Patent Description:
As a heat exchanger, a multi-flow type heat exchanger including a plurality of flat tubes, a plurality of fins, and a pair of headers is known.

The plurality of flat tubes are inserted into the plurality of fins in a state with an interval in the vertical direction. Each flat tube is formed with a plurality of flow paths disposed at intervals in the width direction. The plurality of fins are disposed at intervals in a direction in which the flat tube extends.

Each of the pair of headers extends in the vertical direction. One header is connected to the plurality of flat tubes in a state in which one end portion of each of the plurality of flat tubes is accommodated. Another header is connected to the plurality of flat tubes in a state in which another end portion of each of the plurality of flat tubes is accommodated.

When the heat exchanger is used as an evaporator, gas-liquid two-phase refrigerant is introduced into the header from the outside as refrigerant.

From the viewpoint of fully utilizing a heat transfer region of the heat exchanger, it is necessary to prevent the bias of the distribution of the refrigerant to each flat tube and the plurality of flow paths formed in each flat tube without depending on the flow rate of the refrigerant introduced into the header.

However, in a simple configuration in which the one end portion of each of the plurality of flat tubes is simply inserted into the header, the distribution of the refrigerant to each flat tube is biased due to the influence of inertial force and gravity. That is, when the flow rate of the refrigerant is small, the influence of gravity becomes dominant and a large amount of the liquid phase refrigerant is supplied to the flat tube positioned below the header. Further, when the flow rate of the refrigerant is large, the influence of the inertial force becomes dominant and a large amount of the liquid phase refrigerant is supplied to the flat tube positioned above the header.

PTL <NUM> discloses a heat exchanger for the purpose of preventing the flow distortion of the refrigerant due to the amount of the circulation of the refrigerant.

Specifically, PTL <NUM> discloses a heat exchanger including a first straightening plate that partitions between a first internal space, which is disposed at a lower portion of an internal space of a header, and a space, which is disposed above the first internal space, and a first partition plate that partitions the space, which is disposed above the first internal space, into a first outflow space and a first loop space, in which the refrigerant, which is introduced into the first internal space, is guided to the first outflow space through the two first inflow ports formed in the first straightening plate, and the refrigerant is circulated between the first outflow space and the first loop space.

On the other hand, there is a fin of a heat exchanger having a flat shape including a thin plate-shaped fin body that extends in the vertical direction, a plurality of flat tube insertion portions into which flat tubes are inserted, and a communication portion that guides condensed water from an upper side to a lower side.

The flat tube insertion portion is formed in the fin body and extends in the horizontal direction orthogonal to the vertical direction. The flat tube insertion portion is formed such that the flat tube insertion portion does not divide the fin body in the horizontal direction.

The communication portion is configured with a part, of the fin body, that is positioned outside the plurality of flat tube insertion portions. The communication portion extends continuously in the vertical direction.

When the fin having the above configuration is used, there is a problem that the fin tends to collapse at a part, of the communication portion, that faces the flat tube insertion portion in the horizontal direction. As a technique for solving such a problem, there is a heat exchanger disclosed in PTL <NUM>.

PTL <NUM> discloses the formation of a heat transfer acceleration portion that is formed in a communication portion, that faces a flat tube insertion portion in the horizontal direction between fin interval adjustment portions formed at intervals in the vertical direction, and that protrudes to one side in a disposition direction (hereinafter referred to as a "fin disposition direction") of a plurality of fins. A plurality of heat transfer acceleration portions are disposed at intervals in the vertical direction.

On the other hand, PTL <NUM> discloses that an interval (fin pitch) between fins adjacent to each other is regulated by first and second interval holding portions formed on the plate-shaped fins.

The first interval holding portion is formed on a leading edge (an edge positioned on an upstream-side in an air flow direction) side of a flat tube in a state in which the flat tube is disposed on the fin. The second interval holding portion is formed in the fin positioned between the flat tubes disposed in the vertical direction.

PTL <NUM> discloses that the first and second interval holding portions are formed by folding a part of the fin.

Further, PTL <NUM> discloses that the part of the fin is folded so as to face the air flow direction when the first interval holding portion is formed.

Further, PTL <NUM> discloses a configuration in which a tip portion of the flat tube is in contact with only a part of the first interval holding portion.

PTL4 discloses a heat exchanger according to the preamble of claim <NUM>.

In general, when the number of flat tubes is large, a space in the header is divided into a plurality of spaces by disposing a horizontal partition plate, which extends in the horizontal direction in a header, in the vertical direction.

In order to equalize the distribution by using the heat exchanger described in PTL <NUM>, it is desirable to dispose the first outflow space and the first loop space continuously in the vertical direction. Therefore, it may be difficult to secure a space for providing the first internal space, and it may be difficult to provide the first internal space. Further, the number of horizontal partition plates may increase, which may complicate the manufacturing step.

Further, in PTL <NUM>, in order to guide the refrigerant, which is introduced into the first internal space, to the first outflow space through the two first inflow ports that are formed in the first straightening plate, the state of the refrigerant may differ in the width direction of the flat tube. In this case, it may be difficult to prevent the bias of the distribution of the refrigerant with respect to the plurality of flow paths formed in each flat tube in the width direction.

On the other hand, the heat transfer acceleration portion disclosed in PTL <NUM> is formed by performing a press process on a plate-shaped base material member which is a base material of the fin. Therefore, a recess having a bottom is formed on another side of the heat transfer acceleration portion in the fin disposition direction. As a result, the condensed water flowing through the communication portion may be accumulated at the bottom of the heat transfer acceleration portion, and it may be difficult to drain the condensed water downward through the communication portion.

On the other hand, in PTL <NUM>, the part of the fin is folded so as to face the air flow direction when the first interval holding portion is formed. Therefore, the first interval holding portion becomes a flow resistance, and there is a possibility that the pressure loss of air increases.

Further, in PTL <NUM>, since the tip portion of the flat tube is in contact with only the part of the first interval holding portion, it may be difficult to improve the thermal conductivity between the fin and the flat tube.

The present disclosure has been made in order to solve the above problems, and the object of the present disclosure is to provide a heat exchanger, a heat exchanger unit, and a refrigeration cycle device capable of simplifying a manufacturing step and capable of preventing a bias in distribution of refrigerant with respect to each flat tube and a plurality of flow paths formed in each flat tube in the width direction without depending on the flow rate of the refrigerant supplied in a header.

Further, the present disclosure has been made in order to solve the above problems, and the object of the present disclosure is to provide a heat exchanger, a heat exchanger unit, and a refrigeration cycle device capable of preventing the fin from collapsing while preventing the obstruction of the flow of condensed water in a communication portion.

Further, the present disclosure has been made in order to solve the above problems, and the object of the present disclosure is to provide a heat exchanger, a heat exchanger unit, and a refrigeration cycle device capable of regulating a fin pitch while preventing a pressure loss of air and improving the thermal conductivity between a flat tube and a fin.

In order to solve the above problems, a heat exchanger according to the present invention is defined in claim <NUM>.

According to a heat exchanger, a heat exchanger unit, and a refrigeration cycle device of the present disclosure, it is possible to prevent a bias in distribution of refrigerant with respect to each flat tube and a plurality of flow paths formed in each flat tube in the width direction without depending on the flow rate of the refrigerant supplied in a header while preventing the complexity of a manufacturing step.

On the other hand, according to the heat exchanger, the heat exchanger unit, and the refrigeration cycle device of the present disclosure, it is possible to prevent a fin from collapsing while preventing the obstruction of a flow of condensed water in a communication portion.

On the other hand, according to the heat exchanger, the heat exchanger unit, and the refrigeration cycle device of the present disclosure, the fin pitch can be regulated while preventing the pressure loss of air, and the thermal conductivity between the flat tube and the fin can be improved.

With reference to <FIG>, an overall configuration of a refrigeration cycle device <NUM> of a first embodiment will be described. In <FIG>, a solid arrow indicates a direction in which refrigerant flows during heating operation, and a dotted arrow indicates a direction in which the refrigerant flows during cooling operation.

The refrigeration cycle device <NUM> has a configuration in which a four-way valve <NUM>, a compressor <NUM>, a first heat exchanger unit <NUM>, an expansion valve <NUM>, and a second heat exchanger unit <NUM> are connected by a refrigerant pipe <NUM>. The refrigeration cycle device <NUM> includes an outdoor unit <NUM> and an indoor unit <NUM>.

The outdoor unit <NUM> includes the four-way valve <NUM>, the compressor <NUM>, the first heat exchanger unit <NUM>, and the expansion valve <NUM>.

The four-way valve <NUM> includes connecting portions 15A to 15D to which any one of both ends of first and second refrigerant pipes 14A and 14B configuring the refrigerant pipe <NUM> is connected.

One end of the first refrigerant pipe 14A is connected to the connecting portion 15A. The other end of the first refrigerant pipe 14A is connected to the connecting portion 15B.

One end of the second refrigerant pipe 14B is connected to the connecting portion 15C. The other end of the second refrigerant pipe 14B is connected to the connecting portion 15D.

The four-way valve <NUM> having the above configuration switches the direction in which the refrigerant flows between the heating operation and the cooling operation. Specifically, during the cooling operation, the refrigerant is circulated in the order of the compressor <NUM>, the first heat exchanger unit <NUM>, the expansion valve <NUM>, and the second heat exchanger unit <NUM>.

On the other hand, during the heating operation, the refrigerant is circulated in the order of the compressor <NUM>, the second heat exchanger unit <NUM>, the expansion valve <NUM>, and the first heat exchanger unit <NUM>.

The compressor <NUM> is provided in the second refrigerant pipe 14B. The compressor <NUM> compresses the refrigerant that flows through the second refrigerant pipe 14B.

