JP7210744B2 - Heat exchanger and refrigeration cycle equipment - Google Patents

Description

An embodiment of the present invention relates to a heat exchanger and a refrigerating cycle device.

A refrigeration cycle device is equipped with a heat exchanger for performing heat exchange between a refrigerant and heat exchange air. This type of heat exchanger includes a pair of headers arranged along the direction of gravity, a plurality of heat transfer tubes connected in parallel between the headers, and fins joined between adjacent heat transfer tubes. ing. A connecting pipe that communicates the inside and outside of the heat exchanger is connected to the header from the side of the header.

When the heat exchanger described above functions as an evaporator, one header is supplied with a liquid-rich refrigerant through a connecting pipe. The refrigerant supplied to one header is distributed to each heat transfer tube in the process of upward circulation in one header. The refrigerant distributed to the heat transfer tubes exchanges heat with the heat exchange air passing between the heat transfer tubes through the fins while flowing through the heat transfer tubes.

However, in the heat exchanger described above, since the connecting pipe is connected to the header from the side, an invalid space in which the liquid refrigerant stays is formed in a portion of the header located below the opening of the connecting pipe. There is a possibility that In this case, the amount of refrigerant held in the heat exchanger increases by the refrigerant staying in the void space. Further, when an invalid space is formed in one of the headers, when the heat exchanger functions as a condenser, it becomes difficult for the refrigerant to flow through the heat transfer tubes opening into the invalid space. As a result, it causes deterioration of heat exchange performance.

JP 2019-56542 A

The problem to be solved by the present invention is to provide a heat exchanger and a refrigerating cycle apparatus capable of suppressing the formation of void spaces in the header and improving the heat exchange performance.

A heat exchanger according to an embodiment includes a first header, a second header, a plurality of heat transfer tubes, and connecting tubes. The first header and the second header extend along the direction of gravity and are arranged side by side with an interval therebetween. The heat transfer tubes connect between the first header and the second header, and are arranged at intervals in the direction of gravity. The connection pipe is connected to one of the first header and the second header, and supplies the refrigerant into the one header. The connection pipe has a partition and a drawer. The partition section has a refrigerant flow path that partitions the one header in the direction of gravity and allows the refrigerant to flow within the one header. The partition is formed with an opening that allows the inside of one of the headers and the refrigerant flow path to communicate in the direction of gravity. The lead-out includes a transition. The transition portion is integrally formed with the partition portion. The transition portion gradually shrinks in a direction crossing the extending direction of one header when viewed from the direction of gravity while gradually increasing in the direction of gravity as the distance from the partition portion increases.

1 is a schematic configuration diagram of an air conditioner according to a first embodiment; FIG. FIG. 2 is a partial cross-sectional view of the outdoor heat exchanger according to the first embodiment; The enlarged perspective view of the outdoor heat exchanger which shows the periphery of the connection pipe for 1st partitions. FIG. 3 is an enlarged cross-sectional view of part IV in FIG. 2 ; FIG. 4 is a cross-sectional view corresponding to line VV of FIG. 3; FIG. 3 is an enlarged cross-sectional view of a VI portion in FIG. 2; Sectional drawing corresponding to FIG. 4 in the outdoor heat exchanger which concerns on 2nd Embodiment.

Hereinafter, heat exchangers and refrigerating cycle devices according to embodiments will be described with reference to the drawings. In the following description, expressions of relative or absolute arrangement such as "parallel", "perpendicular", "center", "coaxial", etc. not only express such arrangement strictly, but also tolerances and It also represents a state of relative displacement with an angle or distance that provides the same function.

(First embodiment)
FIG. 1 is a schematic configuration diagram of an air conditioner 1. As shown in FIG.
As shown in FIG. 1, an air conditioner 1, which is a refrigeration cycle device of the present embodiment, includes a compressor 2, a four-way valve 3, an outdoor heat exchanger (heat exchanger) 4, an expansion valve 5, and an indoor heat exchanger ( Heat exchangers 6 are sequentially connected by refrigerant flow paths 7 . In the example shown in FIG. 1, solid line arrows indicate the flow direction of the refrigerant during cooling, and broken line arrows indicate the flow direction of the refrigerant during heating.

The compressor 2 includes a compressor body 11 and an accumulator 12 .
The accumulator 12 is configured to capture liquid refrigerant among the refrigerant supplied to the compressor main body 11 and supply gas refrigerant to the compressor main body 11 .
The compressor main body 11 compresses the gas refrigerant taken inside through the accumulator 12 into a high-temperature and high-pressure gas refrigerant.

