WO2015063858A1

WO2015063858A1 - Pipe joint, heat exchanger, and air conditioner

Info

Publication number: WO2015063858A1
Application number: PCT/JP2013/079248
Authority: WO
Inventors: 真哉東井上; 繁佳松井; 石橋　晃; 岡崎　多佳志; 伊東　大輔; 裕樹宇賀神
Original assignee: 三菱電機株式会社
Priority date: 2013-10-29
Filing date: 2013-10-29
Publication date: 2015-05-07
Also published as: EP3064819A4; JPWO2015063858A1; CN105683639A; US20160245560A1; JP6207624B2; CN105683639B; EP3064819B1; EP3064819A1

Abstract

A pipe joint according to the present invention has a passage section (71) formed therein. A flat pipe is connected to one end section (72) of the passage section (71), and another pipe having a different cross-sectional shape than the flat pipe is attached to the other end section (73) of the passage section (71). The central axis of the one end section (72) and the central axis of the other end section (73) are eccentric with respect to one another.

Description

Pipe fitting, heat exchanger, and air conditioner

The present invention relates to a pipe joint, a heat exchanger, and an air conditioner.

As a conventional pipe joint, a penetration part is formed, a flat tube is connected to one end of the penetration part, and a pipe having a cross-sectional shape different from that of the flat pipe, for example, a circular pipe, is connected to the other end of the penetration part. Some are connected. A plurality of flow paths are formed in the flat tube in the long axis direction (see, for example, Patent Document 1).

JP 2013-142454 A (paragraph [0009], FIGS. 1 and 2)

In a conventional pipe joint, for example, if an inertial force of a component parallel to the long axis direction of a flat tube is acting on a fluid passing through a pipe having a cross-sectional shape different from that of the flat tube, the inertial force causes the flat tube to The balance of the fluid flowing into each formed flow path changes. In particular, when the fluid passing through a tube having a cross-sectional shape different from that of a flat tube is a gas-liquid two-phase refrigerant, the phenomenon becomes significant. However, in such a pipe joint, the central axis of one end to which the flat tube is connected and the central axis of the other end to which the tube having a different cross-sectional shape from the flat tube is connected are coaxial. The change of the balance of the fluid flowing into each flow path formed in the flat tube cannot be dealt with. In other words, such a pipe joint has a problem that the balance of the fluid flowing into the plurality of flow paths of the flat tube cannot be optimized.

The present invention has been made against the background of the above problems, and an object thereof is to obtain a pipe joint capable of optimizing the balance of fluid flowing into a plurality of flow paths of a flat tube. Moreover, an object of this invention is to obtain the heat exchanger provided with such a pipe joint. Moreover, an object of this invention is to obtain the air conditioning apparatus provided with such a heat exchanger.

In the pipe joint according to the present invention, a penetrating portion is formed, a flat tube is connected to one end of the penetrating portion, and another pipe having a cross-sectional shape different from that of the flat tube is connected to the other end of the penetrating portion. In the pipe joint to be connected, the central axis of the one end and the central axis of the other end are eccentric from each other.

In the pipe joint according to the present invention, for example, even when an inertial force of a component parallel to the long axis direction of the flat tube is acting on a fluid passing through a pipe having a cross-sectional shape different from that of the flat tube, By decentering the central axis of the end portion and the central axis of the other end portion of the penetrating portion, the balance of the fluid flowing into each flow path formed in the flat tube can be optimized.

1 is a perspective view of a heat exchanger according to Embodiment 1. FIG. It is a perspective view in the state which the laminated header of the heat exchanger which concerns on Embodiment 1 decomposed | disassembled. It is a perspective view of the cylindrical header of the heat exchanger which concerns on Embodiment 1. FIG. It is a figure explaining the connection of the heat exchange part and splitting flow part of the heat exchanger which concerns on Embodiment 1. FIG. It is a figure explaining the connection of the heat exchange part and splitting flow part of the heat exchanger which concerns on Embodiment 1. FIG. It is a figure explaining the connection of the heat exchange part and split mixing flow part of the modification of the heat exchanger which concerns on Embodiment 1. FIG. It is a figure explaining the connection of the heat exchange part and split mixing flow part of the modification of the heat exchanger which concerns on Embodiment 1. FIG. It is a figure explaining the connection of the heat exchange part and split mixing flow part of the modification of the heat exchanger which concerns on Embodiment 1. FIG. It is a figure which shows the structure of the windward concentric pipe joint of the heat exchanger which concerns on Embodiment 1, and a leeward concentric pipe joint. It is a figure which shows the structure of the windward concentric pipe joint and leeward concentric pipe joint of the heat exchanger which concerns on a comparative example. It is a figure which shows the structure of the windward eccentric pipe joint and leeward eccentric pipe joint of the heat exchanger which concerns on Embodiment 1. FIG. It is a figure which shows the structure of the air conditioning apparatus to which the heat exchanger which concerns on Embodiment 1 is applied. It is a figure which shows the structure of the air conditioning apparatus to which the heat exchanger which concerns on Embodiment 1 is applied. It is a figure explaining the liquid quantity distribution of the refrigerant | coolant which flows in into a leeward side heat exchanger tube in case the heat exchanger which concerns on Embodiment 1 acts as an evaporator. It is a figure explaining the liquid quantity distribution of the refrigerant | coolant which flows in into a leeward side heat exchanger tube in case the heat exchanger which concerns on Embodiment 1 acts as an evaporator. It is a figure explaining the gas amount distribution of the refrigerant | coolant which flows in into an upwind heat exchanger tube in case the heat exchanger which concerns on Embodiment 1 acts as a condenser. It is a figure explaining the gas amount distribution of the refrigerant | coolant which flows in into an upwind heat exchanger tube in case the heat exchanger which concerns on Embodiment 1 acts as a condenser. It is a perspective view of the heat exchanger which concerns on Embodiment 2. FIG. It is a figure explaining the connection of the heat exchange part and splitting flow part of the heat exchanger which concerns on Embodiment 2. FIG. It is a figure explaining the connection of the heat exchange part and splitting flow part of the heat exchanger which concerns on Embodiment 2. FIG. It is a figure explaining the connection of the heat exchange part and split mixing flow part of the modification of the heat exchanger which concerns on Embodiment 2. FIG. It is a figure which shows the structure of the air conditioning apparatus to which the heat exchanger which concerns on Embodiment 2 is applied. It is a figure which shows the structure of the air conditioning apparatus to which the heat exchanger which concerns on Embodiment 2 is applied.

Hereinafter, the pipe joint concerning the present invention is explained using a drawing.
In addition, the structure, operation | movement, etc. which are demonstrated below are only examples, and the pipe joint which concerns on this invention is not limited to a case where it is such a structure, operation | movement, etc. Moreover, in each figure, the same code | symbol is attached | subjected to the same or similar thing, or attaching | subjecting code | symbol is abbreviate | omitted. Further, the illustration of the fine structure is simplified or omitted as appropriate. In addition, overlapping or similar descriptions are appropriately simplified or omitted.