The first heat exchanger unit <NUM> includes a first blower <NUM> and a heat exchanger <NUM>.

The first blower <NUM> supplies air to the heat exchanger <NUM>.

The heat exchanger <NUM> will be described with reference to <FIG>. In <FIG> and <FIG>, the Z direction indicates the vertical direction. In <FIG>, the X direction indicates the extending direction of the flat tube <NUM> orthogonal to the Z direction. In <FIG>, <FIG>, the Y direction indicates the width direction of the flat tube <NUM> (the width direction of a nozzle portion <NUM>) orthogonal to the X direction and the Z direction. In <FIG>, the air flows in a direction of a paper surface (for example, a direction toward the paper surface). In <FIG>, the arrows indicate a direction in which the refrigerant flows when the heat exchanger <NUM> is used as an evaporator, and H indicates the height of a header body <NUM> (hereinafter referred to as the "height H"), respectively.

The heat exchanger <NUM> is used as a condenser during the cooling operation to dissipate heat to the outside and is used as an evaporator during the heating operation to absorb heat from the outside.

The heat exchanger <NUM> is provided in the first refrigerant pipe 14A positioned between the four-way valve <NUM> and the expansion valve <NUM>. The heat exchanger <NUM> includes a plurality of flat tubes <NUM>, a plurality of fins <NUM>, and a pair of headers <NUM>.

Next, the flat tube <NUM> will be described with reference to <FIG> and <FIG>. The flat tube <NUM> is a heat transfer tube in which an outside appearance has a flat shape. The flat tube <NUM> extends in the X direction. Inside the flat tube <NUM>, a plurality of flow paths 41A through which the refrigerant flows are formed at intervals in the Y direction.

The plurality of flat tubes <NUM> include a flat tube 41F disposed at the bottom and a flat tube <NUM> disposed second from the bottom.

The flat tube <NUM> includes a pair of end portions 41B and 41C disposed in the X direction. One end portion 41B is accommodated in one header <NUM>. The other end portion 41C is accommodated in the other header <NUM>. The plurality of flat tubes <NUM> are disposed in a state with an interval in the Z direction, and both sides in the X direction are supported by the pair of headers <NUM>.

Next, the plurality of fins <NUM> will be described with reference to <FIG>.

Each of the plurality of fins <NUM> includes a flat tube insertion portion 42A formed at intervals in the Z direction. The flat tube <NUM> is inserted into the flat tube insertion portion 42A.

Next, the configuration of the pair of headers <NUM> will be described with reference to <FIG> and <FIG> to <FIG>.

The pair of headers <NUM> are disposed so as to face each other in the X direction. One header <NUM> is connected to the plurality of flat tubes <NUM> such that one end portion 41B of each of the plurality of flat tubes <NUM> is disposed on an inner side of the one header <NUM>. The other header <NUM> is connected to the plurality of flat tubes <NUM> such that the other end portion 41C of each of the plurality of flat tubes <NUM> is disposed on an inner side of the other header <NUM>.

Here, the configuration of the header <NUM> on the evaporator inlet side, among the pair of headers <NUM>, will be described.

The header <NUM> includes a header body <NUM>, a partition plate <NUM>, a nozzle portion <NUM>, and a porous plate <NUM>.

Next, the header body <NUM> will be described with reference to <FIG>. The header body <NUM> is a tube-shaped member that extends in the Z direction and has upper and lower ends closed. The header body <NUM> partitions a column-shaped internal space <NUM> inside.

The header body <NUM> includes an opening 45A and a bottom surface 45a.

The opening 45A is formed on a side wall of the header body <NUM>. The tip portion of a first refrigerant pipe 14A is inserted into the opening 45A. The opening 45A is formed at a position facing the nozzle portion <NUM> in the X direction.

The bottom surface 45a has a first bottom surface 45aa, a second bottom surface 45ab, and a third bottom surface 45ac.

The first bottom surface 45aa is a surface for partitioning a lower end of a first space <NUM>. The second bottom surface 45ab is a surface for partitioning a lower end of a second space <NUM>.

The third bottom surface 45ac is disposed between the first bottom surface 45aa and the second bottom surface 45ab that are disposed in the X direction. The third bottom surface 45ac is connected to the first bottom surface 45aa and the second bottom surface 45ab.

Next, the partition plate <NUM> will be described with reference to <FIG>.

The partition plate <NUM> is disposed in the header body <NUM> in a state of extending in the Z direction. In the partition plate <NUM>, both ends of the partition plate <NUM>, which are disposed in the Y direction, are connected to the header body <NUM>.

The partition plate <NUM> divides the internal space <NUM> into the first space <NUM> and the second space <NUM>, which are disposed in the X direction, in a state in which the refrigerant can be circulated at an upper end portion and a lower end portion of the internal space <NUM>.

The first space <NUM> is disposed on a side to which the first refrigerant pipe 14A is connected. The second space <NUM> is disposed on a side to which the plurality of flat tubes <NUM> are connected. The partition plate <NUM> forms a circulation passage for the refrigerant.

The partition plate <NUM> includes an upper end surface 47a, a first surface 47b, a second surface 47c, a pair of lower end portions 47A and 47B (one lower end portion and the other lower end portion), and a cutout portion 47C.

The upper end surface 47a is disposed at a position separated downward from the header body <NUM> that faces the upper end surface 47a in the Z direction. The refrigerant moves between the first space <NUM> and the second space <NUM> through the opening formed between the header body <NUM>, which faces the upper end surface 47a, and the upper end surface 47a.

The first surface 47b is a plane orthogonal to the X direction and partitions the other side of the first space <NUM> in the X direction.

The second surface 47c is a surface disposed on the opposite side of the first surface 47b. The second surface 47c is a plane orthogonal to the X direction and partitions one side of the second space <NUM> in the X direction.

The lower end portion 47A is disposed on one side in the Y direction. The lower end 47Aa of the lower end portion 47A reaches the bottom surface 45a of the header body <NUM>.

The lower end portion 47B is disposed on the other side in the Y direction. The lower end 47Ba of the lower end portion 47B reaches the bottom surface 45a of the header body <NUM>.

The cutout portion 47C is formed between the lower end portion 47A and the lower end portion 47B. The cutout portion 47C has a rectangular shape. The refrigerant moves between the first space <NUM> and the second space <NUM> through the opening partitioned by the cutout portion 47C and the bottom surface 45a.

For example, when a round-shaped hole is used as a discharge outlet 49A of the nozzle portion <NUM>, the refrigerant is circulated from the first space <NUM> to the second space <NUM> through the cutout portion 47C that is positioned between the lower end portion 47A and the lower end portion 47B. At this time, the lower end portions 47A and 47B can prevent the refrigerant from flowing back from the second space <NUM> to the first space <NUM>.

Next, the nozzle portion <NUM> will be described with reference to <FIG> and <FIG>.

The nozzle portion <NUM> is disposed in the first space <NUM>. The nozzle portion <NUM> is fixed to the header body <NUM> and the partition plate <NUM>. Refrigerant circulation portions 54A through which the refrigerant passes are each formed on both sides of the nozzle portion <NUM> in the Y direction. The refrigerant circulation portion 54A is configured as a part of the first space <NUM>.

The nozzle portion <NUM> includes the discharge outlet 49A disposed on the lower end side. The discharge outlet 49A has a round shape when viewed from the Z direction.

When the heat exchanger <NUM> is operated as an evaporator, the refrigerant (gas-liquid two-phase refrigerant) is supplied into the nozzle portion <NUM> through the first refrigerant pipe 14A. The discharge outlet 49A causes the refrigerant to collide with the first bottom surface 45aa by blowing out the refrigerant in a direction toward the first bottom surface 45aa and reduces a difference in a state of the refrigerant in the Y direction. After colliding with the first bottom surface 45aa, the refrigerant flows to a lower portion of the second space <NUM> through the cutout portion 47C and then flows in a direction toward an upper end of the second space <NUM>, and is guided into the plurality of flow paths 41A formed in each flat tube <NUM>. The refrigerant, which is moved to the upper end portion of the second space <NUM>, flows to the upper end portion of the first space <NUM> and then flows in a direction toward the first bottom surface 45aa.

When the heat exchanger <NUM> is operated as a condenser, the refrigerant that flows into the second space <NUM> from the plurality of flat tubes <NUM> flows into the first refrigerant pipe 14A through the discharge outlet 49A.

By having the nozzle portion <NUM> with the above configuration, it is possible to reduce the difference in state of the refrigerant in the Y direction by causing the refrigerant, which is blown out from the discharge outlet 49A, to collide with the first bottom surface 45aa of the header body <NUM>. As a result, since the refrigerant having a small difference in state in the Y direction flows from the first space <NUM> toward the second space <NUM> (a space in which one end portion 41B of each of the plurality of flat tubes <NUM> is disposed), the bias of the distribution of the refrigerant with respect to the plurality of flow paths 41A, which are formed in each flat tube <NUM> in the Y direction, can be prevented without depending on the flow rate of the refrigerant that is introduced in the header <NUM>.

The nozzle portion <NUM> having the above configuration may be desirably disposed at a position lower than, for example, <NUM>/<NUM> the height of the header body <NUM>, more desirably at a position lower than <NUM>/<NUM> of the height of the header body <NUM>, and still more desirably at a position lower than <NUM>/<NUM> of the height of the header body <NUM>.

Further, the nozzle portion <NUM> having the above configuration may be disposed between, for example, the flat tube 41F disposed at the bottom and the flat tube <NUM> disposed second from the bottom, among the plurality of flat tubes <NUM>.

