pipes 4, that is, the number of the first heat transfer pipes 4 decreases, and the AK value of the heat exchanger 1 decreases. Therefore, as shown in fig. 13, the effective AK value varies as follows: until the straight-line ratio L1/De1 and the straight-line ratio L2/De2 reach 3.0, the effective AK value increases, and when the straight-line ratio reaches 3.0 or more, the effective AK value decreases while decreasing the decrease amount. That is, when the straight line ratio L1/De1 and the straight line ratio L2/De2 are set to 3.0 or more, the effective AK value, that is, the performance of the heat exchanger 1 can be maintained.

As shown in fig. 9 and 10, the distances from the center of the region of the flow path 23A into which the refrigerant flows, i.e., the center 23m of the opening 23j to the end 23h and the end 23i of the third straight portion 23g are defined as straight distances L3 and L4, respectively. The hydraulic equivalent diameter of the flow path from the center 23m of the opening 23j to the end 23h of the third linear portion 23g is defined as a hydraulic equivalent diameter De3, and the ratio of the linear distance L3 to the hydraulic equivalent diameter De3 is defined as a linear ratio L3/De 3. The hydraulic equivalent diameter of the flow path from the center 23m of the opening 23j to the end 23i of the third linear portion 23g is defined as a hydraulic equivalent diameter De4, and the ratio of the linear distance L4 to the hydraulic equivalent diameter De4 is defined as a linear ratio L4/De 4.

Fig. 14 is a diagram showing a relationship between a distribution ratio and a linear ratio of the third linear portion of the flow passage formed in the third plate-like member in the heat exchanger according to embodiment 1. Fig. 14 shows a change in the distribution ratio R in the flow passage 23A when the straight-line ratio L3/De3 (L4/De 4) is changed in a state where the straight-line ratio L3/De3 is equal to the straight-line ratio L4/De 4.

As shown in fig. 14, the distribution ratio R is changed as follows: until the straight-line ratio L3/De3 and the straight-line ratio L4/De4 reach 1.0, the distribution ratio R increases, and the distribution ratio R becomes 0.5 when the straight-line ratio reaches 1.0 or more. If the straight line ratio L3/De3 and the straight line ratio L4/De4 are less than 1.0, the following effects are exerted: the region of the connecting portion 23k communicating with the end portion 23h of the third straight portion 23g and the region of the connecting portion 23l communicating with the end portion 23i of the third straight portion 23g are bent in different directions with respect to the direction of gravity so that the distribution ratio R does not reach 0.5. That is, the uniformity of refrigerant distribution can be further improved by setting the straight line ratio L3/De3 and the straight line ratio L4/De4 to 1.0 or more.

As shown in fig. 9 and 10, an angle between the center line of the connecting portion 23k and the center line of the third linear portion 23g is defined as an angle θ 1, and an angle between the center line of the connecting portion 23l and the center line of the third linear portion 23g is defined as an angle θ 2.

Fig. 15 is a diagram showing a relationship between a bend angle of a connection portion and a distribution ratio in a flow passage formed in a third plate member in the heat exchanger according to embodiment 1. Fig. 15 shows a change in the distribution ratio R in the flow passage 23A when the angle θ 1 (equal to the angle θ 2) is changed in a state where the angle θ 1 is equal to the angle θ 2.

As shown in fig. 15, the closer the angle θ 1 and the angle θ 2 are to 90 °, the closer the distribution ratio R is to 0.5. That is, by increasing the angles θ 1 and θ 2, the uniformity of refrigerant distribution can be further improved. In particular, as shown in fig. 6, when the flow path 23A is configured such that the lower end 23c of the first straight portion 23A is close to the end 23h of the third straight portion 23g and the upper end 23f of the second straight portion 23d is close to the end 23i of the third straight portion 23g, the uniformity of refrigerant distribution is further improved.

< method of using heat exchanger >

An example of a usage of the heat exchanger according to embodiment 1 will be described below.

Note that, although a case where the heat exchanger according to embodiment 1 is used in an air conditioner will be described below, the present invention is not limited to this case, and may be used in other refrigeration cycle apparatuses having a refrigerant circulation circuit, for example. Further, although the case where the air conditioner is a device that switches between the cooling operation and the heating operation is described, the air conditioner is not limited to this case, and only the cooling operation or the heating operation may be performed.

Fig. 16 is a diagram showing a configuration of an air conditioning apparatus to which the heat exchanger according to embodiment 1 is applied. In fig. 16, the solid arrows show the flow of the refrigerant during the cooling operation, and the broken arrows show the flow of the refrigerant during the heating operation.

As shown in fig. 16, the air conditioner 51 includes a compressor 52, a four-way valve 53, a heat source side heat exchanger 54, a throttle device 55, a load side heat exchanger 56, a heat source side fan 57, a load side fan 58, and a control device 59. The compressor 52, the four-way valve 53, the heat source side heat exchanger 54, the expansion device 55, and the load side heat exchanger 56 are connected by refrigerant pipes to form a refrigerant circulation circuit.

The controller 59 is connected to, for example, the compressor 52, the four-way valve 53, the throttle device 55, the heat source side fan 57, the load side fan 58, and various sensors. The control device 59 switches the flow path of the four-way valve 53 to switch the cooling operation and the heating operation. The heat source side heat exchanger 54 functions as a condenser during the cooling operation and functions as an evaporator during the heating operation. The load side heat exchanger 56 functions as an evaporator during the cooling operation and functions as a condenser during the heating operation.

