JP7228356B2 - Heat exchanger and air conditioner provided with the same - Google Patents

Description

The present invention relates to heat exchangers and the like.

Parallel flow heat exchangers are known as heat exchangers used in air conditioners and the like. A parallel-flow heat exchanger is a heat exchanger that distributes a refrigerant to a plurality of flat tubes via a header (refrigerant distributor), and merges the refrigerant at another header via each flat tube. As a header for such a parallel flow heat exchanger, for example, the technology described in Patent Document 1 is known.

That is, in Patent Document 1, in a laminated header including a first plate-shaped body and a second plate-shaped body, a predetermined distribution channel is provided in the second plate-shaped body, and the distribution channel is inclined. configuration is described.

Japanese Patent No. 6138264

In the laminated header described in Patent Document 1, the refrigerant is divided into two at each branch point of the refrigerant flow. With such a configuration, when distributing the refrigerant to a large number of flat tubes, the number of plate-like bodies constituting the laminated header increases. As a result, the structure of the heat exchanger including the laminated header is complicated, the weight is increased, and the installation space is increased.

SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a heat exchanger or the like capable of appropriately distributing a refrigerant with a simple configuration.

In order to solve the above problems, a heat exchanger according to the present invention includes a refrigerant distributor formed by stacking a plurality of plate-like bodies, a plurality of fins arranged at predetermined intervals, and the plurality of fins. a plurality of heat transfer tubes penetrating through and connected to the refrigerant distributor, wherein each of the plurality of plate-shaped bodies is provided with a refrigerant channel through which a refrigerant flows; includes a first plate-like body having a recess formed by being recessed on one side, and a second plate-like body adjacent to the other side of the first plate-like body, and the recess includes one first plate-like body Holes are provided as the coolant channels, and the second plate-like body is provided with a plurality of second holes communicating with the space between the recesses as the coolant channels, and the first holes are provided. A plate surface of the second plate-like body exists in a projection area when projected onto the second plate-like body , and the plurality of second holes are formed in the projection area in the second plate-like body. are scattered as separate holes so as to surround the periphery of the second plate, and when the recess is projected onto the second plate-shaped body, the edge of the surface of the recess facing the space surrounds the plurality of second holes It is characterized by existing as

ADVANTAGE OF THE INVENTION According to this invention, the heat exchanger etc. which can distribute a refrigerant|coolant appropriately by simple structure can be provided.

1 is a perspective view of a heat exchanger according to a first embodiment of the invention; FIG. 1 is an exploded perspective view including a header of a heat exchanger according to a first embodiment of the present invention; FIG. FIG. 2 is a vertical cross-sectional view (cross-sectional view taken along the line I-I in FIG. 1) of the header of the heat exchanger according to the first embodiment of the present invention; FIG. 4 is a side view of the header of the heat exchanger according to the first embodiment of the present invention; FIG. 7 is an exploded perspective view including a header of the heat exchanger according to the second embodiment of the present invention; FIG. 5 is a side view of a header of a heat exchanger according to a second embodiment of the invention; FIG. 10 is a perspective view of a heat exchanger according to a third embodiment of the invention; FIG. 11 is a configuration diagram including a refrigerant circuit of an air conditioner according to a fourth embodiment of the present invention;

<<First Embodiment>>
FIG. 1 is a perspective view of a heat exchanger 1 according to the first embodiment.
The heat exchanger 1 shown in FIG. 1 is a parallel flow heat exchanger in which heat is exchanged between refrigerant and air. As shown in FIG. 1, the heat exchanger 1 includes a header 11 (refrigerant distributor), a plurality of fins F, and a plurality of flat tubes M (heat transfer tubes).

The header 11 is a refrigerant distributor that distributes the refrigerant flowing into itself through the pipes K to each flat tube M, or joins the refrigerant flowing into itself from each flat pipe M and guides it to the pipes K. The header 11 includes a plurality of elongated rectangular plate-like bodies (plate-like bodies P1 to P9 shown in FIG. 2), and has a structure in which the plurality of plate-like bodies are stacked. Note that the recess R1 and the insertion portion R2 shown in FIG. 1 will be described later.

The flat tube M is a heat transfer tube through which a refrigerant flows, and has a flat shape when viewed in longitudinal section. The flat tube M passes through a plurality of fins F, one end of which is connected to the header 11, and the other end of which is connected to another header (not shown). Refrigerant flows through a plurality of holes (not shown) provided side by side inside the flat tube M. As shown in FIG.