For example, when the nozzle portion <NUM> is disposed at a position higher than <NUM>/<NUM> of the height H of the header body <NUM>, since a distance from the discharge outlet 49A of the nozzle portion <NUM> to the first bottom surface 45aa of the header body <NUM> becomes too long, the flow of the refrigerant, which is blow out from the discharge outlet 49A, may slow down and it may be difficult to form a circulation flow of refrigerant in the header <NUM>.

Therefore, by disposing the nozzle portion <NUM> at a position lower than <NUM>/<NUM> of the height H of the header body <NUM>, it is possible to reduce the distance from the discharge outlet 49A to the first bottom surface 45aa of the header body <NUM>, thereby it becomes easy to form the circulation flow of the refrigerant in the header <NUM>.

Further, by disposing the nozzle portion <NUM> at a position lower than <NUM>/<NUM> of the height of the header body <NUM>, it is possible to further reduce the distance from the discharge outlet 49A to the first bottom surface 45aa of the header body <NUM>, thereby it becomes easier to form the circulation flow of the refrigerant in the header <NUM>.

Further, by disposing the nozzle portion <NUM> at a position lower than <NUM>/<NUM> of the height of the header body <NUM>, it is possible to still further reduce the distance from the discharge outlet 49A to the first bottom surface 45aa of the header body <NUM>, thereby it becomes still easier to form the circulation flow of the refrigerant in the header <NUM>.

As described above, by disposing the nozzle portion <NUM> between the flat tube 41F disposed at the bottom and the flat tube <NUM> disposed second from the bottom, the circulation flow of refrigerant in the header <NUM> can be easily formed.

Further, when the heat exchanger <NUM> is used as a condenser, the refrigerant (liquid phase refrigerant) that flows in the header <NUM> can be easily discharged to the outside of the header through the plurality of flat tubes <NUM>.

Next, the porous plate <NUM> will be described with reference to <FIG>.

The porous plate <NUM> is disposed so as to cover, in the horizontal direction, the first space <NUM> that is positioned above the nozzle portion <NUM>. The porous plate <NUM> is fixed to the header body <NUM> and the partition plate <NUM>. The porous plate <NUM> is formed with a plurality of holes 51A that allow the first space <NUM> to communicate in the Z direction. As the porous plate <NUM>, for example, a punching plate can be used.

In <FIG>, as an example, the punching plate is illustrated as an example of the porous plate <NUM>, but as the porous plate <NUM>, for example, a mesh-shaped member, a porous plate, or the like may be used.

By including the porous plate <NUM> having such a configuration, it is possible to prevent the movement of gas (gas refrigerant) from flowing back in a direction from the lower side toward the upper side of the first space <NUM>, thereby it becomes easy to form the circulation flow of the refrigerant in the header <NUM>.

According to the heat exchanger <NUM> of the first embodiment, by having the nozzle portion <NUM> with the above configuration, it is possible to reduce the difference in state of the refrigerant in the Y direction by causing the refrigerant, which is blown out from the discharge outlet 49A, to collide with the first bottom surface 45aa of the header body <NUM>. As a result, since the refrigerant having a small difference in state in the Y direction flows from the first space <NUM> toward the second space <NUM> (a space in which one end portion 41B of each of the plurality of flat tubes <NUM> is disposed), the bias of the distribution of the refrigerant with respect to the plurality of flow paths 41A, which are formed in each flat tube <NUM> in the width direction (Y direction), can be prevented while preventing the complexity of a manufacturing step and preventing the bias of the distribution of the refrigerant with respect to each flat tube <NUM>, by forming the circulation flow of the refrigerant (a flow that descends from the first space <NUM> and rises from the second space <NUM>) in the header <NUM> without depending on the flow rate of the refrigerant that is introduced in the header <NUM>.

According to first and second heat exchanger units <NUM> and <NUM> of the first embodiment, by providing the heat exchanger <NUM> having the above configuration, the heat exchange efficiency can be improved.

Next, the expansion valve <NUM> will be described with reference to <FIG>.

The expansion valve <NUM> is provided in 14A that is positioned between the first heat exchanger unit <NUM> and the second heat exchanger unit <NUM>.

The expansion valve <NUM> lowers the pressure of the refrigerant by expanding the liquefied high-pressure refrigerant by performing the heat exchanging.

The indoor unit <NUM> includes the second heat exchanger unit <NUM>. The second heat exchanger unit <NUM> includes the heat exchanger <NUM> and a second blower <NUM>.

The heat exchanger <NUM> that configures the second heat exchanger unit <NUM> is provided in the first refrigerant pipe 14A positioned between the expansion valve <NUM> and the four-way valve <NUM>.

According to the refrigeration cycle device <NUM> of the first embodiment, by having the first and second heat exchanger units <NUM> and <NUM> having the above configuration, the heat exchange efficiency can be improved.

The nozzle portion <NUM> and the first refrigerant pipe 14A may be integrally configured. For example, the first refrigerant pipe 14A may be inserted until the first refrigerant pipe 14A is in contact with the partition plate <NUM>, and a round hole (the discharge outlet 49A) may be provided on the side surface in the vicinity of the tip of the first refrigerant pipe 14A.

The heat exchanger <NUM> according to a modification example of the first embodiment will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals. In <FIG>, W1 indicates the width of the nozzle portion <NUM> in the Y direction (hereinafter referred to as a "width W1"), and W2 indicates the width of the refrigerant circulation portion 54A in the Y direction (hereinafter referred to as a "width W2"), respectively.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM> except that the heat exchanger <NUM> includes a pair of headers <NUM> in place of the pair of headers <NUM> that configure the heat exchanger <NUM> of the first embodiment.

The header <NUM> is configured in the same manner as the header <NUM> except that the header <NUM> includes the nozzle portion <NUM> in place of the nozzle portion <NUM> that configures the header <NUM>.

The nozzle portion <NUM> includes an discharge outlet 62A having a groove shape extending in the Y direction. The discharge outlet 62A blows out the refrigerant toward the bottom surface of the header body <NUM>.

The width W1 of the nozzle portion <NUM> is configured to be wider than the width of the nozzle portion <NUM> shown in <FIG>. As a result, the width W2 of the pair of refrigerant circulation portions 54A disposed on both sides of the nozzle portion <NUM> in the Y direction is configured to be narrower than the width of the pair of refrigerant circulation portions 54A shown in <FIG>.

A total value (= <NUM> × W2) of the width W2 of the pair of refrigerant circulation portions 54A, which are disposed on both sides of the nozzle portion <NUM> in the width direction (Y direction), may be configured to be smaller than a value of the width W1 of the nozzle portion <NUM>, for example.

According to the heat exchanger <NUM> according to the modification example of the first embodiment, by forming the discharge outlet 62A into a groove shape extending in the Y direction, the difference in state of the refrigerant in the Y direction can be further reduced as compared with a case where a shape of the discharge outlet is a round shape.

Further, by making a total value (= <NUM> × W2) of the width W2 of the pair of refrigerant circulation portions 54A, which are disposed on both sides of the nozzle portion <NUM> in the width direction (Y direction), to be smaller than a value of the width W1 of the nozzle portion <NUM>, it is possible to make a cross-sectional area of the flow path of the pair of refrigerant circulation portions 54A small. As a result, the occurrence of the flowing back of the refrigerant from the lower side toward the upper side in the first space <NUM> can be prevented.

A heat exchanger <NUM> according to a second embodiment will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals. The arrows shown in <FIG> indicate a direction in which the refrigerant flows when the heat exchanger <NUM> is used as an evaporator.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM> except that the heat exchanger <NUM> includes a header <NUM> in place of the header <NUM> that configures the heat exchanger <NUM> of the first embodiment. The header <NUM> is configured in the same manner as the header <NUM> except that the header <NUM> includes a first refrigerant guide portion <NUM>.

The first refrigerant guide portion <NUM> is provided on the first bottom surface 45aa of the header body <NUM>. The first refrigerant guide portion <NUM> includes a first guide surface 73a.

The first guide surface 73a is disposed such that a part of the first guide surface 73a and the discharge outlet 49A face each other in the Z direction. The first guide surface 73a guides the refrigerant in a direction from the first space <NUM> toward the second space <NUM>, causes the refrigerant to collide with an inner wall surface 45b of the header body <NUM>, which faces the first guide surface 73a in the X direction, and reduces the difference in state of the refrigerant in the width direction.

As the first guide surface 73a, for example, a recessed curved surface that is recessed in a direction separated from the lower end portion of the partition plate <NUM> can be used.

According to the heat exchanger <NUM> of the second embodiment, by including the first refrigerant guide portion <NUM> having the above configuration, the refrigerant that is blown out from the discharge outlet 49A of the nozzle portion <NUM> is guided to the second space <NUM>, and by causing the refrigerant to collide with the inner wall surface 45b of the header body <NUM> that partitions the second space <NUM>, the difference in state of the refrigerant in the width direction can be reduced.

Further, when the refrigerant is gas-liquid two-phase refrigerant and the flow rate of the refrigerant that is introduced into the header body <NUM> is small, it is possible to prevent the refrigerant from gas-liquid separation in the first space <NUM> and prevent the gas phase refrigerant from rising in the first space <NUM>. That is, the refrigerant circulation flow can be prevented from becoming difficult to form in the header body <NUM>.

Further, by making the first guide surface 73a a recessed curved surface that is recessed in the direction separated from the lower end portion of the partition plate, the refrigerant can be smoothly guided from the first space <NUM> to the second space <NUM>.

In the second embodiment, the nozzle portion <NUM> shown in <FIG> may be used in place of the nozzle portion <NUM> that configures the heat exchanger <NUM>.

A heat exchanger <NUM> according to a first modification example of the second embodiment will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals. The arrows shown in <FIG> indicate a direction in which the refrigerant flows when the heat exchanger <NUM> is used as an evaporator.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM> except that the heat exchanger <NUM> includes a header <NUM> in place of the header <NUM> that configures the heat exchanger <NUM> of the second embodiment. The header <NUM> is configured in the same manner as the header <NUM>, except that the header <NUM> is provided with a third refrigerant guide portion <NUM> with the configuration of the header <NUM>.