The flow of the refrigerant during the cooling operation will be described.

The high-pressure high-temperature gaseous refrigerant discharged from the compressor 52 flows into the heat source side heat exchanger 54 via the four-way valve 53, is condensed by heat exchange with the outside air supplied by the heat source side fan 57, becomes a high-pressure liquid refrigerant, and flows out of the heat source side heat exchanger 54. The high-pressure liquid refrigerant flowing out of the heat source side heat exchanger 54 flows into the expansion device 55, and turns into a low-pressure gas-liquid two-phase refrigerant. The low-pressure gas-liquid two-phase refrigerant flowing out of the expansion device 55 flows into the load-side heat exchanger 56, is evaporated by heat exchange with the indoor air supplied by the load-side fan 58, becomes a low-pressure gaseous refrigerant, and flows out of the load-side heat exchanger 56. The low-pressure gaseous refrigerant flowing out of the load side heat exchanger 56 is sucked into the compressor 52 through the four-way valve 53.

The flow of the refrigerant during the heating operation will be described.

The high-pressure high-temperature gaseous refrigerant discharged from the compressor 52 flows into the load-side heat exchanger 56 via the four-way valve 53, is condensed by heat exchange with the indoor air supplied by the load-side fan 58, becomes a high-pressure liquid refrigerant, and flows out of the load-side heat exchanger 56. The high-pressure liquid refrigerant flowing out of the load side heat exchanger 56 flows into the expansion device 55, and turns into a low-pressure gas-liquid two-phase refrigerant. The low-pressure gas-liquid two-phase refrigerant flowing out of the expansion device 55 flows into the heat source side heat exchanger 54, is evaporated by heat exchange with the outside air supplied by the heat source side fan 57, becomes a low-pressure gaseous refrigerant, and flows out of the heat source side heat exchanger 54. The low-pressure gaseous refrigerant flowing out of the heat source side heat exchanger 54 is sucked into the compressor 52 through the four-way valve 53.

The heat exchanger 1 is used as at least one of the heat source-side heat exchanger 54 and the load-side heat exchanger 56. When the heat exchanger 1 functions as an evaporator, the heat exchanger 1 is connected such that the refrigerant flows in from the laminated header 2 and the refrigerant flows out from the header 3. That is, when the heat exchanger 1 functions as an evaporator, the refrigerant in a gas-liquid two-phase state flows from the refrigerant pipe into the laminated header 2, and the refrigerant in a gas state flows from the first heat transfer pipes 4 into the header 3. When the heat exchanger 1 functions as a condenser, the gaseous refrigerant flows into the header 3 from the refrigerant pipe, and the liquid refrigerant flows into the laminated header 2 from the first heat transfer pipes 4.

< Effect of Heat exchanger >

The operation of the heat exchanger according to embodiment 1 will be described below.

A distribution channel 12A including a branch channel 12b is formed in the second plate-like body 12 of the laminated header 2, and the branch channel 12b includes: an opening 23 j; a first straight portion 23a parallel to the direction of gravity, a lower end 23c of which communicates with the opening 23j via a connecting portion 23 k; and a second straight portion 23d parallel to the direction of gravity, the upper end 23f of which communicates with the opening 23j via a connecting portion 23l. Then, after the uneven flow in the direction perpendicular to the direction of gravity, which is generated as at least a part of the uneven flow passes through the connection portions 23k and 23l that are not parallel to the direction of gravity, is made uniform at the first straight portion 23a and the second straight portion 23d, the refrigerant flowing in from the opening 23j of the branch flow path 12b flows out from the upper end 23b of the first straight portion 23a and the lower end 23e of the second straight portion 23d. Therefore, the refrigerant is suppressed from flowing out of the branch flow path 12b in a state where a drift occurs, and the uniformity of refrigerant distribution is improved.

The flow passage 23A formed in the third plate 23 is a through groove, and the branch flow passage 12b is formed by laminating the third plate 23. Therefore, the processing and assembly can be simplified, thereby improving the production efficiency and reducing the manufacturing cost.

In particular, even when the heat exchanger 1 is used in an inclined manner, that is, even when the arrangement direction of the first outlet channels 11A intersects the direction of gravitational force, since the branch channel 12b has the first straight portion 23a and the second straight portion 23d parallel to the direction of gravitational force, the refrigerant can be suppressed from flowing out of the branch channel 12b in a state where a drift occurs, and the uniformity of refrigerant distribution can be improved.

In particular, in the conventional laminated header, when the refrigerant flowing into the header is in a gas-liquid two-phase state, the refrigerant is likely to be affected by gravity, and it is difficult to make the flow rate and the dryness of the refrigerant flowing into each heat transfer tube uniform, but in the laminated header 2, the refrigerant is unlikely to be affected by gravity regardless of the flow rate and the dryness of the refrigerant flowing into the gas-liquid two-phase state, and it is possible to make the flow rate and the dryness of the refrigerant flowing into each first heat transfer tube 4 uniform.

