JPWO2014184913A1 - Laminated header, heat exchanger, and air conditioner - Google Patents

Abstract

The laminated header 2 according to the present invention includes a first plate 11 having a plurality of first outlet channels 11A, and a refrigerant that is stacked on the first plate 11 and flows from the first inlet channel 12a. And a second plate-like body 12 in which a distribution channel 12A is formed to distribute and flow out to a plurality of first outlet channels 11A, and the distribution channel 12A includes at least one branch channel 12b, The second plate-like body 12 has at least one first plate-like member in which at least one first projecting portion is formed by press working, and the branch channel 12b has a refrigerant inside the first projecting portion. It is formed by closing regions other than the region where the refrigerant flows and the region where the refrigerant flows.

Description

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

  As a conventional laminated header, a first plate-like body in which a plurality of outlet channels are formed, and a refrigerant that is stacked on the first plate-like body and flows in from the inlet channel is formed in the first plate-like body. And a second plate-like body in which a distribution channel that distributes and flows out to a plurality of outlet channels is formed. The distribution flow path includes a branch flow path having a plurality of grooves perpendicular to the refrigerant inflow direction. The refrigerant flowing into the branch channel from the inlet channel is branched into a plurality by passing through the plurality of grooves, and flows out through the plurality of outlet channels formed in the first plate-like body (for example, patents). Reference 1).

JP 2000-161818 (paragraph [0012] to paragraph [0020], FIG. 1 and FIG. 2)

  In such a laminated header, it is necessary to reduce the cross-sectional area of the plurality of grooves in order to reduce the component cost and weight by thinning the plate-like member constituting the second plate-like body. In such a case, the pressure loss of the refrigerant passing through the plurality of grooves increases. In other words, the conventional laminated header has a problem that it is difficult to realize reduction in parts cost, weight reduction, and the like while suppressing an increase in pressure loss of the refrigerant.

  The present invention has been made against the background of the above problems, and is to obtain a multilayer header capable of realizing reduction in parts cost, weight reduction, etc. while suppressing an increase in refrigerant pressure loss. Objective. Moreover, an object of this invention is to obtain the heat exchanger provided with such a laminated header. Moreover, an object of this invention is to obtain the air conditioning apparatus provided with such a heat exchanger.

  The laminated header according to the present invention includes a first plate body in which a plurality of first outlet channels are formed, and a refrigerant that is stacked on the first plate body and flows in from the first inlet channel. A second plate-like body formed with a distribution channel that is distributed to the first outlet channel and flows out, and the distribution channel includes at least one branch channel, and the second plate-like body includes: The at least one first protrusion has at least one first plate-like member formed by press working, and the branch channel has a region where the refrigerant flows in and the inside of the first protrusion. It is formed by closing the region other than the region where the refrigerant flows out.

  In the multi-layer header according to the present invention, the distribution flow path includes at least one branch flow path, the second plate-shaped body, at least one first protrusion is formed by pressing. A branch channel is formed by closing a region other than the region where the refrigerant flows in and the region where the refrigerant flows out inside the first protrusion. Therefore, even if the first plate-like member is thinned, the cross-sectional area of the branch flow path can be secured, and it is possible to realize a reduction in parts cost, weight reduction, etc. while suppressing an increase in refrigerant pressure loss. It is.

It is a figure which shows the structure of the heat exchanger which concerns on Embodiment 1. FIG. It is a perspective view in the state which decomposed | disassembled the laminated header of the heat exchanger which concerns on Embodiment 1. FIG. It is sectional drawing in the state which laminated | stacked the laminated header of the heat exchanger which concerns on Embodiment 1. FIG. It is sectional drawing in the state which laminated | stacked the laminated header of the heat exchanger which concerns on Embodiment 1. FIG. It is the perspective view and sectional drawing of the principal part in the state which decomposed | disassembled the laminated header of the heat exchanger which concerns on Embodiment 1. FIG. It is the perspective view and sectional drawing of the principal part in the state which decomposed | disassembled the laminated header of the heat exchanger which concerns on Embodiment 1. FIG. FIG. 3 is a development view of a stacked header of the heat exchanger according to the first embodiment. 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 perspective view in the state which decomposed | disassembled the laminated header of the modification-1 of the heat exchanger which concerns on Embodiment 1. FIG. It is sectional drawing in the state which laminated | stacked the laminated header of the modification-1 of the heat exchanger which concerns on Embodiment 1. FIG. It is an expanded view of the laminated header of the modification-1 of the heat exchanger which concerns on Embodiment 1. FIG. It is the perspective view of the principal part in the state which decomposed | disassembled the laminated header of the modification-2 of the heat exchanger which concerns on Embodiment 1, and sectional drawing of the principal part. It is a perspective view in the state which decomposed | disassembled the laminated header of the modification-3 of the heat exchanger which concerns on Embodiment 1. FIG. It is a perspective view in the state which decomposed | disassembled the laminated header of the modification-4 of the heat exchanger which concerns on Embodiment 1. FIG. It is a figure which shows the structure of the heat exchanger which concerns on Embodiment 2. FIG. It is a perspective view in the state which decomposed | disassembled the laminated header of the heat exchanger which concerns on Embodiment 2. FIG. It is an expanded view of the laminated header 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 heat exchanger which concerns on Embodiment 3. FIG. It is a perspective view in the state which decomposed | disassembled the laminated header of the heat exchanger which concerns on Embodiment 3. FIG. 6 is a development view of a stacked header of a heat exchanger according to Embodiment 3. FIG. It is a figure which shows the structure of the air conditioning apparatus to which the heat exchanger which concerns on Embodiment 3 is applied.

Hereinafter, the laminated header according to the present invention will be described with reference to the drawings.
In the following, the case where the laminated header according to the present invention distributes the refrigerant flowing into the heat exchanger is described, but the laminated header according to the present invention flows into other devices. A refrigerant may be distributed. Further, the configuration, operation, and the like described below are merely examples, and are not limited to such configuration, operation, and the like. 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.

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.
FIG. 1 is a diagram illustrating a configuration of a heat exchanger according to the first embodiment.
As shown in FIG. 1, the heat exchanger 1 includes a stacked header 2, a header 3, a plurality of first heat transfer tubes 4, and a plurality of fins 5.

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

  The first heat transfer tube 4 is a flat tube in which a plurality of flow paths are formed. The first heat transfer tube 4 is made of, for example, aluminum. The ends of the plurality of first heat transfer tubes 4 on the stacked header 2 side are connected to the plurality of refrigerant outflow portions 2 </ b> B of the stacked header 2. The plurality of refrigerant outflow portions 2B of the multilayer header 2 may be connected in a state where the end portions of the plurality of first heat transfer tubes 4 on the multilayer header 2 side are held by a plate-like holding member. A plurality of fins 5 are joined to the first heat transfer tube 4. The fin 5 is made of, for example, aluminum. The first heat transfer tube 4 and the fin 5 may be joined by brazing. In addition, although the case where the 1st heat exchanger tube 4 is eight is shown in FIG. 1, it is not limited to such a case. Moreover, it is not limited to when the 1st heat exchanger tube 4 is a flat tube.

<Flow of refrigerant in heat exchanger>
Below, the flow of the refrigerant in the heat exchanger according to Embodiment 1 will be described.
The refrigerant flowing through the refrigerant pipe flows into the stacked header 2 through the refrigerant inflow portion 2A and is distributed, and flows out to the plurality of first heat transfer tubes 4 through the plurality of refrigerant outflow portions 2B. The refrigerant exchanges heat with, for example, air supplied by a fan in the plurality of first heat transfer tubes 4. The refrigerant flowing through the plurality of first heat transfer tubes 4 flows into and merges with the header 3 through the plurality of refrigerant inflow portions 3A, and flows out into the refrigerant pipe through the refrigerant outflow portion 3B. The refrigerant can flow backward.

<Configuration of laminated 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.
As shown in FIG. 2, the stacked header 2 includes a first plate-like body 11 and a second plate-like body 12. The first plate-like body 11 and the second plate-like body 12 are stacked.