The third refrigerant guide portion <NUM> is provided in a part, of the lower end portion of the partition plate <NUM>, that is separated upward from the bottom surface 45a of the header body <NUM>. The third refrigerant guide portion <NUM> includes a third guide surface 83a.

The third guide surface 83a is disposed so as to face the first guide surface 73a. The third guide surface 83a guides the refrigerant in a direction from the first space <NUM> toward the second space <NUM>. As the third refrigerant guide portion <NUM>, for example, a cylinder-shaped member extending in the width direction of the partition plate <NUM> can be used.

According to the heat exchanger <NUM> of the first modification example of the second embodiment, by providing the third refrigerant guide portion <NUM> having the above configuration, the third guide surface 83a (the outer peripheral surface of the cylinder-shaped member) can guide the refrigerant in the direction from the first space <NUM> toward the second space <NUM>.

In the first modification example of the second embodiment, the nozzle portion <NUM> shown in <FIG> may be used in place of the nozzle portion <NUM> that configures the heat exchanger <NUM>.

A heat exchanger <NUM> according to a second modification example of the second embodiment will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals. The arrows shown in <FIG> indicate a direction in which the refrigerant flows when the heat exchanger <NUM> is used as an evaporator.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM> except that the heat exchanger <NUM> includes a header <NUM> in place of the header <NUM> that configures the heat exchanger <NUM> of the second embodiment. The header <NUM> is configured in the same manner as the header <NUM>, except that the header <NUM> is provided with a second refrigerant guide portion <NUM> with the configuration of the header <NUM>.

The second refrigerant guide portion <NUM> is provided on the second bottom surface 45ab. The second refrigerant guide portion <NUM> includes a second guide surface 93a. The second guide surface 93a guides the refrigerant (the refrigerant in which the difference in state in the width direction is reduced by colliding with the first bottom surface 45aa), which flows from the lower end portion of the first space <NUM> to the lower end portion of the second space <NUM>, in a direction from the lower side toward the upper side of the second space <NUM>.

As the second guide surface 93a, for example, a recessed curved surface that is recessed in a direction separated from the lower end portion of the partition plate <NUM> can be used.

According to the heat exchanger <NUM> of the second modification example of the second embodiment, by including the second refrigerant guide portion <NUM> having the above configuration, the refrigerant, which is generated by colliding with the first bottom surface 45aa of the header body <NUM>, having a small difference in state in the width direction can be guided in a direction from the lower side toward the upper side of the second space <NUM>.

Further, by making the second guide surface 93a a recessed curved surface that is recessed in a direction separated from the lower end portion of the partition plate <NUM>, the refrigerant having a small difference in state in the width direction can be easily guided in the direction from the lower side toward the upper side of the second space <NUM>.

In the heat exchanger <NUM> according to the second modification example of the second embodiment, at least one of the first refrigerant guide portion <NUM> and the third refrigerant guide portion <NUM> shown in <FIG> may be provided.

A heat exchanger <NUM> according to a third modification example of the second embodiment will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals. The arrows shown in <FIG> indicate a direction in which the refrigerant flows when the heat exchanger <NUM> is used as an evaporator.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM> except that the heat exchanger <NUM> includes a header <NUM> in place of the header <NUM> that configures the heat exchanger <NUM> of the second modification example of the second embodiment. The header <NUM> is configured in the same manner as the header <NUM>, except that the header <NUM> is provided with the first refrigerant guide portion <NUM> with the configuration of the header <NUM>.

According to the heat exchanger <NUM> of the third modification example of the second embodiment, the refrigerant, which is generated by colliding with the first guide surface 73a, having a small difference in state in the width direction can be smoothly guided to the direction from the lower side toward the upper side of the second space <NUM>.

In the heat exchanger <NUM> according to the third modification example of the second embodiment, the third refrigerant guide portion <NUM> shown in <FIG> may be provided.

The heat exchanger <NUM> according to a third embodiment will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals. The arrows shown in <FIG> indicate a direction in which the refrigerant flows when the heat exchanger <NUM> is used as an evaporator.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM>, except that one end 41Fa of the flat tube 41F is moved back from a position of one end 41a of the other flat tube <NUM> in the direction from the first space <NUM> toward the second space <NUM>, with respect to the header <NUM> that configures the heat exchanger <NUM> of the first embodiment.

As a result, it is configured such that a distance Ds1 from the one end 41Fa of the flat tube 41F to the second surface 47c of the partition plate <NUM> is longer than a distance Ds2 from the one end 41a of the other flat tube <NUM> to the second surface 47c of the partition plate <NUM>.

According to the heat exchanger <NUM> of the third embodiment, among the plurality of flat tubes <NUM>, by making a distance Ds1, which is from the one end 41Fa of the flat tube 41F disposed at the bottom to the partition plate <NUM>, longer than a distance Ds2, which is from the one end 41a of the other flat tube <NUM> to the partition plate <NUM>, it is possible to increase the cross-sectional area of the refrigerant flow path formed between the one end 41Fa of the flat tube 41F disposed at the bottom and the partition plate <NUM>.

As a result, since the degree of contraction flow at a height position of the flat tube 41F can be relaxed and the flow of the refrigerant is less likely to separate, the liquid phase refrigerant can be easily supplied to the flat tube 41F, which may be difficult for the liquid phase refrigerant to flow in due to the influence of separation (contraction flow) in the related art, thereby the distribution of the refrigerant to each flat tube <NUM> can be equalized.

In the heat exchanger <NUM> according to the third embodiment, at least one of the first refrigerant guide portion <NUM> shown in <FIG>, the third refrigerant guide portion <NUM> shown in <FIG>, and the second refrigerant guide portion <NUM> shown in <FIG> may be provided.

The heat exchanger <NUM> according to a first modification example of the third embodiment will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structures shown in <FIG> and <FIG> are designated by the same reference numerals. The arrows shown in <FIG> indicate a direction in which the refrigerant flows when the heat exchanger <NUM> is used as an evaporator.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM>, except that one end 41Fa of the flat tube 41F is moved back from a position of one end 41a of the other flat tube <NUM> in the direction from the first space <NUM> toward the second space <NUM>, with respect to the header <NUM> that configures the heat exchanger <NUM> of the second embodiment.

As described above, the distance Ds1, which is from the one end 41Fa of the flat tube 41F disposed at the bottom to the partition plate <NUM>, is configured to be longer than the distance Ds2, which is from the one end 41a of the other flat tube <NUM> to the partition plate <NUM>, and then the first refrigerant guide portion <NUM> may be provided.

Further, the heat exchanger <NUM> having the above configuration may be provided with the third refrigerant guide portion <NUM> shown in <FIG>.

The heat exchanger <NUM> according to a second modification example of the third embodiment will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals. The arrows shown in <FIG> indicate a direction in which the refrigerant flows when the heat exchanger <NUM> is used as an evaporator.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM> except that the heat exchanger <NUM> includes a header <NUM> in place of the header <NUM> that configures the heat exchanger <NUM> of the first embodiment. The header <NUM> is configured in the same manner as the header <NUM> except that the header <NUM> includes the partition plate <NUM> in place of the partition plate <NUM> that configures the header <NUM> of the first embodiment.

Positions of one ends 41a and 41Fa of the plurality of flat tubes <NUM> in the X direction are at the same position.

The partition plate <NUM> includes a lower end portion 133A that faces the one end 41Fa of the flat tube 41F in the X direction. The lower end portion 133A is disposed at a position deviated from a direction from the second space <NUM> toward the first space <NUM> with the partition plate <NUM>, which excludes the lower end portion 133A, as a reference. As a result, the distance Ds1, which is from the one end 41Fa of the flat tube 41F disposed at the bottom to the partition plate <NUM>, is configured to be longer than the distance Ds2, which is from the one end 41a of the other flat tube <NUM> to the partition plate <NUM>.

According to the heat exchanger <NUM> of the second modification example of the third embodiment, among the plurality of flat tubes <NUM>, by disposing the lower end portion 133A of the partition plate <NUM> that faces the one end 41Fa of the flat tube 41F disposed at the bottom at a position deviated from the direction from the second space <NUM> toward the first space <NUM>, the cross-sectional area of the refrigerant flow path, which is formed between the one end 41Fa of the flat tube 41F disposed at the bottom and the partition plate <NUM>, can be increased.

In the heat exchanger <NUM> according to the second modification example of the third embodiment, at least one of the first refrigerant guide portion <NUM> shown in <FIG>, the third refrigerant guide portion <NUM> shown in <FIG>, and the second refrigerant guide portion <NUM> shown in <FIG> may be provided.

The heat exchanger <NUM> according to a fourth embodiment will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals. The arrows shown in <FIG> indicate a direction in which the refrigerant flows when the heat exchanger <NUM> is used as an evaporator.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM> except that the heat exchanger <NUM> includes a header <NUM> in place of the header <NUM> that configures the heat exchanger <NUM> of the first embodiment. The header <NUM> is configured in the same manner as the header <NUM>, except that the header <NUM> is further provided with a rectification member <NUM> with the configuration of the header <NUM> of the first embodiment.

The rectification member <NUM> is a baffle plate <NUM> provided on an inner wall surface 45b of the header body <NUM> that partitions the second space <NUM>.

The baffle plate <NUM> is disposed at a position below the flat tube 41F and separated from the flat tube 41F. The baffle plate <NUM> extends in a direction from the inner wall surface 45b of the header body <NUM> toward the partition plate. The amount of protrusion of the baffle plate <NUM> from the inner wall surface 45b is configured to be equal to the amount of protrusion of one end portion 41B of the flat tube 41F.

