EP3064880A1

EP3064880A1 - Laminated header, heat exchanger, and air-conditioning apparatus

Info

Publication number: EP3064880A1
Application number: EP13896215.4A
Authority: EP
Inventors: Takumi NISHIYAMA; Takashi Okazaki; Akira Ishibashi; Shinya Higashiiue; Shigeyoshi MATSUI; Atsushi Mochizuki
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2013-10-30
Filing date: 2013-10-30
Publication date: 2016-09-07
Anticipated expiration: 2033-10-30
Also published as: JPWO2015063875A1; WO2015063875A1; JP6116702B2; EP3064880A4; EP3064880B1

Abstract

A stacking-type header of the present invention includes a first plate-like body and a plurality of second plate-like bodies. The first plate body has first opening ports 30. Flat tubes 20 are connected to the opening ports 30 of the first plate-like body. The plurality of second plate-like bodies have second opening ports 40. The plurality of second plate-like bodies are stacked on the first plate-like body so that the second opening ports 40 communicate with the first opening ports 30 to form flow passages. Each of the flow passages has a flow passage area that continuously or gradually changes in a stacking direction of the plurality of second plate-like bodies.

Description

Technical Field

The present invention relates to a stacking-type header, a heat exchanger, and an air-conditioning apparatus.

Background Art

A conventionally-known heat exchanger has a return header including a tube joining member configured to join a flat tube and a member, a tube fixing member configured to position an end of the flat tube, a spacer section configured to move refrigerant in a row-wise direction, and a back board (e.g., see Patent Literature 1).

Citation List

Patent Literature

Patent Literature 1: Japanese Unexamined Patent Application Publication No. 2013-29243 (paragraph [0033], Fig. 6)

Summary of Invention

Technical Problem

In the heat exchanger disclosed in Patent Literature 1, inflow of refrigerant from each separate flow passage hole of the flat tube into a header tank meet at the spacer section and move in a direction orthogonal to flow passages of the flat tube. Then, the refrigerant having moved through the spacer section flows into each separate flow passage hole of another flat tube.
However, since the refrigerant flowing through the spacer section is subject to influence of inertial force, imbalances are caused in the inflow of refrigerant from the spacer section into each separate flow passage hole of the flat tube, thus making it difficult to evenly distribute the refrigerant.
Further, liquid refrigerant flowing out through the end of the flat tube to the spacer section comes to flow in a more laminar flow state, as the spacer section increases in space. This creates imbalances in the inflow of refrigerant from the spacer section into each separate flow passage hole of the flat tube, thus making it difficult to evenly distribute the refrigerant.
The present invention has been made to solve problems such as those described above. It is an object of the present invention to provide a stacking-type header connected to a plurality of tubes, configured to allow inflow of fluid from one of the tubes and inflow of the fluid into another one of the tubes, and configured to be able to reduce imbalances in the inflow of the fluid into the tube. Further, it is another object of the present invention to provide a heat exchanger including such a stacking-type header. Further, it is still another object of the present invention to provide an air-conditioning apparatus including such a heat exchanger.

Solution to Problem

A stacking-type header according to the present invention is a stacking-type header connected to a plurality of tubes and configured to allow inflow of fluid from one of the tubes and inflow of the fluid into another one of the tubes, including: a first plate-like body having first opening ports, each of the plurality of tubes being connected to the first opening ports of the first plate-like body, and a plurality of second plate-like bodies having second opening ports, the plurality of second plate-like bodies being stacked on the first plate-like body so that the second opening ports communicate with the first opening ports to form flow passages, in which each of the flow passages has a flow passage area that continuously or gradually changes in a stacking direction of the plurality of second plate-like bodies.

Advantageous Effects of Invention

According to the present invention, a stacking-type header is connected to a plurality of tubes, configured to allow inflow of fluid from one of the tubes and inflow of the fluid into another one of the tubes, and configured to be able to reduce imbalances in the inflow of the fluid into the tube.

Brief Description of Drawings

[Fig. 1] Fig. 1 is a side view schematically showing a configuration of a heat exchanger 1 according to Embodiment 1 of the present invention.
[Fig. 2] Fig. 2 is a top view schematically showing the configuration of the heat exchanger 1 according to Embodiment 1 of the present invention.
[Fig. 3] Fig. 3 is a schematic view showing a cross-section of a flat tube 20 of the heat exchanger 1 according to Embodiment 1 of the present invention.
[Fig. 4] Fig. 4 is a schematic exploded perspective view showing a stacking-type header 10 of the heat exchanger 1 according to Embodiment 1 of the present invention.
[Fig. 5] Fig. 5 is a schematic perspective view showing a stacked state of the stacking-type header 10 according to Embodiment 1 of the present invention.
[Fig. 6] Fig. 6 is a schematic cross-sectional view of the stacking-type header 10 according to Embodiment 1 of the present invention.
[Fig. 7] Fig. 7 is a schematic cross-sectional view illustrating flows of refrigerant in the stacking-type header 10 according to Embodiment 1 of the present invention.
[Fig. 8] Fig. 8 is a schematic cross-sectional view showing a modification example of the stacking-type header 10 according to Embodiment 1 of the present invention.
[Fig. 9] Fig. 9 is a schematic cross-sectional view of a stacking-type header 10 according to Embodiment 2 of the present invention.
[Fig. 10] Fig. 10 is a schematic cross-sectional view showing a modification example of the stacking-type header 10 according to Embodiment 2 of the present invention.
[Fig. 11] Fig. 11 is a schematic cross-sectional view showing a modification example of the stacking-type header 10 according to Embodiment 2 of the present invention.
[Fig. 12] Fig. 12 is a schematic cross-sectional view of a stacking-type header 10 according to Embodiment 3 of the present invention.
[Fig. 13] Fig. 13 is a schematic cross-sectional view illustrating the action of the stacking-type header 10 according to Embodiment 3 of the present invention during brazing.
[Fig. 14] Fig. 14 is a schematic cross-sectional view of a stacking-type header 10 according to Embodiment 4 of the present invention.
[Fig. 15] Fig. 15 is an enlarged view of C of Fig. 14.
[Fig. 16] Fig. 16 is a schematic cross-sectional view of the stacking-type header 10 according to Embodiment 4 of the present invention, with a flat tube 20 inserted therein.
[Fig. 17] Fig. 17 is an enlarged view of part D of Fig. 16.
[Fig. 18] Fig. 18 is a schematic cross-sectional view illustrating the action of the stacking-type header 10 according to Embodiment 4 of the present invention during brazing.
[Fig. 19] Fig. 19 is an enlarged view of part E of Fig. 18.
[Fig. 20] Fig. 20 is a diagram schematically showing a configuration of an air-conditioning apparatus 91 according to Embodiment 5 of the present invention.
[Fig. 21] Fig. 21 is a diagram schematically showing the configuration of the air-conditioning apparatus 91 according to Embodiment 5 of the present invention.
[Fig. 22] Fig. 22 is a schematic cross-sectional view of a stacking-type header 10 according to Embodiment 5 of the present invention.
[Fig. 23] Fig. 23 is a diagram illustrating a liquid distribution of refrigerant that flows into a flat tube 20b in a case where a heat exchanger 1 according to Embodiment 5 of the present invention acts as an evaporator.
[Fig. 24] Fig. 24 is a graph illustrating the liquid distribution of refrigerant that flows into the flat tube 20b in a case where the heat exchanger 1 according to Embodiment 5 of the present invention acts as the evaporator.
[Fig. 25] Fig. 25 is a diagram illustrating a liquid distribution of refrigerant that flows into a flat tube 20a in a case where the heat exchanger 1 according to Embodiment 5 of the present invention acts as a condenser.
[Fig. 26] Fig. 26 is a graph illustrating the liquid distribution of refrigerant that flows into the flat tube 20a in a case where the heat exchanger 1 according to Embodiment 5 of the present invention acts as the condenser.