  The first plate-like body 11 is stacked on the refrigerant outflow side. The first plate-like body 11 includes a first plate-like member 21 and a second plate-like member 22. In the first plate-like body 11, a plurality of first outlet channels 11A are formed. The plurality of first outlet channels 11A correspond to the plurality of refrigerant outflow portions 2B in FIG.

  The second plate-like body 12 is stacked on the refrigerant inflow side. The second plate-like body 12 includes a third plate-like member 23 and a plurality of fourth plate-like members 24_1 to 24_3. A distribution channel 12A is formed in the second plate-like body 12. The distribution flow path 12A includes a first inlet flow path 12a and a plurality of branch flow paths 12b. The first inlet channel 12a corresponds to the refrigerant inflow portion 2A in FIG.

  The first plate-like member 21 has a first protrusion 21A and a second protrusion 21B that are formed by pressing such as drawing and bending, and protrude toward the refrigerant inflow side. . The first protruding portion 21A has a bottom, and in a state where the first plate-like member 21 is laminated, a part of the inner surface 21a functions as a part of the first outlet channel 11A, and a part of the outer surface 21b It functions as a part of the branch flow path 12b. The 2nd protrusion part 21B has a bottom, and functions as a junction reinforcement part in the state in which the 1st plate-shaped member 21 was laminated | stacked. The first plate member 21 is made of, for example, aluminum.

  The second plate-like member 22 includes a first protrusion 22A and a second protrusion 22B that are formed by pressing such as drawing and bending, and protrude toward the refrigerant inflow side. . 22 A of 1st protrusion parts do not have a bottom, and the inner surface 22a functions as a junction part with the 1st heat exchanger tube 4 in the state in which the 2nd plate-shaped member 22 was laminated | stacked. The 2nd protrusion part 22B has a bottom, and functions as a junction reinforcement part in the state in which the 2nd plate-shaped member 22 was laminated | stacked. The second plate member 22 is made of, for example, aluminum.

  The inner surface 21 a of the first protrusion 21 </ b> A of the first plate member 21 and the inner surface 22 a of the first protrusion 22 </ b> A of the second plate member 22 are shaped along the outer peripheral surface of the first heat transfer tube 4. The outer peripheral surface of the first heat transfer tube 4 is joined to the inner surface 22a of the first protrusion 22A of the second plate-like member 22 by, for example, brazing or bonding. The bottom of the first projecting portion 21A of the first plate member 21 and the end surface of the first heat transfer tube 4 have a gap in the joined state.

  The third plate-like member 23 is formed by press working such as drawing or bending, and has a first projecting portion 23A that projects toward the side into which the refrigerant flows. 23 A of 1st protrusion parts do not have a bottom, and the inner surface 23a functions as the 1st inlet flow path 12a in the state in which the 3rd plate-shaped member 23 was laminated | stacked. The third plate member 23 is made of, for example, aluminum.

  The inner surface 23a of the first protrusion 23A of the third plate member 23 has a shape along the outer peripheral surface of the refrigerant pipe. The outer peripheral surface of the refrigerant pipe is joined to the inner surface 23a of the first protrusion 23A of the third plate-like member 23 by, for example, brazing or bonding. A base or the like may be attached to the outer surface of the first projecting portion 23A of the third plate-like member 23, and the refrigerant pipe may be connected through the base or the like.

  The fourth plate members 24_1 to 24_3 are formed by pressing such as drawing and bending, and protrude toward the refrigerant inflow side, and the first protrusions 24A_1 to 24A_3 and the second protrusions 24B_1. To 24B_3. The first protrusion 24A_1 of the fourth plate member 24_1 has a bottom, and the inner surface 24a_1 functions as a part of the branch flow path 12b in a state where the fourth plate member 24_1 is stacked. The first protrusions 24A_2 and 24A_3 of the fourth plate members 24_2 and 24_3 have a bottom, and the inner surfaces 24a_2 and 24a_3 and the outer surfaces 24b_2 and 24b_3 branch in a state where the fourth plate members 24_2 and 24_3 are stacked. It functions as a part of the path 12b. The second protrusions 24B_1 to 24B_3 have a bottom and function as a joint reinforcement in a state where the fourth plate-like members 24_1 to 24_3 are stacked. The fourth plate-like members 24_1 to 24_3 are made of, for example, aluminum.

  Hereinafter, the fourth plate-like members 24_1 to 24_3 may be collectively referred to as the fourth plate-like member 24 in some cases. Hereinafter, the first protrusions 24A_1 to 24A_3 of the fourth plate-like member 24 may be collectively referred to as the first protrusion 24A. The inner surfaces 24a_1 to 24a_3 of the first protrusion 24A of the fourth plate member 24 may be collectively referred to as an inner surface 24a. The outer surfaces 24b_1 to 24b_3 of the first protrusion 24A of the fourth plate member 24 may be collectively referred to as the outer surface 24b. The second protrusions 24B_1 to 24B_3 of the fourth plate member 24 may be collectively referred to as a second protrusion 24B. Below, the 1st plate-shaped member 21, the 2nd plate-shaped member 22, the 3rd plate-shaped member 23, and the 4th plate-shaped member 24 may be named generically, and may be described as a plate-shaped member. The fourth plate member 24 corresponds to the “first plate member” of the present invention.

3 and 4 are cross-sectional views of the heat exchanger according to Embodiment 1 in a state in which stacked headers are stacked. 3 shows a cross-sectional view taken along the line AA in FIG. 2, and FIG. 4 shows a cross-sectional view taken along the line BB in FIG. In FIG.3 and FIG.4, the part into which a refrigerant | coolant flows is shown with the oblique line.
As shown in FIGS. 3 and 4, the periphery of the plate-like member is bent in the stacking direction, and the tip of the periphery is joined to the side surface of the plate-like member that is stacked adjacent to the side into which the refrigerant flows. Is done.

  Further, it is formed on the inner surface 24a of the first projecting portion 24A formed on the fourth plate-like member 24 and the fourth plate-like member 24 or the first plate-like member 21 stacked adjacent to the refrigerant outflow side. Further, each branch flow path 12b is formed by joining the outer surfaces 24b and 21b of the first projecting portions 24A and 21A in a fitted state.

  Further, the inner surface of the second projecting portions 21B and 24B formed on the first plate-like member 21 or the fourth plate-like member 24 and the second plate-like member 22 stacked adjacent to the side from which the refrigerant flows out, the second The reinforcing portion is formed by joining the outer surfaces of the first plate member 21 or the second projecting portions 22B, 21B, and 24B of the fourth plate member 24 in a fitted state. The outer surface of the second protrusion 24B_1 of the fourth plate member 24_1 is joined to the surface of the third plate member 23.

  5 and 6 are a perspective view and a cross-sectional view of the main part of the heat exchanger according to Embodiment 1 in a state where the stacked header is disassembled. 5 and 6 are a perspective view and a cross-sectional view of the portion X in FIG. FIG. 5B shows a cross-sectional view taken along the line CC in FIG. 5A, and FIG. 6B shows a cross-sectional view taken along the line DD in FIG. 6A. In FIG. 5B and FIG. 6B, the portion into which the refrigerant flows is indicated by hatching. In the following, the branch flow path 12b formed by the inner surface 24a_3 of the first protrusion 24A_3 of the fourth plate member 24_3 and the outer surface 21b of the first protrusion 21A of the first plate member 21 will be described. However, the same applies to the other branch flow paths 12b.

  As shown in FIG. 5, the Z-shaped region of the first protrusion 24A_3 of the fourth plate member 24_3 (hereinafter, the Z-shaped region of the plate-like member on the side into which the refrigerant flows is generically named, The inner surface of the inflow side Z-shaped region 12b_1a (hereinafter, the inner surface of the inflow side Z-shaped region 12b_1a is collectively referred to as the inner surface 12b_1b), and the first protrusion 21A of the first plate member 21. The outer surface (hereinafter referred to as the outflow side Z-shaped region) of the Z-shaped region (hereinafter, the Z-shaped region of the plate-like member on the refrigerant outflow side is collectively referred to as the outflow side Z-shaped region 12b_2a). The outer surface of 12b_2a is collectively referred to as the outer surface 12b_2b) and joined in a fitted state to form the branch flow path 12b.