According to the heat exchanger <NUM> of the fourth embodiment, by including the baffle plate <NUM> (the rectification member <NUM>) having the above configuration, the flow of the refrigerant is separated in a front stage of the one end portion 41B of the flat tube 41F that is disposed at the bottom, thereby it is possible to rectify the flow of the refrigerant at the one end of the flat tube 41F.

As a result, the liquid phase refrigerant can be easily supplied to the flat tube 41F, which may be difficult for the liquid phase refrigerant to flow in due to the influence of separation (contraction flow) in the related art, thereby the distribution of the refrigerant to each flat tube <NUM> can be equalized.

The heat exchanger <NUM> according to a first modification example of the fourth embodiment will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals. The arrows shown in <FIG> indicate a direction in which the refrigerant flows when the heat exchanger <NUM> is used as an evaporator.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM> except that the heat exchanger <NUM> includes a header <NUM> in place of the header <NUM> that configures the heat exchanger <NUM> of the fourth embodiment. The header <NUM> is configured in the same manner as the header <NUM>, except that the header <NUM> is further provided with the first refrigerant guide portion <NUM> with the configuration of the header <NUM> of the fourth embodiment.

As described above, the baffle plate <NUM> described in the fourth embodiment and the first refrigerant guide portion <NUM> described in the second embodiment may be used in combination.

The heat exchanger <NUM> according to a second modification example of the fourth embodiment will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals. The arrows shown in <FIG> indicate a direction in which the refrigerant flows when the heat exchanger <NUM> is used as an evaporator.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM> except that the heat exchanger <NUM> is provided with a block <NUM>, which is a rectification member <NUM>, in place of the baffle plate <NUM> that configures the heat exchanger <NUM> of the fourth embodiment.

The block <NUM> is disposed below the one end portion 41B so as to be in contact with a lower surface of the one end portion 41B of the flat tube 41F. The block <NUM> extends in a direction from the inner wall surface 45b of the header body <NUM> toward the partition plate <NUM>.

The amount of protrusion of the block <NUM> when the inner wall surface 45b of the header body <NUM> is used as a reference is equal to the amount of protrusion of the one end portion 41B of the flat tube <NUM>.

According to the heat exchanger <NUM> of the second modification example of the fourth embodiment, by using the block <NUM> having the above configuration as the rectification member <NUM>, the flow of the refrigerant is separated in a front stage of the one end portion 41B of the flat tube 41F that is disposed at the bottom, thereby it is possible to rectify the flow of the refrigerant at the one end of the flat tube 41F.

The heat exchanger <NUM> according to a third modification example of the fourth embodiment will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals. The arrows shown in <FIG> indicate a direction in which the refrigerant flows when the heat exchanger <NUM> is used as an evaporator.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM> except that the heat exchanger <NUM> is provided with a block <NUM>, which is a rectification member <NUM>, in place of the block <NUM> that configures the heat exchanger <NUM> of the second modification example of the fourth embodiment.

The block <NUM> is disposed below the one end portion 41B so as to be in contact with a lower surface of the one end portion 41B of the flat tube 41F. The block <NUM> is formed on the partition plate <NUM> side and includes a curved surface 174a for guiding the flow of the refrigerant upward.

According to the heat exchanger <NUM> of the third modification example of the fourth embodiment, since the block <NUM> has the curved surface 174a, the refrigerant can be guided above the second space <NUM> without the separation of the flow.

The heat exchanger <NUM> according to a fourth modification example of the fourth embodiment will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structures shown in <FIG> and <FIG> are designated by the same reference numerals. The arrows shown in <FIG> indicate a direction in which the refrigerant flows when the heat exchanger <NUM> is used as an evaporator.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM> except that the heat exchanger <NUM> is further provided with the first refrigerant guide portion <NUM> and the second refrigerant guide portion <NUM> shown in <FIG> with the configuration of the heat exchanger <NUM> according to the third modification example of the fourth embodiment.

As described above, the block <NUM>, the first refrigerant guide portion <NUM>, and the second refrigerant guide portion <NUM> may be used in combination.

The heat exchanger <NUM> according to a fifth modification example of the fourth embodiment will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structures shown in <FIG> and <FIG> are designated by the same reference numerals. The arrows shown in <FIG> indicate a direction in which the refrigerant flows when the heat exchanger <NUM> is used as an evaporator.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM> except that the heat exchanger <NUM> includes the partition plate <NUM> shown in <FIG> in place of the partition plate <NUM> that configures the heat exchanger <NUM> according to the second modification example of the fourth embodiment.

As described above, the block <NUM>, the first refrigerant guide portion <NUM>, the second refrigerant guide portion <NUM>, and the partition plate <NUM> may be used in combination.

A refrigeration cycle device <NUM> of a fifth embodiment will be described with reference to <FIG>. In <FIG>, a solid arrow indicates a direction in which refrigerant flows during heating operation, and a dotted arrow indicates a direction in which the refrigerant flows during cooling operation. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals.

The refrigeration cycle device <NUM> is configured in the same manner as the refrigeration cycle device <NUM> except that the refrigeration cycle device <NUM> includes first and second heat exchanger units <NUM> and <NUM> in place of the first and second heat exchanger units <NUM> and <NUM> that configure the refrigeration cycle device <NUM> of the first embodiment.

The first heat exchanger unit <NUM> is configured in the same manner as the first heat exchanger unit <NUM> except that the first heat exchanger unit <NUM> includes a heat exchanger <NUM> in place of the heat exchanger <NUM>.

The second heat exchanger unit <NUM> is configured in the same manner as the second heat exchanger unit <NUM> except that the second heat exchanger unit <NUM> includes a heat exchanger <NUM> in place of the heat exchanger <NUM>.

The heat exchanger <NUM> will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals. Further, in <FIG>, the X direction indicates the extending direction of the flat tube <NUM> orthogonal to the Z direction (the vertical direction). In <FIG>, the Y direction indicates the horizontal direction (the width direction of the flat tube <NUM> in a state in which the flat tube <NUM> is attached to the fin <NUM>) that is orthogonal to the X direction and the Z direction, and J indicates a direction in which air flows (hereinafter referred to as a "direction J"), respectively.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM> except that the heat exchanger <NUM> includes an gateway header <NUM>, a turnback header <NUM>, and a fin <NUM> in place of the pair of headers <NUM> and the fin <NUM>.

The gateway header <NUM> is a tube-shaped member that extends in the Z direction, and an upper end and a lower end of the gateway header <NUM> are closed. The gateway header <NUM> is connected to the first refrigerant pipe 14A and one end portion of each of the plurality of flat tubes <NUM> (the end portion disposed on one side in the X direction).

The gateway header <NUM> guides the refrigerant, which is supplied through the first refrigerant pipe 14A, to the flow paths in the plurality of flat tubes <NUM> and returns the refrigerant, which is turned back to the gateway header <NUM> through the turnback header <NUM>, to the first refrigerant pipe 14A.

The turnback header <NUM> is disposed so as to face the gateway header <NUM> in the X direction. The turnback header <NUM> is a tube-shaped member that extends in the Z direction, and an upper end and a lower end of the turnback header <NUM> are closed. The turnback header <NUM> is connected to the other end portion of each of the plurality of flat tubes <NUM> (the end portion disposed on the other side in the X direction).

The turnback header <NUM> returns the refrigerant to the gateway header <NUM> through the plurality of flat tubes <NUM>.

The flat tube <NUM> will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structures shown in <FIG> and <FIG> are designated by the same reference numerals.

The flat tube <NUM> further includes a first end portion 41D disposed on one side of the flat tube <NUM> in the width direction (Y direction), a second end portion 41E disposed on the other side of the flat tube <NUM> in the width direction (Y direction), and an outer peripheral surface 41b.

The outside appearances of the first and second end portions 41D and 41E are a round shape or an elliptical shape.

The plurality of flat tubes <NUM> are supported by a plurality of fins <NUM> in a state with an interval in the Z direction. One end portion of each of the plurality of flat tubes <NUM>, which is disposed in the X direction, is connected to the gateway header <NUM>. The other end portion of each of the plurality of flat tubes <NUM>, which is disposed in the X direction, is connected to the turnback header <NUM>.

The fin <NUM> will be described with reference to <FIG>, <FIG>, and <FIG> to <FIG>. In <FIG>, the same configuration parts as those of the structures shown in <FIG> and <FIG> are designated by the same reference numerals.

The plurality of fins <NUM> are disposed at a predetermined pitch with respect to the X direction. The fin <NUM> includes a fin body <NUM>, a plurality of flat tube insertion portions <NUM>, a plurality of uneven portions <NUM>, a communication portion <NUM>, and a plurality of fin pitch regulation portions <NUM>.

The fin body <NUM> has a plate shape and extends in the Z direction. The fin body <NUM> includes first and second surfaces 207a and 207b disposed in the X direction, and a second plane portion 207A.

The first surface 207a is disposed so as to face the gateway header <NUM>. The second surface 207b is a surface disposed on the opposite side of the first surface 207a. The second surface 207b is disposed so as to face the turnback header <NUM>.

The second plane portion 207A is a part, of the fin body <NUM> disposed between the flat tube insertion portions <NUM> adjacent to each other, that excludes the uneven portion <NUM> and the fin pitch regulation portion <NUM> in the Z direction.

Of the first and second surfaces 207a and 207b, the first and second surfaces 207a and 207b that configure the second plane portion 207A are surfaces orthogonal to the X direction and parallel to the Y direction and the Z direction.

A part, of the second plane portion 207A, that is disposed on one side in the Y direction, configures one end portion 206A of the fin <NUM>.