Moreover, although the case where the pipe joint which concerns on this invention is a member which comprises a heat exchanger below is demonstrated, the pipe joint which concerns on this invention may be a member which comprises another apparatus. . In the following, a case where the heat exchanger provided with the pipe joint according to the present invention is applied to an air conditioner is described. However, the present invention is not limited to such a case, and includes, for example, a refrigerant circulation circuit. You may apply to another refrigeration cycle apparatus. Moreover, although the case where the heat exchanger provided with the pipe joint according to the present invention is an outdoor heat exchanger of an air conditioner is described, it is not limited to such a case, and the indoor heat exchange of the air conditioner It may be a vessel. Moreover, although the case where an air conditioning apparatus switches between heating operation and cooling operation is demonstrated, it is not limited to such a case, You may perform only heating operation or cooling operation.

Embodiment 1 FIG.
The heat exchanger according to Embodiment 1 will be described.
<Configuration of heat exchanger>
Below, the structure of the heat exchanger which concerns on Embodiment 1 is demonstrated.
(Schematic configuration of heat exchanger)
Below, schematic structure of the heat exchanger which concerns on Embodiment 1 is demonstrated.
1 is a perspective view of a heat exchanger according to Embodiment 1. FIG.
As shown in FIG. 1, the heat exchanger 1 includes a heat exchanging unit 2 and a split blending unit 3.

The heat exchange unit 2 includes an upwind heat exchange unit 21 disposed on the leeward side and a leeward side disposed on the leeward side in the direction of passage of air passing through the heat exchange unit 2 (the white arrow in the figure). And a heat exchanging unit 31. The windward heat exchange unit 21 includes a plurality of windward heat transfer tubes 22 and a plurality of windward fins 23 joined to the plurality of windward heat transfer tubes 22 by, for example, brazing. The leeward side heat exchange unit 31 includes a plurality of leeward side heat transfer tubes 32 and a plurality of leeward side fins 33 joined to the plurality of leeward side heat transfer tubes 32 by brazing or the like, for example. The heat exchanging unit 2 may be configured by two rows of the windward side heat exchanging unit 21 and the leeward side heat exchanging unit 31, or may be configured by three or more rows.

The windward side heat transfer tube 22 and the leeward side heat transfer tube 32 are flat tubes, and a plurality of flow paths are formed in the major axis direction. Each of the plurality of windward side heat transfer tubes 22 and the plurality of leeward side heat transfer tubes 32 is bent in a hairpin shape between one end and the other end to form folded

portions

22a and 32a. The windward side heat transfer tubes 22 and the leeward side heat transfer tubes 32 are arranged in a plurality of stages in a direction intersecting with the passage direction of air passing through the heat exchanging unit 2 (the white arrow in the figure). One end and the other end of each of the plurality of windward side heat transfer tubes 22 and the plurality of leeward side heat transfer tubes 32 are arranged in parallel so as to face the mixing / mixing flow portion 3.

The distribution flow unit 3 includes a laminated header 51 and a cylindrical header 61. The laminated header 51 and the cylindrical header 61 are arranged side by side so as to follow the passage direction of air passing through the heat exchanging unit 2 (the white arrow in the figure). A refrigerant pipe (not shown) is connected to the laminated header 51 via a connecting pipe 52. Refrigerant piping (not shown) is connected to the tubular header 61 via a connecting pipe 62. The connection pipe 52 and the connection pipe 62 are, for example, circular pipes.

The laminated header 51 is connected to the windward heat exchanging unit 21, and a split flow channel 51 a is formed therein. When the heat exchange unit 2 acts as an evaporator, the split-mixing flow channel 51a distributes the refrigerant flowing from the refrigerant pipe (not shown) to the plurality of windward side heat transfer tubes 22 of the windward side heat exchange unit 21. It becomes an outflow distribution channel. When the heat exchange unit 2 acts as a condenser, the split flow channel 51a joins refrigerant flowing in from the plurality of windward side heat transfer tubes 22 of the windward side heat exchange unit 21 to a refrigerant pipe (not shown). It becomes the merging channel that flows out. The stacked header 51 corresponds to the “header disposed on the windward side” of the present invention.

The cylindrical header 61 is connected to the leeward side heat exchanging portion 31 and a split flow channel 61a is formed therein. When the heat exchange unit 2 acts as a condenser, the split flow channel 61a distributes the refrigerant flowing from the refrigerant pipe (not shown) to the plurality of leeward heat transfer tubes 32 of the leeward heat exchange unit 31. It becomes an outflow distribution channel. When the heat exchange unit 2 acts as an evaporator, the split-mixing flow channel 61a joins refrigerant flowing in from the plurality of leeward heat transfer tubes 32 of the leeward heat exchange unit 31 to a refrigerant pipe (not shown). It becomes the merging channel that flows out. The cylindrical header 61 corresponds to the “header arranged on the leeward side” of the present invention.

(Configuration of stacked header)
Below, the structure of the laminated header of the heat exchanger which concerns on Embodiment 1 is demonstrated.
FIG. 2 is a perspective view of the heat exchanger according to Embodiment 1 in a state where the stacked header is disassembled. In addition, in FIG. 2, the flow of the refrigerant | coolant in case the distribution flow path 51a of the laminated header 51 functions as a distribution flow path is shown by the arrow.

As shown in FIG. 2, the first plate member 53 in which the partial flow channel 53a is formed, the plurality of second plate members 54_1 to 54_3 in which the partial flow channels 54a_1 to 54a_3 are formed, and the partial flow channel 55a. The third plate-like member 55 formed with is laminated via a plurality of clad members 56_1 to 56_4 in which the partial flow passages 56a are formed, whereby the laminated header 51 is configured. A brazing material is applied to both surfaces or one surface of the cladding materials 56_1 to 56_4. Hereinafter, the first plate member 53, the plurality of second plate members 54_1 to 54_3, the third plate member 55, and the plurality of clad members 56_1 to 56_4 are collectively referred to as “plate members”. May be described.

The

partial flow paths

53a, 55a, and 56a are circular through holes. Each of the partial flow paths 54a_1 to 54a_3 is a linear (for example, Z-shaped, S-shaped, etc.) through groove in which the height in the gravity direction of one end and the other end is different from each other. A refrigerant pipe (not shown) is connected to the partial flow path 53a through the connection pipe 52. The windward heat transfer tube 22 is connected to each of the partial flow paths 55a via the connection pipe 57. The connection pipe 57 is, for example, a circular pipe or an elliptical pipe.

The partial flow path 56a of the cladding material 56_1 is formed at a position facing the partial flow path 53a. The partial flow path 56a of the cladding material 56_4 is formed at a position facing the partial flow path 55a. One end and the other end of the partial flow paths 54a_1 to 54a_3 are opposed to the partial flow paths 56a of the clad members 56_2 to 56_4 laminated adjacent to the side close to the windward heat exchange section 21. A portion between one end portion and the other end portion of the partial flow paths 54a_1 to 54a_3 is a partial flow path 56a of the clad material 56_1 to 56_3 laminated adjacent to the side far from the windward heat exchange section 21. Opposite.