A plurality of fins F are metal thin plates for securing a heat transfer area between the coolant and the air. In the example shown in FIG. 1, a plate fin having an elongated rectangular plate surface is used as the fin F. As shown in FIG. The respective fins F are arranged such that their plate surfaces are parallel to each other, and that adjacent fins F, F are spaced apart from each other by a predetermined distance.

Each fin F is provided with a plurality of openings ha through which the flat tubes M pass. That is, eight openings ha are provided at equal intervals in the height direction so as to correspond to the eight flat tubes M one-to-one. In addition, a U-shaped opening (not shown) opening on the lateral side of the fins F may be provided, and the flat tube M may be inserted (passed through) from the lateral side into this opening.

Hereinafter, the side of the heat exchanger 1 where the pipe K is provided is called "one side", and the opposite side is called "the other side". Also, the case where the coolant flows toward the other side will be mainly described (in the direction of the dashed arrow in FIG. 2), but the coolant may also flow toward the one side in the opposite direction.

FIG. 2 is an exploded perspective view including the header 11 of the heat exchanger.
As shown in FIG. 2, the header 11 is constructed by stacking nine plates P1 to P9. Each of these plate-like bodies P1 to P9 has a predetermined coolant channel (first hole h1, second hole h2, coolant channels h3 to h9, etc. shown in FIG. 2) in an elongated rectangular metal plate. configuration. These plate-shaped bodies P1 to P9 include a first plate-shaped body P1, a second plate-shaped body P2 adjacent to the other side of the first plate-shaped body P1, and a plate-shaped body P2 on the other side of the second plate-shaped body P2. and seven other plate-like bodies P3 to P9 to be stacked.

The first plate-like body P1 includes a recess R1 and an insertion portion R2. In the example shown in FIG. 2, a concave portion R1 and an insertion portion R2 are provided in the upper portion of the first plate-like body P1. The recess R1 has a circular shape when viewed from one side, and is recessed to one side when viewed in longitudinal section (see also FIG. 3). Near the center of the recess R1, one circular first hole h1 is provided as the coolant channel described above.

The insertion portion R2 is a portion into which the pipe K is inserted, and is formed integrally with the recess R1. The insertion portion R2 has a cylindrical shape, and the inside communicates with the first hole h1 of the recess R1. Refrigerant is introduced to the first hole h1 of the recess R1 through the pipe K inserted into the insertion portion R2. In this way, the first plate-like body P1 exists at one end of the plurality of laminated plate-like bodies P1 to P9, and the pipe K for guiding the coolant is connected to the first hole h1.

The second plate-like body P2 is adjacent to the other side of the first plate-like body P1. As described above, the recess R1 of the first plate-like body P1 is recessed toward one side when viewed from the other side. Therefore, in the state where the second plate-like body P2 is laminated on the other side of the first plate-like body P1, there is a disk-shaped body between the recess R1 of the first plate-like body P1 and the second plate-like body P2. A space G (see FIG. 3) of is formed. This space G is a space for radially dispersing the coolant that has collided with the plate surface of the second plate-like body P2 via the pipe K. As shown in FIG.

Four second holes h2 communicating with the space G (see FIG. 3) between the second plate-like body P2 and the recess R1 are provided as coolant flow paths. In the example shown in FIG. 2, the four second holes h2 are circular and have substantially the same diameter. Then, the coolant that collides with the plate surface of the second plate-like body P2 is radially dispersed in the space G (see FIG. 3), and the dispersed coolant is distributed substantially evenly to the four second holes h2. It has become. Note that the diameter of the second hole h2 may be smaller than the inner diameter of the pipe K in consideration of the flow resistance when the refrigerant flows.

In the second plate-like body P2, two separate elongated refrigerant flow paths h21 are provided below the four second holes h2. These coolant flow paths h21 do not communicate with the space G (see FIG. 3) between the second plate-like body P2 and the recess R1. It communicates with part of the flow path h3. Thus, in the second plate-like body P2, the remaining area other than the four second holes h2 is effectively utilized.

Seven plate-like bodies P3 to P9 are stacked on the other side of the second plate-like body P2. That is, plate-like bodies P3, P4, P5, P6, P7, P8, and P9 are stacked in order toward the other side. These plate-like bodies P3 to P9 are for further dividing the refrigerant divided into four by the second hole h2 and guiding the refrigerant to the eight flat tubes M (see FIG. 1) on the downstream side.