The plurality of flat tube insertion portions <NUM> are formed on the fin body <NUM>. The plurality of flat tube insertion portions <NUM> are disposed at intervals in the Z direction. The flat tube insertion portion <NUM> extends from one side to the other side in the Y direction. The flat tube insertion portion <NUM> includes a tip portion 209A disposed on the other side in the Y direction and a rear end portion 209B disposed on one side in the Y direction.

The tip portion 209A is closed and restricts a position of the second end portion 41E of the flat tube <NUM>. The rear end portion 209B is open from the viewpoint of inserting the flat tube <NUM>.

The rear end portion side of the flat tube insertion portion <NUM> is open for inserting the flat tube <NUM> into the flat tube insertion portion <NUM>. The flat tube insertion portion <NUM> accommodates the flat tube <NUM> that is inserted from the first end portion 41D side.

The shape of the tip portion 209A is set to a shape such that the outer peripheral surface of the second end portion 41E and the fin body <NUM> partitioning the tip portion 209A are in surface contact with each other. That is, when the second end portion 41E has a round shape, the shape of the tip portion 209A is set to a round shape that makes surface contact with the second end portion 41E, and when the second end portion 41E has an elliptical shape, the shape of the tip portion 209A is set to an elliptical shape that makes surface contact with the second end portion 41E.

With such a configuration, it is possible to increase the contact area between the flat tube <NUM> and the fin body <NUM>, thereby the thermal conductivity between the flat tube <NUM> and the fin <NUM> can be improved.

The uneven portion <NUM> is formed in the fin body <NUM> that is positioned between the flat tube insertion portions <NUM> adjacent to each other in the Z direction. The periphery of the uneven portion <NUM> is surrounded by the second plane portion 207A.

The uneven portion <NUM> is formed by alternately disposing peaks and valleys protruding in a direction separated from the first surface 207a of the second plane portion 207A. The uneven portions <NUM> are disposed at intervals in the Z direction.

By providing the uneven portion <NUM> having such a configuration, it is possible to improve the heat transfer coefficient on the air side while increasing the area of the fin body <NUM>, thereby the efficiency of the heat exchanging between the air and the fin body <NUM> can be increased.

The communication portion <NUM> is a part, of the fin body <NUM>, that is disposed on the other side from the plurality of flat tube insertion portions <NUM> in the Y direction, and extends continuously in the Z direction. The communication portion <NUM> includes a first plane portion 207B and a condensed water guide portion <NUM>.

The first plane portion 207B is disposed on both sides of the condensed water guide portion <NUM> so as to interpose the condensed water guide portion <NUM> from the Y direction.

A surface, of the first and second surfaces 207a and 207b, that configures the first plane portion 207B, is a surface orthogonal to the X direction and parallel to the Y direction and the Z direction.

A part, of the first plane portion 207B, that is disposed on the other side in the Y direction, configures the other end portion 206B of the fin <NUM>.

A surface, of the second surface 207b, that configures one end portion 206A of the fin <NUM>, and a surface, of the second surface 207b, that configures the other end portion 206B, are disposed on the same plane.

The condensed water guide portion <NUM> protrudes on the first surface 207a of the first plane portion 207B in a state of being bent in a direction intersecting the first surface 207a of the first plane portion 207B. The condensed water guide portion <NUM> extends continuously over the Z direction. The condensed water guide portion <NUM> is a projecting portion <NUM> in which a cross-sectional shape is a V shape when cut on a plane orthogonal to the Z direction and the cross-sectional shape is uniform in the Z direction.

The first surface 207a, which configures the projecting portion <NUM>, protrudes in a V shape in a direction from the second surface 207b of the first plane portion 207B toward the first surface 207a.

The second surface 207b, which configures the projecting portion <NUM>, is a surface recessed in a V shape in the direction from the second surface 207b of the first plane portion 207B toward the first surface 207a.

The fin pitch regulation portion <NUM> is formed between the rear end portions of the flat tube insertion portions <NUM> adjacent to each other in the Z direction. The fin pitch regulation portion <NUM> is disposed on one side of the uneven portion <NUM> in the Y direction.

The fin pitch regulation portion <NUM> is formed by folding a part of the fin body <NUM> downward (one side in the Z direction). The fin pitch regulation portion <NUM> is formed so as to protrude on the first surface 207a.

The fin pitch regulation portion <NUM> keeps the pitch (fin pitch) of the fins <NUM> that are disposed in the X direction at a desired value by being in contact with the second surface 207b of the fin <NUM> disposed on one side in the X direction. The shape of the fin pitch regulation portion <NUM> can be, for example, an L shape.

Here, with reference to <FIG>, a cutting step that is performed when manufacturing a plurality of fins <NUM> will be described. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals. In <FIG> and <FIG>, Cp indicates a position for cutting the structure shown in <FIG> (hereinafter referred to as a "cutting position Cp") in the cutting step.

The fin <NUM> having the above configuration is manufactured by performing a press process on a single plate member, by cutting the cutting position Cp of the structure <NUM> (see <FIG>) in which a plurality of fins <NUM> are connected in the horizontal direction, and by separating the plurality of fins <NUM> into individual pieces.

As described above, of the second surface 207b, a surface that configures one end portion 206A of the fin <NUM> and a surface that configures the other end portion 206B are disposed on the same plane.

With such a configuration, in the cutting step of the structure <NUM> that is performed after the manufacturing of the structure <NUM> in which the plurality of fins <NUM> are connected by performing the press process on the plate member (the base material of the plurality of fins <NUM>), it is possible to make the second surface 207b that corresponds to the cutting position Cp being in contact with an upper surface of a stage of a cutting device. As a result, it is possible to dispose the structure <NUM> on the stage in a stable state, thereby the structure <NUM> can be cut with high accuracy.

In <FIG>, as an example of the structure that serves as a base material for the plurality of fins <NUM>, the case where the plurality of fins <NUM> are connected such that the tip portions 209A of the flat tube insertion portions <NUM>, which configure the fins <NUM> adjacent to each other, face in the same direction has been described as an example, but the structure <NUM> that is disposed such that the rear end portions 209B of the flat tube insertion portions <NUM>, which configure the pair of fins <NUM> adjacent to each other, face each other may be used as shown in <FIG>, for example.

The heat exchanger <NUM> having the above configuration is used as a condenser during the cooling operation to dissipate heat to the outside and is used as an evaporator during the heating operation to absorb heat from the outside.

According to the heat exchanger <NUM> of the first embodiment, by configuring the condensed water guide portion <NUM>, which is formed in the communication portion <NUM>, with a projecting portion <NUM> that protrudes from the first surface 207a configuring the first plane portion 207B, the condensed water can be guided in the direction from the upper side toward the lower side along the first and second surfaces 207a and 207b that configure the projecting portion <NUM> while preventing the obstruction of the flow of the condensed water.

Further, by providing the projecting portion <NUM> having the above configuration, it is possible to improve the strength of the communication portion <NUM>. As a result, the occurrence of breakage of the fin can be prevented in a part, of the fin <NUM>, that faces the flat tube insertion portion <NUM> in the Y direction (a part where the strength of the fin <NUM> is weak).

Further, by providing the projecting portion <NUM> having the above configuration, it is possible to improve the heat transfer coefficient on the air side while increasing the surface area of the condensed water guide portion <NUM>. As a result, the heat exchange efficiency between the condensed water guide portion <NUM> and the air can be improved.

By including the heat exchanger <NUM> described above having excellent drainage of condensed water, the first heat exchanger unit <NUM> can be operated stably.

By including the first and second heat exchanger units <NUM> and <NUM> described above, the refrigeration cycle device <NUM> can be operated stably while improving the performance of the refrigeration cycle device <NUM>.

The heat exchanger <NUM> of the sixth embodiment will be described with reference to <FIG> and <FIG>. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals. In <FIG> and <FIG>, the same configuration parts are designated by the same reference numerals.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM> except that the heat exchanger <NUM> includes a plurality of fins <NUM> in place of the plurality of fins <NUM> that configure the heat exchanger <NUM> of the fifth embodiment.

The fin <NUM> is configured in the same manner as the fin <NUM> except that the fin <NUM> includes a communication portion <NUM> in place of the communication portion <NUM> that configures the fin <NUM>.

The communication portion <NUM> is configured in the same manner as the communication portion <NUM>, except that the communication portion <NUM> includes a condensed water guide portion <NUM> in place of the condensed water guide portion <NUM> (the projecting portion <NUM>) that is formed in the communication portion <NUM>.

The condensed water guide portion <NUM> protrudes from the first surface 207a that configures the first plane portion 207B, and is configured with an uneven portion <NUM> including a projecting portion <NUM> (two projecting portions <NUM> in <FIG> and <FIG> as an example), which is disposed in horizontal direction, and a recessed portion <NUM> (one recessed portion <NUM> in <FIG> and <FIG> as an example), which is disposed between the projecting portions <NUM> adjacent to each other in the Y direction.

The uneven portion <NUM> is bent in a direction intersecting with the first plane portion 207B and continuously extends over the Z direction, and a cross-sectional shape (W shape in a case of <FIG>) of the uneven portion <NUM> when cut on a plane orthogonal to the Z direction is uniform in the Z direction.

By using the uneven portion <NUM> having the above configuration as the condensed water guide portion <NUM>, the condensed water can be guided in the direction from the upper side toward the lower side along the first and second surfaces 207a and 207b that configure the uneven portion <NUM> while preventing the obstruction of the flow of the condensed water.

Further, by using the uneven portion <NUM> as the condensed water guide portion <NUM>, it is possible to improve the strength of the communication portion <NUM>, thereby the occurrence of the breakage of the fin can be prevented at a part (a part where the strength of the fin <NUM> is weak), of the fin <NUM>, that faces the flat tube insertion portion <NUM> in the horizontal direction (Y direction).