When the plate-like members are stacked, the partial flow paths 53a, 54a_1 to 54a_3, 55a, 56a are communicated to form the split flow path 51a. The split flow channel 51a functions as a distribution channel when the refrigerant flows in the direction of the arrow in the figure, and functions as a merging channel when the refrigerant flows in the direction opposite to the arrow in the figure.

When the split flow channel 51a functions as a distribution channel, the refrigerant that has flowed into the partial flow channel 53a via the connection pipe 52 passes through the partial flow channel 56a and is at one end of the partial flow channel 54a_1. Between the first end and the other end, hits the surface of the clad material 56_2, and is branched in two directions. The branched refrigerant flows out from one end and the other end of the partial flow channel 54a_1, and passes between the one end and the other end of the partial flow channel 54a_2 via the partial flow channel 56a. , And hits the surface of the clad material 56_3 to be branched in two directions. The branched refrigerant flows out from one end and the other end of the partial flow path 54a_2, and passes between the one end and the other end of the partial flow path 54a_3 through the partial flow path 56a. , And hits the surface of the clad material 56_4 to be branched in two directions. The branched refrigerant flows out from one end and the other end of the partial flow path 54a_3, and flows into the connection pipe 57 through the partial flow path 56a and the partial flow path 55a.

When the split flow channel 51a functions as a merging channel, the refrigerant that has flowed into the partial channel 55a via the connection pipe 57 passes through the partial channel 56a and is at one end of the partial channel 54a_3. And flows into the other end, and flows into the partial flow path 56a communicating between one end and the other end of the partial flow path 54a_3, thereby being merged. The merged refrigerant flows into one end and the other end of the partial flow path 54a_2, and flows into the partial flow path 56a that communicates between one end and the other end of the partial flow path 54a_2. To be merged. The merged refrigerant flows into one end and the other end of the partial flow path 54a_1, and flows into the partial flow path 56a that communicates between one end and the other end of the partial flow path 54a_1. To be merged. The merged refrigerant flows into the connecting pipe 52 through the partial flow path 53a.

Note that the first plate-like member 53, the second plate-like members 54_1 to 54_3, and the third plate-like member 55 may be directly laminated without using the clad members 56_1 to 56_4. In the case of being laminated via the cladding materials 56_1 to 56_4, the partial flow path 56a functions as a refrigerant isolation flow path, so that the refrigerant passing through the partial flow paths 53a, 54a_1 to 54a_3, 55a can be isolated from each other. Ensured. Each of the first plate-like member 53, the second plate-like members 54_1 to 54_3, and the third plate-like member 55, and the clad members 56_1 to 56_4 laminated adjacent to each other are integrated into a plate shape. The members may be directly laminated.

(Configuration of cylindrical header)
Below, the structure of the cylindrical header of the heat exchanger which concerns on Embodiment 1 is demonstrated.
FIG. 3 is a perspective view of a cylindrical header of the heat exchanger according to the first embodiment. In addition, in FIG. 3, the flow of the refrigerant | coolant in case the mixing | blending flow path 61a of the cylindrical header 61 functions as a confluence | merging flow path is shown by the arrow.

As shown in FIG. 3, the cylindrical header 61 includes a cylindrical portion 63 in which one end and the other end are closed so that the axial direction is parallel to the direction of gravity. is there. The axial direction of the cylindrical portion 63 may not be parallel to the direction of gravity. Since the cylindrical header 61 is disposed so that the axial direction of the cylindrical portion 63 and the longitudinal direction of the laminated header 51 are parallel to each other, the split flow portion 3 is saved. The cylindrical portion 63 may be, for example, a cylindrical portion having an elliptical cross section.

A refrigerant pipe (not shown) is connected to the side wall of the cylindrical portion 63 via a connecting pipe 62. The leeward heat transfer tube 32 is connected to the side wall of the cylindrical portion 63 via a plurality of connection tubes 64. The connection pipe 64 is, for example, a circular pipe or an elliptical pipe. The inner side of the cylindrical portion 63 is a split blending flow path 61a. The split flow channel 61a functions as a merge channel when the refrigerant flows in the direction of the arrow in the figure, and functions as a distribution channel when the refrigerant flows in the direction opposite to the arrow in the figure.

When the split flow channel 61a functions as a merge channel, the refrigerant that has flowed into the plurality of connection pipes 64 merges by passing through the inside of the cylindrical portion 63 and flowing into the connection pipe 62. When the mixing / mixing flow path 61a functions as a distribution flow path, the refrigerant flowing into the connection pipe 62 is distributed by passing through the inside of the cylindrical portion 63 and flowing into the plurality of connection pipes 64.

Of the circumferential direction of the cylindrical portion 63, the connection pipe 62 and the plurality of connection pipes 64 are arranged so that the direction in which the connection pipe 62 is connected and the direction in which the plurality of connection pipes 64 are connected are not aligned. It is good to be connected. By being configured in this way, it is possible to improve the uniformity of the refrigerant flowing into the plurality of connection pipes 64 when the mixing / mixing flow path 61a functions as a distribution flow path.

(Connection of heat exchange section and split mixing section)
Below, the connection of the heat exchange part of the heat exchanger which concerns on Embodiment 1, and a part mix flow part is demonstrated.
4 and 5 are diagrams for explaining the connection between the heat exchange unit and the mixing and mixing unit of the heat exchanger according to the first embodiment. FIG. 5 is a cross-sectional view taken along line AA in FIG.

4 and 5, the windward concentric pipe joint 41 A is joined to one end 22 b of the windward heat transfer pipe 22. The upwind eccentric pipe joint 41 B is joined to the other end 22 c of the upwind heat transfer tube 22. The leeward concentric pipe joint 42 A is joined to the other end 32 c of the leeward heat transfer pipe 32. The leeward eccentric pipe joint 42 B is joined to one end 32 b of the leeward heat transfer tube 32.

The connecting pipe 57 of the laminated header 51 is connected to the windward concentric pipe joint 41A. A connecting pipe 64 of the tubular header 61 is connected to the leeward side concentric pipe joint 42A. The upwind eccentric pipe joint 41B and the downwind eccentric pipe joint 42B are connected by a crossover pipe 43. The cross-over tube 43 is, for example, a circular tube or an elliptic tube bent in an arc shape.

FIG. 6 is a diagram for explaining the connection of the heat exchange unit and the mixing and mixing unit in the modification of the heat exchanger according to the first embodiment. 6 is a cross-sectional view taken along the line AA in FIG.
As shown in FIG. 5, the windward side heat transfer tube 22 and the leeward side heat transfer tube 32 include one end 22 b and the other end 22 c of the windward side heat transfer tube 22 and one of the leeward side heat transfer tubes 32. The end portion 32b and the other end portion 32c may be arranged in a zigzag shape when the heat exchanger 1 is viewed from the side, and as shown in FIG. You may arrange | position so that it may become a shape.