Specifically, the plate-like body P3 is provided with four coolant passages h3 for guiding the coolant split into four through the second holes h2 to predetermined positions in the vertical direction (the plate-like body Same for P4). In addition, the plate-like body P5 is provided with four coolant passages h5 for dividing the coolant into two each at regular intervals in the vertical direction (the same applies to the plate-like body P6). As a result, the flow of the coolant divided into four by the plate-like members P1 to P4 is further divided into two by each of the plate-like members P5 and P6.

The plate-like body P7 is provided with eight coolant passages h7 at regular intervals in the vertical direction. The plate-like bodies P8 and P9 are also the same. These coolant channels h7 to h9 communicate with the respective coolant channels of the plate-like bodies P1 to P6. The ends of the flat tubes M (see FIG. 1) are respectively inserted into the eight coolant flow paths h9 provided in the plate-like body P9.

FIG. 3 is a vertical cross-sectional view (cross-sectional view taken along the line II in FIG. 1) including the header 11 of the heat exchanger.
Note that FIG. 3 is a vertical cross-sectional view at a position where the four second holes h2 (see FIG. 2) provided in the second plate-like body P2 cannot be seen. Actually, there are two second holes h2 on the front side of the paper surface of FIG. 3, and the remaining two second holes h2 on the back side of the paper surface.

As described above, a disk-shaped space G is formed between the recess R1 of the first plate-shaped body P1 and the second plate-shaped body P2. Further, the positions of the first hole h1 of the recess R1 and the four second holes (see FIG. 2) of the second plate-like body P2 are shifted when viewed from the side. In other words, in the present embodiment, instead of directing the coolant flowing through the pipe K to the four second holes h2 as it is, the coolant is made to once collide with the plate surface of the second plate-like body P2.

A projection area J shown in FIG. 3 is a circular area when the first hole h1 of the first plate-like body P1 is projected onto one side plate surface of the second plate-like body P2. Here, the term "projection" means projecting the region of the first hole h1 onto the second plate P2 in the axial direction of the first hole h1 (refrigerant flow direction). there is

FIG. 4 is a side view of the header 11 of the heat exchanger.
In addition, in FIG. 4, the second hole h2 and the refrigerant flow path h21, which are not actually visible, are indicated by two-dot chain lines. As shown in FIGS. 4 and 3, in a circular projection area J (dot display area) when the first hole h1 of the recess R1 of the first plate P1 is projected onto the second plate P2, , the plate surface of the second plate-like body P2 exists. As a result, the coolant traveling to the other side through the first hole h1 collides with the plate surface of the second plate-shaped body P2, and the coolant after the collision flows into the space G between the recess R1 and the second plate-shaped body P2. (see FIG. 3) are distributed radially.

Also, the four second holes h2 are scattered around the projection area J in the second plate-like body P2. For such four second holes h2, it is preferable that the distances between the respective second holes h2 and the center c of the projection area J are equal. As a result, the coolant that has collided with the plate surface of the second plate-like body P2 can be distributed substantially evenly to the four second holes h2.

In the example shown in FIG. 4, the diameters of the four circular second holes h2 are equal, and the distances between adjacent second holes h2 are equal. This facilitates even distribution of the coolant to the four second holes h2.

Further, it is preferable that four second holes h2 exist outside the projection area J, as shown in FIG. As a result, the coolant flowing through the first holes h1 is not directly guided to the second holes h2, and once collides with the projection area J of the second plate P2, so that the coolant is distributed substantially evenly to the four second holes h2. distributed. Incidentally, the configuration in which a part of the second hole h2 overlaps the projection area J is also included in the fact that the plate surface of the second plate-like body P2 exists outside the projection area J.

<effect>
According to the first embodiment, the plate surface of the second plate-like body P2 exists in the projection area J when the first hole h1 is projected onto the second plate-like body P2 (see FIGS. 3 and 4). The periphery of the projection area J is dotted with four second holes h2. According to such a configuration, the coolant that is guided to the first hole h1 and directed to the other side once collides with the plate surface of the second plate-like body P2, causing a gap between the recess R1 and the second plate-like body P2. Radially dispersed in space G (see FIG. 3). As a result, the coolant is substantially evenly distributed to the four second holes h2 provided in the second plate-like body P2.

As a configuration different from the first embodiment, for example, an "x"-shaped hole (not shown) is provided in the second plate-like body P2, and the coolant flowing through the first hole h1 is "x". It is also conceivable to direct the coolant directly to the shaped holes and divide the coolant into four flows. However, in such a configuration, there is a high possibility that more refrigerant will flow into the lower portion than the upper portion of the "X"-shaped hole due to the effect of gravity, resulting in uneven distribution of the refrigerant.