Description of Embodiments

A stacking-type header according to the present invention is described below with reference to the drawings.
The following describes a case where a stacking-type header according to the present invention is applied to a heat exchanger. Note, however, that a stacking-type header according to the present invention may be applied to another device.
The configurations, operations, etc. described below are merely exemplary, and the present invention is not limited to such configurations, operations, etc. In each of the drawings, the same reference signs are used for the same or similar components, or the signs therefor are omitted. Illustrations of detailed structures are simplified or omitted as appropriate. Descriptions of the same or similar configurations are simplified or omitted as appropriate.

Embodiment 1

Fig. 1 is a side view schematically showing a configuration of a heat exchanger 1 according to Embodiment 1 of the present invention.
Fig. 2 is a top view schematically showing the configuration of the heat exchanger 1 according to Embodiment 1 of the present invention.
As shown in Figs. 1 and 2, the heat exchanger 1 includes a stacking-type header 10, a plurality of flat tubes 20, and a plurality of fins 3.
The stacking-type header 10, to which an end of each flat tube 20 is connected, allows inflow of fluid (e.g., refrigerant) from one of the flat tubes 20 and inflow of the fluid into another one of the flat tubes 20. The stacking-type header 10 will be described in detail later.
The fins 3 are for example in the form of plates. The fins 3 are stacked at predetermined intervals. The fins 3 allow passage of a heat medium (e.g., air) therebetween. The fins 3 are for example made of a metal material such as aluminum or copper.
The flat tubes 20 are flat in cross-section. The flat tubes 20 are for example made of a metal material such as aluminum or copper. The flat tubes 20 have flat shapes whose longer axes are oriented in a direction of passage of air. The flat tubes 20 are placed at intervals along the short axes of the flat shapes. The flat tubes 20 include plural columns of flat tubes 20 arranged in a column-wise direction crossing a direction of flow of air. Further, the flat tubes 20 include plural rows of flat tubes 20 arranged in a row-wise direction along the direction of flow of air.
Embodiment 1 describes a case where the flat tubes 20 include two rows of flat tubes 20. The following assumes that the two rows of flat tubes 20 include a flat tube 20a through which the refrigerant flows into the stacking-type header 10 and a flat tube 20b through which the refrigerant flows out of the stacking-type header 10. It should be noted that the absence of the suffixes means that the content of descriptions is common to all of the flat tubes 20.
Fig. 3 is a schematic view showing a cross-section of each flat tube 20 of the heat exchanger 1 according to Embodiment 1 of the present invention.
As shown in Fig. 3, the flat tube 20 has at least one divider provided therein to form a plurality of flow passages. The following assumes that the tube height H21 is the short axis length of the flat tube 20, the tube width L22 is the long axis length of the flat tube 20, and the tube thickness t23 is the length between the outer circumference of the flat tube 20 and the inner circumference of each flow passage.
The flat tubes 20 correspond to the "tubes" of the present invention.
Although Embodiment 1 describes a case where the flat tubes 20 are used, the present invention is not limited thereto and can use tubes of any shape such as circular tubes or rectangular or square tubes.
Fig. 4 is a schematic exploded perspective view showing the stacking-type header 10 of the heat exchanger 1 according to Embodiment 1 of the present invention. Fig. 4 is also an enlarged view of part A of Fig. 1.
As shown in Fig. 4, the stacking-type header 10 includes a plurality of bare materials 11 and a plurality of clad materials 12. The clad materials 12 are plate-like members coated with a brazing material. The bare materials 11 are plate-like members coated with no brazing material. The stacking-type header 10 is constituted by the bare materials 11 and the clad members 12 being alternately stacked.
Further, in the stacking-type header 10, the bare materials 11 and the clad materials 12 include a bare material 11 and a clad material 12 each having first opening ports 30 formed therethrough, bear materials 11 and clad materials 12 each having second opening ports 40 formed therethrough to communicate with the first opening ports 30, a bare material 11 and a clad material 12 each having third opening ports 50 formed therethrough to each communicate with a plurality of the second opening ports 40, and a bare material 11 having no opening port formed therethrough. All of these bear materials 11 and clad materials 12 are stacked to form flow passages through which the fluid flows.
It should be noted that any numbers of bear materials 11 and clad materials 12 may be stacked to form the stacking-type header 10.
In Embodiment 1, the bear materials 11 and the clad materials 12 are assigned the suffixes a to f as they are stacked from the side of insertion of the flat tubes 20. The first opening ports 30, the second opening ports 40, and the third opening ports 50 are assigned the same suffixes as the corresponding bare materials 11 or clad materials 12. It should be noted that the absence of the suffixes means that the content of descriptions is common to all suffixes.
Fig. 5 is a schematic perspective view showing a stacked state of the stacking-type header 10 of the heat exchanger 1 according to Embodiment 1 of the present invention. Fig. 5 illustrates layers of the bare materials 11 and the clad materials 12 with varying column-wise lengths.
Fig. 6 is a schematic cross-sectional view of the stacking-type header 10 according to Embodiment 1 of the present invention. Fig. 6 is also an enlarged view of cross-section B-B of Fig. 1.
A configuration of the stacking-type header 10 according to Embodiment 1 is described below with reference to Figs. 5 and 6.
The layers of the bare materials 11 and the clad materials 12 of the stacking-type header 10 constitute the first opening ports 30, to which the flat tubes 20 are connected, contracted flow passages 41 formed by the second opening ports 40, and a row-connecting flow passage 51 formed by the third opening ports 50.
The contracted flow passages 41 are assigned the same suffixes as the corresponding flat tubes 20. It should be noted that the absence of the suffixes means that the content of descriptions is common to all suffixes.