7 and 8 are diagrams for explaining the connection of the heat exchange unit and the mixing and mixing unit in the modification of the heat exchanger according to the first embodiment. 7 and 8 are cross-sectional views taken along the line AA in FIG.
Further, as shown in FIGS. 7 and 8, the other end 22c of the windward heat transfer tube 22, and one end 22b of the windward heat transfer tube 22 adjacent to the windward heat transfer tube 22, Are connected using the windward side transition pipe 44 and the windward concentric pipe joint 41 A, and the other end 32 c of the leeward side heat transfer pipe 32 and the leeward side heat transfer pipe 32 on the next stage of the leeward side heat transfer pipe 32. May be connected using the leeward side crossover pipe 45 and the leeward side concentric pipe joint 42A. The windward side transition pipe 44 and the leeward side transition pipe 45 are, for example, a circular pipe or an elliptical pipe bent in an arc shape.

In addition, the windward heat transfer tube 22 and the leeward heat transfer tube 32 are not bent into a hairpin shape between one end and the other end, and the folded

portions

22a and 32a are not formed. One end portion of the heat pipe 22 and one end portion of the windward heat transfer pipe 22 adjacent to the heat pipe 22 are connected using the windward transition pipe 44 and the windward concentric pipe joint 41A, and the windward side One end portion of the side heat transfer tube 32 and one end portion of the leeward side heat transfer tube 32 adjacent to the side heat transfer tube 32 are connected using the leeward side crossover tube 45 and the leeward side concentric pipe joint 42A. Thus, the refrigerant may be folded back.

(Details of the structure of the leeward concentric pipe joint and leeward concentric pipe joint)
Details of the structures of the windward concentric pipe joint and the leeward concentric pipe joint of the heat exchanger according to Embodiment 1 will be described below.
FIG. 9 is a diagram illustrating the structures of the windward concentric pipe joint and the leeward concentric pipe joint of the heat exchanger according to Embodiment 1. In addition, in FIG. 9, sectional drawing in the state which looked at the windward concentric pipe joint 41A and the leeward side concentric pipe coupling 42A, the sectional view in the state seen from the side, those top views, and those A bottom view is shown. In FIG. 9, the pipes connected to one end 72 and the other end 73 of the upwind concentric pipe joint 41A and the downwind concentric pipe joint 42A are shown by dotted lines. FIG. 9 shows a case where the connection pipe 57 of the laminated header 51 and the connection pipe 64 of the cylindrical header 61 are circular pipes.

As shown in FIG. 9, a penetration portion 71 is formed in the windward concentric pipe joint 41 A and the leeward concentric pipe joint 42 A. The cross-sectional shape of one end 72 of the penetrating portion 71 is a shape that follows the cross-sectional shape of the windward side heat transfer tube 22 or the leeward side heat transfer tube 32. The cross-sectional shape of the other end 73 of the penetrating portion 71 is a shape that follows the cross-sectional shape of the connection pipe 57 of the laminated header 51 or the connection pipe 64 of the cylindrical header 61. The central axis of one end 72 and the central axis of the other end 73 are coaxial.

In a state where the windward concentric pipe joint 41A and the leeward concentric pipe joint 42A are viewed from the front, when the inner diameter (the inner diameter in the major axis direction) of one end 72 is W1, the inner diameter D1 of the other end 73 is D1. ≦ W1. Further, in a state in which the windward concentric pipe joint 41A and the leeward concentric pipe joint 42A are viewed from the side, when the inner diameter (the inner diameter in the minor axis direction) of one end 72 is W2, the inner diameter D2 of the other end 73 is , D2 ≧ W2. That is, the inner diameter D (D1, D2) in the entire circumferential direction of the cross-sectional shape of the other end portion 73 is W2 ≦ D ≦ W1. The flow path cross-sectional area (d1 ² × π / 4) of the connection pipe 57 of the laminated header 51 and the connection pipe 64 of the cylindrical header 61 is the flow path cross-sectional area of the windward side heat transfer pipe 22 and the leeward side heat transfer pipe 32. Larger than (w1 × w2 × number of flow paths). When the connection pipe 57 of the laminated header 51 and the connection pipe 64 of the cylindrical header 61 are elliptical pipes, D1> D2 or D1 <D2.

By being configured in this manner, D1 can be shortened to downsize the windward concentric pipe joint 41A and the leeward side concentric pipe joint 42A, and D2 can be lengthened to join a pipe having a large channel cross-sectional area. Thus, it is compatible to reduce the pressure loss generated in the refrigerant passing through the windward concentric pipe joint 41A and the leeward concentric pipe joint 42A. In addition, since W2 ≦ D ≦ W1, the degree of freedom of bending of the connection pipe 57 of the laminated header 51 and the connection pipe 64 of the cylindrical header 61 is improved.

FIG. 10 is a diagram illustrating the structures of the windward concentric pipe joint and the leeward concentric pipe joint of the heat exchanger according to the comparative example. FIG. 10 shows a cross-sectional view of the windward concentric pipe joint 41A and the leeward concentric pipe joint 42A as viewed from the front. In FIG. 10, the pipes connected to one end 72 and the other end 73 of the upwind concentric pipe joint 41A and the downwind concentric pipe joint 42A are shown by dotted lines.
Further, in the region between the one end 72 and the other end 73 of the penetrating portion 71, the cross-sectional shape of the inner peripheral surface of the one end 72 is changed to the cross-sectional shape of the inner peripheral surface of the other end 73. A shape converting portion 74 that is continuously changed is formed. As shown in FIG. 10, when the shape converting portion 74 is not formed in the penetrating portion 71, that is, when one end 72 and the other end 73 are in direct communication, one end A vortex is produced at the corner of 72, and pressure loss occurs in the refrigerant passing through the windward concentric pipe joint 41A and the leeward concentric pipe joint 42A. Such a phenomenon is suppressed by forming the shape conversion part 74 in the area | region between the edge parts 73 of this.

Further, the connection pipe 57 of the laminated header 51 and the connection pipe 64 of the cylindrical header 61 are joined in a state where they are inserted up to the boundary between the other end 73 and the shape conversion part 74. That is, the region where the outer peripheral surface of the connection pipe 57 of the multilayer header 51 and the outer peripheral surface of the connection pipe 64 of the cylindrical header 61 is joined to the inner peripheral surface of the other end 73 is adjacent to the shape conversion unit 74. Therefore, the refrigerant flowing in from the connection pipe 57 of the laminated header 51 and the connection pipe 64 of the cylindrical header 61 flows into the windward side heat transfer pipe 22 and the leeward side heat transfer pipe 32 without passing through the steps, resulting in pressure loss. Occurrence is further suppressed. In addition, the axial dimension of the other end 73 can be reduced, and the downwind concentric pipe joint 41A and the downwind concentric pipe joint 42A are reduced in size.

(Details of the structure of the upwind eccentric fitting and leeward eccentric fitting)
Below, the detail of the structure of the windward eccentric pipe joint and leeward eccentric pipe joint of the heat exchanger which concerns on Embodiment 1 is demonstrated.
FIG. 11 is a diagram illustrating the structure of the upwind eccentric pipe joint and the downwind eccentric pipe joint of the heat exchanger according to the first embodiment. In addition, in FIG. 11, the cross section of the windward eccentric pipe joint 41B and the leeward eccentric pipe joint 42B in the state seen from the front and its peripheral members are illustrated.