  The inflow side Z-shaped region 12b_1a has a shape that connects the two end portions 12b_1c and 12b_1d via a straight line portion 12b_1e perpendicular to the gravity direction. A through hole 12b_1f is formed at the center of the inflow side Z-shaped region 12b_1a. The peripheral portions 12b_1h and 12b_1i of the two end portions 12b_1c and 12b_1d of the inflow side Z-shaped region 12b_1a on the surface of the fourth plate-like member 24_3 protrude to the side where the refrigerant flows out.

  The outflow side Z-shaped region 12b_2a has a shape connecting the two end portions 12b_2c and 12b_2d via a straight line portion 12b_2e perpendicular to the direction of gravity. Through holes 12b_2f and 12b_2g are formed in the two end portions 12b_2c and 12b_2d of the outflow side Z-shaped region 12b_2a, respectively. The peripheral portions 12b_2h and 12b_2i of the two end portions 12b_2c and 12b_2d of the outflow side Z-shaped region 12b_2a of the first projecting portion 21A of the first plate-like member 21 are recessed toward the refrigerant outflow side.

  The peripheral portions 12b_1h and 12b_1i that protrude toward the refrigerant outflow side and the peripheral portions 12b_2h and 12b_2i that are recessed toward the refrigerant outflow side are joined in a fitted state so that they flow into the through hole 12b_1f. The refrigerant branched into two passes through between the inner surface 12b_1b of the inflow side Z-shaped region 12b_1a and the outer surface 12b_2b of the outflow side Z-shaped region 12b_2a and flows out of the through holes 12b_2f and 12b_2g without leaking.

  A protrusion 12b_2j is formed below the center of the outflow side Z-shaped region 12b_2a in the drawing. The protrusion 12b_2j is connected to the inner surface of the outflow side Z-shaped region 12b_2a of the other branch passage 12b that communicates with the lower side of the center of the inflow side Z-shaped region 12b_1a and is adjacent to the refrigerant outflow side. The refrigerant that is joined and flows in from the through hole 12b_1f is prevented from leaking from the branch flow path 12b through the inner surface of the outflow side Z-shaped region 12b_2a of the other branch flow path 12b adjacent to the refrigerant flow-out side. In addition, the inner surface of the outflow side Z-shaped region 12b_2a of another branch flow path 12b adjacent to the refrigerant outflow side may be blocked by another method.

  As shown in FIG. 6, peripheral portions 12b_1h and 12b_1i protruding to the refrigerant outflow side are recessed to the refrigerant inflow side, and peripheral portions 12b_2h and 12b_2i recessed to the refrigerant outflow side are inflow of the refrigerant. You may project to the side. Even in such a case, the peripheral portions 12b_1h and 12b_1i that are recessed toward the refrigerant inflow side and the peripheral portions 12b_2h and 12b_2i that protrude toward the refrigerant inflow side are joined in a fitted state, so that a through hole is obtained. The refrigerant that has flowed in from 12b_1f and branched into two passes between the inner surface 12b_1b of the inflow side Z-shaped region 12b_1a and the outer surface 12b_2b of the outflow side Z-shaped region 12b_2a without leaking, and passes through the through holes 12b_2f, It flows out of 12b_2g.

  That is, the branch flow path 12b branches the refrigerant flowing into two and flows out. Therefore, when there are eight first heat transfer tubes 4 connected, at least three fourth plate-like members 24 are required. When 16 first heat transfer tubes 4 are connected, at least four fourth plate members 24 are required. The number of connected first heat transfer tubes 4 is not limited to a power of 2. In such a case, the branched flow path 12b and the non-branched flow path may be combined. Two first heat transfer tubes 4 may be connected.

  Further, in order to branch out the refrigerant flowing into different heights and flow out, the end portion 12b_1c of the inflow side Z-shaped region 12b_1a, the end portion 12b_2c of the outflow side Z-shaped region 12b_2a, and the end portion of the inflow side Z-shaped region 12b_1a 12b_1d and the end 12b_2d of the outflow side Z-shaped region 12b_2a are located at different heights. In particular, one is on the upper side compared to the straight line portion 12b_1e of the inflow side Z-shaped region 12b_1a and the straight line portion 12b_2e of the outflow side Z-shaped region 12b_2a, and the other is the straight line portion 12b_1e and the outflow side of the inflow side Z-shaped region 12b_1a. In the case of being on the lower side compared to the straight portion 12b_2e of the Z-shaped region 12b_2a, the shape of the deviation of each distance from the through hole 12b_1f to the through hole 12b_2f and the through hole 12b_2g along the branch flow path 12b is formed. The size can be reduced without complication. Since the straight line connecting the through hole 12b_2f and the through hole 12b_2g is parallel to the longitudinal direction of the plate-like member, it is possible to reduce the dimension in the short direction of the plate-like member, thereby reducing component costs, weight, etc. Is done. Furthermore, since the straight line connecting the through hole 12b_2f and the through hole 12b_2g is parallel to the arrangement direction of the first heat transfer tubes 4, the heat exchanger 1 is saved in space.

  The stacked header 2 is not limited to one in which the plurality of first outlet channels 11A are arranged along the direction of gravity. For example, a wall-mounted room air conditioner indoor unit, an air conditioner outdoor unit, a chiller outdoor unit It may be used when the heat exchanger 1 is disposed at an inclination like a heat exchanger such as a machine. In such a case, the straight portion 12b_1e and the straight portion 12b_2e may be the inflow side Z-shaped region 12b_1a and the outflow side Z-shaped region 12b_2a that are not perpendicular to the longitudinal direction of the plate-like member.

  Further, the branch channel 12b may have other shapes. That is, it does not have to be Z-shaped. For example, the inflow side Z-shaped region 12b_1a and the outflow side Z-shaped region 12b_2a do not have to include the straight portion 12b_1e and the straight portion 12b_2e. In the case where the straight portion 12b_1e and the straight portion 12b_2e are provided, when the refrigerant flows from the through hole 12b_1f and branches into two, it is difficult to be affected by gravity. That is, regardless of the flow rate and the dryness of the refrigerant in the gas-liquid two-phase state that flows in, it becomes difficult to be affected by gravity, and the flow rate and the dryness of the refrigerant flowing into each of the first heat transfer tubes 4 can be made uniform. It becomes possible. Further, for example, the inflow side Z-shaped region 12b_1a and the outflow side Z-shaped region 12b_2a may have a branched shape. When the inflow side Z-shaped region 12b_1a and the outflow side Z-shaped region 12b_2a are not branched, the uniformity of refrigerant distribution can be improved.

  Each plate-like member is preferably laminated by brazing joint. By laminating by brazing and joining, the plate-like members are laminated without gaps, leakage of the refrigerant is suppressed, and pressure resistance is ensured. In the case of brazing and joining the plate-like members while applying pressure, the occurrence of brazing defects is further suppressed. In the case where processing that promotes the formation of fillets, such as formation of ribs, is performed at locations where refrigerant leakage is likely to occur, the occurrence of brazing defects is further suppressed.

  Furthermore, when all the members to be brazed including the first heat transfer tube 4 and the fins 5 are made of the same material (for example, made of aluminum), it is possible to braze and join together. , Productivity is improved. The brazing of the first header tube 4 and the fins 5 may be performed after the laminated header 2 is brazed. Alternatively, only the first plate 11 may be brazed to the first heat transfer tube 4 first, and the second plate 12 may be brazed afterwards.

<Refrigerant flow in stacked header>
Hereinafter, the flow of the refrigerant in the stacked header of the heat exchanger according to Embodiment 1 will be described.
FIG. 7 is a development view of the stacked header of the heat exchanger according to the first embodiment.
As shown by arrows in FIGS. 2 and 7, the refrigerant that has passed through the first protrusion 23A of the third plate member 23 is a through hole formed in the first protrusion 24A_1 of the fourth plate member 24_1. That is, it flows into the inside of the first protrusion 24A_1 of the fourth plate-like member 24_1 through the through hole 12b_1f of the inflow side Z-shaped region 12b_1a. The refrigerant hits the protruding portion of the adjacent stacked members and branches into two. The branched refrigerant passes between the inner surface 12b_1b of the inflow side Z region 12b_1a and the outer surface 12b_2b of the outflow side Z region 12b_2a, and is a through hole formed in the first protrusion 24A_2 of the fourth plate member 24_2. That is, it passes through the through holes 12b_2f and 12b_2b of the outflow side Z-shaped region 12b_2a.

