WO2018142460A1

WO2018142460A1 - Heat exchanger and refrigeration cycle apparatus

Info

Publication number: WO2018142460A1
Application number: PCT/JP2017/003401
Authority: WO
Inventors: 石橋　晃; 中村　伸; 真哉東井上; 伊東　大輔; 前田　剛志; 良太赤岩; 暁八柳; 厚志望月
Original assignee: 三菱電機株式会社
Priority date: 2017-01-31
Filing date: 2017-01-31
Publication date: 2018-08-09
Also published as: EP3578913B1; EP3578913A1; EP3578913A4; JP6826133B2; JPWO2018142460A1

Abstract

A heat exchanger for which manufacturing costs can be reduced and a refrigeration cycle apparatus are obtained. A heat exchanger (10) is provided with first and second flat pipes (6) and a header (1). The header (1) connects one-end parts of the first and second flat pipes (6) to each other. The header (1) is configured from a first member included in a first plate-shaped body (11) and a second member included in a second plate-shaped body (12). The one-end parts of the first and second flat pipes (6) are secured to the first member. The second member is connected so as to overlap the first member. The second member has formed therein a recess extending from a position faced by the one-end part of the first flat pipe (6) to a position faced by the one-end part of the second flat pipe (6).

Description

Heat exchanger and refrigeration cycle apparatus

The present invention relates to a heat exchanger and a refrigeration cycle apparatus.

Conventionally, a heat exchanger using a flat tube through which a refrigerant flows is known (see, for example, JP 2013-29243 A (hereinafter referred to as Patent Document 1)). In Patent Document 1, by connecting the ends of flat tubes arranged in different rows with a return head, the effective length of the heat exchanger in which heat is exchanged between the refrigerant and the outside air is lengthened, and the heat exchanger We are trying to make it compact.

JP 2013-29243 A

In the heat exchanger disclosed in Patent Document 1, the return head is composed of four members: a tube bonding member, a tube fixing member, a spacer member, and a back plate. If the return head is configured with such a large number of parts, the cost of the return head parts and the number of manufacturing processes increase, and the manufacturing cost of the heat exchanger and the air conditioner to which the heat exchanger is applied is increased. It was.

The present invention has been made to solve the problems as described above, and is to provide a heat exchanger and a refrigeration cycle apparatus capable of reducing the manufacturing cost.

The heat exchanger according to the present disclosure includes a first flat tube, a second flat tube, and a header. The first and second flat tubes extend in a direction intersecting with the fluid flow direction, and are arranged so as to line up along the flow direction, thereby circulating the refrigerant. The header connects one ends of the first and second flat tubes. The header is composed of a first member and a second member. The first member is fixed at one end of the first and second flat tubes. The second member is connected so as to overlap the first member. The second member is formed with a recess extending from a position facing one end of the first flat tube to a position facing one end of the second flat tube.

The refrigeration cycle apparatus according to the present disclosure includes a compressor, a first heat exchanger, an expansion valve, and a second heat exchanger, and includes a refrigerant circuit in which the refrigerant circulates. At least one of the first heat exchanger and the second heat exchanger is the heat exchanger.

According to the above, since the header can be mainly composed of two members, the first member and the second member, the header structure can be simplified and the number of parts can be reduced and the header manufacturing cost can be reduced. Furthermore, if the volume of the concave portion is made the minimum necessary in consideration of the flow rate of the refrigerant in the first and second flat tubes, the amount of refrigerant held in the heat exchanger can be reduced.