In particular, in the conventional stacked header, when the heat transfer tubes are changed from circular tubes to flat tubes for the purpose of reducing the amount of refrigerant, saving space in the heat exchanger, and the like, it is necessary to increase the size of the stacked header 2 in the entire circumferential direction perpendicular to the inflow direction of the refrigerant, but the heat exchanger 1 can be saved space without increasing the size of the stacked header in the entire circumferential direction perpendicular to the inflow direction of the refrigerant. That is, in the conventional laminated header, when the heat transfer tubes are changed from round tubes to flat tubes, the flow path cross-sectional area in the heat transfer tubes is reduced, and the pressure loss generated in the heat transfer tubes is increased, so that it is necessary to further narrow the angular intervals of the plurality of grooves forming the branch flow paths and increase the number of paths (that is, the number of heat transfer tubes), and the laminated header is increased in size in the entire circumferential direction perpendicular to the inflow direction of the refrigerant. On the other hand, in the laminated header 2, even if the number of paths needs to be increased, the number of the third plate members 23 needs to be increased, and therefore, the laminated header 2 is prevented from becoming large in the entire circumferential direction perpendicular to the inflow direction of the refrigerant. The laminated header 2 is not limited to the case where the first heat transfer tubes 4 are flat tubes.

< modification-1 >

Fig. 17 is a perspective view of a heat exchanger according to variation-1 of embodiment 1, in which the laminated header is disassembled. In the drawings shown below in fig. 17, the double-sided tape 24 is shown in a stacked state (the state shown in fig. 7 and 8), but it is needless to say that the double-sided tape 24 may not be stacked (the state shown in fig. 2 and 3).

As shown in fig. 17, the second plate-like member 22 may be provided with a plurality of flow passages 22A, that is, the second plate-like member 12 may be provided with a plurality of first inlet flow passages 12A, thereby reducing the number of third plate-like members 23. By configuring in this manner, the component cost, weight, and the like are reduced.

The plurality of flow passages 22A may be provided in a region facing a region of the flow passage 23A formed in the third plate-like member 23 into which the refrigerant flows. As shown in fig. 18, for example, the plurality of flow passages 22A may be formed at one location, and the refrigerant passing through the plurality of flow passages 22A may be guided to regions facing the regions into which the refrigerant in the flow passage 23A formed in the third plate-like member 23 flows, by the flow passages 25A of the other plate-like member 25 laminated between the second plate-like member 22 and the third plate-like member 23 _ 1.

< modification example-2 >

As shown in fig. 19, any one of the third plate-like members 23 may be replaced with another plate-like member 25 in which the opening 23j is formed in the flow path 25B not located in the third linear portion 23g. For example, the opening 23j of the flow path 25B is not located at the third straight portion 23g but located at the intersection, and the refrigerant flows into the intersection to form 4 branches. The number of branches may be any number. The larger the number of branches, the more the number of third plate members 23 can be reduced. With this configuration, the uniformity of refrigerant distribution is reduced, but the cost of components, weight, and the like are reduced.

< modification-3 >

Fig. 20 is a perspective view showing a state in which the laminated header is disassembled, according to a modification example-3 of the heat exchanger according to embodiment 1. Fig. 21 is a development view of a laminated header according to modification-3 of the heat exchanger according to embodiment 1. In fig. 21, illustration of the both-side wrapping member 24 is omitted.

As shown in fig. 20 and 21, any one of the third plate members 23 (for example, the third plate member 23 _ 2) may have: a flow path 23A functioning as a branch flow path 12b through which the refrigerant flows out without being turned back to the side where the first plate-like member 11 is provided; and a flow path 23B that functions as a branch flow path 12B through which the refrigerant flows out without being turned back to the side opposite to the side where the first plate-like member 11 is provided. The flow path 23B has the same structure as the flow path 23A. That is, the flow path 23B has a first straight portion 23a and a second straight portion 23d parallel to the direction of gravity, and the refrigerant flows in the flow path 23B from the opening 23j and flows out from the upper end 23B of the first straight portion 23a and the lower end 23e of the second straight portion 23d. With this configuration, the number of the third plate-like members 23 is reduced, and the member cost, the weight, and the like are reduced. In addition, the frequency of occurrence of brazing defects is reduced.

The third plate member 23 (for example, the third plate member 23 _ 1) laminated on the opposite side to the side on which the first plate member 11 is provided, of the third plate members 23 in which the flow paths 23B are formed, may have a flow path 23C for returning the refrigerant flowing from the flow path 23B without branching off the flow path 23A of the third plate member 23 in which the flow path 23B is formed, or may have a flow path 23A for branching off and returning the refrigerant. As shown in fig. 21, when the flow path 23C is a flow path having a straight portion 23n parallel to the direction of gravity on the side where the refrigerant flows out, the uniformity of refrigerant distribution is further improved.

< modification-4 >

As shown in fig. 22, a convex portion 26 may be formed on the surface of any one of the plate-like member and the double-sided tape 24, that is, any one of the stacked members. The position, shape, size, etc. of the projection 26 are specific to each of the stacked components. The convex portion 26 may be a spacer or the like. The adjacently stacked members are formed with recesses 27 into which the projections 26 are inserted. The recess 27 may or may not be a through hole. With this configuration, the error in the stacking order of the stacked components is suppressed, and the defective fraction is reduced. The convex portion 26 and the concave portion 27 can be fitted. In this case, a plurality of the convex portions 26 and the concave portions 27 may be formed, and the stacked members may be positioned by fitting them. Instead of forming the concave portion 27, the convex portion 26 may be inserted into a part of the flow path formed by the members stacked adjacently. In this case, the height, size, etc. of the projection 26 may be set to such an extent that the flow of the refrigerant is not obstructed.