[First Opening Ports]

The bare material 11 a and the clad material 12a have first opening ports 30a formed therethrough. Each of the first opening ports 30a has a flat shape corresponding to the shape of the corresponding one of the flat tubes 20. Each of the first opening ports 30a has its long axis oriented in the row-wise direction. The first opening ports 30a are larger than outer circumferences of the flat tubes 20. That is, the hole height H31, which is the short axis length of each first opening port 30, is equal to or greater than the tube height H21 of the corresponding one of the flat tubes 20, and the hole width L32, which is the long axis length of each first opening port 30, is equal to or greater than the tube width L22 of the corresponding one of the flat tubes 20.
An end of each flat tube 20 is inserted into the corresponding one of the first opening ports 30a.

[Contracted Flow Passages]

The bare materials 11 b to 11 d and the clad materials 12b to 12d have second opening ports 40b to 40d formed therethrough, respectively. Each of the second opening ports 40b to 40d has a flat shape corresponding to the shape of the corresponding one of the flat tubes 20. Each of the second opening ports 40b to 40d has its long axis oriented in the row-wise direction.
The bare materials 11 b to 11 d and the clad materials 12b to 12d are stacked so that the second opening ports 40b to 40d communicate with the first opening ports 30a to form the contracted flow passages 41.
The second opening ports 40b of the bare material 11 b, which is adjacent to the clad material 12a, are smaller than the outer circumferences of the flat tubes 20. That is, the hole height H41, which is the short axis length of each second opening port 40b of the bare material 11 b, is less than the tube height H21 of the corresponding one of the flat tubes 20, and the hole width L42, which is the long axis length of each second opening port 40b, is less than the tube width L22 of the corresponding one of the flat tubes 20.
An end face of each of the flat tubes 20 inserted in the first opening ports 30a makes partial contact with a side surface of the bare material 11 b. Thus included is a structure in which the position of insertion of each flat tube 20 is defined by the bare material 11 b receiving an end of the flat tube 20.
It is desirable that each of the second opening ports 40b be in size equal to or larger than inner circumference of the corresponding one of the flat tubes 20. That is, the following relationships hold: Tube height H21 > Hole height H41 ≥ (Tube height H21 - 2 x Tube thickness t23) and Tube width L22 > Hole width L42 ≥ (Tube width L22 - 2 x Tube thickness t23). This prevents the flow passages in each flat tube 20 from being closed by the bare material 11 b, thus allowing a reduction in flow passage resistance.
During brazing, the brazing material of the clad material 12a is heated in a state where each of the flat tubes 20 is inserted in the corresponding ones of the first opening ports 30 and an end face of the flat tube 20 is in partial contact with the bare material 11 b, and the brazing material thus molten connects a side surface of the flat tube 20 and inner circumferential surfaces of the corresponding first opening ports 30a.
Further, the end face of the flat tube 20 is connected in partial contact with the bare material 11 b coated with no brazing material.
Further, the second opening ports 40c of the bare material 11c and the second opening ports 40c of the clad material 12c are smaller than the second opening ports 40b of the bare material 11 b and the second opening ports 40b of the clad material 12b. Furthermore, the second opening ports 40d of the bare material 11 d and the second opening ports 40d of the clad material 12d are smaller than the second opening ports 40c of the bare material 11 c and the second opening ports 40c of the clad material 12c.
In this manner, a size of each of the second opening ports 40b to 40d becomes larger with decreasing distance from the bare material 11a and the clad material 12a. That is, each of the contracted flow passages 41 is structured to have a flow passage area (opening port cross-sectional area) that gradually increases in a stacking direction of the bare materials 11 and the clad materials 12.
Further, the bare material 11 d and the clad material 12d, which are located farthest away from the bare material 11a of the pluralities of bare materials 11 and clad materials 12 having the second opening ports 40, have their second opening ports 40d formed to be smallest in size. That is, the flow passage area (opening cross-sectional area) of each contracted flow passage 41 is smallest in a position farthest away from the bare material 11a.
It should be noted that only either the bare material 11 d or the clad material 12d may have its second opening ports 40d formed to be smallest.
Although Embodiment 1 has described a case where the contracted flow passages 41 are formed by the second opening ports 40b to 40d of the bare materials 11 b to 11 d and the second opening ports 40b to 40d of the clad materials 12b to 12d, the number of layers that are stacked can be arbitrarily set. It is desirable that each of the contracted flow passages 41 be formed so that the length thereof in the stacking direction is greater than the total thickness of two bare materials 11.
It should be noted that the length by which an end of each flat tube 20 is inserted can be varied by staking pluralities of bare materials 11 a and clad materials 12a having first opening ports 30. Accordingly, an area of contact where each of the flat tubes 20 is joined to the stacking-type header 10 may be arbitrarily changed. Each of the flat tubes 20 is inserted into at least one clad material 12a.

[Row-Connecting Flow Passage]