On the other hand, according to the first embodiment, as described above, the coolant is caused to once collide with the plate surface of the second plate-like body P2 and is radially dispersed, so that the coolant is substantially evenly distributed in the four second holes h2. Refrigerant can be distributed. As described above, according to the first embodiment, it is possible to provide the heat exchanger 1 that can appropriately distribute the refrigerant with a simple configuration.

Further, when the number of refrigerant distributions is changed in the design stage of the header 11, the number of the second holes h2 is appropriately changed, and accordingly, the plate on the other side (downstream side) of the second plate-like body P2 is changed. The number of the shaped bodies and the like may be appropriately changed. Thus, according to the first embodiment, the number of refrigerant distributions can be easily changed. Further, by appropriately changing the volume of the recess R1, the size and arrangement of the first hole h1 and the second hole h2, etc., it is possible to intentionally make the distribution ratio of the refrigerant uneven.

<<Second embodiment>>
The second embodiment differs from the first embodiment in that eight second holes h2A (see FIG. 5) are provided at predetermined locations of the second plate-like body P12 (see FIG. 5). The second embodiment differs from the first embodiment in that five other plate-like bodies P13 to P17 (see FIG. 5) are provided on the other side of the second plate-like body P12 (see FIG. 5). is different. In addition, about others, it is the same as that of 1st Embodiment. Therefore, the portions different from the first embodiment will be described, and the description of the overlapping portions will be omitted.

FIG. 5 is an exploded perspective view including a header 11A of the heat exchanger according to the second embodiment.
As shown in FIG. 5, the header 11A includes a first plate-like body P11 to which the pipe K is connected, a second plate-like body P12 adjacent to the other side of the first plate-like body P11, and a second plate-like body P11. and five other plate-like bodies P13 to P17 laminated on the other side of the body P12.

The first plate-like body P11 has a concave portion R1 and an insertion portion R2. The recess R1 has a circular shape when viewed from one side, and is recessed to one side in a vertical cross-sectional view. A single circular first hole h1 is provided as a coolant flow path at a predetermined location above the center of the recess R1. The insertion portion R2 is a cylindrical portion into which the pipe K is inserted, and is formed integrally with the recess R1.

Eight second holes h2A communicating with a space (not shown) between the second plate-like body P12 and the recess R1 are provided as refrigerant flow paths. That is, eight circular second holes h2A are scattered around the first hole h1 provided in the recess R1.

Then, the coolant that collides with the plate surface of the second plate-like body P12 through the pipe K and the first holes h1 in sequence is radially dispersed, and the dispersed coolant is distributed substantially evenly to the eight second holes h2A. It's like The arrangement of the eight second holes h2A will be described later.

In addition, in the second plate-like body P2, two longitudinally elongated coolant passages h21 are provided below the eight second holes h2A. These coolant channels h21 do not communicate with the space (not shown) between the second plate P12 and the recess R1, but instead communicate with the coolant channels h13 of the other plate P13. communicates with a part of

The plate-like body P13 shown in FIG. 5 is laminated on the other side of the second plate-like body P12. The plate-like body P13 is provided with coolant flow paths h13 for guiding the coolant divided into eight by the second holes h2A to predetermined positions in the vertical direction.
The four plate-like bodies P14 to P17 are stacked on the other side of the plate-like body P13. The plate-like body P14 is provided with eight coolant passages h14 at regular intervals in the vertical direction. The same applies to the remaining plate-like bodies P15 to P17. Ends of flat tubes (not shown) are respectively inserted into the eight coolant channels h17 of the plate-like body P17 arranged at the other end of the header 11A.

FIG. 6 is a side view of the header 11A of the heat exchanger.
In addition, in FIG. 6, the second hole h2A and the refrigerant flow path h21, which are not actually visible, are illustrated by chain double-dashed lines.
As shown in FIG. 6, the projection area JA (dot display area) when the first hole h1 provided in the concave portion R1 of the first plate P11 is projected onto the second plate P12 includes the second A plate surface of the plate-like body P12 (see FIG. 5) exists. As a result, the coolant flowing through the first hole h1 collides with the plate surface of the second plate-shaped body P12, and the coolant after the collision radiates in the space between the recess R1 and the second plate-shaped body P12. distributed to

The eight second holes h2A provided in the second plate P12 include five upper holes h2u existing above the projection area JA and three lower holes h2d existing below the projection area JA. ,It is included.
Note that being "above" the projection area JA means that the height of the center of the upper hole h2u is equal to or higher than the height of the center cA of the projection area JA. Also, being "below" the projection area JA means that the height of the center of the lower hole h2d is less than the height of the center cA of the projection area JA.