< modification-5 >

Fig. 23 is a perspective view of a main part of a heat exchanger according to variation-5 of embodiment 1 in a state where a laminated header is disassembled. Fig. 24 is a sectional view of a main portion of a heat exchanger according to variation-5 of embodiment 1, in a state in which the laminated header is disassembled. Further, fig. 24 is a sectional view of the first plate-like member 21 at the line a-a in fig. 23.

As shown in fig. 23 and 24, any one of the plurality of flow paths 21A formed in the first plate-like member 21 may be a tapered through-hole as follows: the surface of the first plate-like member 21 on the side where the second plate-like body 12 is provided is formed in a circular shape, and the surface of the first plate-like member 21 on the side where the holding member 5 is provided is formed in a shape along the outer peripheral surface of the first heat transfer pipe 4. In particular, when the first heat transfer pipe 4 is a flat pipe, the through-hole is formed in a shape gradually expanding from the surface on the side where the second platelike body 12 is provided to the surface on the side where the holding member 5 is provided. With this configuration, the pressure loss of the refrigerant when passing through the first outlet flow path 11A is reduced.

< modification-6 >

Fig. 25 is a perspective view of a main part of a heat exchanger according to variation-6 of embodiment 1 in a state where a laminated header is disassembled. Fig. 26 is a sectional view of a main portion of a heat exchanger according to variation-6 of embodiment 1, in a state in which the laminated header is disassembled. Further, fig. 26 is a sectional view of the third plate member 23 at the line B-B in fig. 25.

As shown in fig. 25 and 26, any one of the flow passages 23A formed in the third plate-like member 23 may be a bottomed groove. In this case, circular through holes 23q are formed in the end portions 23o and 23p of the bottom surfaces of the grooves in the flow path 23A. With this configuration, the flow path 24A functioning as the refrigerant isolation flow path is interposed between the branch flow paths 12b without laminating the side covers 24 between the plate-like members, and the production efficiency can be improved. In fig. 25 and 26, the outflow side of the refrigerant in the flow path 23A is shown as the bottom surface, but the inflow side of the refrigerant in the flow path 23A may be the bottom surface. In this case, a through hole may be formed in a region corresponding to the opening 23j.

< modification example-7 >

As shown in fig. 27, the flow path 22A functioning as the first inlet flow path 12A may be formed in a stacked member other than the second plate-like member 22, that is, in the both-side cover 24 or the like which is another plate-like member. In this case, flow channel 22A may be formed as a through hole that penetrates from a side surface of another plate-like member to a surface on which second plate-like member 22 is provided, for example. That is, the present invention includes a configuration in which the first inlet channel 12A is formed in the first plate-like member 11, and the "distribution channel" of the present invention includes a distribution channel in which the first inlet channel 12A is formed in the second plate-like member 12 other than the distribution channel 12A.

Embodiment 2.

A heat exchanger according to embodiment 2 will be described.

Note that description overlapping with or similar to embodiment mode 1 is appropriately simplified or omitted.

< Structure of Heat exchanger >

The structure of the heat exchanger according to embodiment 2 will be described below.

As shown in fig. 28, the heat exchanger 1 has a laminated header 2, a plurality of first heat transfer pipes 4, a holding member 5, and a plurality of fins 6.

The laminated header 2 has a refrigerant inflow portion 2A, a plurality of refrigerant outflow portions 2B, a plurality of refrigerant inflow portions 2C, and a refrigerant outflow portion 2D. The refrigerant pipe is connected to the refrigerant inflow portion 2A of the laminated header 2 and the refrigerant outflow portion 2D of the laminated header 2. The first heat transfer pipe 4 is a flat pipe subjected to hairpin bending. A plurality of first heat transfer pipes 4 are connected between the plurality of refrigerant outflow portions 2B of the laminated header 2 and the plurality of refrigerant inflow portions 2C of the laminated header 2.

< flow of refrigerant in Heat exchanger >

The flow of the refrigerant in the heat exchanger according to embodiment 2 will be described below.

The refrigerant flowing through the refrigerant pipe is distributed to flow into the laminated header 2 through the refrigerant inflow portion 2A, and flows out to the plurality of first heat transfer tubes 4 through the plurality of refrigerant outflow portions 2B. The refrigerant exchanges heat with, for example, air supplied by a fan in the plurality of first heat transfer pipes 4. The refrigerant passing through the plurality of first heat transfer tubes 4 flows into the laminated header 2 through the plurality of refrigerant inflow portions 2C, is joined, and further flows out to the refrigerant pipes through the refrigerant outflow portion 2D. The refrigerant can flow backwards.

< Structure of laminated header >

The structure of the laminated header of the heat exchanger according to embodiment 2 will be described below.

Fig. 29 is a perspective view of the heat exchanger according to embodiment 2 in a state in which the laminated header is disassembled. Fig. 30 is a development view of a laminated header of a heat exchanger according to embodiment 2. In fig. 30, the illustration of the both-side wrapping member 24 is omitted.

As shown in fig. 29 and 30, the laminated header 2 includes a first plate-like member 11 and a second plate-like member 12. The first plate-like body 11 and the second plate-like body 12 are laminated together.

The first plate-like body 11 has a plurality of first outlet channels 11A and a plurality of second inlet channels 11B. The plurality of second inlet channels 11B correspond to the plurality of refrigerant inflow portions 2C in fig. 28.

The first plate-like member 21 has a plurality of flow passages 21B formed therein. The plurality of flow paths 21B are through holes whose inner peripheral surfaces are shaped to follow the outer peripheral surface of the first heat transfer pipe 4. When the first plate-like member 21 is laminated, the plurality of flow passages 21B function as the plurality of second inlet flow passages 11B.