The windward eccentric pipe joint 41B and the leeward eccentric pipe joint 42B have the same configuration as the windward concentric pipe joint 41A and the leeward side concentric pipe joint 42A, but as shown in FIG. The difference is that the central axis and the central axis of the other end 73 are eccentric from each other. The amount of eccentricity Z is 0 <Z <W3 / 2, where W3 is the outer diameter in the major axis direction of the windward side heat transfer tube 22 and the leeward side heat transfer tube 32. The distance between the central axis of the other end 73 of the penetration part 71 of the upwind eccentric pipe joint 41B and the central axis of the leeward side heat transfer pipe 32 is one of the penetration parts 71 of the upwind eccentric pipe joint 41B. It is eccentric so as to be shorter than the distance between the central axis of the end portion 72 and the central axis of the leeward heat transfer tube 32. In addition, the distance between the central axis of the other end 73 of the penetrating portion 71 of the leeward side eccentric pipe joint 42B and the central axis of the upwind heat transfer pipe 22 is such that the distance between the penetrating part 71 of the leeward side eccentric pipe joint 42B. It is eccentric so as to be shorter than the distance between the central axis of one end 72 and the central axis of the windward heat transfer tube 22.

<Configuration of air conditioner to which heat exchanger is applied>
Below, the structure of the air conditioning apparatus to which the heat exchanger which concerns on Embodiment 1 is applied is demonstrated.
12 and 13 are diagrams showing a configuration of an air conditioner to which the heat exchanger according to Embodiment 1 is applied. In addition, FIG. 12 has shown the case where the air conditioning apparatus 91 performs heating operation. FIG. 13 shows a case where the air conditioner 91 performs a cooling operation.

As shown in FIGS. 12 and 13, the air conditioner 91 includes a compressor 92, a four-way valve 93, an outdoor heat exchanger (heat source side heat exchanger) 94, an expansion device 95, and an indoor heat exchanger. (Load side heat exchanger) 96, outdoor fan (heat source side fan) 97, indoor fan (load side fan) 98, and control device 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 by a refrigerant pipe to form a refrigerant circulation circuit. The four-way valve 93 may be another flow path switching device.

The outdoor heat exchanger 94 is the heat exchanger 1. The heat exchanger 1 is provided such that the laminated header 51 is disposed on the windward side of the air flow generated by driving the outdoor fan 97 and the cylindrical header 61 is disposed on the leeward side. The outdoor fan 97 may be provided on the leeward side of the heat exchanger 1 or may be provided on the leeward side of the heat exchanger 1.

For example, a compressor 92, a four-way valve 93, a throttle device 95, an outdoor fan 97, an indoor fan 98, various sensors, and the like are connected to the control device 99. By switching the flow path of the four-way valve 93 by the control device 99, the heating operation and the cooling operation are switched.

<Operation of heat exchanger and air conditioner>
Below, the operation | movement of the heat exchanger which concerns on Embodiment 1, and the air conditioning apparatus to which the heat exchanger is applied is demonstrated.
(Operation of heat exchanger and air conditioner during heating operation)
Hereinafter, the refrigerant flow during the heating operation will be described with reference to FIG.
The high-pressure and high-temperature gaseous refrigerant discharged from the compressor 92 flows into the indoor heat exchanger 96 through the four-way valve 93 and is condensed by heat exchange with the air supplied by the indoor fan 98. Heat up. The condensed refrigerant enters a high-pressure supercooled liquid state, flows out of the indoor heat exchanger 96, and becomes a low-pressure gas-liquid two-phase refrigerant by the expansion device 95. The low-pressure gas-liquid two-phase refrigerant flows into the outdoor heat exchanger 94, exchanges heat with the air supplied by the outdoor fan 97, and evaporates. The evaporated refrigerant enters a low-pressure superheated gas state, flows out of the outdoor heat exchanger 94, and is sucked into the compressor 92 through the four-way valve 93. That is, during the heating operation, the outdoor heat exchanger 94 acts as an evaporator.

In the outdoor heat exchanger 94, the refrigerant flows into the split flow channel 51 a of the laminated header 51 and is distributed, passes through the windward concentric pipe joint 41 A, and reaches the windward heat transfer tube 22 of the windward heat exchange unit 21. Flow into. The refrigerant flowing into the windward side heat transfer tube 22 sequentially passes through the windward side eccentric pipe joint 41B, the crossover pipe 43, and the leeward side eccentric pipe joint 42B, and flows into the leeward side heat transfer pipe 32 of the leeward side heat exchange section 31. To do. The refrigerant that has flowed into the leeward heat transfer pipe 32 passes through the leeward side concentric pipe joint 42 A, flows into the mixed flow passage 61 a of the tubular header 61, and is merged.

(Operation of heat exchanger and air conditioner during cooling operation)
Hereinafter, the flow of the refrigerant during the cooling operation will be described with reference to FIG.
The high-pressure and high-temperature gas refrigerant discharged from the compressor 92 flows into the outdoor heat exchanger 94 through the four-way valve 93, exchanges heat with the air supplied by the outdoor fan 97, and condenses. The condensed refrigerant enters a high-pressure supercooled liquid state or a low dryness state, flows out of the outdoor heat exchanger 94, and enters a low-pressure gas-liquid two-phase state by the expansion device 95. The low-pressure gas-liquid two-phase refrigerant flows into the indoor heat exchanger 96 and evaporates by heat exchange with the air supplied by the indoor fan 98, thereby cooling the room. The evaporated refrigerant becomes a low-pressure superheated gas state, flows out of the indoor heat exchanger 96, and is sucked into the compressor 92 through the four-way valve 93. That is, during the cooling operation, the outdoor heat exchanger 94 functions as a condenser.

In the outdoor heat exchanger 94, the refrigerant flows into the split flow passage 61 a of the cylindrical header 61 and is distributed, passes through the leeward concentric pipe joint 42 A, and passes through the leeward heat transfer tube 32 of the leeward heat exchanger 31. Flow into. The refrigerant that has flowed into the leeward heat transfer pipe 32 sequentially passes through the leeward eccentric pipe joint 42B, the crossover pipe 43, and the windward eccentric pipe joint 41B, and then flows into the windward heat transfer pipe 22 of the windward heat exchange section 21. To do. The refrigerant that has flowed into the windward heat transfer pipe 22 passes through the windward concentric pipe joint 41 A, flows into the mixed flow passage 51 a of the laminated header 51, and is merged.

<Operation of heat exchanger>
Below, the effect | action of the heat exchanger which concerns on Embodiment 1 is demonstrated.
In the heat exchanger 1, in the upwind eccentric pipe joint 41B and the downwind eccentric pipe joint 42B, the central axis of one end 72 and the central axis of the other end 73 are eccentric from each other. Therefore, each balance of the fluid which flows into the windward side heat exchanger tube 22 and the leeward side heat exchanger tube 32 is optimized.