It is a schematic diagram which shows the heat exchanger which concerns on Embodiment 1 of this invention. It is a partial cross section schematic diagram containing the header of the heat exchanger shown in FIG. It is a decomposition | disassembly schematic diagram of the header of the heat exchanger shown in FIG. It is an external appearance schematic diagram of the header of the heat exchanger shown in FIG. It is an external appearance schematic diagram of the header of the heat exchanger shown in FIG. FIG. 6 is a partial cross-sectional schematic view taken along line VI-VI in FIG. 4. FIG. 7 is a schematic cross-sectional view taken along line VII-VII in FIG. It is an external appearance schematic diagram in the 1st modification of the heat exchanger which concerns on Embodiment 1 of this invention. FIG. 9 is a partial schematic cross-sectional view taken along line IX-IX in FIG. 8. It is a partial cross section schematic diagram of the header in the 2nd modification of a heat exchanger. It is a partial cross section schematic diagram of the header in the 3rd modification of a heat exchanger. It is a partial cross section schematic diagram of the header in the 4th modification of a heat exchanger. It is a partial cross section schematic diagram of the header in the 5th modification of a heat exchanger. It is an external appearance schematic diagram in the 6th modification of a heat exchanger. It is an external appearance schematic diagram in the 6th modification of a heat exchanger. It is a cross-sectional schematic diagram in the 6th modification of a heat exchanger. It is a schematic diagram which shows the refrigerant circuit of the air conditioning apparatus which concerns on Embodiment 2 of this invention. It is a schematic diagram for demonstrating the size of the header of the heat exchanger which concerns on the Example of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following drawings, the same or corresponding parts are denoted by the same reference numerals, and the description thereof will not be repeated. Moreover, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one. Furthermore, the forms of the constituent elements shown in the entire specification are merely examples, and are not limited to these descriptions.

Embodiment 1 FIG.
<Configuration of heat exchanger>
FIG. 1 is a schematic diagram showing a heat exchanger according to Embodiment 1 of the present invention. FIG. 2 is a partial cross-sectional schematic view including the header of the heat exchanger shown in FIG. FIG. 3 is an exploded schematic view of the header of the heat exchanger shown in FIG. 4 and 5 are schematic external views of the header of the heat exchanger shown in FIG. 6 is a partial cross-sectional schematic view taken along line VI-VI in FIG. FIG. 7 is a schematic cross-sectional view taken along line VII-VII in FIG.

The heat exchanger shown in FIGS. 1 to 7 has a plurality of flat tubes 6 and a plurality of openings that extend in a direction intersecting the extending direction of the flat tubes 6 and through which the at least two flat tubes 6 pass. The fin 5 and the header 1 which connects the edge part of the said flat tube 6 are provided. The plurality of fins 5 are connected and fixed to a flat tube 6 arranged so as to penetrate the opening. A liquid header 7, which is a distribution header, is connected to the windward flat tube 6 at the end opposite to the end to which the header 1, which is a liquid delivery header, is connected in the flat tube 6. A gas header 8 is connected. A plurality of flat tubes 6 are arranged at intervals from each other in a direction perpendicular to the paper surface of FIG. An assembly of the plurality of flat tubes 6 and the plurality of fins 5 is also referred to as a heat exchanger core. As shown in FIG. 1, the ends of the plurality of flat tubes 6 constituting the heat exchanger core are aligned in a windward side row and a leeward side row, and the end portions of the flat tubes 6 are connected to the opening of the header 1. When inserting, the positioning of the header 1 with respect to the flat tube 6 can be easily performed.

The header 1 shown in FIGS. 1 to 6 is installed in the heat exchanger shown in FIG. 1, and is arranged along the flow direction of the fluid, and is arranged in a row of the windward flat tubes 6 and the flat tube 6 on the leeward side. This is a header 1 that connects the columns to the other column. The header 1 is composed of two aluminum plates. Specifically, the header 1 has an aluminum plate as the first plate-like body 11 in which a flat opening 4 is formed on one side, and a recess having a semicircular arc-shaped cross section formed on one side. An aluminum plate as the second plate-like body 12 is fixed and overlapped. The ends of the flat tubes 6 are inserted and fixed in the openings 4 respectively. The header 1 constitutes a refrigerant flow path connecting between the flat tubes 6 between the windward side row and the leeward side row as shown in FIG. The two aluminum plates are fixed by the caulking portion 3. Further, a brazing material is clad on the mating surfaces of the two aluminum plates, and the brazing material is brazed by heating in a state where the aluminum plates are stacked after flux is applied to the brazing material.

As shown in FIG. 2, for example, the refrigerant flowing into the header 1 from the first flat tube 6 on the windward side is the opening 4 (FIG. 3) having a shape along the cross-sectional shape of the flat tube 6 as indicated by an arrow 30. And reaches the space inside the header 1. This space is the refrigerant flow path 2 having a semicircular cross section, and is a space surrounded by the recess of the second plate 12 and the first plate 11. The refrigerant flowing into the refrigerant flow path 2 flows through the refrigerant flow path as indicated by an arrow 30 in FIG. Flows out into the flat tube 6. At this time, the internal volume of the refrigerant flow path can be made smaller than that of the conventional header by minimizing the depth of the refrigerant flow path 2 and the width of the formation region. For this reason, the quantity of the refrigerant | coolant stored by the header 1 can be decreased, and the refrigerant | coolant filling amount of the heat exchanger 10 can be reduced.