  The refrigerant that has passed through the through hole formed in the first protrusion 24A_2 of the fourth plate member 24_2, that is, the through hole 12b_1f of the inflow side Z-shaped region 12b_1a of the adjacent branch flow path 12b, is transferred to the fourth plate member 24_2. It flows into the inside of the formed first protrusion 24A_2. The refrigerant hits the protruding portion of the adjacent stacked members and branches into two. The branched refrigerant passes between the inner surface 12b_1b of the inflow side Z region 12b_1a and the outer surface 12b_2b of the outflow side Z region 12b_2a, and is a through hole formed in the first protrusion 24A_3 of the fourth plate member 24_3. That is, it passes through the through holes 12b_2f and 12b_2b of the outflow side Z-shaped region 12b_2a.

  The refrigerant that has passed through the through hole formed in the first protruding portion 24A_3 of the fourth plate member 24_3, that is, the through hole 12b_1f of the inflow side Z-shaped region 12b_1a of the adjacent branch flow path 12b, enters the fourth plate member 24_3. It flows into the inside of the formed first protrusion 24A_3. The refrigerant hits the protruding portion of the adjacent stacked members and branches into two. The branched refrigerant passes between the inner surface 12b_1b of the inflow side Z-shaped region 12b_1a and the outer surface 12b_2b of the outflow side Z-shaped region 12b_2a, and is a through hole formed in the first protruding portion 21A of the first plate member 21. That is, it passes through the through holes 12b_2f and 12b_2b of the outflow side Z-shaped region 12b_2a.

  The refrigerant that has passed through the through hole formed in the first protrusion 21 </ b> A of the first plate member 21 passes through the first protrusion 22 </ b> A of the second plate member 22 and flows into the first heat transfer tube 4.

<Usage of heat exchanger>
Below, an example of the usage aspect of the heat exchanger which concerns on Embodiment 1 is demonstrated.
In addition, although the case where the heat exchanger which concerns on Embodiment 1 is used for an air conditioning apparatus is demonstrated below, it is not limited to such a case, For example, the other refrigeration cycle which has a refrigerant circulation circuit It may be used in the device. Moreover, although the case where an air conditioning apparatus switches between cooling operation and heating operation is demonstrated, it is not limited to such a case, You may perform only cooling operation or heating operation.

FIG. 8 is a diagram illustrating a configuration of an air-conditioning apparatus to which the heat exchanger according to Embodiment 1 is applied. In FIG. 8, the refrigerant flow during the cooling operation is indicated by a solid arrow, and the refrigerant flow during the heating operation is indicated by a dotted arrow.
As shown in FIG. 8, the air conditioner 51 includes a compressor 52, a four-way valve 53, a heat source side heat exchanger 54, a throttle device 55, a load side heat exchanger 56, a heat source side fan 57, A load-side fan 58 and a control device 59. The compressor 52, the four-way valve 53, the heat source side heat exchanger 54, the expansion device 55, and the load side heat exchanger 56 are connected by refrigerant piping to form a refrigerant circulation circuit.

  For example, a compressor 52, a four-way valve 53, a throttle device 55, a heat source side fan 57, a load side fan 58, various sensors, and the like are connected to the control device 59. By switching the flow path of the four-way valve 53 by the control device 59, the cooling operation and the heating operation are switched. The heat source side heat exchanger 54 acts as a condenser during the cooling operation, and acts as an evaporator during the heating operation. The load side heat exchanger 56 acts as an evaporator during the cooling operation, and acts as a condenser during the heating operation.

The flow of the refrigerant during the cooling operation will be described.
The high-pressure and high-temperature gas refrigerant discharged from the compressor 52 flows into the heat source side heat exchanger 54 via the four-way valve 53 and condenses by heat exchange with the outside air supplied by the heat source side fan 57. It becomes a high-pressure liquid refrigerant and flows out of the heat source side heat exchanger 54. The high-pressure liquid refrigerant flowing out of the heat source side heat exchanger 54 flows into the expansion device 55 and becomes a low-pressure gas-liquid two-phase refrigerant. The low-pressure gas-liquid two-phase refrigerant flowing out of the expansion device 55 flows into the load-side heat exchanger 56 and evaporates by heat exchange with the indoor air supplied by the load-side fan 58, thereby causing a low-pressure gas state. And flows out of the load-side heat exchanger 56. The low-pressure gaseous refrigerant flowing out from the load-side heat exchanger 56 is sucked into the compressor 52 through the four-way valve 53.

The flow of the refrigerant during the heating operation will be described.
The high-pressure and high-temperature gas refrigerant discharged from the compressor 52 flows into the load-side heat exchanger 56 through the four-way valve 53 and condenses by heat exchange with the indoor air supplied by the load-side fan 58. And becomes a high-pressure liquid refrigerant and flows out of the load-side heat exchanger 56. The high-pressure liquid refrigerant flowing out of the load-side heat exchanger 56 flows into the expansion device 55 and becomes a low-pressure gas-liquid two-phase refrigerant. The low-pressure gas-liquid two-phase refrigerant that flows out of the expansion device 55 flows into the heat source side heat exchanger 54 and evaporates by heat exchange with the outside air supplied by the heat source side fan 57, so that the low-pressure gas state It becomes a refrigerant and flows out of the heat source side heat exchanger 54. The low-pressure gaseous refrigerant flowing out from the heat source side heat exchanger 54 is sucked into the compressor 52 through the four-way valve 53.

  The heat exchanger 1 is used for at least one of the heat source side heat exchanger 54 and the load side heat exchanger 56. The heat exchanger 1 is connected so that the refrigerant flows in from the stacked header 2 and the refrigerant flows out of the header 3 when the heat exchanger 1 acts as an evaporator. That is, when the heat exchanger 1 acts as an evaporator, the gas-liquid two-phase refrigerant flows from the refrigerant pipe to the stacked header 2, and the gas refrigerant flows from the first heat transfer pipe 4 to the header 3. . When the heat exchanger 1 acts as a condenser, a gaseous refrigerant flows from the refrigerant pipe to the header 3, and a liquid refrigerant flows from the first heat transfer tube 4 to the stacked header 2.

<Operation of heat exchanger>
Below, the effect | action of the heat exchanger which concerns on Embodiment 1 is demonstrated.
The branch flow path 12b of the stacked header 2 includes the inner surface 12b_1b of the inflow side Z-shaped region 12b_1a, that is, the inner surface of the first protrusion of the plate member, and the outer surface 12b_2b of the outflow side Z region 12b_2a, that is, another plate-shaped member. And the outer surface of the first protrusion. Therefore, even if the plate-like member is thinned, the cross-sectional area of the branch flow path 12b can be secured, and it is possible to realize reduction in parts cost, weight reduction, etc. while suppressing an increase in pressure loss of the refrigerant. is there.

  Further, since the plate-like member can be thinned, the heat capacity can be reduced, the time required for heating and cooling in joining such as brazing is shortened, and the production efficiency is improved.

  Moreover, since the protrusion part of a plate-shaped member can be formed by press work, such as a drawing process and a bending process, a process cost is reduced.

  In addition, since a space is formed between the plate-like members, heat insulation can be improved compared to the case where a thick plate-like member is cut to form a flow path, and the laminated header It is suppressed that the refrigerant which passes 2 is heated and cooled. The space between the plate-like members may be filled with a heat insulating material.