FIG.14 and FIG.15 is a figure explaining the liquid quantity distribution of the refrigerant | coolant which flows in into a leeward heat exchanger tube when the heat exchanger which concerns on Embodiment 1 acts as an evaporator. In FIG. 14, the flow direction of the refrigerant is indicated by black arrows.
That is, when the heat exchanging unit 2 acts as an evaporator, as shown in FIGS. 14 and 15, the refrigerant is in a parallel flow with the air flow generated by driving the outdoor fan 97, that is, the wind It flows from the upper heat transfer tube 22 to the leeward heat transfer tube 32, and flows from the crossover tube 43 into the leeward eccentric tube joint 42B in a gas-liquid two-phase state. The refrigerant in the gas-liquid two-phase state that passes through the crossover pipe 43 is affected by the centrifugal force, so that a refrigerant having a high density flows outside and a refrigerant having a low density flows inside. Therefore, in the leeward side eccentric pipe joint 42B, when the amount of eccentricity Z between the central axis of the one end 72 and the central axis of the other end 73 is Z = 0, the leeward side eccentric pipe joint 42B The amount of liquid refrigerant that has flowed in flows more into the L point side of the leeward heat transfer tube 32 than at the S point side.

On the other hand, in the heat exchanger 1, in the leeward side eccentric pipe joint 42B, the eccentric amount Z between the central axis of one end 72 and the central axis of the other end 73 is Z> 0. A large amount of the liquid refrigerant that has flowed into the eccentric pipe joint 42 B flows into the S point side of the leeward heat transfer pipe 32. When the heat exchanger 1 acts as an evaporator, since the heat load (heat exchange amount) on the windward side of the air flow generated by driving the outdoor fan 97 is large, the S point side of the leeward heat transfer tube 32, that is, on the windward side. By distributing the liquid refrigerant to the flow path holes of the flat tube so that a large amount of liquid refrigerant flows in the flow path, evaporation of the liquid refrigerant is promoted and heat exchange efficiency is improved. Furthermore, the radius of curvature of the crossover tube 43 can be reduced, and the volume of the heat exchanging unit 2 can be increased, so that the heat exchange efficiency is further improved. And with the improvement in heat exchange efficiency, the operating efficiency of the refrigeration cycle is improved and the energy saving performance is improved. Moreover, it is also possible to save the space of the heat exchanger 1 while maintaining the performance of the refrigeration cycle.

FIG.16 and FIG.17 is a figure explaining the gas quantity distribution of the refrigerant | coolant which flows in into an upwind heat exchanger tube in case the heat exchanger which concerns on Embodiment 1 acts as a condenser. In FIG. 16, the flow direction of the refrigerant is indicated by black arrows.
In the case where the heat exchanging unit 2 acts as a condenser, as shown in FIGS. 16 and 17, the refrigerant is in a relationship opposite to the air flow generated by driving the outdoor fan 97, that is, downwind. It flows from the side heat transfer pipe 32 to the windward side heat transfer pipe 22, and flows from the row connecting pipe 43 into the windward side eccentric pipe joint 41B in a gas-liquid two-phase state. The refrigerant in the gas-liquid two-phase state that passes through the crossover pipe 43 is affected by the centrifugal force, so that a refrigerant having a high density flows outside and a refrigerant having a low density flows inside. Therefore, in the upwind eccentric pipe joint 41B, when the eccentric amount Z between the central axis of the one end 72 and the central axis of the other end 73 is Z = 0, the upwind eccentric pipe joint 41B A larger amount of the flowing liquid refrigerant flows into the L point side of the windward side heat transfer tube 22 as compared with the S point side.

On the other hand, in the heat exchanger 1, in the upwind eccentric pipe joint 41B, the eccentric amount Z between the central axis of one end 72 and the central axis of the other end 73 is Z> 0. The gas refrigerant that has flowed into the eccentric pipe joint 41 B flows into the L point side of the windward heat transfer tube 22 as much liquid refrigerant flows into the S point side. When the heat exchanger 1 acts as a condenser, since the heat load (heat exchange amount) on the windward side of the air flow generated by driving the outdoor fan 97 is large, the L point side of the windward heat transfer tube 22, that is, the windward side By distributing the gas refrigerant in the flow path hole of the flat tube so that a large amount of the gas refrigerant flows in the flow path, condensation of the gas refrigerant is promoted and heat exchange efficiency is improved. Furthermore, the radius of curvature of the crossover tube 43 can be reduced, and the volume of the heat exchanging unit 2 can be increased, so that the heat exchange efficiency is further improved. And with the improvement in heat exchange efficiency, the operating efficiency of the refrigeration cycle is improved and the energy saving performance is improved. Moreover, it is also possible to save the space of the heat exchanger 1 while maintaining the performance of the refrigeration cycle.

In the heat exchanger 1, in the windward concentric pipe joint 41A, the leeward concentric pipe joint 42A, the windward eccentric pipe joint 41B, and the leeward eccentric pipe joint 42B, the inner diameter in the major axis direction of one end 72 is set to W1. If the inner diameter in the minor axis direction is W2, the inner diameter D (D1, D2) in the entire circumferential direction of the cross-sectional shape of the other end 73 is W2 ≦ D ≦ W1, so that the size can be reduced and the pressure It is compatible with reducing the loss. Therefore, the space | interval of the heat exchange part 2 and the split mixing flow part 3 can be narrowed, the volume of the heat exchange part 2 can be expanded, and heat exchange efficiency is improved. And with the improvement in heat exchange efficiency, the operating efficiency of the refrigeration cycle is improved and the energy saving performance is improved. Moreover, it is also possible to save the space of the heat exchanger 1 while maintaining the performance of the refrigeration cycle.

In the heat exchanger 1, in the windward concentric pipe joint 41A, the leeward concentric pipe joint 42A, the windward eccentric pipe joint 41B, and the leeward eccentric pipe joint 42B, one end 72 and the other end of the penetrating part 71 are provided. A shape conversion portion 74 is formed in a region between the portions 73, and the connection pipe 57 of the laminated header 51, the connection pipe 64 of the cylindrical header 61, and the crossover pipe on the inner peripheral surface of the other end 73 Since the area | region where the outer peripheral surface of 43 is joined is adjacent to the shape conversion part 74, size reduction and reducing pressure loss are compatible. Therefore, the space | interval of the heat exchange part 2 and the split mixing flow part 3 can be narrowed, the volume of the heat exchange part 2 can be expanded, and heat exchange efficiency is improved. And with the improvement in heat exchange efficiency, the operating efficiency of the refrigeration cycle is improved and the energy saving performance is improved. Moreover, it is also possible to save the space of the heat exchanger 1 while maintaining the performance of the refrigeration cycle.