The bare material 11e and the clad material 12e have third opening ports 50e formed therethrough. Each of the third opening ports 50e is formed by a single opening of a size encompassing the two second opening ports 40d formed in the bare material 11 d and the two second opening ports 40d formed in the clad material 12d. The bare material 11f has no opening provided in a part thereof that faces the third opening ports 50e. The bare material 11 e, the clad material 12e, and the bare material 11f are stacked to form the row-connecting flow passage 51, through which the plurality of contracted flow passages 41 communicate with each other.
That is, the row-connecting flow passage 51 allows communication between a contracted flow passage 41 a corresponding to the flat tube 20a and a contracted flow passage 41 b corresponding to the flat tube 20b.
Although Embodiment 1 has described a case where the bare material 11e, the clad material 12e, and the bare material 11f are stacked to form the row-connecting flow passage 51, the present invention is not limited thereto.
For example, a single plate-like member having a groove-like flow passage formed therein may be stacked on the clad material 12d. Alternatively, instead of the bare material 11e, the clad material 12e, and the bare material 11 f, a connecting tube such as a U-bend tube may be provided to allow communication between the contracted flow passage 41 a corresponding to the flat tube 20a and the contracted flow passage 41 b corresponding to the flat tube 20b.
The numbers of bare materials 11e and clad materials 12e that are stacked to form the row-connecting flow passage 51 are not limited to one but may be arbitrarily changed.
For example, as shown in Fig. 8, two bare materials 11e having third opening ports 50 formed therethrough and two clad materials 12e each having third opening ports 50 formed therethrough may be alternately stacked to form the row-connecting flow passage 51.
By thus stacking a plurality of bare materials 11e and a plurality of clad materials 12e to increase the flow passage area of the row-connecting flow passage 51, a pressure loss reduction can be achieved.
The bare material 11a and the clad material 12a correspond to the "first plate-like bodies" of the present invention.
Further, the bare materials 11 b to 11 d and the clad materials 12b to 12d correspond to the "second plate-like bodies" of the present invention.
Further, the bare materials 11e and 11f and the clad materials 12e and 12f correspond to the "third plate-like bodies" of the present invention.
The following describes flows of refrigerant in the stacking-type header 10 according to Embodiment 1.
Fig. 7 is a schematic cross-sectional view illustrating flows of refrigerant in the stacking-type header 10 according to Embodiment 1 of the present invention.
The arrows shown in Fig. 7 indicate the directions of flows of refrigerant.
A description is given here by taking as an example a case where refrigerant flows from the flat tube 20a into the stacking-type header 10 and flows out of the stacking-type header 10 into the flat tube 20a.
The inflow of refrigerant through an end of the flat tube 20a into the stacking-type header 10 is contracted by the contracted flow passage 41 a and flows through the row-connecting flow passage 51. Note here that the flow passage area (opening cross-sectional area) of the flow passage of the refrigerant from the end of the flat tube 20a toward the row-connecting flow passage 51 gradually decreases. This suppresses imbalances in the outflow of two-phase gas-liquid refrigerant from the flat tube 20.
Further, the contraction of the flow by the contracted flow passage 41 allows the refrigerant to flow in a more atomized state.
The refrigerant flowing through the row-connecting flow passage 51 flows into the contracted flow passage 41 b corresponding to the flat tube 20b. The refrigerant flowing into the contracted flow passage 41 b flows into the flat tube 20b. Note here that the flow passage area (opening cross-sectional area) of the flow passage of the refrigerant from the contracted flow passage 41 b toward the flat tube 20b gradually increases. This allows the refrigerant to be evenly distributed to each flow passage of the flat tube 20b.
The direction of passage of the refrigerant is not limited to that described above, but the refrigerant may flow in the opposite direction.
It should be noted that the direction of flow of a heat medium (e.g., air) that exchanges heat with the refrigerant in the flat tubes 20 may be parallel to or opposite to the direction of flow of the row-connecting flow passage 51.
The following describes the advantageous effects of the stacking-type header 10 according to Embodiment 1.
In the stacking-type header 10 according to Embodiment 1, the bare materials 11 and clad materials 12 having the second opening ports 40 are stacked to form the contracted flow passages 41, whose flow passage areas gradually change in the stacking direction.
This makes it possible to suppress imbalances in the inflow of refrigerant from a flat tube 20 into the corresponding contracted flow passage 41 and in the outflow of refrigerant from the contracted flow passage 41. This also makes it possible to suppress imbalances in the inflow of refrigerant from the contracted flow passage 41 into the corresponding flat tube 20.
Further, a size of each of the second opening ports 40 becomes larger with decreasing distance from the flat tubes 20.
This achieves a structure in which the flow passage area of each contracted flow passage 41 from an end of the corresponding one of the flat tubes 20 toward the row-connecting flow passage 51 decreases, thus making it possible to suppress imbalances in the outflow of two-phase refrigerant from the flat tube 20.
Further, the bare material 11 and the clad material 12 that are located farthest away from the flat tubes 20 of the bare materials 11 and clad materials 12 having the second opening ports 40 formed therethrough have their second opening ports 40 formed to be smallest in size.
This allows refrigerant to flow from the flat tube 20 into the corresponding contracted flow passage 41 and flow out of the contracted flow passage 41 in a more atomized state.
Further, the first opening ports 30a of the bare material 11 a and clad material 12a, into which an end of each flat tube 20 is inserted, are larger than the outer circumferences of the flat tubes 20. That is, the hole height H31 of each first opening port 30a is equal to or greater than the tube height H21, and the hole width L32 of each first opening port 30a is equal to or greater than the tube width L22.
This makes it possible to form a surface (edge for insertion) where each of the flat tubes 20 is joined to the stacking-type header 10 during brazing.
Further, the edge for insertion of each flat tube 20 can be arbitrarily defined by arbitrarily setting the numbers of bare materials 11 a and clad materials 12a that are stacked.
Further, the second opening ports 40b of the bare material 11 b, which is adjacent to the clad material 12a, are smaller than the outer circumferences of the flat tubes 20. That is, the hole height H41 of each second opening port 40b is less than the tube height H21, and the hole width L42 of each second opening port 40b is less than the tube width L22.
An end face of each of the flat tubes 20 inserted in the first opening ports 30 can be brought into partial contact with the side surface of the bare material 11 b to define the position of insertion of the flat tube 20. That is, an end of each flat tube 20 can be prevented from sticking out of the bare material 11 b.
Further, since an end face of each flat tube 20 makes partial contact with the bare material 11 b coated with no brazing material, the inflow of a brazing material into the flat tube 20 can be prevented.
Further, by defining the position of insertion of each flat tube 20, a heat exchanger can be manufactured without excessive lengthening of the edge for insertion, and the proportion of a heat exchange section in a heat exchanger of the same size can be increased.
Further, shortening of the edge for insertion of each flat tube 20 can reduce the size of the heat exchanger 1 in achieving equal heat-exchange capabilities.
Further, lengthening of the edge for insertion of each flat tube 20 can increase the joint area between the flat tube 20 and the stacking-type header 10 and therefore improve the joint strength.
Further, the second opening ports 40b are in size equal to or larger than the inner circumference of the flat tubes 20. That is, the following relationships hold: Tube height H21 > Hole height H41 of second opening port 40b ≥ (Tube height H21 - 2 x Tube thickness t23) and Tube width L22 > Hole width L42 of second opening port 40b ≥ (Tube width L22 - 2 x Tube thickness t23).
This prevents the flow passages in each flat tube 20 from being closed by the bare material 11 b, thus allowing a reduction in flow passage resistance.
Further, the shaping of each contracted flow passage in a staircase pattern can make manufacturing easier than chamfering or curved surface shape processing can. Further, the ease of manufacture can reduce manufacturing costs.
The staircase pattern of simple shapes can make the making of molds easy also in the case of manufacture in molds by cutting, casting, or the like. Further, the ease of making can reduce manufacturing costs.