As shown in FIGS. 3 to 6, the flat opening 4 in the header 1 is arranged to extend in the horizontal direction (the direction perpendicular to the direction of gravity). Further, in the illustrated header 1, the windward side opening 4 and the leeward side opening 4 are arranged in a horizontal direction. The plurality of openings 4 on the windward side are arranged so as to be spaced apart from each other in the direction of gravity. The plurality of openings 4 on the leeward side are also arranged so as to be spaced apart from each other in the direction of gravity. As shown in FIG. 5, the central axis in the gravity direction (column direction) in the flat opening 4 is linearly arranged in two openings 4 adjacent on the windward side and leeward side in the air flow direction. Is done. In this way, by arranging the flat openings 4 in the windward and leeward rows so that their central axes are parallel or linear, the central axes are shifted or intersected. The planar shape of the refrigerant flow path 2 can be made smaller than when the openings 4 in each row are formed so as to extend. As a result, the volume of the refrigerant flow path in the header 1 can be reduced. In FIG. 5, the central axis is indicated by a one-dot chain line. The central axis coincides with the central axis of the end portion when the end portion of the flat tube 6 is inserted into the opening 4. That is, the central axis indicated by the alternate long and short dash line in FIG. 5 corresponds to the central axis of the end portion of the flat tube 6.

As shown in FIG. 6, in the header 1, the first plate-like body 11 includes a plate-like first member 11a and a brazing material 11b. The brazing material 11 b joins the first member 11 a to the second plate-like body 12. The brazing material 11b can also be used as a bonding material for bonding the first member 11a and the flat tube 6 (not shown).

By arranging the flat tubes 6 so as to line up from the windward side to the leeward side as described above, as shown in FIG. 7, the flat tubes 6 arranged so as to penetrate the fins 5 in the heat exchanger core. Are arranged so as to overlap when viewed from the windward side. If it says from a different viewpoint, the center axis | shaft of the flat tube 6 located in a line on the leeward side and the leeward side will be arrange | positioned so that the distribution direction of air may be met.

<Configuration of modification of heat exchanger>
FIG. 8 is a schematic external view of a header in a first modification of the heat exchanger according to Embodiment 1 of the present invention. FIG. 9 is a partial cross-sectional schematic view taken along line IX-IX in FIG. The heat exchanger shown in FIGS. 8 and 9 basically has the same configuration as the heat exchanger shown in FIGS. 1 to 7, but the configuration of the connection portion between the header 1 and the flat tube 6 is different. Yes. That is, in the heat exchanger shown in FIGS. 8 and 9, the first opening 4 is formed on the first side wall 11 c of the first member 11 a that protrudes from the second member 12 a side to the first flat tube 6 side. Located at the tip. The tip of the first side wall 11c is connected to a location 6a spaced from the end face of one end of the first flat tube 6 via a brazing material 11b. The second opening 4 is an opening having a central axis that is collinear with the first opening 4, and has the same configuration as the first opening 4. That is, the second opening is located at the tip of the second side wall 11c in the first member 11a protruding from the second member 12a side to the second flat tube 6 side. The distal end of the second side wall portion 11c is connected to a location 6a spaced from the end surface of one end portion of the second flat tube 6 via a brazing material 11b. In addition, the edge part of the 1st and 2nd flat tube 6 is processed so that the width | variety may become narrower than the center part of the extension direction of the 1st and 2nd flat tube 6. FIG. The narrowed end is disposed in the first or second opening 4.

FIG. 10 is a partial cross-sectional schematic diagram of the header in the second modification of the heat exchanger. The heat exchanger shown in FIG. 10 basically has the same configuration as the heat exchanger shown in FIGS. 8 and 9, but the configuration of the connection portion between the header 1 and the flat tube 6 is different. That is, in the heat exchanger shown in FIG. 10, the first opening 4 is located at the tip of the first side wall 11c in the first member 11a protruding from the first flat tube 6 side to the second member 12a side. To do. The tip of the first side wall 11c is connected to a location 6a spaced from the end face of one end of the first flat tube 6 via a brazing material. The 2nd opening part 4 is located in the front-end | tip of the 2nd side wall part 11c in the 1st member 11a which protrudes from the 2nd flat tube 6 side to the 2nd member 12a side. The tip of the second side wall 11c is connected to a place 6a spaced from the end face of one end of the second flat tube 6 via a brazing material.