The second plate-like body 12 is formed with a distribution channel 12A and a junction channel 12B. The merged channel 12B has a mixing channel 12c and a second outlet channel 12d. The second outlet flow path 12D corresponds to the refrigerant outflow portion 2D in fig. 28.

The second plate-like member 22 has a flow passage 22B formed therein. The flow path 22B is a circular through hole. When the second plate-like member 22 is laminated, the flow passage 22B functions as the second outlet flow passage 12d. A plurality of flow paths 22B, i.e., the second outlet flow paths 12d may be formed.

A plurality of flow passages 23D _ 1 to 23D _ 3 are formed in the plurality of third plate members 23 _ 1 to 23 _ 3. The plurality of flow paths 23D _ 1 to 23D _ 3 are rectangular through holes that penetrate almost the entire range of the third plate-like member 23 in the height direction. When the plurality of third plate members 23 _ 1 to 23 _ 3 are laminated, the plurality of flow passages 23D _ 1 to 23D _ 3 function as the mixing flow passage 12c, respectively. The plurality of flow paths 23D _ 1 to 23D _ 3 may not be rectangular. Hereinafter, the plurality of channels 23D _ 1 to 23D _ 3 may be collectively referred to as a channel 23D.

In particular, the brazing material can be supplied by laminating the both-side covers 24, which are obtained by rolling the brazing material on both sides, between the plate-shaped members. The flow path 24B formed by the both-side covers 24 _ 5 stacked between the holding member 5 and the first plate-like member 21 is a through hole having an inner peripheral surface along the shape of the outer peripheral surface of the first heat transfer pipe 4. The flow passage 24B formed by the both-side covers 24 _ 4 laminated between the first plate-like member 21 and the third plate-like member 23 _ 3 is a circular through hole. The flow path 24B formed by the side covers 24 laminated on the other third plate-like member 23 and the second plate-like member 22 is a rectangular through hole that penetrates almost the entire height direction of the side covers 24. When the both-side covers 24 are laminated, the flow path 24B functions as a refrigerant isolation flow path of the second inlet flow path 11B and the merged flow path 12B.

The flow path 22B functioning as the second outlet flow path 12d may be formed in a plate-like member other than the second plate-like member 22 of the second plate-like body 12, the both-side cover 24, or the like. In this case, a notch may be formed to communicate a part of the flow path 23D or the flow path 24B with, for example, a side surface of another plate-like member or the both-side cover 24. The mixing channel 12c may be folded back to form a channel 22B functioning as the second outlet channel 12d in the first plate-like member 21. That is, the present invention includes a configuration in which the second outlet channel 12d is formed in the first plate-like member 11, and the "merged channel" of the present invention includes a merged channel in which the second outlet channel 12d is formed in the second plate-like member 12 other than the merged channel 12B.

< flow of refrigerant in laminated header >

The flow of the refrigerant in the laminated header of the heat exchanger according to embodiment 2 will be described below.

As shown in fig. 29 and 30, the refrigerant that has flowed out of the flow passages 21A of the first plate-like member 21 and passed through the first heat transfer tubes 4 flows into the flow passages 21B of the first plate-like member 21. The refrigerant having flowed into the flow passage 21B of the first plate-like member 21 further flows into the flow passage 23D formed in the third plate-like member 23 and is mixed. The mixed refrigerant passes through the flow passages 22B of the second plate-like member 22 and flows out to the refrigerant pipes.

< method of using heat exchanger >

An example of a usage of the heat exchanger according to embodiment 2 will be described below.

As shown in fig. 31, the heat exchanger 1 is used as at least one of the heat source-side heat exchanger 54 and the load-side heat exchanger 56. When the heat exchanger 1 functions as an evaporator, the heat exchanger 1 is connected such that the refrigerant flows from the distribution flow path 12A of the laminated header 2 into the first heat transfer tubes 4, and the refrigerant flows from the first heat transfer tubes 4 into the junction flow path 12B of the laminated header 2. That is, when the heat exchanger 1 functions as an evaporator, the refrigerant in a gas-liquid two-phase state flows from the refrigerant pipe into the distribution flow path 12A of the laminated header 2, and the refrigerant in a gas state flows from the first heat transfer pipes 4 into the junction flow path 12B of the laminated header 2. When the heat exchanger 1 functions as a condenser, the gaseous refrigerant flows from the refrigerant pipe into the combined flow path 12B of the laminated header 2, and the liquid refrigerant flows from the first heat transfer pipes 4 into the distribution flow path 12A of the laminated header 2.

< Effect of Heat exchanger >

The operation of the heat exchanger according to embodiment 2 will be described below.

In the laminated header 2, the plurality of second inlet channels 11B are formed in the first plate-like member 11, and the merged channel 12B is formed in the second plate-like member 12. Therefore, the header 3 is not required, and the component cost of the heat exchanger 1 and the like are reduced. In addition, the first heat transfer pipes 4 can be extended to increase the number of fins 6 and the like according to the unnecessary header 3, that is, the installation volume of the heat exchange portion of the heat exchanger 1 can be increased.

Embodiment 3.

A heat exchanger according to embodiment 3 will be described.

Note that descriptions overlapping with or similar to those of embodiment mode 1 and embodiment mode 2 are appropriately simplified or omitted.