  Moreover, the periphery of a plate-shaped member is bend | folded in the lamination direction, and the front-end | tip of the periphery is joined to the side surface of the plate-shaped member laminated | stacked adjacently. Therefore, compared to the case where unfolded plate-like members are stacked and bonded over a wide area, the brazing material is more easily concentrated by the surface tension at the tip of the periphery, and the brazing material becomes non-uniform and joined. The frequency of defects and the amount of brazing material used are reduced. Furthermore, a process for finishing the flatness of the joint surface, a jig for evenly pressurizing a large area at the time of brazing, and the like are unnecessary, and the manufacturing cost is reduced. That is, when brazing is performed in a state where the intervals between the members to be bonded are not uniform, the brazing material is concentrated at a narrow interval, and uneven bonding, shrinkage nests, and the like are generated. In the laminated header 2, since the interval between the members to be joined and the joining surface are reduced and the brazing materials are joined together, it is possible to suppress occurrence of uneven joining, shrinkage nests, and the like. In particular, as shown in FIGS. 3 and 4, when the peripheral edge of the plate-like member is bent obliquely in the stacking direction, the bonding area is increased and the bonding strength is improved.

  Moreover, the 2nd protrusion part is formed in a plate-shaped member, and the inner surface of a 2nd protrusion part is joined to the outer surface of the 2nd protrusion part formed in the plate-shaped member laminated | stacked adjacently. For this reason, the protrusions are joined in a state close to line contact, so that the brazing material is easily aggregated due to surface tension, and the frequency at which the brazing material becomes non-uniform and defective joining is reduced. Certainty is improved. Furthermore, the amount of brazing material used is reduced. Furthermore, a process for finishing the flatness of the joint surface, a jig for evenly pressurizing a large area at the time of brazing, and the like are unnecessary, and the manufacturing cost is reduced.

  Further, the inner surface 12b_1b of the inflow side Z-shaped region 12b_1a, that is, the inner surface of the first protruding portion of the plate-shaped member, the outer surface 12b_2b of the outflow-side Z-shaped region 12b_2a, that is, the outer surface of the first protruding portion of the other plate-shaped member, Are joined in a fitted state. Therefore, the protrusions are joined in a state close to line contact, and the brazing material is easily aggregated due to surface tension, the frequency at which the brazing material becomes uneven and the joining is poor, and the amount of brazing material used Reduced. Furthermore, a process for finishing the flatness of the joint surface, a jig for evenly pressurizing a large area at the time of brazing, and the like are unnecessary, and the manufacturing cost is reduced. Furthermore, since it cannot join by changing a lamination order, it is suppressed that a lamination order is mistaken at the time of manufacture.

<Modification-1>
FIG. 9 is a perspective view of a modified example-1 of the heat exchanger according to Embodiment 1 in a state where the stacked header is disassembled. FIG. 10 is a cross-sectional view of the modified example-1 of the heat exchanger according to Embodiment 1 in a state in which stacked headers are stacked. FIG. 11 is a development view of a stacked header of Modification Example 1 of the heat exchanger according to the first embodiment. FIG. 10 shows a cross-sectional view taken along line EE in FIG. In FIG. 10, the portion into which the refrigerant flows is indicated by hatching. In FIG. 11, the first plate member 21, the second plate member 22, the third plate member 23, the fourth plate member 24, and the fifth plate members 25_1 to 25_5 are joined. Show.

  As shown in FIGS. 9 to 11, the first plate member 21, the second plate member 22, the third plate member 23, and the fourth plate member 24 include fifth plate members 25 </ b> _ <b> 1 to 25_ <b> 5. It may be joined. The plate-like member has first projecting portions 21A, 22A, 23A, and 24A that are formed by pressing such as drawing and bending, and project toward the side where the refrigerant flows. The first protrusions 21A, 22A, 23A, 24A do not have a bottom, and the inner surfaces 21a, 22a, 23a, 24a function as a part of the branch flow path 12b in a state where the plate-like members are stacked. Hereinafter, the fifth plate-like members 25_1 to 25_5 may be collectively referred to as the fifth plate-like member 25. The fifth plate-like member 25 corresponds to the “second plate-like member” of the present invention.

  Through holes 25A_1 to 25A_5 are formed in the fifth plate members 25_1 to 25_5, and the outer circumferences of the tips of the first projecting portions 21A, 22A, 23A, and 24A are joined to the through holes 25A_1 to 25A_5 in a fitted state. Is done. The plate-like members are laminated, and the insides of the first projecting portions 21A, 22A, 23A, and 24A are laminated on the surface of the fifth plate-like member 25 laminated on the refrigerant outflow side and the refrigerant inflow side. The other flow path 12b is formed by closing the area other than the area where the refrigerant flows in and the area where the refrigerant flows out by the surface of the other plate-like member.

<Modification-2>
FIG. 12 is a perspective view of a main part and a cross-sectional view of the main part in a state where the stacked header is disassembled in Modification-2 of the heat exchanger according to the first embodiment. 12A is a perspective view of the main part in a state in which the laminated header is disassembled, and FIG. 12B is a first plate-like member taken along line FF in FIG. FIG. In FIG.12 (b), the part into which a refrigerant | coolant flows in is shown with the oblique line.
As shown in FIG. 12, the inner surface 21a of the region other than the outflow side Z-shaped region 12b_2a of the first projecting portion 21A of the first plate-shaped member 21 has a shape that gradually expands toward the refrigerant outflow side. May be. By comprising in this way, when the 1st heat exchanger tube 4 is a flat tube, the pressure loss of the refrigerant | coolant at the time of passing 11 A of 1st exit flow paths is reduced.

<Modification-3>
FIG. 13: is a perspective view in the state which decomposed | disassembled the laminated header of the modification 3 of the heat exchanger which concerns on Embodiment 1. FIG.
As shown in FIG. 13, a plurality of first inlet channels 12 a may be formed in the third plate member 23, and the number of fourth plate members 24 may be reduced. By being configured in this way, parts cost, weight, etc. are reduced.

<Modification-4>
FIG. 14 is a perspective view of a modification 4 of the heat exchanger according to Embodiment 1 in a state where the stacked header is disassembled.
As shown in FIG. 14, the first inlet channel 12 a may be formed on a plate-like member other than the third plate-like member 23. In such a case, through holes are formed in the other plate-shaped members, and the inner surfaces of the first protrusions 24A_1 of the fourth plate-shaped member 24_1 are formed in the other plate-shaped members and the peripheral plate-shaped members from the through holes. What is necessary is just to form the protrusion part for guide | inducing a refrigerant | coolant to 24a_1. That is, the present invention includes those in which the first inlet channel 12 a is formed in the first plate-like body 11, and the “distribution channel” of the present invention has the first inlet channel 12 a as the second plate-like body 12. Other than the distribution flow path 12A formed in the above.

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.
FIG. 15 is a diagram illustrating a configuration of the heat exchanger according to the second embodiment.
As shown in FIG. 15, the heat exchanger 1 includes a stacked header 2, a plurality of first heat transfer tubes 4, and a plurality of fins 5.

  The stacked header 2 includes a refrigerant inflow portion 2A, a plurality of refrigerant outflow portions 2B, a plurality of refrigerant inflow portions 2C, and a refrigerant outflow portion 2D. A refrigerant pipe is connected to the refrigerant inflow portion 2A of the multilayer header 2 and the refrigerant outflow portion 2D of the multilayer header 2. The first heat transfer tube 4 is a flat tube that has been subjected to hairpin bending. A plurality of first heat transfer tubes 4 are connected between the plurality of refrigerant outflow portions 2B of the multilayer header 2 and the plurality of refrigerant inflow portions 2C of the multilayer header 2.

<Flow of refrigerant in heat exchanger>
Below, the flow of the refrigerant in the heat exchanger according to the second embodiment will be described.
The refrigerant flowing through the refrigerant pipe flows into the stacked header 2 through the refrigerant inflow portion 2A and is distributed, and flows out to the plurality of first heat transfer tubes 4 through the plurality of refrigerant outflow portions 2B. The refrigerant exchanges heat with, for example, air supplied by a fan in the plurality of first heat transfer tubes 4. The refrigerant that has passed through the plurality of first heat transfer tubes 4 flows into and merges with the stacked header 2 through the plurality of refrigerant inflow portions 2C, and flows out to the refrigerant piping through the refrigerant outflow portion 2D. The refrigerant can flow backward.