In such an air conditioner 1, the four-way valve 3 changes the flow of the refrigerant to switch between the cooling operation, the heating operation, and the like. For example, in cooling operation, the refrigerant flows through the refrigerant passage 7 in the order of the compressor 2, the four-way valve 3, the outdoor heat exchanger 4, the expansion valve 5, and the indoor heat exchanger 6. At this time, the outdoor heat exchanger 4 is made to function as a condenser and the indoor heat exchanger 6 is made to function as an evaporator to cool the room.
On the other hand, in the heating operation, the refrigerant flows through the refrigerant passage 7 in the order of the compressor 2 , the four-way valve 3 , the indoor heat exchanger 6 , the expansion valve 5 and the outdoor heat exchanger 4 . At this time, the indoor heat exchanger 6 is made to function as a condenser, and the outdoor heat exchanger 4 is made to function as an evaporator to heat the room.

Next, the outdoor heat exchanger 4 will be explained. FIG. 2 is a partial cross-sectional view of the outdoor heat exchanger 4. FIG.
As shown in FIG. 2, the outdoor heat exchanger 4 is a so-called parallel flow heat exchanger. The outdoor heat exchanger 4 includes a first header unit 21 and a second header unit 22 , multiple heat transfer tubes 23 , and fins 24 . In the following description, it is assumed that the direction in which the header units 21 and 22 extend is the Z direction, and two directions orthogonal to the Z direction are the X direction and the Y direction. Further, of the X direction, Y direction and Z direction, the direction indicated by the arrow in the drawing will be referred to as the plus (+) side, and the direction opposite to the arrow will be referred to as the minus (−) side. In this embodiment, the outdoor heat exchanger 4 is installed so that the Z direction is along the direction of gravity. In this case, the +Z side is set upward and the -Z side is set downward.

The first header unit 21 and the second header unit 22 extend parallel to each other along the Z direction while being spaced apart in the X direction. In the following description, the case where the outdoor heat exchanger 4 functions as an evaporator will be described as an example. In this case, the first header unit 21 functions as a refrigerant inlet header. The second header unit 22 functions as a refrigerant outlet header.

The first header unit 21 includes a first tubular portion (first header) 31 , a first lid portion 32 , and first connection pipes 33 and 34 .
The first cylindrical portion 31 is formed in a cylindrical shape extending in the Z direction, for example.
The first lid portion 32 closes the upper end opening of the first cylindrical portion 31 . In addition, in the present embodiment, the outer peripheral edge of the first lid portion 32 is joined to the upper end opening edge of the first cylindrical portion 31 by brazing or the like.

Each of the first connection pipes 33 and 34 has the function of introducing the refrigerant into the first cylindrical portion 31 and partitioning the first cylindrical portion 31 in the Z direction. In this embodiment, the first connection pipes 33 and 34 are, for example, the first partition connection pipe 33 and the first lid connection pipe 34 . Refrigerant is distributed to each of the first connection pipes 33 and 34 via a distributor (not shown) provided on the refrigerant flow path 7 . A detailed configuration of each of the first connection pipes 33 and 34 will be described later.

The second header unit 22 includes a second tubular portion (second header) 36 , a second lid portion 37 , and second connection pipes 38 and 39 .
The second cylindrical portion 36 is formed, for example, in a cylindrical shape extending in the Z direction.
The second lid portion 37 closes the lower end opening of the second cylindrical portion 36 . In addition, in this embodiment, the outer peripheral edge of the second lid portion 37 is joined to the lower end opening edge of the second cylindrical portion 36 by brazing or the like.

Each of the second connecting pipes 38 and 39 has a function of discharging the refrigerant from the inside of the second cylindrical portion 36 and partitioning the second cylindrical portion 36 in the Z direction. In this embodiment, the second connection pipes 38 and 39 are, for example, the second partition connection pipe 38 and the second lid connection pipe 39 .

FIG. 3 is an enlarged perspective view of the outdoor heat exchanger 4 showing the periphery of the first partition connecting pipe 33. As shown in FIG. FIG. 4 is an enlarged cross-sectional view of part IV in FIG.
As shown in FIGS. 3 and 4, the heat transfer tubes 23 extend in the X direction and are arranged in parallel with each other at intervals in the Z direction. The heat transfer tube 23 is, for example, a flat tube whose long axis is in the Y direction. As shown in FIG. 3, the heat transfer tube 23 is formed with a plurality of through holes 23a that penetrate the heat transfer tube 23 in the X direction and are aligned in the Y direction. Note that the cross-sectional shape of each heat transfer tube 23 can be changed as appropriate.

The −X side end of each heat transfer tube 23 is connected to the first header unit 21 (first cylindrical portion 31). Specifically, a pipe insertion port 41 that opens toward the +X side is formed in the above-described first cylindrical portion 31 . A plurality of pipe insertion openings 41 are formed at intervals in the Z direction. The −X side end of each heat transfer tube 23 is connected to the inner peripheral surface of the corresponding pipe insertion port 41 by brazing or the like while being separately inserted into the corresponding pipe insertion port 41 . In this case, the −X side end of each heat transfer tube 23 protrudes into the first cylindrical portion 31 . In this embodiment, the -X side edge of each heat transfer tube 23 is located on the axis O1 of the first tubular portion 31 . The −X side edge of each heat transfer tube 23 may be located on the +X side or the −X side with respect to the axis O1. The −X side edge of each heat transfer tube 23 may be arranged flush with the inner peripheral surface of the first cylindrical portion 31, for example.