Also, the distance between the upper hole h2u and the center cA of the projection area JA is preferably shorter than the distance between the lower hole h2d and the center cA of the projection area JA. As a result, even if the coolant that has collided with the second plate-like body P12 tends to go slightly downward, the coolant can be distributed substantially evenly to the eight second holes h2A. It should be noted that the degree to which gravity affects the distribution of the refrigerant varies depending on the shape and volume of the recess R1.

Further, among the plurality of second holes h2A, it is preferable that the higher the position, the shorter the distance between the second hole h2A and the center cA of the projection area JA. For example, the distance between the second highest upper hole h2u and the center cA is shorter than the distance between the third highest upper hole h2u and the center cA (other The same applies to the second hole h2A of ). As a result, even if the refrigerant tends to be biased downward due to gravity, the refrigerant can be distributed substantially evenly to the respective second holes h2A.

<effect>
According to the second embodiment, the distance between the upper hole h2u and the center cA of the projection area JA is shorter than the distance between the lower hole h2d and the center cA of the projection area JA. Therefore, even if the coolant that has collided with the second plate-like body P12 tends to move downward, the coolant can be distributed substantially evenly to the eight second holes h2A.

Further, according to the second embodiment, since eight second holes h2A are provided in the second plate-like body P12, the plate-like body stacked on the other side (downstream side) of the second plate-like body P12 The number of sheets of P13 to P17 (see FIG. 5) can be reduced to five. Therefore, the total number of plate-like members P11 to P17 constituting the header 11A (7 plates in total) can be reduced. As a result, the installation space for the header 11A can be reduced, and the manufacturing cost of the header 11A can be reduced.

<<Third Embodiment>>
In the third embodiment, a heat exchanger 1B (see FIG. 7) in which a plurality of headers 11 (see FIG. 7) are arranged side by side in the height direction will be described. The configuration of each header 11 of the heat exchanger 1B is the same as that of the first embodiment. Therefore, the portions different from the first embodiment will be described, and the description of the overlapping portions will be omitted.

FIG. 7 is a perspective view of a heat exchanger 1B according to the third embodiment.
In addition, in FIG. 7, the plurality of fins F1 and F2 arranged at predetermined intervals are illustrated in a simplified manner. As shown in FIG. 7, the heat exchanger 1B includes multiple headers 11, multiple fins F1 and F2, and multiple flat tubes M. As shown in FIG. Also, a plurality of headers 11 are arranged side by side in the vertical direction.

For example, five headers 11 are vertically arranged on one side (the right side of the paper surface of FIG. 7) of a plurality of flat tubes M passing through the fins F1, and a predetermined number of headers 11 are also vertically arranged on the other side. are placed side by side. Another fin F2 is arranged below the fin F1. A predetermined number of headers 11 are also arranged in the vertical direction on both sides of the flat tube M passing through the fins F2.

The number of flat tubes M connected to the header 11 may be, for example, four, six, or eight. Also, the configuration of the header 11 (the first plate-like body P1 and the second plate-like body P2: see FIG. 2) is the same as that of the first embodiment, so the description thereof will be omitted.

<effect>
According to the third embodiment, it is possible to provide the heat exchanger 1B capable of properly distributing the refrigerant via the header 11 having a simple configuration.

<<Fourth Embodiment>>
In the fourth embodiment, the configuration of the heat exchanger 1B (see FIG. 7) described in the third embodiment is applied as the outdoor heat exchanger 4 (see FIG. 8) and the indoor heat exchanger 8 (see FIG. 8). The air conditioner W (see FIG. 8) will be described. The configurations of the outdoor heat exchanger 4 and the indoor heat exchanger 8 are the same as those of the heat exchanger 1B described in the third embodiment, so description thereof will be omitted.