< Structure of Heat exchanger >

The structure of the heat exchanger according to embodiment 3 will be described below.

As shown in fig. 32, the heat exchanger 1 has a laminated header 2, a plurality of first heat transfer tubes 4, a plurality of second heat transfer tubes 7, a retaining member 5, and a plurality of fins 6.

The laminated header 2 has a plurality of refrigerant turn-back portions 2E. The second heat transfer tubes 7 are flat tubes subjected to hairpin bending, as in the first heat transfer tubes 4. A plurality of first heat transfer tubes 4 are connected between the plurality of refrigerant outflow portions 2B and the plurality of refrigerant turn-back portions 2E of the laminated header 2, and a plurality of second heat transfer tubes 7 are connected between the plurality of refrigerant turn-back portions 2E and the plurality of refrigerant inflow portions 2C of the laminated header 2.

< flow of refrigerant in Heat exchanger >

The flow of the refrigerant in the heat exchanger according to embodiment 3 will be described below.

The refrigerant flowing through the refrigerant pipe is distributed to flow into the laminated header 2 through the refrigerant inflow portion 2A, and flows out to the plurality of first heat transfer tubes 4 through the plurality of refrigerant outflow portions 2B. The refrigerant exchanges heat with, for example, air supplied by a fan in the plurality of first heat transfer pipes 4. The refrigerant passing through the plurality of first heat transfer tubes 4 flows into the plurality of refrigerant turn-back portions 2E of the laminated header 2, turns back, and flows out to the plurality of second heat transfer tubes 7. The refrigerant exchanges heat with, for example, air supplied by a fan in the plurality of second heat transfer tubes 7. The refrigerant passing through the plurality of second heat transfer tubes 7 flows into the laminated header 2 through the plurality of refrigerant inflow portions 2C, is joined together, and further flows out to the refrigerant pipes through the refrigerant outflow portions 2D. The refrigerant can flow backwards.

< Structure of laminated header >

The structure of the laminated header of the heat exchanger according to embodiment 3 will be described below.

Fig. 33 is a perspective view of the heat exchanger according to embodiment 3, in a state in which the laminated header is disassembled. Fig. 34 is a development view of a laminated header of a heat exchanger according to embodiment 3. In fig. 34, the illustration of the both-side wrapping member 24 is omitted.

As shown in fig. 33 and 34, the laminated header 2 includes a first plate-like member 11 and a second plate-like member 12. The first plate-like body 11 and the second plate-like body 12 are laminated together.

The first plate-like body 11 is formed with a plurality of first outlet flow paths 11A, a plurality of second inlet flow paths 11B, and a plurality of return flow paths 11C. The plurality of folded flow paths 11C correspond to the plurality of refrigerant folded portions 2E in fig. 32.

The first plate-like member 21 has a plurality of flow passages 21C formed therein. The plurality of flow passages 21C are through holes having an inner peripheral surface that surrounds the outer peripheral surface of the end portion on the refrigerant outflow side of the first heat transfer pipe 4 and the outer peripheral surface of the end portion on the refrigerant inflow side of the second heat transfer pipe 7. When the first plate-like members 21 are laminated, the plurality of flow paths 21C function as the plurality of folded flow paths 11C.

In particular, the brazing material can be supplied by laminating the both-side covers 24, which are obtained by rolling the brazing material on both sides, between the plate-shaped members. The flow passage 24C formed by the opposite-side covers 24 _ 5 laminated between the holding member 5 and the first plate-like member 21 is a through-hole having an inner peripheral surface in a shape surrounding the outer peripheral surface of the end portion on the refrigerant outflow side of the first heat transfer pipe 4 and the outer peripheral surface of the end portion on the refrigerant inflow side of the second heat transfer pipe 7. When the both-side covers 24 are laminated, the flow path 24C functions as a refrigerant isolation flow path of the folded flow path 11C.

< flow of refrigerant in laminated header >

The flow of the refrigerant in the laminated header of the heat exchanger according to embodiment 3 will be described below.

As shown in fig. 33 and 34, the refrigerant that has flowed out of the flow passages 21A of the first plate-like member 21 and passed through the first heat transfer tubes 4 flows into the flow passages 21C of the first plate-like member 21, turns back, and further flows into the second heat transfer tubes 7. The refrigerant passing through the second heat transfer tubes 7 flows into the flow channels 21B of the first plate-like member 21. The refrigerant having flowed into the flow passage 21B of the first plate-like member 21 further flows into the flow passage 23D formed in the third plate-like member 23 and is mixed. The mixed refrigerant passes through the flow passages 22B of the second plate-like member 22 and flows out to the refrigerant pipes.

< method of using heat exchanger >

An example of a usage of the heat exchanger according to embodiment 3 will be described below.

As shown in fig. 35, the heat exchanger 1 is used as at least one of the heat source-side heat exchanger 54 and the load-side heat exchanger 56. When the heat exchanger 1 functions as an evaporator, the heat exchanger 1 is connected such that the refrigerant flows from the distribution flow channels 12A of the laminated header 2 into the first heat transfer tubes 4 and the refrigerant flows from the second heat transfer tubes 7 into the junction flow channels 12B of the laminated header 2. That is, when the heat exchanger 1 functions as an evaporator, the refrigerant in a gas-liquid two-phase state flows from the refrigerant pipe into the distribution flow path 12A of the laminated header 2, and the refrigerant in a gas state flows from the second heat transfer tubes 7 into the junction flow path 12B of the laminated header 2. When the heat exchanger 1 functions as a condenser, the gaseous refrigerant flows from the refrigerant pipe into the combined flow path 12B of the laminated header 2, and the liquid refrigerant flows from the first heat transfer pipes 4 into the distribution flow path 12A of the laminated header 2.