FIG. 11 is a partial schematic cross-sectional view of a header in a third modification of the heat exchanger. The heat exchanger shown in FIG. 11 basically has the same configuration as the heat exchanger shown in FIGS. 1 to 7, but the configuration of the connection portion between the header 1 and the flat tube 6 is different. That is, in the heat exchanger shown in FIG. 11, the recess formed in the second plate-like body 12 as the second member constituting the header 1 is formed by the step portion 22 and the first member 11 a from the step portion 22. A remote bottom 23. As for the 1st and 2nd flat tube 6, the edge part is inserted in the 1st and 2nd opening part 4, respectively. An end of the flat tube 6 protrudes into the refrigerant flow path 2. Part of the end surface of the end portion of the first and second flat tubes 6 is in contact with the stepped portion 22. The brazing material 11b is formed on the surface of the first member 11a that faces the second plate-like body 12. The brazing material 11 b also has a function as a joining material for joining the first member 11 a and the first and second flat tubes 6.

FIG. 12 is a partial schematic cross-sectional view of a header in a fourth modification of the heat exchanger. The heat exchanger shown in FIG. 12 basically has the same configuration as the heat exchanger shown in FIGS. 1 to 7, but the sectional shape of the recess formed in the second member 12a is shown in FIG. It is different from the cross-sectional shape of the recess. In other words, in the heat exchanger shown in FIG. 12, the cross-sectional shape of the recess is a triangular shape with curved corners.

FIG. 13 is a partial cross-sectional schematic diagram of a header in a fifth modification of the heat exchanger. The heat exchanger shown in FIG. 13 basically has the same configuration as the heat exchanger shown in FIGS. 1 to 7, but the sectional shape of the recess formed in the second member 12a is shown in FIG. It is different from the cross-sectional shape of the recess. That is, in the heat exchanger shown in FIG. 13, the cross-sectional shape of the recess is a quadrangular shape with curved corners. From a different point of view, in the heat exchanger shown in FIG. 13, the cross-sectional shape of the recess is a trapezoid whose corners are curved.

14 and 15 are schematic external views of the header in the sixth modification of the heat exchanger. FIG. 16 is a schematic cross-sectional view of a sixth modification of the heat exchanger. 14 and 15 correspond to FIGS. 4 and 5, respectively. FIG. 16 corresponds to FIG. The heat exchanger shown in FIGS. 14 to 16 basically has the same configuration as the heat exchanger shown in FIGS. 1 to 7, but the configuration of the header 1 and the arrangement of the flat tubes 6 are the same as those shown in FIGS. It is different from the heat exchanger shown in FIG. That is, in the heat exchangers shown in FIGS. 14 to 16, the flat opening 4 is arranged to be inclined by an angle θ with respect to the horizontal direction (the direction perpendicular to the direction of gravity). Moreover, the 1st and 2nd opening part 4 which adjoins by the windward side and the leeward side is arrange | positioned so that the column direction center axis | shaft of the opening part 4 may align linearly.

<Manufacturing method of heat exchanger>
The manufacturing method of the heat exchanger which concerns on this embodiment can be implemented with the following processes. First, the process (S10) which prepares the components which comprise a heat exchanger is implemented. In this step (S10), the flat tube 6, the fin 5, the first plate-like body 11, the second plate-like body 12, the liquid header 7 and the gas header 8 constituting the header 1 are prepared. A brazing material is disposed on at least one surface of the first plate 11 and the second plate.

Next, an assembly process (S20) is performed. In this step (S20), the first plate body 11 and the second plate body 12 are first overlapped, the caulking portion 3 is bent, and the first plate body 11 and the second plate body 12 are fixed. The header assembly process is performed. Moreover, the core assembly process which assembles a heat exchanger core is implemented by inserting the opening part of the fin 5 by which the some flat tube 6 was arranged in parallel. Next, the process of inserting the edge part of the flat tube of a heat exchanger core into the opening part 4 (refer FIG. 3) of the header 1 is implemented. At this time, the liquid header 7 and the gas header 8 may be connected to the other end of the flat tube 6. Thus, the composite_body | complex with which the header 1 was connected to the heat exchanger core is comprised. Next, a flux is applied to a predetermined portion of the composite, and the composite is placed in a heating furnace and heated. By this heating, the brazing material arranged in the first plate-like body 11 or the second plate-like body 12 is melted, and the first plate-like body 11 and the second plate-like body are joined to form the header 1. Moreover, these members can be fixed to each other by arranging a brazing material between the first plate-like body 11 and the plurality of flat tubes 6 or between the flat tubes 6 and the fins 5 in advance. it can. In this way, the heat exchanger according to the present embodiment can be manufactured.