Further, by configuring the condensed water guide portion <NUM> with the uneven portion <NUM>, it is possible to improve the heat transfer coefficient on the air side while increasing the surface area of the condensed water guide portion <NUM> as compared with the case where the condensed water guide portion <NUM> is configured with one projecting portion <NUM>. As a result, the heat exchange efficiency between the condensed water guide portion <NUM> and the air can be improved.

The heat exchanger <NUM> of the seventh embodiment will be described with reference to <FIG> and <FIG>. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals. In <FIG> and <FIG>, the same configuration parts are designated by the same reference numerals.

The communication portion <NUM> includes a condensed water guide portion <NUM> that extends continuously in the Z direction. The condensed water guide portion <NUM> is a step portion <NUM> and includes a first part 243A and a second part 243B that configure the first plane portion 207B, and a connecting portion <NUM>.

The first part 243A is a part, of the first plane portion 207B, that is disposed on the one end portion 206A side of the fin body <NUM> and extends continuously in the Z direction.

The second part 243B configures the other end portion 206B of the fin <NUM> in the first plane portion 207B and extends continuously in the Z direction.

The second part 243B is disposed at a position offset to the other side in the X direction from a position where the first part 243A is formed. The first and second surfaces 207a and 207b that configure the second part 243B are parallel to the first and second surfaces 207a and 207b that configure the first part 243A.

The connecting portion <NUM> is disposed between the first part 243A and the second part 243B and extends continuously in the Z direction.

One end portion of the connecting portion <NUM> is connected to the first part 243A. The other end portion of the connecting portion <NUM> is connected to the second part 243B.

The first and second surfaces 207a and 207b that configure the connecting portion <NUM> are inclined with respect to the first and second surfaces 207a and 207b that configure the first and second parts 243A and 243B.

The condensed water guide portion <NUM> (the step portion <NUM>) has a configuration in which a step is formed in the X direction.

By using the step portion <NUM> having such a configuration as the condensed water guide portion <NUM>, the condensed water can be guided in the direction from the upper side toward the lower side along the first and second surfaces 207a and 207b that configure the connecting portion <NUM> while preventing the obstruction of the flow of the condensed water.

Further, by configuring the condensed water guide portion <NUM> with the step portion <NUM>, it is possible to improve the strength of the communication portion <NUM>, thereby the occurrence of the breakage of the fin can be prevented at a part (a part where the strength of the fin <NUM> is weak), of the fin <NUM>, that faces the flat tube insertion portion <NUM> in the Y direction.

Further, by configuring the condensed water guide portion <NUM> with the step portion <NUM>, it is possible to improve the heat transfer coefficient on the air side while increasing the surface area of the condensed water guide portion <NUM>. As a result, the heat exchange efficiency between the condensed water guide portion <NUM> and the air can be improved.

The heat exchanger <NUM> of the eighth embodiment will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals. In <FIG>, the same configuration parts are designated by the same reference numerals.

The fin <NUM> is configured in the same manner as the fin <NUM> described above except that a pedestal portion <NUM>, which protrudes on the first surface 207a side of the first plane portion 207B is provided at the periphery of the flat tube insertion portion <NUM>, the height H<NUM> of the tip 218A of the projecting portion <NUM> (the condensed water guide portion <NUM>) in the X direction with the first surface 207a of the first plane portion 207B as a reference is made equal to the height H<NUM> of the pedestal portion <NUM> in the X direction with the first surface 207a of the first plane portion 207B as a reference, and the projecting portion <NUM> and the pedestal portion <NUM> are connected to each other at a position of the tip 218A of the projecting portion <NUM>.

As described above, by making the height H<NUM> of the projecting portion <NUM> and the height H<NUM> of the pedestal portion <NUM> equal to each other in the X direction and by connecting the projecting portion <NUM> and the pedestal portion <NUM> at the position of the tip 218A of the projecting portion <NUM>, there is no possibility that the first plane portion 207B is disposed between the pedestal portion <NUM> and the projecting portion <NUM> in the Y direction. As a result, it is possible for the first plane portion 207B to be discontinuous in the Z direction between the pedestal portion <NUM> and the projecting portion <NUM>, thereby the occurrence of the breakage of the fin between the pedestal portion <NUM> and the projecting portion <NUM> can be prevented.

In the eighth embodiment, the case where the projecting portion <NUM> (the condensed water guide portion <NUM>) and the pedestal portion <NUM> are connected to each other has been described as an example, but the projecting portion <NUM>, which configures the uneven portion <NUM>, and the pedestal portion <NUM> may be connected to each other, for example.

The heat exchanger <NUM> according to a first modification example of the eighth embodiment will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM> except that the heat exchanger <NUM> includes a fin <NUM> in place of the fin <NUM> that configures the heat exchanger <NUM> of the eighth embodiment.

The fin <NUM> is configured in the same manner as the fin <NUM> except that the fin <NUM> includes a pedestal portion <NUM> in place of the pedestal portion <NUM> that configures the fin <NUM>.

The pedestal portion <NUM> is configured in the same manner as the pedestal portion <NUM>, except that an upper side of a part that is connected to the projecting portion <NUM> is inclined diagonally downward from the pedestal portion <NUM> toward the projecting portion <NUM>.

By providing the pedestal portion <NUM> having such a configuration, it is possible to prevent the accumulation of the condensed water on the upper portion side of a part where the pedestal portion <NUM> and the projecting portion <NUM> are connected to each other, thereby the pedestal portion <NUM> can be prevented from obstructing the flow of the condensed water.

The heat exchanger <NUM> according to a second modification example of the eighth embodiment will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM> except that the heat exchanger <NUM> includes a fin <NUM> in place of the fin <NUM> that configures the heat exchanger <NUM> according to the first modification example of the eighth embodiment.

The pedestal portion <NUM> is configured in the same manner as the pedestal portion <NUM>, except that an upper side and lower side of a part that is connected to the projecting portion <NUM> is inclined diagonally downward from the pedestal portion <NUM> toward the projecting portion <NUM>.

By providing the pedestal portion <NUM> having such a configuration, it is possible to prevent the accumulation of the condensed water not only on the upper portion side of the part where the pedestal portion <NUM> and the projecting portion <NUM> are connected to each other but also on the lower portion of a back side of the pedestal portion <NUM> (the back side of the paper surface in <FIG>), thereby the effect of preventing the pedestal portion <NUM> from obstructing the flow of the condensed water can be enhanced.

The refrigeration cycle device <NUM> of a ninth embodiment will be described with reference to <FIG>. In <FIG>, a solid arrow indicates a direction in which refrigerant flows during the heating operation, and a dotted arrow indicates a direction in which the refrigerant flows during the cooling operation. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals.

The refrigeration cycle device <NUM> is configured in the same manner as the refrigeration cycle device <NUM> except that the refrigeration cycle device <NUM> includes first and second heat exchanger units <NUM> and <NUM> in place of the first and second heat exchanger units <NUM> and <NUM> that configure the refrigeration cycle device <NUM> of the second embodiment. The first heat exchanger unit <NUM> is configured in the same manner as the first heat exchanger unit <NUM> except that the first heat exchanger unit <NUM> includes a heat exchanger <NUM> in place of the heat exchanger <NUM>.

The heat exchanger <NUM> will be described with reference to <FIG>. In <FIG> and <FIG>, the Z direction indicates a first direction. In <FIG>, the X direction indicates the extending direction of the flat tube <NUM> orthogonal to the Z direction. In <FIG>, the Y direction indicates a second direction (the width direction of the flat tube <NUM> in a state in which the flat tube <NUM> is attached to the fin <NUM>) that is orthogonal to the X direction and the Z direction, and P indicates a direction in which air flows (hereinafter referred to as a "direction P"), respectively.

In the present embodiment, as an example of the Z direction, the following description will be given by taking the case where the Z direction is the vertical direction as an example.

The heat exchanger <NUM> is configured in the same manner as the heat exchanger <NUM> except that the heat exchanger <NUM> includes a plurality of fins <NUM> in place of the plurality of fins <NUM> that configure the heat exchanger <NUM> of the second embodiment.

The plurality of fins <NUM> will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structures shown in <FIG> and <FIG> are designated by the same reference numerals.

The plurality of fins <NUM> are disposed at a predetermined pitch with respect to the X direction.

The fin <NUM> is configured in the same manner as the fin <NUM> except that the fin <NUM> includes a fin body <NUM> in place of the fin body <NUM> that configures the fin <NUM> described in the fifth embodiment, and further includes a plurality of thermally conductive portions <NUM>, a plurality of first fin pitch regulation portions <NUM>, and a plurality of second fin pitch regulation portions <NUM>.

The fin body <NUM> has a plate shape and extends in the Z direction. The fin body <NUM> includes first and second surfaces 291a and 291b disposed in the X direction.

The first surface 291a is disposed so as to face the gateway header <NUM>. The second surface 291b is a surface disposed on the opposite side of the first surface 291a. The second surface 291b is disposed so as to face the turnback header <NUM>. The fin body <NUM> has a plate shape and includes a communication portion <NUM> that extends in the Z direction.

The thermally conductive portion <NUM> is formed at the periphery of the flat tube insertion portion <NUM> so as to rise from the first surface 291a. The thermally conductive portion <NUM> protrudes in the X direction. In a state in which the flat tube <NUM> is inserted into the flat tube insertion portion <NUM>, an inner peripheral surface 305a of the thermally conductive portion <NUM> is in surface contact with an outer peripheral surface 41b of the flat tube <NUM>. The height of the thermally conductive portion <NUM> in the X direction is set to a height at which the thermally conductive portion <NUM> is not in contact with the fins <NUM> that are disposed on the first surface 291a side when the plurality of fins <NUM> are disposed in the X direction.