<Configuration of laminated header>
Below, the structure of the laminated header of the heat exchanger which concerns on Embodiment 2 is demonstrated.
FIG. 16 is a perspective view of the heat exchanger according to Embodiment 2 in a state where the stacked header is disassembled. FIG. 17 is a development view of the stacked header of the heat exchanger according to the second embodiment.
As shown in FIGS. 16 and 17, the stacked header 2 includes a first plate-like body 11 and a second plate-like body 12. The first plate-like body 11 and the second plate-like body 12 are stacked.

  The first plate-like body 11 is formed with a plurality of first outlet channels 11A and a plurality of second inlet channels 11B. The first plate-like body 11 includes a first plate-like member 21, a sixth plate-like member 26, and a second plate-like member 22. The plurality of second inlet channels 11B correspond to the plurality of refrigerant inflow portions 2C in FIG. Hereinafter, the first plate member 21, the second plate member 22, the third plate member 23, the fourth plate member 24, and the sixth plate member 26 are collectively referred to as a plate member. There is.

  In the second plate-like body 12, a distribution channel 12A and a merging channel 12B are formed. The merging channel 12B includes a mixing channel 12c and a second outlet channel 12d. The second outlet channel 12d corresponds to the refrigerant outflow portion 2D in FIG.

  The second plate-like member 22 has, for example, a third protruding portion 22C that is formed by pressing such as drawing or bending and protrudes toward the side from which the refrigerant flows out. The third protrusion 22C does not have a bottom only in the region connected to the end of the first heat transfer tube 4 on the side from which the refrigerant flows out, and the outer surface 22d is the second plate-like member 22 in a stacked state. It functions as a part of the 2-inlet channel 11B.

  The sixth plate-like member 26 is formed by, for example, press working such as drawing or bending, and protrudes toward the refrigerant outflow side, the first protrusion 26A, the second protrusion 26B, It has the 3rd protrusion part 26C. In the third protrusion 26C, the region of the first heat transfer tube 4 that does not face the end of the refrigerant flowing out does not have a bottom, and the inner surface 26c is the second in a state where the sixth plate member 26 is laminated. It functions as a part of the inlet channel 11B.

  The first plate-like member 21 has, for example, a through-hole 21 </ b> C that is formed by pressing and does not protrude toward the refrigerant outflow side and the refrigerant inflow side. The through portion 21C functions as a part of the second inlet channel 11B in a state where the first plate-like member 21 is stacked.

  For example, the fourth plate member 24 includes third projecting portions 24 </ b> C_ <b> 1 to 24 </ b> __ <b> 3 that are formed by pressing such as drawing or bending and project toward the side where the refrigerant flows. Hereinafter, the third protrusions 24C_1 to 24C_3 of the fourth plate-like member 24 may be collectively referred to as a third protrusion 24C. The third protrusion 24C does not have a bottom, and the inner surfaces 24c_1 to 24c_3 function as a part of the mixing channel 12c in a state where the fourth plate-like member 24 is stacked. Hereinafter, the inner surfaces 24c_1 to 24c_3 of the third protruding portion 24C of the fourth plate-like member 24 may be collectively referred to as an inner surface 24c.

  The third plate-like member 23 is formed in, for example, a third projecting portion 23C and a third projecting portion 23C that are formed by press working such as drawing and bending, and project toward the refrigerant inflow side. And a fourth projecting portion 23D projecting toward the refrigerant outflow side. The third protrusion 23C has a bottom, and the outer surface 23d functions as a part of the mixing channel 12c in a state where the third plate member 23 is laminated. The fourth protrusion 23D does not have a bottom, and the inner surface 23e functions as the second outlet channel 12d in a state where the third plate member 23 is stacked.

  Note that the second outlet channel 12 d may be formed in a plate-like member other than the third plate-like member 23. In such a case, a through hole is formed in the other plate-shaped member, and a protrusion for guiding the refrigerant to the through hole may be formed in the other plate-shaped member and the peripheral plate-shaped member. That is, the present invention includes the one in which the second outlet channel 12d is formed in the first plate-like body 11, and the “merging channel” of the present invention has the second outlet channel 12d in the second plate-like body 12. Other than the merging channel 12B formed in the above.

<Refrigerant flow in stacked header>
Below, the flow of the refrigerant in the stacked header of the heat exchanger according to Embodiment 2 will be described.
As shown by arrows in FIGS. 16 and 17, the refrigerant that has passed through the first heat transfer tube 4 passes through the third protrusion 22 </ b> C of the second plate member 22, and the third plate 26 of the sixth plate member 26. It flows into the protrusion 26C. The refrigerant that has flowed into the inside of the third protrusion 26 </ b> C of the sixth plate member 26 passes through the through portion 21 </ b> C of the first plate member 21 and enters the inside of the third protrusion 24 </ b> C of the fourth plate member 24. Inflow and mix. The mixed refrigerant passes through the fourth protrusion 23D of the third plate member 23 and flows out to the refrigerant pipe.

<Usage of heat exchanger>
Below, an example of the usage condition of the heat exchanger which concerns on Embodiment 2 is demonstrated.
FIG. 18 is a diagram illustrating a configuration of an air-conditioning apparatus to which the heat exchanger according to Embodiment 2 is applied.
As shown in FIG. 18, the heat exchanger 1 is used for at least one of the heat source side heat exchanger 54 and the load side heat exchanger 56. In the heat exchanger 1, when the heat exchanger 1 acts as an evaporator, the refrigerant flows into the first heat transfer tube 4 from the distribution flow path 12 </ b> A of the stacked header 2, and the stacked header 2 is transferred from the first heat transfer tube 4. Are connected so that the refrigerant flows into the merging flow path 12B. That is, when the heat exchanger 1 acts as an evaporator, a gas-liquid two-phase refrigerant flows from the refrigerant pipe into the distribution flow path 12A of the laminated header 2 and flows from the first heat transfer tube 4 to the laminated header 2. The refrigerant in the gas state flows into the merge channel 12B. When the heat exchanger 1 acts as a condenser, a gaseous refrigerant flows from the refrigerant pipe into the merged flow path 12B of the laminated header 2 and the distribution flow path of the laminated header 2 from the first heat transfer pipe 4. Liquid refrigerant flows into 12A.

<Operation of heat exchanger>
Below, the effect | action of the heat exchanger which concerns on Embodiment 2 is demonstrated.
In the stacked header 2, a plurality of second inlet channels 11 </ b> B are formed in the first plate 11, and a merge channel 12 </ b> B is formed in the second plate 12. For this reason, the header 3 is not required, and the parts cost of the heat exchanger 1 is reduced. Further, since the header 3 is not required, the number of the fins 5 can be increased by extending the first heat transfer tube 4, that is, the mounting volume of the heat exchange part of the heat exchanger 1 can be increased.

Embodiment 3 FIG.
A heat exchanger according to Embodiment 3 will be described.
Note that the description overlapping or similar to the first embodiment and the second embodiment is appropriately simplified or omitted.
<Configuration of heat exchanger>
Below, the structure of the heat exchanger which concerns on Embodiment 3 is demonstrated.
FIG. 19 is a diagram illustrating a configuration of a heat exchanger according to the third embodiment.
As shown in FIG. 19, the heat exchanger 1 includes a stacked header 2, a plurality of first heat transfer tubes 4, a plurality of second heat transfer tubes 6, and a plurality of fins 5.

  The stacked header 2 has a plurality of refrigerant folding portions 2E. Similar to the first heat transfer tube 4, the second heat transfer tube 6 is a flat tube that has been subjected to hairpin bending. A plurality of first heat transfer tubes 4 are connected between the plurality of refrigerant outflow portions 2B and the plurality of refrigerant folding portions 2E of the multilayer header 2, and the plurality of refrigerant folding portions 2E and the plurality of refrigerant inflows of the multilayer header 2 are connected. A plurality of second heat transfer tubes 6 are connected between the portion 2C.