<Characteristic configuration and effect of heat exchanger>
To summarize the characteristic configuration of the heat exchanger according to the present disclosure described above, the heat exchanger 10 includes first and second flat tubes 6 and a header 1. The first and second flat tubes 6 extend in a direction intersecting the flow direction of a fluid such as air indicated by an arrow 40 in FIG. 2 and are arranged so as to line up along the flow direction so as to circulate the refrigerant. is there. The header 1 connects one ends of the first and second flat tubes 6. The header 1 includes a first member 11 a included in the first plate-like body 11 and a second member 12 a included in the second plate-like body 12. The header 1 may include brazing

materials

11b and 12b as bonding layers for bonding the first member 11a and the second member 12a. As for the 1st member 11a, one edge part of the 1st and 2nd flat tube 6 is fixed. The second member 12a is connected so as to overlap the first member 11a. The second member 12a is formed with a recess extending from a position where one end of the first flat tube 6 faces to a position where one end of the second flat tube 6 faces.

In this way, the header 1 can be mainly composed of two members, ie, the first member 11a and the second member 12a. Therefore, the header structure can be simplified and the number of parts can be reduced compared to the prior art. Cost can be reduced. Moreover, if the 1st member 11a and the 2nd member 12a are each comprised by a plate-shaped member, the recessed part of the 2nd member 12a can be easily formed by press work etc. Further, if the volume of the refrigerant flow path constituted by the recesses is minimized in consideration of the refrigerant flow amount in the first and second flat tubes 6, the amount of refrigerant held in the heat exchanger 10 is reduced. it can.

In the heat exchanger 10, the inner peripheral surface of the concave portion has one end portion of the second flat tube 6 from a position where one end portion of the first flat tube 6 faces as shown in FIGS. 2 to 4. 6 includes a curved portion as shown in FIG. 6 in the cross section in the transverse direction that intersects the direction toward the position facing the. The inner peripheral surface of the recess in the cross section may be arcuate.

In this case, even if the pressure of the refrigerant increases, it is possible to avoid stress concentrated due to the pressure of the refrigerant from being excessively concentrated at one portion in the curved section, that is, the curved concave portion. . Therefore, it is possible to suppress the occurrence of a problem such as breakage of the header 1 due to the pressure.

In the heat exchanger 10, as viewed from the first member 11a side, the outer peripheral shape of the end 2a in the extending direction of the recess includes a curved portion as shown in FIGS. In this case, it is possible to avoid the stress received from the pressure of the refrigerant from being excessively concentrated in one place even in the curved portion at the end 2a of the recess.

In the heat exchanger 10, as seen from the first member 11 a side, as shown in FIGS. 2, 3, 5, 15, and the like, the central axis of the end portion of the first flat tube 6, and the second The flat tube 6 is parallel to the central axis of the end portion. Further, the first and second flat tubes 6 may include a plurality of refrigerant channels arranged in a direction along the central axis. In this case, the planar size of the concave portion formed at a position facing the end portions of the first and second flat tubes 6 is made larger than the case where the central axes of the first and second flat tubes 6 extend in different directions. Can be small. For this reason, the quantity of the refrigerant | coolant stored inside the recessed part of the header 1 can be reduced.

In the heat exchanger 10, the first flat tube 6 and the second flat tube 6 are arranged so as to extend in a direction intersecting the direction of gravity as shown in FIGS. 1, 15, 16, and the like. Is done. As seen from the first member 11a side, as shown in FIG. 15, the center axis of the end portion of the first flat tube 6 and the center axis of the end portion of the second flat tube 6 are in the direction of gravity. It is inclined by an angle θ with respect to the vertical horizontal direction. As shown in FIG. 16, the first and second flat tubes 6 are disposed so as to be inclined downward in the gravitational direction toward the downstream side in the flow direction of fluid such as air indicated by an arrow 40. Has been.