Embodiment 2

A stacking-type header 10 according to Embodiment 2 is described below with a focus on the differences from Embodiment 1.
It should be noted that the same signs are used for the same components as those of Embodiment 1.
Fig. 9 is a schematic cross-sectional view of the stacking-type header 10 according to Embodiment 2 of the present invention.
In the stacking-type header 10 according to Embodiment 2, each of the contracted flow passages 41 is structured to have a flow passage area (opening cross-sectional area) that continuously changes in the stacking direction of the bare materials 11 and the clad materials 12.
For example, as shown in Fig. 9, a wall surface shape 13 of a cross-section of each contracted flow passage 41 in the stacking direction of the bare materials 11 b to 11d and the clad materials 12b to 12d is formed in a linear shape (chamfered shape). Moreover, the flow passage area of each contracted flow passage 41 continuously changes in such a manner as to increase toward the corresponding one of the flat tubes 20.
The wall surface shape of each contracted flow passage 41 needs only be a shape that continuously changes, and is not limited to the linear shape. Alternatively, the bare materials 11 b to 11 d and the clad materials 12b to 12d may be only partially formed into shapes that continuously change.
For example, as shown in Fig. 10, a wall surface shape 14 of a cross-section in the stacking direction of the bare materials 11c and 11 d and the clad materials 12c and 12d of the bare materials 11 b to 11 d and the clad materials 12b to 12d may be formed in a curved shape (rounded shape).
Alternatively, for example, as shown in Fig. 11, a wall surface shape 15 of all of the bare materials 11 b to 11 d and clad materials 12b to 12d may be formed in a curved shape (rounded shape).
The following describes the advantageous effects of the stacking-type header 10 according to Embodiment 2.
In the stacking-type header 10 according to Embodiment 2, the bare materials 11 and clad materials 12 having the second opening ports 40 are stacked to form the contracted flow passages 41, whose flow passage areas continuously change in the stacking direction.
This makes it possible to suppress imbalances in the inflow of refrigerant from a flat tube 20 into the corresponding contracted flow passage 41 and in the outflow of refrigerant from the contracted flow passage 41. This also makes it possible to suppress imbalances in the inflow of refrigerant from a contracted flow passage 41 into the corresponding flat tube 20.
Further, as compared with a case where the flow passage area of each contracted flow passage 41 gradually changes, the flow separation and vortex development of refrigerant in the contracted flow passage 41 can be reduced.
Further, the reduction in the flow separation and vortex development can lead to a reduction in loss of pressure in the flow passage.
Further, the reduction in the flow separation and vortex development can lead to reduce a sound that is generated when the refrigerant flows.
Further, the reduction in the flow separation and vortex development allows the refrigerant to be evenly distributed to each flow passage provided in the flat tube 20.
Further, a reduction in the number of steps of each contracted flow passage 41 can suppress the retention of liquid refrigerant or oil.

Embodiment 3

A stacking-type header 10 according to Embodiment 3 is described below with a focus on the differences from Embodiment 1.
It should be noted that the same signs are used for the same components as those of Embodiment 1.
Fig. 12 is a schematic cross-sectional view of the stacking-type header 10 according to Embodiment 3 of the present invention. Fig. 12 is also an enlarged view of main components of the stacking-type header 10.
As shown in Fig. 12, the stacking-type header 10 according to Embodiment 3 includes clearances 60 in which the molten brazing material accumulates. Each of the clearances 60 is provided between a side surface of the corresponding one of the flat tubes 20 and inner circumferential surfaces of the corresponding ones of the first opening ports 30a of the bare material 11 a and clad material 12a.
That is, the following relationship holds among the tube height H21 of each flat tube 20, the hole height H31 of each of the corresponding ones of the first opening ports 30a, and the height of the corresponding one of the clearances 60 (distance along the short axis of the flat tube 20): Height of clearance 60 ≥ (Hole height H31 - Tube height H21)/2.
Further, the following relationship holds among the tube width L22 of each flat tube 20, the hole width L32 of each of the corresponding ones of the first opening ports 30a, and the width of the corresponding one of the clearances 60 (distance along the long axis of the flat tube 20): Width of clearance 60 ≥ (Hole width L32 - Tube width L22)/2. It should be noted that the height and width of each clearance 60 may be different.
The clearances 60 correspond to the "gaps" of the present invention.
If the height and width (distance between a side surface of each flat tube 20 and inner circumference surfaces of the corresponding ones of the first opening ports 30a) of each clearance 60 are too large, the molten brazing material does not sufficiently spread onto the flat tube 20 and the inner circumference surfaces of the corresponding first opening ports 30. This makes it difficult to join the flat tube 20 to the stacking-type header 10. For this reason, for example, it is desirable that sizes of the height and width of each clearance 60 be equal to or less than 0.10 mm.
The following describes the action of the stacking-type header 10 according to Embodiment 3.
Fig. 13 is a schematic cross-sectional view illustrating the action of the stacking-type header 10 according to Embodiment 3 of the present invention during brazing.
During brazing, the brazing material of the clad material 12a is heated and molten in a state where each of the flat tubes 20 is inserted in the corresponding ones of the first opening ports 30 and an end face of the flat pie 20 is in partial contact with the bare material 11 b. Gravitation or surface tension causes the molten brazing material 61 to penetrate between a side surface of the flat tube 20 and inner circumferential surfaces of the corresponding first opening ports 30a. At this point in time, the molten brazing material 61 flows onto the side surface of the flat tube 20 (in the directions of arrows shown in Fig. 13) along the clearance 60, which is an open end. This causes the side surface of the flat tube 20 to be joined to the bare material 11 a and the clad material 12a.
The following describes the advantageous effects of the stacking-type header 10 according to Embodiment 3.
The stacking-type header 10 according to Embodiment 3 includes clearances 60 in which the molten brazing material accumulates. Each of the clearances 60 is provided between a side surface of the corresponding one of the flat tubes 20 and inner circumferential surfaces of the corresponding ones of the first opening ports 30 of the bare material 11 a and clad material 12a.
This makes it possible to prevent the brazing material molten from the clad material 12a from flowing into an end of the flat tube 20 during brazing.
Further, such a structure that makes it hard for the brazing material to enter the end of the flat tube 20 prevents the flow passages in the flat tube 20 from being closed, thus allowing the refrigerant to be evenly distributed.
Further, the provision of the clearances 60 makes it possible to absorb displacements that are caused by dimension errors in the simultaneous insertion of the plurality of flat tubes 20 into the stacking-type header 10. This makes it possible to easily insert the flat tubes 20 into the stacking-type header 10.
Further, the ease of insertion of the flat tubes 20 into the stacking-type header 10 can reduce manufacturing costs.
Further, by causing each clearance 60 to have a length of 0.10 mm or less, the number of imperfect joints between the bare material 11 a and the side surface of each flat tube 20 can be reduced.
Further, the reduction in the number of imperfect joints between the bare material 11 a and the side surface of each flat tube 20 can lead to improved joint strength.
Further, the improved joint strength can lead to improved reliability.
Further, the provision of the clearances 60 allows a fillet to be formed at a contact boundary surface between the bare material 11 b and the vicinity of an end of each flat tube 20.
Further, the formation of such fillets can lead to improved joint strength.