<Flow of refrigerant in heat exchanger>
Below, the flow of the refrigerant in the heat exchanger according to Embodiment 3 will be described.
The refrigerant flowing through the refrigerant pipe flows into the stacked header 2 through the refrigerant inflow portion 2A and is distributed, and flows out to the plurality of first heat transfer tubes 4 through the plurality of refrigerant outflow portions 2B. The refrigerant exchanges heat with, for example, air supplied by a fan in the plurality of first heat transfer tubes 4. The refrigerant that has passed through the plurality of first heat transfer tubes 4 flows into the plurality of refrigerant folding portions 2 </ b> E of the stacked header 2, is turned back, and flows out to the plurality of second heat transfer tubes 6. The refrigerant exchanges heat with, for example, air supplied by a fan in the plurality of second heat transfer tubes 6. The refrigerant that has passed through the plurality of second heat transfer tubes 6 flows into and joins the stacked header 2 through the plurality of refrigerant inflow portions 2C, and flows out to the refrigerant pipe through the refrigerant outflow portion 2D. The refrigerant can flow backward.

<Configuration of laminated header>
Below, the structure of the laminated header of the heat exchanger which concerns on Embodiment 3 is demonstrated.
FIG. 20 is a perspective view of the heat exchanger according to Embodiment 3 in a state where the stacked header is disassembled. FIG. 21 is a development view of the stacked header of the heat exchanger according to the third embodiment.
As shown in FIGS. 20 and 21, the stacked header 2 includes a first plate-like body 11 and a second plate-like body 12. The first plate-like body 11 and the second plate-like body 12 are stacked.

  The first plate 11 is formed with a plurality of first outlet channels 11A, a plurality of second inlet channels 11B, and a plurality of folded channels 11C. The plurality of folding channels 11C correspond to the plurality of refrigerant folding sections 2E in FIG.

  The second plate-like member 22 is formed by, for example, pressing such as drawing or bending, and protrudes toward the side opposite to the side into which the refrigerant from the first heat transfer tube 4 flows. 22C and, for example, a fourth projecting portion 22D that is formed by press working such as drawing or bending, and projects toward the side from which the refrigerant from the second heat transfer tube 6 flows out. The fourth protrusion 22D does not have a bottom only in the region connected to the end of the first heat transfer tube 4 on the side where the refrigerant flows out and the end of the second heat transfer tube 6 on the side where the refrigerant flows in. In the state where the plate-like member 22 is laminated, the outer surface 22f functions as a part of the return channel 11C.

  The sixth plate-like member 26 is formed by, for example, pressing such as drawing or bending, and protrudes toward the side opposite to the side into which the refrigerant from the first heat transfer tube 4 flows. 26C and, for example, a fourth projecting portion 26D that is formed by pressing such as drawing or bending and projects toward the side from which the refrigerant from the second heat transfer tube 6 flows out. The fourth protrusion 26D has a bottom, and the inner surface 26e functions as a part of the folded flow path 11C in a state where the sixth plate member 26 is laminated.

<Refrigerant flow in stacked header>
The refrigerant flow in the stacked header of the heat exchanger according to Embodiment 3 will be described below.
As shown by arrows in FIGS. 20 and 21, the refrigerant that has passed through the first heat transfer tube 4 passes through the fourth projecting portion 22 </ b> D of the second plate-like member 22 and the fourth plate-like member 26 of the sixth plate-like member 26. It flows into the inside of the protrusion 26D. The refrigerant that has flowed inside the fourth protrusion 26D of the sixth plate member 26 passes through the fourth protrusion 22D of the second plate member 22 again and flows into the second heat transfer tube 6. The refrigerant that has passed through the second heat transfer tube 6 passes through the third protrusion 22C of the second plate member 22 and the third protrusion 26C of the sixth plate member 26, so It flows into the inside of the protrusion 24C and is mixed. The mixed refrigerant passes through the fourth protrusion 23D of the third plate member 23 and flows out to the refrigerant pipe.

<Usage of heat exchanger>
Below, an example of the usage mode of the heat exchanger which concerns on Embodiment 3 is demonstrated.
FIG. 22 is a diagram illustrating a configuration of an air-conditioning apparatus to which the heat exchanger according to Embodiment 3 is applied.
As shown in FIG. 22, the heat exchanger 1 is used for at least one of the heat source side heat exchanger 54 and the load side heat exchanger 56. In the heat exchanger 1, when the heat exchanger 1 acts as an evaporator, the refrigerant flows into the first heat transfer tube 4 from the distribution flow path 12 </ b> A of the stacked header 2 and from the second heat transfer tube 6 to the stacked header 2. Are connected so that the refrigerant flows into the merging flow path 12B. That is, when the heat exchanger 1 acts as an evaporator, a gas-liquid two-phase refrigerant flows from the refrigerant pipe into the distribution flow path 12A of the laminated header 2 and flows from the second heat transfer pipe 6 to the laminated header 2. The refrigerant in the gas state flows into the merge channel 12B. When the heat exchanger 1 acts as a condenser, a gaseous refrigerant flows from the refrigerant pipe into the merged flow path 12B of the laminated header 2 and the distribution flow path of the laminated header 2 from the first heat transfer pipe 4. Liquid refrigerant flows into 12A.

  Furthermore, when the heat exchanger 1 acts as a condenser, the first heat transfer tube 4 is compared with the second heat transfer tube 6 on the upstream side (windward side) of the airflow generated by the heat source side fan 57 or the load side fan 58. ), The heat exchanger 1 is disposed. That is, the refrigerant flow from the second heat transfer tube 6 to the first heat transfer tube 4 and the airflow face each other. The refrigerant of the first heat transfer tube 4 has a lower temperature than the refrigerant of the second heat transfer tube 6. The airflow generated by the heat source side fan 57 or the load side fan 58 has a lower temperature on the upstream side of the heat exchanger 1 than on the downstream side of the heat exchanger 1. As a result, in particular, the refrigerant can be supercooled (so-called SC) with a low-temperature airflow flowing upstream of the heat exchanger 1, and the condenser performance is improved. The heat source side fan 57 and the load side fan 58 may be provided on the leeward side or may be provided on the leeward side.

<Operation of heat exchanger>
Below, the effect | action of the heat exchanger which concerns on Embodiment 3 is demonstrated.
In the heat exchanger 1, a plurality of folded flow paths 11 </ b> C are formed in the first plate body 11, and a plurality of second heat transfer tubes 6 are connected in addition to the plurality of first heat transfer tubes 4. For example, it is possible to increase the amount of heat exchange by increasing the area of the heat exchanger 1 as viewed from the front, but in that case, the housing containing the heat exchanger 1 is enlarged. End up. In addition, it is possible to increase the number of fins 5 by reducing the interval between the fins 5 and increase the amount of heat exchange, but in that case, from the viewpoint of drainage, frosting performance, dust resistance, It is difficult to make the interval between the fins 5 less than about 1 mm, and the increase in the heat exchange amount may be insufficient. On the other hand, when the number of rows of heat transfer tubes is increased as in the heat exchanger 1, the heat exchange amount is increased without changing the area of the heat exchanger 1 as viewed from the front, the spacing between the fins 5, and the like. It is possible to make it. When the number of rows of heat transfer tubes becomes two, the amount of heat exchange increases by about 1.5 times or more. Note that the number of rows of heat transfer tubes may be three or more. Furthermore, the area of the heat exchanger 1 as viewed from the front, the interval between the fins 5 and the like may be changed.

  Further, a header (laminated header 2) is provided only on one side of the heat exchanger 1. In order to increase the mounting volume of the heat exchanging part, for example, when the heat exchanger 1 is bent and arranged along a plurality of side surfaces of the housing incorporating the heat exchanger 1, Due to the fact that the curvature radius of the bent portion is different for each row of heat tubes, the end portion is shifted for each row of heat transfer tubes. When the header (stacked header 2) is provided only on one side of the heat exchanger 1 as in the stacked header 2, even if the end is shifted for each row of heat transfer tubes, only the end on one side Compared to the case where headers (laminated header 2 and header 3) are provided on both sides of the heat exchanger 1 as in the heat exchanger according to Embodiment 1, the degree of freedom in design, production efficiency, etc. Is improved. In particular, it is possible to bend the heat exchanger 1 after joining the members of the heat exchanger 1, and the production efficiency is further improved.