In this case, when condensed water adheres to the surfaces of the first and second flat tubes 6, the condensed water can easily flow on the surfaces of the first and second flat tubes 6. As a result, the drainage of the heat exchanger 10 can be improved. That is, in the heat exchanger core in which the fins 5 are stacked, the drainage of condensed water (condensed water) when the heat exchanger 10 is used as an evaporator is improved, and the performance of the heat exchanger 10 is improved.

In the heat exchanger 10, when viewed from the first member 11a side, the central axis of the end portion of the first flat tube 6 and the central axis of the end portion of the second flat tube 6 are shown in FIGS. As shown in FIG. 15 and the like, they are arranged on the same straight line. In this case, the area occupied by the first flat tube 6 and the second flat tube 6 as viewed from the windward side in the fluid flow direction indicated by the arrow 40 can be minimized. Therefore, the flow resistance of the fluid in the heat exchanger 10 can be reduced.

In the heat exchanger 10, as shown in FIG. 1, the first and second flat tubes 6 include a refrigerant inlet and outlet at the other end opposite to one end to which the header 1 is connected. A liquid header 7 and a gas header 8 are connected as the header. In this case, for example, a liquid header 7 including a refrigerant inlet is connected to the other end of the first flat tube 6, and a gas header 8 including a refrigerant outlet is connected to the other end of the second flat tube 6. For example, a refrigerant passage through which the refrigerant flows from the first flat tube 6 through the header 1 to the second flat tube 6 can be formed.

Further, for example, a plurality of first flat tubes 6 are arranged in a direction perpendicular to the fluid flow direction and intersecting the direction in which the first flat tubes 6 extend, for example, a direction perpendicular to the paper surface of FIG. Also, a configuration in which a plurality of second flat tubes 6 are arranged in a direction perpendicular to the fluid flow direction and intersecting with the direction in which the second flat tubes 6 extend, for example, in a direction perpendicular to the first sheet of paper. Then, the plurality of first and second flat tubes 6 can be connected to the liquid header 7 and the gas header 8 which are other headers. In addition, about the some 1st and 2nd flat tube 6, as shown in FIG.1, FIG.2, etc., it connects so that the 1st and 2nd flat tube 6 arranged in the flow direction of the fluid shown by the arrow 40 may be connected. , Header 1 is configured. For example, a plurality of openings 4 for fixing a plurality of first and second flat tubes 6 are formed in the first member 11a. The second member 12a has a plurality of recesses extending along the fluid flow direction. The plurality of recesses are formed at positions facing the opening 4.

In the heat exchanger 10, the header 1 includes a caulking portion 3 for caulking and fixing the first member 11a and the second member 12a. First and second openings 4 are formed in the first member 11a. One end of the first flat tube 6 is inserted into the first opening 4. One end of the second flat tube 6 is inserted into the second opening 4. The header 1 further includes a brazing material 11b that connects one end of the first and second flat tubes 6 and the surface of the first member 11a.

In this case, since the first member 11a and the second member 12a can be fixed by the caulking portion 3, the configuration of the header 1 can be simplified as compared with the case where another member such as an adhesive or a fixing bolt is used. Cost can also be reduced. Further, the header 1 and the first and second flat tubes 6 are connected by joining the first member 11a of the header 1 and one end of the first and second flat tubes 6 with the brazing material 11b. The leakage of the refrigerant in the section can be suppressed.

In the heat exchanger shown in FIGS. 8 and 9, the first member 11 a, the first and second flat tubes 6, at a location 6 a away from the end surface of one end of the first and second flat tubes 6, Are connected by a brazing material 11b. For this reason, it can suppress that the said brazing material 11b penetrate | invades into the flow path inside the flat tube 6 from the end surface of the one end part of the flat tube 6. FIG. Therefore, it is possible to suppress the occurrence of the problem that the refrigerant flow path inside the first and second flat tubes 6 is blocked by the brazing material 11b.

In the heat exchanger shown in FIG. 10, the first member 11 a and the first and second flat tubes 6 are located at a location 6 a away from the end surface of one end of the first and second flat tubes 6. Since it is connected by the brazing material, the same effect as the heat exchanger shown in FIGS. 8 and 9 can be obtained. Further, when the header 1 is assembled, the first flat tube 6 or the second flat tube 6 is connected to the first opening 4 or the second opening 4 along the first side wall 11c and the second side wall 11c, respectively. Since it can be inserted into the header, the assembly of the header can be improved.