Embodiment 4

A stacking-type header 10 according to Embodiment 4 is described below with a focus on the differences from Embodiment 1.
It should be noted that the same signs are used for the same components as those of Embodiment 1.
Fig. 14 is a schematic cross-sectional view of the stacking-type header 10 according to Embodiment 4 of the present invention.
Fig. 15 is an enlarged view of part C of Fig. 14.
In the stacking-type header 10 according to Embodiment 3, as shown in Figs. 14 and 15, the bare material 11 b, with which an end face of each flat tube 20 makes partial contact, is smaller in thickness in a portion with which the end face of the flat tube 20 makes partial contact than in a portion with which the end face of the flat tube 20 makes no contact. In this manner, the bare material 11 b varies in size of the opening ports between an insertion side into which the end of the flat tube 20 is inserted and a side (back surface side) with which the end of the flat tube 20 makes contact. The portion with which the end face of the flat tube 20 makes partial contact is hereinafter referred to as "projection-shaped portion 110".
That is, an insertion side of each second opening port 40b of the bare material 11 b into which the end of the flat tube 20 is inserted is sized such that the following relationships hold: Hole height H31 of first opening port 30a ≥ Hole height H41 of second opening port 40b ≥ Tube height H21, and Hole width L32 of first opening port 30a ≥ Hole width L42 of second opening port 40b ≥ Tube width L22.
Further, the back surface side with which the end of the flat tube 20 makes contact is sized such that the following relationships hold: Tube height H21 ≥ Hole height H41 of second opening port 40b ≥ (Tube height H21 - 2 x Tube thickness t23), and Tube width L22 ≥ Hole width L42 of second opening port 40b ≥ (Tube width L22 - 2 x Tube thickness t23).
The following describes the action of the stacking-type header 10 according to Embodiment 4.
Fig. 16 is a schematic cross-sectional view of the stacking-type header 10 according to Embodiment 4 of the present invention, with a flat tube 20 inserted therein.
Fig. 17 is an enlarged view of part D of Fig. 16.
Fig. 18 is a schematic cross-sectional view illustrating the action of the stacking-type header 10 according to Embodiment 4 of the present invention during brazing.
Fig. 19 is an enlarged view of part E of Fig. 18.
As shown in Figs. 16 and 17, when the flat tube 20 is inserted into the stacking-type header 10, the end of the flat tube 20 communicates with the insertion side of the bare material 11 b in which the flat tube 20 is inserted, and the end face of the flat tube 20 makes surface contact with the projection-shaped portion 110 on the back surface side.
As shown in Figs. 18 and 19, during brazing, gravitation or surface tension causes the molten brazing material 61 to penetrate between a side surface of the flat tube 20 and inner circumferential surfaces of the corresponding first opening ports 30a and into the insertion side of the bare material 11 b in which the flat tube 20 is inserted. At this point in time, the molten brazing material 61 flows onto the side surface of the flat tube 20 (in the directions of arrows shown in Figs. 18 and 19), which has an open end. This causes the side surface of the flat tube 20 to be joined to the bare material 11 a and the clad material 12a and to the insertion side of the bare material 11 b in which the flat tube 20 is inserted.
The following describes the advantageous effects of the stacking-type header 10 according to Embodiment 4.
In the stacking-type header 10 according to Embodiment 4, the bare material 11 a is smaller in thickness in a portion with which the end face of the flat tube 20 makes partial contact than in a portion with which the end face of the flat tube 20 makes no contact. That is, the bare material 11 b has a projection-shaped portion 110 provided on the back surface side thereof.
This makes it possible to define the edge for insertion of the end of the flat tube 20.
Further, since the flat tube 20 does not have its end on the contact boundary surface between the bare material 11 b and the clad material 12a, the entrance of the brazing material 61 into the flat tube 20 can be prevented.
Further, the fixation of the end of the flat tube 20 in the bare material 11 b allows a larger edge for insertion.
Further, the larger edge for insertion allows a larger joint area during brazing.
Further, the larger joint area can lead to improved joint strength.
Further, the improved contact strength can lead to improved reliability.
Further, such a structure in which the end of the flat tube 20 is at a longer distance from the clad material 12a can prevent the brazing material 61 from flowing into the flat tube 20 even if the brazing material 61 flows toward the flat tube 20.
Further, such a structure that makes it hard for the brazing material 61 to enter the end of the flat tube 20 prevents the flow passages on both sides of the flat tube 20 from being closed, thus allowing the refrigerant to be evenly distributed.

Embodiment 5

Embodiment 5 describes a configuration of an air-conditioning apparatus to which a stacking-type header 10 and a heat exchanger including the stacking-type header 10 are applied.
Figs. 20 and 21 are diagrams schematically illustrating a configuration of an air-conditioning apparatus 91 according to Embodiment 5 of the present invention.
Fig. 20 shows a case where the air-conditioning apparatus 91 is in a heating operation. Fig. 21 shows a case where the air-conditioning apparatus 91 is in a cooling operation.
As shown in Figs. 20 and 21, the air-conditioning apparatus 91 includes a compressor 92, a four-way valve 93, an outdoor heat exchanger 94, an expansion device 95, an indoor heat exchanger 96, an outdoor fan 97, an indoor fan 98, and a controller 99.
The compressor 92, the four-way valve 93, the outdoor heat exchanger 94, the expansion device 95, and the indoor heat exchanger 96 are connected through refrigerant tubes to form a refrigerant circuit. The four-way valve 93 may be replaced by another flow passage switching device.
The outdoor heat exchanger 94 is a heat exchanger 1. The heat exchanger 1 allows passage of air generated by driving the outdoor fan 97. The outdoor fan 97 may be provided on the windward side of the heat exchanger 1. Alternatively, the outdoor fan 97 may be provided on the leeward side of the heat exchanger 1.
Connected to the controller 99 are for example the compressor 92, the four-way valve 93, the expansion device 95, the outdoor fan 97, the indoor fan 98, and various types of sensor. The controller 99 switches flow passages of the four-way valve 93, thereby switching between the heating operation and the cooling operation.
The following describes the operation of the air-conditioning apparatus.

[Heating Operation]

The flow of refrigerant during the heating operation is described with reference to Fig. 20.
High pressure and temperature gaseous refrigerant that is discharged from the compressor 92 flows through the four-way valve 93 into the indoor heat exchanger 96, condenses by exchanging heat with air that is supplied by the indoor fan 98, and thereby heats the interior of a room.
The condensed refrigerant flows out of the indoor heat exchanger 96 in the form of high-pressure subcooled liquid (or low-quality two-phase gas-liquid refrigerant) and turns into low-pressure two-phase gas-liquid refrigerant through the expansion device 95. The low-pressure two-phase gas-liquid refrigerant flows into the outdoor heat exchanger 94, exchanges heat with air that is supplied by the outdoor fan 97, and evaporates.
The evaporated refrigerant turns into low-pressure superheated gas, flows out of the outdoor heat exchanger 94, and is sucked into the compressor 92 through the four-way valve 93. That is, the outdoor heat exchanger 94 acts as an evaporator during heating operation. Further, in the outdoor heat exchanger 94, the refrigerant passes through the row of flat tubes 20a located on the windward side and flows through the stacking-type header 10 into the row of flat tubes 20b located on the leeward side.