FIG. 8 is a configuration diagram including a refrigerant circuit Q of an air conditioner W according to the fourth embodiment.
8 indicate the flow of the refrigerant during the cooling operation.
On the other hand, the dashed arrows in FIG. 8 indicate the flow of refrigerant during heating operation.
The air conditioner W is a device that performs air conditioning such as cooling operation and heating operation. As shown in FIG. 8, the air conditioner W includes a compressor 2, an accumulator 3, an outdoor heat exchanger 4 (heat exchanger), an outdoor fan 5, and an outdoor expansion valve 6 (expansion valve). I have. In addition to the configuration described above, the air conditioner W includes an indoor expansion valve 7 (expansion valve), an indoor heat exchanger 8 (heat exchanger), an indoor fan 9, and a four-way valve 10. there is

In the example shown in FIG. 8, a compressor 2, an accumulator 3, an outdoor heat exchanger 4, an outdoor fan 5, an outdoor expansion valve 6, and a four-way valve 10 are provided in the outdoor unit Uo. On the other hand, the indoor expansion valve 7, the indoor heat exchanger 8, and the indoor fan 9 are provided in the indoor unit Ui. The outdoor unit Uo and the indoor unit Ui are connected via a check valve V and a pipe k that form part of the refrigerant circuit Q, which will be described later.

The compressor 2 is a device that compresses gaseous refrigerant. As such a compressor 2, for example, a scroll compressor or a rotary compressor is used, but the compressor 2 is not limited thereto.

The outdoor heat exchanger 4 is a heat exchanger in which heat is exchanged between the refrigerant flowing through the heat transfer tubes and the outside air sent from the outdoor fan 5 . This outdoor heat exchanger 4 has the same configuration as the heat exchanger 1B (see FIG. 7) described in the third embodiment.
The outdoor fan 5 is a fan that sends outside air to the outdoor heat exchanger 4 and is arranged near the outdoor heat exchanger 4 .

The outdoor expansion valve 6 is a valve that reduces the pressure of refrigerant condensed in a "condenser" (one of the outdoor heat exchanger 4 and the indoor heat exchanger 8). Then, the refrigerant decompressed by the outdoor expansion valve 6 is guided to the "evaporator" (the other of the outdoor heat exchanger 4 and the indoor heat exchanger 8) through the pipe k. The indoor expansion valve 7 provided near the indoor heat exchanger 8 also has the same function as the outdoor expansion valve 6 .

The indoor heat exchanger 8 is a heat exchanger in which heat is exchanged between the refrigerant flowing through the heat transfer tubes and the indoor air sent from the indoor fan 9 (the air in the air-conditioned space). This indoor heat exchanger 8 also has the same configuration as the heat exchanger 1B (see FIG. 7) described in the third embodiment.
The indoor fan 9 is a fan that sends indoor air into the indoor heat exchanger 8 and is arranged near the indoor heat exchanger 8 .

The four-way valve 10 is a valve that switches the flow path of the refrigerant according to the operation mode of the air conditioner W. For example, during cooling operation (see solid line arrows in FIG. 8), the compressor 2, the outdoor heat exchanger 4 (condenser), the outdoor expansion valve 6 (expansion valve), the indoor expansion valve 7 (expansion valve), and The refrigerant circulates in the refrigeration cycle through the indoor heat exchangers 8 (evaporators) in sequence.

On the other hand, during heating operation, the compressor 2, the indoor heat exchanger 8 (condenser), the indoor expansion valve 7 (expansion valve), the outdoor expansion valve 6 (expansion valve), and the outdoor heat exchanger 4 (evaporator) are sequentially operated. , the refrigerant circulates in the refrigeration cycle. Thus, in the refrigerant circuit Q in which the refrigerant flows sequentially through the compressor 2, the "condenser", the "expansion valve", and the "evaporator", one of the "condenser" and the "evaporator" is One is the outdoor heat exchanger 4 and the other is the indoor heat exchanger 8 .
Devices such as the compressor 2, the outdoor fan 5, the outdoor expansion valve 6, the indoor expansion valve 7, and the indoor fan 9 are driven based on commands from a control device (not shown).

<effect>
According to the fourth embodiment, it is possible to provide an air conditioner W that can appropriately distribute the refrigerant in the outdoor heat exchanger 4 and the indoor heat exchanger 8 . As a result, it is possible to prevent the liquid refrigerant from accumulating in the lower portions of the outdoor heat exchanger 4 and the indoor heat exchanger 8, thereby improving the heat exchange efficiency.