Further, in the heat exchanger shown in FIG. 11, part of the end surfaces of the end portions of the first and second flat tubes 6 are in contact with the step portion 22 of the second plate 12. As a result, it is easy to position the first and second flat tubes 6 with respect to the first and second openings 4 by inserting the ends of the flat tubes 6 into the openings 4 until they contact the stepped portions 22. Can be done.

In addition, in the heat exchangers shown in FIGS. 14 to 16, the central axes are arranged in parallel or linearly on the two openings 4 adjacent on the windward side and the leeward side of the flat-shaped openings 4. Thus, the volume of the refrigerant flow path 2 can be reduced.

Embodiment 2. FIG.
<Configuration of air conditioner>
FIG. 17 is a schematic diagram illustrating a refrigerant circuit of an air-conditioning apparatus that is an example of a refrigeration cycle apparatus according to Embodiment 2 of the present invention. The refrigerant circuit shown in FIG. 17 includes a compressor 33, a first heat exchanger 34 that acts as a condenser, a throttle device 35 that acts as an expansion valve, a second heat exchanger 36 that acts as an evaporator, and two blowers 37. Prepare. The two fans are each driven by a fan motor 38. The two blowers 37 blow gas (for example, air) to either the first heat exchanger 34 or the second heat exchanger 36, respectively. In the refrigerant circuit, the refrigerant circulates in the order of the compressor 33, the first heat exchanger 34, the expansion device 35, and the second heat exchanger 36. From a different point of view, the air conditioner shown in FIG. 17 includes a compressor 33, a first heat exchanger 34, a throttle device 35 as an expansion valve, and a second heat exchanger 36, and a refrigerant in which the refrigerant circulates. Provide a circuit.

At least one of the first heat exchanger 34 and the second heat exchanger 36 shown in FIG. 17 is the heat exchanger 10 described in the first embodiment. The blower 37 blows gas to each heat exchanger, for example, along the direction indicated by the arrow 40 in FIG. Note that by arranging a four-way valve or the like in the refrigerant circuit, the refrigerant flow direction in the first heat exchanger 34 and the second heat exchanger 36 in the refrigerant circuit is reversed from the direction shown in FIG. The exchanger may act as an evaporator and the second heat exchanger may act as a condenser.

<Operation effect of air conditioner>
Since the air conditioning apparatus according to the present disclosure is the heat exchanger according to Embodiment 1 described above as a heat exchanger, the manufacturing cost is reduced. Furthermore, by applying the heat exchanger according to the first embodiment, an air conditioner with high energy efficiency can be realized. Here, energy efficiency is constituted by the following equation.

Heating energy efficiency = indoor heat exchanger (condenser) capacity / total input Cooling energy efficiency = indoor heat exchanger (evaporator) capacity / total input Note that the heat exchanger according to the above-described embodiment and air using the same About a harmony device, you may use refrigerants, such as R410A, R32, and HFO1234yf. Also in this case, the above-described effect can be obtained.

Moreover, although the example of air and a refrigerant | coolant was shown as a working fluid, even if another gas, a liquid, and a gas-liquid mixed fluid are used as a working fluid, there exists the same effect. In addition, the heat exchanger and the air conditioner using the heat exchanger described in the above-described embodiment are dissolved in a refrigerant and oil such as mineral oil, alkylbenzene oil, ester oil, ether oil, and fluorine oil. Regardless of whether or not any refrigerating machine oil is used, the effect can be achieved.

(Specific configuration example of heat exchanger)
FIG. 18 is a schematic diagram for explaining the size of the header of the heat exchanger according to the embodiment of the present invention. In FIG. 18, the thickness of the first member 11a is, for example, 3.0 mm, and the thickness of the second member 12a is 2.0 mm. Both the first member 11a and the second member 12a are made of an aluminum alloy. For example, the symbol A3003 prescribed | regulated to JIS plan H4000: 2006 can be used as an aluminum alloy. Further, as the brazing material clad on the first member 11a or the second member 12a, a brazing material in which silicon is contained in aluminum can be used. The silicon content can be, for example, 8%.

The inner peripheral surface of the recess in the cross section in the transverse direction perpendicular to the extending direction of the recess shown on the right side of FIG. 18 can have a radius of curvature of 3.5 mm. Moreover, the width | variety of the internal peripheral surface in the extension direction of a recessed part can be 40 mm, for example. Moreover, in order to form one recessed part, the size of the unit area | region which joins the 1st member 11a and the 2nd member 12a can be 52 mm in length and 13.6 mm in width, for example.