By providing the thermally conductive portion <NUM> having such a configuration, it is possible to increase the contact area between the flat tube <NUM> and the plurality of fins <NUM>. As a result, the thermal conductivity between the flat tube <NUM> and the plurality of fins <NUM> can be improved.

Further, by setting the height of the thermally conductive portion <NUM> in the X direction to the height at which the thermally conductive portion <NUM> is not in contact with the fins <NUM> disposed on the first surface 291a side, the thermal conductivity between the flat tube <NUM> and the fins <NUM> can be improved while regulating the fin pitch by using first and second fin pitch regulation portions <NUM> and <NUM>.

The first fin pitch regulation portion <NUM> is formed between the rear end portions of the flat tube insertion portions <NUM> adjacent to each other in the Z direction. The first fin pitch regulation portion <NUM> is disposed on one side of the uneven portion <NUM> in the Y direction.

The first fin pitch regulation portion <NUM> is formed by folding a part of the fin body <NUM> downward (one side in the Z direction). The first fin pitch regulation portion <NUM> is formed so as to protrude on the first surface 291a.

The first fin pitch regulation portion <NUM> keeps the pitch (fin pitch) of the fins <NUM> that are disposed in the X direction at a desired value by being in contact with the second surface 291b of the fin <NUM> disposed on one side in the X direction. The first fin pitch regulation portion <NUM> desirably has an L shape, for example.

As described above, by forming the first fin pitch regulation portion <NUM> on the rear end portion side of the flat tube insertion portions <NUM> that are adjacent to each other, the deformation or buckling of the fin <NUM>, which tends to occur in the initial stage when the flat tube <NUM> is inserted into the flat tube insertion portion <NUM>, can be prevented.

As described above, by forming the first fin pitch regulation portion <NUM> into an L shape, the probability that the first fin pitch regulation portion <NUM> is in contact with the second surface 291b can be increased as compared with the case where the first fin pitch regulation portion <NUM> has an I shape, for example.

Further, by forming the first fin pitch regulation portion <NUM> into an L shape, it is possible to increase the contact area between the first fin pitch regulation portion <NUM> and the second surface 291b, thereby the fin pitch can be maintained stably.

The second fin pitch regulation portion <NUM> is disposed at the periphery of the flat tube insertion portion <NUM> positioned on the upper side of the first fin pitch regulation portion <NUM> among the two flat tube insertion portions <NUM> that interpose the first fin pitch regulation portion <NUM> in the Z direction.

Specifically, the second fin pitch regulation portion <NUM> is disposed the lower side of the flat tube insertion portion <NUM> and near the tip portion 209A (tip portion 209A side at the rear end portion side of the flat tube insertion portion <NUM> with respect to the tip portion 209A).

The second fin pitch regulation portion <NUM> is formed by folding a part of the fin body <NUM> downward (one side in the Z direction) and making the part of the fin body <NUM> protrude on the first surface 291a.

Together with the first fin pitch regulation portion <NUM> described above, the second fin pitch regulation portion <NUM> keeps the pitch (fin pitch) of the fins <NUM> that are disposed in the X direction at a desired value by being in contact with the second surface 291b of the fin <NUM> disposed on the other side in the X direction.

The amounts of protrusion of the first and second fin pitch regulation portions <NUM> and <NUM> in the X direction are equal, and the fin pitch is set to a size that can be maintained at a desired value.

The second fin pitch regulation portion <NUM> desirably has an L shape, for example. By forming the second fin pitch regulation portion <NUM> into an L shape, the same effect as that of the first fin pitch regulation portion <NUM> having the L shape described above can be obtained.

As described above, by folding the part of the fin body <NUM> downward and by forming the first and second fin pitch regulation portions <NUM> and <NUM>, it is possible to prevent the first and second fin pitch regulation portions <NUM> and <NUM> from becoming a resistor for the air flowing in the P direction (a direction from the other side toward one side in the second direction) as compared with the case where the part of the fin body <NUM> is folded in the Y direction, thereby the pressure loss of the air can be prevented.

Further, by disposing the first fin pitch regulation portion <NUM> on the rear end portion side of the flat tube insertion portion <NUM> and by disposing the second fin pitch regulation portion <NUM> on the tip portion 209A side of the flat tube insertion portion <NUM>, it is possible to dispose the first and second fin pitch regulation portions <NUM> and <NUM> at positions separated from each other in the Z direction and the Y direction. As a result, the fin pitches of the plurality of fins <NUM> disposed in the X direction can be regulated stably.

Further, by forming the outside appearance of the second end portion 41E of the flat tube <NUM> into a round shape or an elliptical shape and by forming the shape of the tip portion 209A of the flat tube insertion portion <NUM>, which accommodates the second end portion 41E, into a shape in which the outer peripheral surface 41b of the second end portion 41E of the flat tube <NUM> and the fin body <NUM> are in surface contact with each other, it is possible to increase the contact area between the flat tube <NUM> and the fin body <NUM>. As a result, the thermal conductivity between the flat tube <NUM> and the fin <NUM> can be improved.

That is, the fin pitch can be regulated stably while preventing the pressure loss of the air, and the thermal conductivity between the flat tube <NUM> and the fin <NUM> can be improved.

Further, by not forming the first and second fin pitch regulation portions <NUM> and <NUM> in the communication portion <NUM> that extends in the first direction (the Z direction), the first and second fin pitch regulation portions <NUM> and <NUM> do not obstruct the flow of the condensed water drained in the first direction (the Z direction), thereby good drainage can be maintained.

Further, by forming the first fin pitch regulation portion <NUM> by folding a part of the fin body <NUM> downward and by forming the second fin pitch regulation portion <NUM> at the periphery of the flat tube insertion portion <NUM>, among the two flat tube insertion portions <NUM> that interpose the first fin pitch regulation portion <NUM> in the Z direction, that is positioned on the upper side of the first fin pitch regulation portion <NUM>, it is possible to dispose positions that regulate the fin pitches at equal intervals in the Z direction, thereby the fin pitch can be regulated stably.

According to the first heat exchanger unit <NUM>, by including the heat exchanger <NUM> described above, the first heat exchanger unit <NUM> can be operated stably while improving the performance of the first heat exchanger unit <NUM>.

The second heat exchanger unit <NUM> that includes the heat exchanger <NUM> can also obtain the same effect as the first heat exchanger unit <NUM>.

By the refrigeration cycle device <NUM> including the first and second heat exchanger units <NUM> and <NUM> described above, the refrigeration cycle device <NUM> can be operated stably while improving the performance of the refrigeration cycle device <NUM>.

The fin <NUM> according to a modification example of the ninth embodiment will be described with reference to <FIG>. In <FIG>, the same configuration parts as those of the structure shown in <FIG> are designated by the same reference numerals.

The fin <NUM> is configured in the same manner as the fin <NUM> as described above except that the first fin pitch regulation portion <NUM> is formed by folding a part of the fin body <NUM> upward, and the second fin pitch regulation portion <NUM> is formed at the periphery of the flat tube insertion portion <NUM>, among the two flat tube insertion portions <NUM> that interpose the first fin pitch regulation portion <NUM> in the Z direction, that is positioned on the lower side of the first fin pitch regulation portion <NUM>.

As described above, by forming the first fin pitch regulation portion <NUM> by folding a part of the fin body <NUM> upward and by forming the second fin pitch regulation portion <NUM> at the periphery of the flat tube insertion portion <NUM>, among the two flat tube insertion portions <NUM> that interpose the first fin pitch regulation portion <NUM> in the Z direction, that is positioned on the lower side of the first fin pitch regulation portion <NUM>, it is possible to dispose positions that regulate the fin pitches at equal intervals in the Z direction. As a result, the fin pitch can be regulated stably.

Claim 1:
A heat exchanger exchanging heat between air and refrigerant, the heat exchanger comprising:
a plurality of flat tubes (<NUM>) that have a flat-shaped outside appearance, that extend in one direction, and that include a plurality of flow paths, which are disposed in a width direction, which extend in the one direction, and through which the refrigerant flows;
a plurality of fins (<NUM>) that are disposed in an extending direction of the flat tube in a state in which the plurality of flat tubes are accommodated; and
a header (<NUM>) that is connected to the plurality of flat tubes such that one end portion of each of the plurality of flat tubes is disposed on an inner side, and through which the refrigerant flows in the inner side, wherein
the header includes
a header body (<NUM>) that has a tube shape extending in a vertical direction and that partitions an internal space having a column shape,
a partition plate (<NUM>,<NUM>) that is accommodated in the header body, that extends in a vertical direction, and that divides the internal space into a first space (<NUM>) and a second space (<NUM>), where the one end portion of each of the plurality of flat tubes is disposed, in the extending direction, in a state in which the refrigerant is capable of being circulated at an upper end portion and a lower end portion of the internal space, and
a nozzle portion (<NUM>,<NUM>) that is disposed at a lower portion of the first space and that includes a discharge outlet (49A,62A) for blowing out the refrigerant supplied from an outside of the header toward a bottom surface of the header body, and
refrigerant circulation portions (54A), which are a part of the first space, are each formed on both sides of the nozzle portion in a width direction, and wherein
the bottom surface (45a) of the header body (<NUM>) includes a first bottom surface (45aa) for partitioning the first space (<NUM>) and a second bottom surface (45ab) for partitioning the second space (<NUM>),
characterized in that the heat exchanger comprises:
a first refrigerant guide portion (<NUM>) that is provided on the first bottom surface and that includes a first guide surface (73a) for guiding the refrigerant in a direction from the first space toward the second space, and
in that the first guide surface (73a) is a recessed curved surface that is recessed in a direction separated from a lower end portion of the partition plate (<NUM>,<NUM>).