<<Modification>>
Although the heat exchanger 1, the air conditioner W, and the like according to the present invention have been described in each embodiment, the present invention is not limited to these descriptions, and various modifications can be made.
For example, in the first embodiment (see FIG. 2), a configuration in which four second holes h2 are provided will be described, and in the second embodiment (see FIG. 5), a configuration in which eight second holes h2A are provided has been described, but it is not limited to this. That is, the number of second holes h2 provided in the second plate-like body P2 may be two, three, five to seven, or nine or more.

Also, in each embodiment, the description has been given of the case where the flow direction of the coolant guided to the first hole h1 through the pipe K (see FIG. 2) is the horizontal direction, but the present invention is not limited to this. That is, the flow direction of the coolant guided to the first hole h1 may be configured not to be parallel to the vertical direction (the direction of gravity). For example, the flow direction of the coolant may be horizontal or may be oblique to the horizontal. According to such a configuration, the coolant collides with the plate surface of the second plate-like body P2 and diffuses radially, so that the influence of gravity on distribution of the coolant can be alleviated.

Further, in the first embodiment (see FIG. 2), the configuration in which the first plate-like body P1 is arranged at one end of the plurality of laminated plate-like bodies P1 to P9 has been described. Not exclusively. For example, on one side of the first plate-like body P1, another plate-like body (not shown) provided with a coolant channel is adjacent, and on the other side of the first plate-like body P1, a plurality of second plate-like bodies are provided. A configuration in which the second plate-like body P2 provided with two holes h2 is adjacent to each other may also be adopted.
Alternatively, the recesses R1 and the first holes h1 may be provided at a plurality of locations on the first plate P1, and correspondingly, a plurality of second holes h2 may be provided at predetermined locations on the second plate P2. good. The same can be said for the second to fourth embodiments.

Further, for example, a structure in which a plurality of pairs of structural bodies each including the first plate-like body P1 and the second plate-like body P2 as a pair may be stacked. Instead of distributing the refrigerant via the pipe K, the structure described above may be used to distribute the refrigerant. As a result, the installation space for the heat exchanger can be further reduced.
Moreover, although each embodiment demonstrated the example which the "heat-transfer tube" connected to the header 11 is the flat tube M, it does not restrict to this. For example, the "heat transfer tube" may be a so-called round pipe, or may be of another type.

Moreover, although each embodiment demonstrated the structure by which recessed part R1 is circular in front view, it does not restrict to this. That is, the shape of the concave portion R1 may be an elliptical shape, a rectangular shape, a polygonal shape, or the like when viewed from the front.
Moreover, although each embodiment demonstrated the structure by which a refrigerant|coolant flows through the other side (or one side) through the header 11, it does not restrict to this. For example, the coolant flow path may be configured appropriately so that the coolant guided to the other side through the header 11 goes to the one side along the route and then moves to the other side.
Also, the first plate-like body P1 does not have to be a single member, and may be composed of a plurality of members. To give a specific example, a member (not shown) forming the recess R1 and the insertion portion R2, and a plate-like member (not shown) provided with a circular hole (not shown) in which this member is fitted ) may be combined to configure the first plate-like body P1.
Similarly, the second plate-like body P2 does not have to be a single member, and may be composed of a plurality of members. For example, the second plate-like body P2 may be configured by stacking two plate-like bodies (not shown) each provided with a plurality of second holes h2.

Further, in the fourth embodiment, both the "condenser" and the "evaporator" have been described as having the same configuration as the heat exchanger 1B (see FIG. 7) of the third embodiment. do not have. That is, the "condenser" or "evaporator" may have the same configuration as the heat exchanger 1B of the third embodiment. That is, at least one of the "condenser" and "evaporator" heat exchanger may have the configuration described in the second embodiment.

Moreover, each embodiment can be appropriately combined. For example, the header 11A (see FIG. 5) described in the second embodiment may be applied to the third embodiment, and a plurality of headers 11A may be arranged vertically. Furthermore, a heat exchanger having such a configuration may be applied to the outdoor heat exchanger 4 and/or the indoor heat exchanger 8 described in the fourth embodiment (see FIG. 8).

Further, in the fourth embodiment (see FIG. 8), the air conditioner W provided with one outdoor unit Uo and one indoor unit Ui has been described, but the present invention is not limited to this. For example, each embodiment can be applied to a multi-type air conditioner in which a plurality of outdoor units are provided in one system of air conditioner. In addition to air conditioners, each embodiment can also be applied to other "refrigeration cycle devices" such as refrigerators, refrigerators, and water heaters.