[Cooling Operation]

The flow of refrigerant during the cooling operation is described with reference to Fig. 21.
High pressure and temperature gaseous refrigerant that is discharged from the compressor 92 flows through the four-way valve 93 into the outdoor heat exchanger 94 and condenses by exchanging heat with air that is supplied by the outdoor fan 97.
The condensed refrigerant flows out of the outdoor heat exchanger 94 in the form of high-pressure subcooled liquid (or low-quality two-phase gas-liquid refrigerant) and turns into low-pressure two-phase gas-liquid refrigerant through the expansion device 95. The low-pressure two-phase gas-liquid refrigerant flows into the indoor heat exchanger 96, evaporates by exchanging heat with air that is supplied by the indoor fan 98, and thereby cools the interior of the room.
The evaporated refrigerant turns into low-pressure superheated gas, flows out of the indoor heat exchanger 96, and is sucked into the compressor 92 through the four-way valve 93. That is, the outdoor heat exchanger 94 acts as a condenser during the cooling operation. Further, in the outdoor heat exchanger 94, the refrigerant passes through the row of flat tubes 20b located on the leeward side and flows through the stacking-type header 10 into the row of flat tubes 20b located on the windward side.

[Eccentric Structure of Contracted Flow Passages 41]

The stacking-type header 10 according to Embodiment 3 is described below with a focus on the differences from Embodiment 1.
It should be noted that the same signs are used for the same components as those of Embodiment 1.
Fig. 22 is a schematic cross-sectional view of the stacking-type header 10 according to Embodiment 5 of the present invention. Fig. 22 is also an enlarged view of main components of the stacking-type header 10.
In the stacking-type header 10 according to Embodiment 5, as shown in Fig. 22, a central axis of each of the first opening port 30a of the bare material 11 a and clad material 12a and a central axis of the corresponding one of the second opening ports 40d, which serves as an outlet of the corresponding one of the contracted flow passages 41, of the bare material 11 d and clad material 12d are eccentric to each other.
That is, the central axis of each second opening port 40d of the contracted flow passage 41 corresponding to one of the two flat tubes 20a and 20b is more eccentric toward the other flat tube 20 than the central axis of each first opening port 30a of the contracted flow passage 41.
When it is assumed that W3 is the outer diameter of each of the flat tubes 20a and 20b along the long axis, the eccentricity Z is greater than 0 and less than W3/2.
Further, the central axes are eccentric so that the distance between the central axis of each of the second opening ports 40d corresponding to the flat tube 20a and the central axis of the flat tube 20a is shorter than the distance between the central axis of the flat tube 20b and the central axis of each of the second opening ports 40d corresponding to the flat tube 20a.
Further, the central axes are eccentric so that the distance between the central axis of each of the second opening ports 40d corresponding to the flat tube 20b and the central axis of the flat tube 20b is shorter than the distance between the central axis of the flat tube 20a and the central axis of each of the second opening ports 40d corresponding to the flat tube 20b.
The following describes the action of the stacking-type header 10 according to Embodiment 5.
Figs. 23 and 24 are a diagram and a graph, respectively, illustrating a liquid distribution of refrigerant that flows into a flat tube 20b in a case where the heat exchanger 1 according to Embodiment 5 of the present invention acts as an evaporator.
As shown in Figs. 23 and 24, in a case where the heat exchanger 1 acts as an evaporator, the flow of refrigerant is parallel to the flow of air that is generated by driving the outdoor fan 97. That is, the refrigerant flows from the flat tube 20a to the contracted flow passage 41 a, and flows from the row-connecting flow passage 51 into the contracted flow passage 41 b in a two-phase gas-liquid state. The two-phase gas-liquid refrigerant passing through the row-connecting flow passage 51 is subject to influence of inertial force, with the result that a high-density refrigerant flows through an outer portion of the row-connecting flow passage 51 and a low-density refrigerant flows through an inner portion of the row-connecting flow passage 51.
Therefore, in a case where the eccentricity Z is equal to 0 in the contracted flow passage 41 b, more of liquid refrigerant flowing into the contracted flow passage 41 b flows into a point L side portion of the flat tube 20b than into a point S side portion of the flat tube 20b.
On the other hand, since, in the heat exchanger 1, the eccentricity Z is greater than 0 in the contracted flow passage 41 b, more of the liquid refrigerant flowing into the contracted flow passage 41 b flows into the point S side portion of the flat tube 20b.
In a case where the heat exchanger 1 acts as an evaporator, there is a large heat load (amount of heat exchange) on the windward side of the flow of air that is generated by driving the outdoor fan 97. Therefore, the liquid refrigerant is distributed into the flow passage holes of the flat tube 20 so that more of the liquid refrigerant flows through the flow passages in the point S side portion, i.e., windward portion, of the flat tube 20b. This facilitates the evaporation of the liquid refrigerant and improves the efficiency of heat exchange.
Figs. 25 and 26 are a diagram and a graph, respectively, illustrating a liquid distribution of refrigerant that flows into a flat tube 20a in a case where the heat exchanger 1 according to Embodiment 5 of the present invention acts as a condenser.
As shown in Figs. 23 and 24, in a case where the heat exchanger 1 acts as the condenser, the flow of refrigerant is opposite to the flow of air that is generated by driving the outdoor fan 97. That is, the refrigerant flows from the flat tube 20b to the contracted flow passage 41 b, and flows from the row-connecting flow passage 51 into the contracted flow passage 41 a in a two-phase gas-liquid state. The two-phase gas-liquid refrigerant passing through the row-connecting flow passage 51 is subject to influence of inertial force, with the result that a high-density refrigerant flows through an outer portion of the row-connecting flow passage 51 and a low-density refrigerant flows through an inner portion of the row-connecting flow passage 51.
Therefore, in a case where the eccentricity Z is equal to 0 in the contracted flow passage 41 a, more of the liquid refrigerant flowing into the contracted flow passage 41 a flows into a point L side portion of the flat tube 20a than into a point S side portion of the flat tube 20a.
On the other hand, since, in the heat exchanger 1, the eccentricity Z is greater than 0 in the contracted flow passage 41 a, more of gas refrigerant flowing into the contracted flow passage 41 a flows into the point S side portion the flat tube 20a.
In a case where the heat exchanger 1 acts as a condenser, there is a large heat load (amount of heat exchange) on the windward side of the flow of air that is generated by driving the outdoor fan 97. Therefore, the gas refrigerant is distributed into the flow passage holes of the flat tube 20 so that more of the gas refrigerant flows through the flow passages in the point L side portion, i.e., windward portion, of the flat tube 20a. This facilitates the condensation of the gas refrigerant and improves the efficiency of heat exchange.
Although the foregoing has described Embodiments 1 to 5, the present invention is not limited to any of the descriptions of Embodiments 1 to 5. For example, it is possible to combine all or part of Embodiments 1 to 5.