The heat exchanger 1 is configured such that: when the heat exchanger 1 functions as a condenser, the first heat transfer tubes 4 are positioned on the upstream side (upstream side) of the airflow generated by the heat-source-side fan 57 or the load-side fan 58 with respect to the second heat transfer tubes 7. That is, the flow of the refrigerant from the second heat transfer tubes 7 toward the first heat transfer tubes 4 is in an opposing relationship with the airflow. The refrigerant in the first heat transfer tubes 4 is lower in temperature than the refrigerant in the second heat transfer tubes 7. Of the air flows generated by the heat source side fan 57 or the load side fan 58, the air flow on the upstream side of the heat exchanger 1 is lower in temperature than the air flow on the downstream side of the heat exchanger 1. As a result, the refrigerant can be supercooled (so-called SC) by the low-temperature air flow flowing on the upstream side of the heat exchanger 1, and the condenser performance can be improved. The heat source-side fan 57 and the load-side fan 58 may be provided on the upstream side or the downstream side.

< Effect of Heat exchanger >

The operation of the heat exchanger according to embodiment 3 will be described below.

In the heat exchanger 1, the plurality of return flow paths 11C are formed in the first plate-like member 11, and the plurality of second heat transfer tubes 7 are connected in addition to the plurality of first heat transfer tubes 4. For example, the area of the heat exchanger 1 in the front view can be increased to increase the amount of heat exchange, but in this case, the size of the casing in which the heat exchanger 1 is incorporated becomes large. Further, the number of fins 6 can be increased by reducing the interval between the fins 6, and the heat exchange amount can be increased. From the viewpoint of dust resistance, it is difficult to make the interval between the fins 6 less than about 1mm, and the increase in the heat exchange amount may become insufficient. On the other hand, when the number of rows of heat transfer tubes is increased as in the heat exchanger 1, the amount of heat exchange can be increased without changing the area of the heat exchanger 1 in a front view, the interval between the fins 6, and the like. If the number of rows of heat transfer tubes is 2, the amount of heat exchange increases by about 1.5 times or more. The number of rows of heat transfer tubes may be 3 or more. Further, the area of the heat exchanger 1 in a front view, the interval between the fins 6, and the like may be changed.

Further, a header (laminated header 2) is provided only on one side of the heat exchanger 1. When the heat exchanger 1 is bent along a plurality of side surfaces of a casing in which the heat exchanger 1 is built in, for example, in order to increase the installation volume of the heat exchange portion, the radius of curvature of the bent portion is different for each row of heat transfer tubes, and therefore, the end portion is offset for each row of heat transfer tubes. In the case where the header (the laminated header 2) is provided only on one side of the heat exchanger 1 as in the laminated header 2, even if the end portions are offset for each row of heat transfer tubes, only the end portions on one side need be aligned, and the degree of freedom in design, production efficiency, and the like are improved as compared with the case where the headers (the laminated headers 2 and the headers 3) are provided on both sides of the heat exchanger 1 as in the heat exchanger according to embodiment 1. In particular, the heat exchanger 1 can be bent after the components of the heat exchanger 1 are joined, thereby further improving the production efficiency.

When the heat exchanger 1 functions as a condenser, the first heat transfer pipes 4 are located on the upstream side of the second heat transfer pipes 7. When headers (laminated headers 2, 3) are provided on both sides of the heat exchanger 1 as in the heat exchanger according to embodiment 1, it is difficult to improve the condenser performance by generating a temperature difference in the refrigerant for each row of the heat transfer tubes. In particular, when the first heat transfer tubes 4 and the second heat transfer tubes 7 are flat tubes, the degree of freedom in bending is low unlike a circular tube, and therefore, it is difficult to achieve a temperature difference of the refrigerant in each row of the heat transfer tubes by deforming the flow path of the refrigerant. On the other hand, when the first heat transfer tubes 4 and the second heat transfer tubes 7 are connected to the laminated header 2 as in the heat exchanger 1, a temperature difference in the refrigerant is inevitably generated in each row of the heat transfer tubes, and the refrigerant flow and the air flow can be easily made to face each other without deforming the refrigerant flow path.

Although embodiments 1 to 3 have been described above, the present invention is not limited to the description of the embodiments. For example, all or a part of the embodiments, the modifications, and the like may be combined.

Description of reference numerals

A heat exchanger; a laminated header; a refrigerant inflow portion; a refrigerant outflow portion; a refrigerant inflow portion; a refrigerant outflow portion; a refrigerant turn-back section; a header; a refrigerant inflow portion; a refrigerant outflow portion; a first heat transfer pipe; a retaining member; a fin; a second heat transfer tube; a first plate-like body; a first outlet flow path; a second inlet flow path; a foldback flow path; a second plate-like body; dispensing a flow path; merging flow paths; a first inlet flow path; a branch flow path; a mixing flow path; a second outlet flow path; a first plate-like member; a flow path; a second plate-like member; 22A, 22b.. the flow path; 23. 23-1 to 23-3. a third plate member; 23A-23D, 23A-1-23A-3, 23D-1-23D-3. the flow path; a first rectilinear portion; an upper end of the first linear portion; a lower end of the first linear portion; a second straight portion; a lower end of the second straight portion; an upper end of the second linear portion; a third straight portion; 23h, 23i.. the end of the third linear portion; an opening portion; a 23k, 23l.. a connecting portion; a center of the opening; a straight portion; 23o, 23p.. ends with bottom slots; a through hole; 24. 24 _ 1 to 24 _ 5.. two side cladding pieces; a flow path 24A-24 c; a plate like member; 25A, 25b.. the flow path; a convex portion; a recess; an air conditioning unit; a compressor; 53.. a four-way valve; a heat source side heat exchanger; a flow restriction device; 56.. a load side heat exchanger; a heat source side fan; 58.. a load side fan; a control device.