Embodiment 2. FIG.
A heat exchanger according to Embodiment 2 will be described.
Note that description overlapping or similar to that in Embodiment 1 is appropriately simplified or omitted.
<Configuration of heat exchanger>
Below, the structure of the heat exchanger which concerns on Embodiment 2 is demonstrated.
(Schematic configuration of heat exchanger)
Below, schematic structure of the heat exchanger which concerns on Embodiment 2 is demonstrated.
FIG. 18 is a perspective view of the heat exchanger according to the second embodiment.
As shown in FIG. 18, the heat exchanging unit 2 includes only the windward heat exchanging unit 21. The windward side heat transfer tubes 22 are arranged in a plurality of stages in a direction intersecting with the passage direction of air passing through the heat exchanging unit 2 (indicated by white arrows in the figure). Each of the plurality of windward side heat transfer tubes 22 is bent in a hairpin shape between one end and the other end to form a folded portion 22a. One end and the other end of each of the plurality of windward side heat transfer tubes 22 are juxtaposed so as to face the laminated header 51.

The laminated header 51 is connected to the windward heat exchanging unit 21, and a split flow channel 51 a is formed therein. When the heat exchange unit 2 acts as an evaporator, the split-mixing flow channel 51a distributes the refrigerant flowing from the refrigerant pipe (not shown) to the plurality of windward side heat transfer tubes 22 of the windward side heat exchange unit 21. It becomes an outflow distribution channel. When the heat exchange unit 2 acts as a condenser, the split flow channel 51a joins refrigerant flowing in from the plurality of windward side heat transfer tubes 22 of the windward side heat exchange unit 21 to a refrigerant pipe (not shown). It becomes the merging channel that flows out.

The cylindrical header 61 is connected to the windward heat exchange unit 21, and a split flow channel 61a is formed therein. When the heat exchange unit 2 acts as a condenser, the split flow channel 61a distributes the refrigerant flowing from the refrigerant pipe (not shown) to the plurality of windward heat transfer tubes 22 of the windward heat exchange unit 21. It becomes an outflow distribution channel. When the heat exchange unit 2 acts as an evaporator, the split-mixing flow channel 61a joins refrigerant flowing in from the plurality of windward side heat transfer tubes 22 of the windward side heat exchange unit 21 to a refrigerant pipe (not shown). It becomes the merging channel that flows out.

(Connection of heat exchange section and split mixing section)
Below, the connection of the heat exchange part of the heat exchanger which concerns on Embodiment 2, and a part mix flow part is demonstrated.
FIG.19 and FIG.20 is a figure explaining the connection of the heat exchange part and splitting flow part of the heat exchanger which concerns on Embodiment 2. FIG. FIG. 20 is a cross-sectional view taken along line BB in FIG.

19 and FIG. 20, the windward concentric pipe joint 41A is joined to one end 22b and the other end 22c of the windward heat transfer tube 22, respectively. The connection pipe 57 of the laminated header 51 is connected to the upwind concentric pipe joint 41 A joined to one end 22 b of the upwind heat transfer pipe 22. The connecting pipe 64 of the tubular header 61 is connected to the upwind concentric pipe joint 41A joined to the other end 22c of the upwind heat transfer pipe 22.

FIG. 21 is a diagram for explaining the connection of the heat exchange unit and the mixing and mixing unit in a modification of the heat exchanger according to the second embodiment. FIG. 21 is a cross-sectional view taken along the line BB in FIG.
As shown in FIG. 21, the other end portion 22 c of the windward side heat transfer tube 22 and one end portion 22 b of the windward side heat transfer tube 22 adjacent to the windward side heat transfer tube 22 are connected to the windward side step. You may connect using the pipe |

tube

44 and 41A of windward concentric pipe joints.

<Operation of heat exchanger and air conditioner>
Below, operation | movement of the heat exchanger which concerns on Embodiment 2, and the air conditioning apparatus to which the heat exchanger is applied is demonstrated.
(Operation of heat exchanger and air conditioner during heating operation)
FIG. 22 is a diagram illustrating a configuration of an air-conditioning apparatus to which the heat exchanger according to Embodiment 2 is applied. In addition, FIG. 22 has shown the case where the air conditioning apparatus 91 performs heating operation.
Hereinafter, the refrigerant flow during the heating operation will be described with reference to FIG.
In the outdoor heat exchanger 94, the refrigerant flows into the split flow channel 51 a of the laminated header 51 and is distributed, passes through the windward concentric pipe joint 41 A, and reaches the windward heat transfer tube 22 of the windward heat exchange unit 21. Flow into. The refrigerant that has flowed into the windward heat transfer pipe 22 passes through the windward concentric pipe joint 41 A, flows into the split flow passage 61 a of the tubular header 61, and is merged.

(Operation of heat exchanger and air conditioner during cooling operation)
FIG. 23 is a diagram illustrating a configuration of an air-conditioning apparatus to which the heat exchanger according to Embodiment 2 is applied. FIG. 23 shows a case where the air conditioner 91 performs a cooling operation.
Hereinafter, the flow of the refrigerant during the cooling operation will be described with reference to FIG.
In the outdoor heat exchanger 94, the refrigerant flows into the split flow passage 61 a of the cylindrical header 61 and is distributed, passes through the windward concentric pipe joint 41 A, and passes through the windward heat transfer tube 22 of the windward heat exchange unit 21. Flow into. The refrigerant that has flowed into the windward heat transfer pipe 22 passes through the windward concentric pipe joint 41 A, flows into the mixed flow passage 51 a of the laminated header 51, and is merged.

<Operation of heat exchanger>
Below, the effect | action of the heat exchanger which concerns on Embodiment 2 is demonstrated.
In the heat exchanger 1, as in the heat exchanger 1 according to the first embodiment, in the upwind concentric pipe joint 41A, the inner diameter in the major axis direction of one end 72 is W1, and the inner diameter in the minor axis direction is W2. Then, since the inner diameter D (D1, D2) in the entire circumferential direction of the cross-sectional shape of the other end portion 73 is W2 ≦ D ≦ W1, both downsizing and reduction in pressure loss are compatible. The Therefore, the space | interval of the heat exchange part 2 and the split mixing flow part 3 can be narrowed, the volume of the heat exchange part 2 can be expanded, and heat exchange efficiency is improved. And with the improvement in heat exchange efficiency, the operating efficiency of the refrigeration cycle is improved and the energy saving performance is improved. Moreover, it is also possible to save the space of the heat exchanger 1 while maintaining the performance of the refrigeration cycle.

Further, in the heat exchanger 1, similarly to the heat exchanger 1 according to Embodiment 1, in the upwind concentric pipe joint 41 A, a region between one end 72 and the other end 73 of the penetrating portion 71. The region where the shape conversion part 74 is formed and the outer peripheral surface of the connection pipe 57 of the laminated header 51 and the connection pipe 64 of the cylindrical header 61 is joined to the inner peripheral surface of the other end 73 is the shape conversion. Since it is adjacent to the portion 74, it is possible to achieve both a reduction in size and a reduction in pressure loss. Therefore, the space | interval of the heat exchange part 2 and the split mixing flow part 3 can be narrowed, the volume of the heat exchange part 2 can be expanded, and heat exchange efficiency is improved. And with the improvement in heat exchange efficiency, the operating efficiency of the refrigeration cycle is improved and the energy saving performance is improved. Moreover, it is also possible to save the space of the heat exchanger 1 while maintaining the performance of the refrigeration cycle.