  Further, when the heat exchanger 1 acts as a condenser, the first heat transfer tube 4 is located on the windward side as compared with the second heat transfer tube 6. In the case where headers (laminated header 2 and header 3) are provided on both sides of the heat exchanger 1 as in the heat exchanger according to Embodiment 1, condensation is performed by giving a temperature difference of the refrigerant for each row of heat transfer tubes. It was difficult to improve the vessel performance. In particular, when the first heat transfer tube 4 and the second heat transfer tube 6 are flat tubes, unlike a circular tube, the degree of freedom of bending is low, so that a temperature difference of the refrigerant is given to each row of heat transfer tubes. It is difficult to realize by deforming the refrigerant flow path. On the other hand, when the first heat transfer tube 4 and the second heat transfer tube 6 are connected to the laminated header 2 as in the heat exchanger 1, a temperature difference of the refrigerant inevitably occurs for each row of heat transfer tubes. In other words, it is possible to easily realize the relationship in which the refrigerant flow and the airflow face each other without deforming the refrigerant flow path.

  Although the first to third embodiments have been described above, the present invention is not limited to the description of each embodiment. For example, it is possible to combine all or a part of each embodiment, each modification, and the like.

  DESCRIPTION OF SYMBOLS 1 Heat exchanger, 2 Stack type header, 2A Refrigerant inflow part, 2B Refrigerant outflow part, 2C Refrigerant inflow part, 2D Refrigerant outflow part, 2E Refrigerant return part, 3 Header, 3A Refrigerant inflow part, 3B Refrigerant outflow part, 4th 1 heat transfer pipe, 5 fins, 6 second heat transfer pipe, 11 first plate-like body, 11A first outlet flow path, 11B second inlet flow path, 11C folded flow path, 12 second plate-like body, 12A distribution flow path 12B merge flow path, 12a first inlet flow path, 12b branch flow path, 12b_1a inflow side Z-shaped area, 12b_2a outflow side Z-shaped area, 12b_1b inner surface of inflow side Z-shaped area, 12b_2b outer surface of outflow side Z-shaped area, 12b_1c, 12b_2c, 12b_1d, 12b_2d End of Z-shaped region, 12b_1e, 12b_2e Straight portion of Z-shaped region, 12b_1f, 12b_2f, 12b_2g through Through hole, 12b_1h, 12b_2h, 12b_1i, 12b_2i peripheral part, 12b_2j protrusion, 12c mixing flow path, 12d second outlet flow path, 21 first plate member, 21A first protrusion, 21B second protrusion, 21C penetrating part , 21a inner surface of the first protrusion, 21b outer surface of the first protrusion, 22 second plate member, 22A first protrusion, 22B second protrusion, 22C third protrusion, 22D fourth protrusion, 22a first 1 protrusion inner surface, 22c third protrusion inner surface, 22d third protrusion outer surface, 22f fourth protrusion outer surface, 23 third plate member, 23A first protrusion, 23C third protrusion, 23D 4th protrusion part, 23a Inner surface of 1st protrusion part, 23d Outer surface of 3rd protrusion part, 23e Inner surface of 4th protrusion part, 24, 24_1-24_3 4th plate-shaped member, 24A, 24A_1-24 _3 first protrusion, 24B, 24B_1 to 24B_3 second protrusion, 24C, 24C_1 to 24C_3 third protrusion, 24a, 24a_1 to 24a_3 inner surface of the first protrusion, 24b, 24b_1 to 24b_3 outer surface of the first protrusion, 24c, 24c_1 to 24c_3 inner surface of the third protrusion, 25, 25_1 to 25_5 fifth plate member, 25A_1 to 25A_5 through hole, 26 sixth plate member, 26A first protrusion, 26B second protrusion, 26C second protrusion 3 projection part, 26D 4th projection part, 26c inner surface of the 3rd projection part, 26e inner surface of the 4th projection part, 51 air conditioner, 52 compressor, 53 four-way valve, 54 heat source side heat exchanger, 55 throttle device, 56 load side heat exchanger, 57 heat source side fan, 58 load side fan, 59 control device.

The laminated header according to the present invention includes a first plate-like body in which a plurality of first outlet channels are formed, and a second plate-like layer that is laminated on the first plate-like body to form a first inlet channel. has a body, a, wherein the second plate-like member, the distribution channel that flows by distributing the refrigerant flowing from the first inlet flow path to the first outlet channel of the plurality is formed, said distribution The flow path includes at least one branch flow path, and the second plate-like body has at least one first protrusion formed with at least one first protrusion protruding in the direction of stacking with the first plate-like body . has a plate-like member, the branch flow path, that area other than the area where the region and the refrigerant in which the refrigerant inside the first protrusion flows flows out is closed, and is formed .

Claims (14)

A first plate-like body formed with a plurality of first outlet channels;
A second plate-like body that is stacked on the first plate-like body and has a distribution channel that distributes the refrigerant flowing from the first inlet channel to the plurality of first outlet channels and flows out;
With
The distribution channel includes at least one branch channel;
The second plate-like body has at least one first plate-like member in which at least one first protrusion is formed by pressing,
The branch flow path is formed by closing an area inside the first projecting portion other than an area where the refrigerant flows in and an area where the refrigerant flows out,
A laminated header characterized by that. The peripheral edge of the first plate-like member is bent in the stacking direction,
The tip of the peripheral edge is joined to the side surface of the adjacent laminated members,
The laminated header according to claim 1, wherein At least one second protrusion is formed in a region different from the region where the first protrusion is formed in the first plate-like member,
The inner surface of the second projecting portion is joined to the outer surface of the projecting portion formed on the adjacent laminated member.
The laminated header according to claim 1 or 2, wherein The first protrusion has a bottom;
The inner side of the first protrusion is closed by fitting the inner surface of the first protrusion with the outer surface of the protrusion formed on the adjacent laminated member.
The laminated header according to any one of claims 1 to 3, wherein The second plate-like body has at least one second plate-like member in which at least one penetrating portion is formed,
The first protrusion has no bottom,
The second plate-like member is joined to the first plate-like member so that the through portion is fitted to the outer surface of the tip of the first projecting portion,
The inside of the first projecting portion is a surface of a member stacked on a side where the first projecting portion of the first plate-like member does not project, and a side of the second plate-like member on which the first plate-like member is present. And the surface of the member laminated on the opposite side,
The laminated header according to any one of claims 1 to 3, wherein A plurality of second inlet channels are formed in the first plate body,
In the second plate-like body, a merged flow path is formed that merges the refrigerant flowing in from the plurality of second inlet flow paths and flows into the second outlet flow path,
The multilayer header according to any one of claims 1 to 5, wherein In the first plate-like body, a plurality of folded flow passages are formed for folding and flowing out the flowing refrigerant.
The laminated header according to any one of claims 1 to 6, wherein The laminated header according to any one of claims 1 to 5,
A plurality of first heat transfer tubes connected to each of the plurality of first outlet channels;
A heat exchanger characterized by comprising: A plurality of second inlet flow paths into which the refrigerant that has passed through the plurality of first heat transfer tubes flows are formed in the first plate-like body,
The second plate-like body is formed with a merge channel that merges the refrigerant flowing in from the plurality of second inlet channels and flows into the second outlet channel,
The heat exchanger according to claim 8. Each of the plurality of first heat transfer tubes is connected to the first plate-like body on the inlet side, and a plurality of folded flow passages are formed for folding and flowing out the refrigerant flowing from the plurality of first heat transfer tubes,
A plurality of second heat transfer tubes connected to each outlet side of the plurality of folded flow paths and each of the plurality of second inlet paths;
The heat exchanger according to claim 9. The heat transfer tube is a flat tube,
The heat exchanger according to any one of claims 8 to 10, wherein The inner peripheral surface of the first outlet channel gradually spreads toward the outer peripheral surface of the first heat transfer tube,
The heat exchanger according to claim 11. A heat exchanger according to any one of claims 8 to 12, comprising:
The distribution channel flows out the refrigerant to the plurality of first outlet channels when the heat exchanger acts as an evaporator.
An air conditioner characterized by that. A heat exchanger according to claim 10,
The distribution channel flows out the refrigerant into the plurality of first outlet channels when the heat exchanger acts as an evaporator,
The first heat transfer tube is located on the windward side as compared to the second heat transfer tube when the heat exchanger acts as a condenser.
An air conditioner characterized by that.

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