Claims

1. A stacked header, wherein,

the laminated header includes:

a first plate-like body having a plurality of first outlet flow paths formed therein; and

a second plate-like body attached to the first plate-like body and having a first inlet channel formed therein,

the second plate-like body is formed with a distribution flow path for distributing the refrigerant flowing in from the first inlet flow path to the plurality of first outlet flow paths and flowing out,

the distribution flow path includes a branch flow path having:

an opening part;

a first straight portion which is parallel to the direction of gravity and of which the lower end communicates with the opening portion via a first connection portion; and

a second linear portion parallel to the direction of gravity and having an upper end communicating with the opening portion via a second connecting portion,

at least a portion of the first connection portion and at least a portion of the second connection portion are not parallel to a direction of gravity,

in the branch flow path, the refrigerant flows from the opening portion to the lower end of the first straight portion and the upper end of the second straight portion via the first connection portion and the second connection portion, and flows out from the upper end of the first straight portion and the lower end of the second straight portion.

2. The laminated header according to claim 1, wherein,

the length of the flow path from the upper end to the lower end of each of the first straight portion and the second straight portion is 3 times or more greater than the hydraulically equivalent diameter of the flow path.

3. The laminated header according to claim 1, wherein,

the branch flow path has a third straight line portion perpendicular to the direction of gravity,

the opening is a portion between both ends of the third linear portion.

4. The laminated header according to claim 3, wherein,

the length of the flow path from the center of the opening to the both ends of the third linear portion is 1 or more times as large as the hydraulically equivalent diameter of the flow path.

5. A laminated header according to any one of claims 1 to 4, wherein,

the second plate-like body has at least one plate-like member in which a flow path is formed,

the branch flow passage is formed in a flow passage of the plate-shaped member, and a region of the branch flow passage other than a region into which the refrigerant flows and a region from which the refrigerant flows out is closed by a member attached adjacent to the plate-shaped member.

6. A laminated header according to any one of claims 1 to 4, wherein,

an arrangement direction of the upper ends of the first linear portions and the lower ends of the second linear portions is along an arrangement direction of the plurality of first outlet flow paths.

7. A laminated header according to any one of claims 1 to 4, wherein,

the first inlet flow path is plural.

8. A laminated header according to any one of claims 1 to 4, wherein,

the branch flow path is a branch flow path that allows the refrigerant to flow out to a side where the first plate-like member is present, and a branch flow path that allows the refrigerant to flow out to a side opposite to the side where the first plate-like member is present.

9. The laminated header according to claim 5, wherein,

the plate-like member is formed with a convex portion unique to the plate-like member,

the convex portion is inserted into a flow path formed by a member attached adjacent to the plate-like member.

10. A heat exchanger in which, in a heat exchanger,

the heat exchanger is provided with:

a laminated header according to any one of claims 1 to 9; and

a plurality of first heat transfer pipes connected to the plurality of first outlet flow paths, respectively.

11. The heat exchanger of claim 10,

a plurality of second inlet flow paths are formed in the first plate-like body, and the refrigerant passing through the plurality of first heat transfer pipes flows into the plurality of second inlet flow paths,

a merging flow path that merges the refrigerant flowing from the plurality of second inlet flow paths and flows into a second outlet flow path is formed in the second plate-like body.

12. The heat exchanger according to claim 10 or 11,

the first heat transfer pipe is a flat pipe.

13. The heat exchanger of claim 12,

an inner peripheral surface of the first outlet flow path gradually expands toward an outer peripheral surface of the first heat transfer pipe.

14. An air conditioning apparatus, wherein,

an air conditioner comprising the heat exchanger according to any one of claims 10 to 13,

when the heat exchanger functions as an evaporator, the distribution flow path causes the refrigerant to flow out to the plurality of first outlet flow paths.

15. An air conditioning apparatus, wherein,

the air conditioner is provided with a heat exchanger, and the heat exchanger is provided with:

a laminated header according to any one of claims 1 to 9; and

a plurality of first heat transfer pipes connected to the plurality of first outlet flow paths, respectively,

the laminated header having a plurality of second inlet flow paths formed in the first plate-like body, the refrigerant passing through the plurality of first heat transfer tubes flowing into the plurality of second inlet flow paths,

and a merging flow path that merges the refrigerant flowing from the plurality of second inlet flow paths and flows into a second outlet flow path is formed in the second plate-like body,

the heat exchanger has a plurality of second heat transfer tubes connected to the plurality of second inlet flow paths, respectively,

the distribution flow path allows the refrigerant to flow out to the plurality of first outlet flow paths when the heat exchanger functions as an evaporator,

when the heat exchanger functions as a condenser, the first heat transfer tubes are located on the upstream side of the second heat transfer tubes.