Moreover, each embodiment is described in detail in order to explain the present invention in an easy-to-understand manner, and is not necessarily limited to those having all the described configurations. Moreover, it is also possible to add, delete, or replace a part of the configuration of each embodiment with another configuration.
Further, the mechanisms and configurations described above show those considered necessary for explanation, and do not necessarily show all the mechanisms and configurations on the product.

1, 1B heat exchanger 2 compressor 3 accumulator 4 outdoor heat exchanger (condenser/evaporator, heat exchanger)
5 outdoor fan 6 outdoor expansion valve (expansion valve)
7 Indoor expansion valve (expansion valve)
8 indoor heat exchanger (evaporator/condenser, heat exchanger)
9 indoor fan 10 four-way valve 11, 11A header (refrigerant distributor)
F, F1, F2 Fin G Space J, JA Projection area K Pipe M Flat tube (heat transfer tube)
P1, P11 first plate-like body (plate-like body)
P2, P12 Second plate-like body (plate-like body)
P3, P4, P5, P6, P7, P8, P9 Plate P13, P14, P15, P16, P17 Plate Q Refrigerant circuit R1 Recess R2 Insertion portion Uo Outdoor unit Ui Indoor unit V Block valve W Air conditioner c, cA Center h1 First hole (refrigerant channel)
h2, h2A Second hole (refrigerant channel)
h3, h4, h5, h6, h7, h8, h9, h13, h14, h15, h16, h17, h21 coolant channel h2u upper hole (refrigerant channel, second hole)
h2d lower hole (refrigerant channel, second hole)

Claims (7)

a refrigerant distributor formed by stacking a plurality of plate-shaped bodies;
a plurality of fins arranged at predetermined intervals;
a plurality of heat transfer tubes passing through the plurality of fins and connected to the refrigerant distributor,
Each of the plurality of plate-shaped bodies is provided with a coolant channel through which a coolant flows,
The plurality of plate-shaped bodies include a first plate-shaped body having a concave portion recessed on one side and a second plate-shaped body adjacent to the other side of the first plate-shaped body,
One first hole is provided in the recess as the coolant flow path,
The second plate-shaped body is provided with a plurality of second holes communicating with the space between the recesses as the coolant flow path,
A plate surface of the second plate-shaped body exists in a projection area when the first hole is projected onto the second plate-shaped body ,
the plurality of second holes are scattered as separate holes in the second plate-like body so as to surround the projection area;
A heat exchanger according to claim 1, wherein, when the recess is projected onto the second plate-shaped body, edges of a surface of the recess facing the space surround the plurality of second holes. the first plate-shaped body is present at one end of the plurality of stacked plate-shaped bodies,
2. The heat exchanger according to claim 1, wherein a pipe that guides a refrigerant is connected to the first hole. 2. The heat exchanger according to claim 1, wherein the plurality of second holes have equal distances between each of the second holes and the center of the projection area. The plurality of second holes include an upper hole existing above the projection area and a lower hole existing below the projection area,
2. The heat exchanger according to claim 1, wherein the distance between the upper hole and the center of the projected area is shorter than the distance between the lower hole and the center of the projected area. The heat exchanger according to claim 1, wherein, among the plurality of second holes, the higher the position of the second hole, the shorter the distance between the second hole and the center of the projection area. . The heat exchanger according to any one of Claims 1 to 5 , wherein the flow direction of the refrigerant guided to the first hole is not parallel to the vertical direction. including a compressor, an outdoor heat exchanger , an expansion valve, and an indoor heat exchanger ;
At least one of the outdoor heat exchanger and the indoor heat exchanger ,
a refrigerant distributor formed by stacking a plurality of plate-shaped bodies;
a plurality of fins arranged at predetermined intervals;
a plurality of heat transfer tubes passing through the plurality of fins and connected to the refrigerant distributor,
Each of the plurality of plate-shaped bodies is provided with a coolant channel through which a coolant flows,
The plurality of plate-shaped bodies include a first plate-shaped body having a concave portion recessed on one side and a second plate-shaped body adjacent to the other side of the first plate-shaped body,
One first hole is provided in the recess as the coolant flow path,
The second plate-shaped body is provided with a plurality of second holes communicating with the space between the recesses as the coolant flow path,
A plate surface of the second plate-shaped body exists in a projection area when the first hole is projected onto the second plate-shaped body ,
the plurality of second holes are scattered as separate holes in the second plate-like body so as to surround the projection area;
An air conditioner according to claim 1, wherein, when the recess is projected onto the second plate-like body, edges of a surface of the recess facing the space surround the plurality of second holes.

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