Although the embodiments of the present invention have been described above, the above-described embodiments can be variously modified. The scope of the present invention is not limited to the above-described embodiment. The scope of the present invention is defined by the terms of the claims, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

The present invention can be applied to refrigeration cycle devices such as air conditioning devices, refrigeration devices, and refrigeration devices, heat pump devices, and the like.

DESCRIPTION OF SYMBOLS 1 Header, 2 Refrigerant flow path, 2a edge part, 3 crimping part, 4 opening part, 5 fin, 6 flat tube, 6a place, 7 liquid header, 8 gas header, 10 heat exchanger, 11 1st plate-shaped body, 11a 1st member, 11b brazing material, 11c side wall part, 12 2nd plate-like body, 12a 2nd member, 22 level difference part, 23 bottom part, 30, 40 arrow, 33 compressor, 34 1st heat exchanger, 35 restrictor Apparatus, 36 2nd heat exchanger, 37 air blower, 38 air blower motor.

Claims

A first flat tube and a second flat tube that extend in a direction intersecting the flow direction of the fluid and flow the refrigerant arranged so as to be aligned along the flow direction;
A header that connects one ends of the first and second flat tubes, and
The header is
A first member to which the one end of the first and second flat tubes is fixed;
A recess is formed which is connected to overlap the first member and extends from a position where the one end of the first flat tube faces to a position where the one end of the second flat tube faces. And a second heat exchanger.
The inner peripheral surface of the recess is in a lateral direction that intersects the direction from the position facing the one end of the first flat tube toward the position facing the one end of the second flat tube. The heat exchanger according to claim 1, comprising a curved portion in cross section.
The heat exchanger according to claim 1 or 2, wherein an outer peripheral shape of an end portion in a direction in which the concave portion extends includes a curved portion when viewed from the first member side.
The central axis of the end portion of the first flat tube and the central axis of the end portion of the second flat tube are parallel to each other when viewed from the first member side. The heat exchanger according to any one of the above.
The first flat tube and the second flat tube are arranged to extend in a direction intersecting the direction of gravity,
When viewed from the first member side, the central axis of the end portion of the first flat tube and the central axis of the end portion of the second flat tube are perpendicular to the direction of gravity. The heat exchanger according to claim 4, wherein the heat exchanger is inclined with respect to.
The central axis of the end portion of the first flat tube and the central axis of the end portion of the second flat tube are arranged on the same straight line when viewed from the first member side. Item 6. The heat exchanger according to item 4 or item 5.
The header according to any one of claims 1 to 6, wherein another header including a refrigerant inlet / outlet is connected to the other end of the first and second flat tubes opposite to the one end. The heat exchanger according to item.
The header includes a caulking portion that caulks and fixes the first member and the second member;
First and second openings are formed in the first member,
The one end of the first flat tube is inserted into the first opening;
The one end of the second flat tube is inserted into the second opening;
8. The header according to claim 1, wherein the header further includes a brazing material that connects the one end of the first and second flat tubes and the surface of the first member. Heat exchanger.
The first opening is located at the tip of the first side wall portion of the first member protruding from the second member side to the first flat tube side,
The tip of the first side wall is connected to a place spaced from the end surface of the one end of the first flat tube via the brazing material,
The second opening is located at the tip of the second side wall portion of the first member protruding from the second member side to the second flat tube side,
The heat exchanger according to claim 8, wherein the tip of the second side wall portion is connected to a place spaced from an end surface of the one end portion of the second flat tube via the brazing material. .
The first opening is located at the tip of the first side wall portion of the first member protruding from the first flat tube side to the second member side,
The tip of the first side wall is connected to a place spaced from the end surface of the one end of the first flat tube via the brazing material,
The second opening is located at the tip of the second side wall portion of the first member protruding from the second flat tube side to the second member side,
The heat exchanger according to claim 8, wherein the tip of the second side wall portion is connected to a place spaced from an end surface of the one end portion of the second flat tube via the brazing material. .
A refrigerant circuit including a compressor, a first heat exchanger, an expansion valve, and a second heat exchanger, in which the refrigerant circulates;
The refrigeration cycle apparatus, wherein at least one of the first heat exchanger and the second heat exchanger is the heat exchanger according to any one of claims 1 to 10.