Reference Signs List

1 heat exchanger 3 fin 10 stacking-type header 11 bare material 12 clad material 13 wall surface shape 14 wall surface shape 15 wall surface shape 20 flat tube 30 first opening port 40 second opening port 41 contracted flow passage 50 third opening port 51 row-connecting flow passage 60 clearance 61 brazing material 91 air-conditioning apparatus 92 compressor 93 four-way valve 94 outdoor heat exchanger 95 expansion device 96 indoor heat exchanger 97 outdoor fan 98 indoor fan 99 controller 110 projection-shaped portion

Claims

A stacking-type header connected to a plurality of tubes and configured to allow inflow of fluid from one of the tubes and inflow of the fluid into another one of the tubes, comprising:
a first plate-like body having first opening ports, each of the plurality of tubes being connected to the first opening ports of the first plate-like body; and

a plurality of second plate-like bodies having second opening ports, the plurality of second plate-like bodies being stacked on the first plate-like body so that the second opening ports communicate with the first opening ports to form flow passages,

wherein each of the flow passages has a flow passage area that continuously or gradually changes in a stacking direction of the plurality of second plate-like bodies.
The stacking-type header of claim 1, wherein one of the plurality of second plate-like bodies that is located farthest away from the first plate-like body has a smallest second opening port.
The stacking-type header of claim 1 or 2, wherein a size of the second opening ports of each of the plurality of second plate-like bodies becomes larger with decreasing a distance from the first plate-like body.
The stacking-type header of any one of claims 1 to 3, wherein each of the flow passages has a linear or curved wall surface shape in a cross-section taken along the stacking direction of the plurality of second plate-like bodies, and the flow passage area of each of the flow passages continuously changes to increase toward the first opening ports.
The stacking-type header of any one of claims 1 to 4, further comprising one or more third plate-like bodies stacked on the plurality of second plate-like bodies,
wherein the flow passages of the second plate-like bodies are provided to correspond to the plurality of tubes connected to the first plate-like body, and
the one or more third plate-like bodies are provided with a connecting flow passage that allows communication between a flow passage corresponding to one of the plurality of tubes and a flow passage corresponding to an other of the plurality of tubes.
The stacking-type header of any one of claims 1 to 4, wherein the flow passages of the second plate-like bodies are provided to correspond to the plurality of tubes connected to the first plate-like body, and
the stacking-type header further comprising a connecting flow tube that allows communication between a flow passage corresponding to one of the plurality of tubes and a flow passage corresponding to an other of the plurality of tubes.
The stacking-type header of claim 5 or 6, wherein a central axis of each of the first opening ports and a central axis of each of the second opening ports of the one of the plurality of second plate-like bodies that is located farthest away from the first plate-like body are eccentric to each other.
The stacking-type header of claim 7, wherein a central axis of a corresponding one of the second opening ports in the flow passage corresponding to the one of the plurality of tubes is eccentric toward the other of the plurality of tubes with respect to a central axis of each of the first opening ports in the flow passage.
The stacking-type header of any one of claims 1 to 8, wherein the plurality of second plate-like bodies are constituted by clad materials coated with a brazing material and bare materials coated with no brazing material, and
the clad materials and the bare materials are alternately stacked.
The stacking-type header of claim 9, wherein each of the flow passages is longer than a thickness of two of the bare materials along the stacking direction of the plurality of second plate-like bodies.
A heat exchanger comprising:
the stacking-type header of any one of claims 1 to 10; and

a plurality of tubes connected to the stacking-type header.
The heat exchanger of claim 11, wherein
each of the first opening ports is larger than an outer circumference of each of the plurality of tubes,
each of the second opening ports of one of the plurality of second plate-like bodies that is adjacent to the first plate-like body is smaller than the outer circumference of each of the plurality of tubes, and
the plurality of tubes are inserted in the first opening ports and have end faces in partial contact with the one of the plurality of second plate-like bodies.
The heat exchanger of claim 12, wherein the one of the plurality of second plate-like bodies with which the end faces of the plurality of tubes are in partial contact is one of the bare materials coated with no brazing material.
The heat exchanger of claim 12 or 13, wherein the one of the plurality of second plate-like bodies that is adjacent to the first plate-like body is smaller in thickness in a portion with which the end faces of the plurality of tubes make partial contact than in a portion with which the end faces of the plurality of tubes make no contact.
The heat exchanger of any one of claims 11 to 14, wherein the plurality of tubes are constituted by flat tubes,
each of the first opening ports and each of the second opening ports has a flat shape having a long axis oriented in a same direction as the flat tubes,
a short axis length of each of the first opening ports is equal to or longer than a short axis length of the flat tubes, and
a long axis length of each of the first opening ports is equal to or longer than a long axis length of the flat tubes.
The heat exchanger of claim 15, wherein a short axis length of each of the second opening ports of the one of the plurality of second plate-like bodies that is adjacent to the first plate-like body is less than the short axis length of the flat tubes, and
a long axis length of each of the second opening ports is less than the long axis length of the flat tubes.
The heat exchanger of any one of claims 11 to 16, comprising a plurality of first plate-like bodies,
wherein the plurality of first plate-like bodies are constituted by a clad material coated with the brazing material and a bare material coated with no brazing material,
the plurality of first plate-like bodies are heated in a state where each of the plurality of tubes is inserted in the corresponding one of the first opening ports and an end face of each of the plurality of tubes is in partial contact with the one of the plurality of second plate-like bodies, and
the brazing material is molten to connect a side surface of each of the plurality of tubes and the corresponding one of the first opening ports of each of the first plate-like bodies.
The heat exchanger of claim 17, wherein a gap in which the brazing material is molten to accumulate is provided between the side surface of each of the plurality of tubes and an inner circumferential surface of the corresponding one of the first opening ports of each of the first plate-like bodies.
An air-conditioning apparatus comprising the heat exchanger of any one of claims 11 to 18.
The air-conditioning apparatus of claim 19, wherein the plurality of tubes of the heat exchanger include plural rows of tubes arranged in a direction of passage of air, and
when the heat exchanger acts as an evaporator, refrigerant flowing through one of the plurality of tubes that is located on a windward side flows into the stacking-type header and flows from the stacking-type header into one of the plurality of tubes that is located on a leeward side.