As mentioned above, although Embodiment 1 and Embodiment 2 were demonstrated, this invention is not limited to description of each embodiment. For example, it is possible to combine all or some of the embodiments.

DESCRIPTION OF SYMBOLS 1 Heat exchanger, 2 Heat exchange part, 3 Mixing flow part, 21 Upwind heat exchange part, 22 Upwind heat exchanger tube, 22a Folding part, 22b One end, 22c The other end, 23 Upwind fin, 31 Leeward heat exchange section, 32 leeward heat transfer tube, 32a folded section, 32b one end, 32c other end, 33 leeward fin, 41A leeward concentric pipe joint, 41B leeward eccentric pipe joint, 42A leeward side Concentric pipe joint, 42B leeward side eccentric pipe joint, 43 crossover pipe, 44 upwind side crossover pipe, 45 leeward side crossover pipe, 51 laminated header, 51a mixed flow path, 52, 57 connecting pipe, 53 1st Plate member, 54_1 to 54_3, second plate member, 55, third plate member, 56_1 to 56_4, clad material, 53a, 54a_1 to 54a_3, 55a, 56a Dividing channel, 61 cylinder header, 61a mixing flow channel, 62, 64 connecting pipe, 63 cylindrical part, 71 penetrating part, 72 one end part, 73 other end part, 74 shape converting part, 91 air conditioner, 92 compressor, 93 four-way valve, 94 outdoor heat exchanger, 95 throttle device, 96 indoor heat exchanger, 97 outdoor fan, 98 indoor fan, 99 control device.

Claims

A pipe joint in which a penetration part is formed, a flat tube is connected to one end of the penetration part, and another pipe having a different cross-sectional shape from the flat pipe is connected to the other end of the penetration part. ,
The central axis of the one end and the central axis of the other end are eccentric from each other;
A pipe joint characterized by that.
The inner diameter D of the other end portion in the cross section perpendicular to the central axis is not more than the inner diameter W1 in the major axis direction and not less than the inner diameter W2 in the minor axis direction of the one end portion. ,
The pipe joint according to claim 1.
The outer peripheral surface of the flat tube is joined to the inner peripheral surface of the one end,
The outer peripheral surface of the other pipe is joined to the inner peripheral surface of the other end,
In the region between the one end and the other end of the penetrating portion, the cross-sectional shape of the inner peripheral surface of the one end is continuous with the cross-sectional shape of the inner peripheral surface of the other end. A shape changing portion that is changed in an automatic manner,
The area of the inner peripheral surface of the other end where the outer peripheral surface of the other pipe is joined is adjacent to the shape conversion unit,
The pipe joint according to claim 1 or 2, characterized by the above-mentioned.
A pipe joint in which a penetration part is formed, a flat tube is connected to one end of the penetration part, and another pipe having a different cross-sectional shape from the flat pipe is connected to the other end of the penetration part. ,
The outer peripheral surface of the flat tube is joined to the inner peripheral surface of the one end,
The outer peripheral surface of the other pipe is joined to the inner peripheral surface of the other end,
In the region between the one end and the other end of the penetrating portion, the cross-sectional shape of the inner peripheral surface of the one end is continuous with the cross-sectional shape of the inner peripheral surface of the other end. A shape changing portion that is changed in an automatic manner,
The area of the inner peripheral surface of the other end where the outer peripheral surface of the other pipe is joined is adjacent to the shape conversion unit,
A pipe joint characterized by that.
The pipe joint according to any one of claims 1 to 3,
A heat exchanging section having the flat tube with at least one end connected to the one end of the pipe joint, and another flat tube disposed on the windward side or leeward side of the flat tube; ,
With
The other end of the pipe joint connected to the flat tube and the other flat tube are connected by a crossover tube,
The distance between the central axis of the other end of the pipe joint connected to the flat pipe and the central axis of the other flat pipe is the one of the pipe joints connected to the flat pipe Shorter than the distance between the central axis of the end of the other and the central axis of the other flat tube,
A heat exchanger characterized by that.
When the heat exchange part acts as an evaporator,
The other flat tube is disposed on the windward side of the flat tube,
The heat exchanger according to claim 5.
When the heat exchange part acts as a condenser,
The other flat tube is disposed on the leeward side of the flat tube,
The heat exchanger according to claim 5 or 6 characterized by things.
A pipe joint in which a penetration part is formed, a flat tube is connected to one end of the penetration part, and another pipe having a different cross-sectional shape from the flat pipe is connected to the other end of the penetration part;
The flat tube having at least one end connected to the one end of the pipe joint, and a heat exchange section disposed on the leeward side and the leeward side;
Connected to the heat exchanging unit, a header disposed on the leeward side and a header disposed on the leeward side;
With
The other end of the pipe joint connected to the flat tube disposed on the leeward side, and the other end of the pipe joint connected to the flat tube disposed on the leeward side; Are connected by a crossover tube,
The crossover tube is disposed between the heat exchange unit, a header disposed on the leeward side, and a header disposed on the leeward side,
In the pipe joint, an inner diameter D of the other end portion in a cross section perpendicular to the central axis is equal to or less than an inner diameter W1 in the major axis direction of the one end portion, and in the minor axis direction. An inner diameter W2 or more,
A heat exchanger characterized by that.
The cross-sectional area of the crossover tube is larger than the cross-sectional area of the flat tube,
The heat exchanger according to any one of claims 5 to 8, wherein
A pipe joint according to claim 4;
A heat exchanging portion provided with the flat tube with at least one end connected to the one end of the pipe joint;
A distribution flow path for distributing and flowing out the refrigerant, or a merge flow path for combining and flowing out the refrigerant is formed, and the other end of the pipe joint is connected to the connecting pipe on the outlet side of the distribution flow path or the A header to which a connecting pipe on the inlet side of the confluence channel is connected;
A heat exchanger characterized by comprising:
A pipe joint in which a penetration part is formed, a flat tube is connected to one end of the penetration part, and another pipe having a different cross-sectional shape from the flat pipe is connected to the other end of the penetration part;
A heat exchanging portion provided with the flat tube with at least one end connected to the one end of the pipe joint;
A distribution flow path for distributing and flowing out the refrigerant, or a merge flow path for combining and flowing out the refrigerant is formed, and the other end of the pipe joint is connected to the connecting pipe on the outlet side of the distribution flow path or the A header to which a connecting pipe on the inlet side of the confluence channel is connected;
With
In the pipe joint, an inner diameter D of the other end portion in a cross section perpendicular to the central axis is equal to or less than an inner diameter W1 in the major axis direction of the one end portion, and in the minor axis direction. An inner diameter W2 or more,
A heat exchanger characterized by that.
The cross-sectional area of the connecting pipe is larger than the cross-sectional area of the flat tube,
The heat exchanger according to claim 10 or 11, characterized in that.
A heat exchanger according to any one of claims 5 to 12 is provided.
An air conditioner characterized by that.