As shown in FIG. 2, the +X side end of each heat transfer tube 23 is connected to the second header unit 22 (the second cylindrical portion 36). In each heat transfer tube 23 , the method of connecting the +X side end to the second header unit 22 is the same as the method of connecting the −X side end to the first header unit 21 . That is, the +X side end of each heat transfer tube 23 is connected to the second cylindrical portion 36 by brazing or the like while being inserted into a pipe insertion opening (not shown) formed in the second cylindrical portion 36 . Thereby, each heat transfer tube 23 connects between each header unit 21 and 22 in parallel.

The fins 24 are arranged between the heat transfer tubes 23 facing each other in the Z direction. The fins 24 are arranged at intervals in the X direction with their upper and lower ends joined (for example, brazed) to the heat transfer tubes 23 facing each other in the Z direction. In the outdoor heat exchanger 4, between the heat transfer tubes 23 facing each other in the Z direction, the heat exchange air passes through the gaps between the fins 24 along the Y direction. At this time, heat is exchanged between the refrigerant flowing through the heat transfer tubes 23 and the heat exchange air via the heat transfer tubes 23 and the fins 24 . Corrugated fins, plate fins, or the like can be used for the fins 24 .

The above-described first partition connection pipe 33 is connected to an intermediate portion of the first tubular portion 31 in the Z direction with a space therebetween in the Z direction. That is, the first partitioning connection pipe 33 partitions the first tubular portion 31 into a plurality of spaces in the Z direction.
The first lid connection pipe 34 closes the lower end opening of the first tubular portion 31 to partition the inside and outside of the first tubular portion 31 .

FIG. 5 is a cross-sectional view corresponding to line VV of FIG.
As shown in FIGS. 3 and 5, the first partition connecting pipe 33 is integrally formed of a pipe material. Specifically, the first partition connection pipe 33 includes a partition portion 51 positioned at the +X side end (distal end) and a connection portion (drawer portion) 52 positioned at the −X side end (base end). , and a transition portion (drawer portion) 53 positioned between the partition portion 51 and the connection portion 52 .

The partition part 51 has a flat shape that is flattened in the Z direction. The partition part 51 has an upper wall and a lower wall, and a coolant flow path 57 (see also FIG. 4) for circulating the coolant is formed between the upper wall and the lower wall. A planar view of the partition portion 51 is formed in a circular shape following the shape of the inner peripheral surface of the tubular portion 31 . The thickness of the partition portion 51 is thinner than the arrangement pitch of the heat transfer tubes 23 adjacent to each other. The partition portion 51 is inserted into the first tubular portion 31 through an assembly hole 55 formed in the first tubular portion 31 . Specifically, the assembly hole 55 is a semicircular slit in a plan view that opens on the -X side in the first tubular portion 31 . The partition part 51 partitions the inside of the first tubular part 31 in the Z direction by being arranged between the adjacent heat transfer tubes 23 .

An upper opening 51a is formed in the upper wall of the partition 51 so as to penetrate the upper wall in the Z direction. The upper opening 51a is positioned on the −X side with respect to the axis O1 of the first cylindrical portion 31. As shown in FIG. In a plan view, the upper opening 51a is formed in a circular shape and arranged at a position not overlapping with the heat transfer tube 23 described above. The upper opening 51a communicates the inside of the first tubular portion 31 with the coolant flow path 57 of the first partitioning connecting pipe 33 (the partitioning portion 51). However, the upper opening 51a may be arranged so as to overlap a portion of the heat transfer tube 23 in plan view. Further, the plan view shape, number, and the like of the upper openings 51a can be changed as appropriate.

As shown in FIG. 5, the partition portion 51 is formed with a positioning protrusion 54 that protrudes in the +X direction. The positioning protrusion 54 may be formed on at least one of the upper wall and the lower wall of the partition portion 51 . The positioning projection 54 is inserted into a positioning hole 56 formed in the first cylindrical portion 31 at a position facing the assembly hole 55 in the X direction.

As shown in FIG. 3, the transition portion 53 continues to the −X side end portion of the partition portion 51 . The transition portion 53 is pulled out from the assembly hole 55 while shrinking in the Y direction toward the -X side and gradually increasing in the Z direction. The +X side edge of the transition portion 53 constitutes an overhanging portion 53a that overhangs both sides in the Y direction from the outer peripheral edge of the partition portion 51 . The protruding portion 53a is close to or in contact with the opening end face of the assembly hole 55 described above.

The connection portion 52 extends from the transition portion 53 to the -X side. The connection portion 52 is formed to have a circular cross-sectional view perpendicular to the X direction. The connecting portion 52 is connected to the coolant flow path 7 described above.

As shown in FIGS. 3 and 5 , in order to assemble the first partition connecting pipe 33 to the first cylindrical portion 31 , first, the partition portion 51 is inserted into the assembly hole 55 . At this time, the positioning protrusion 54 is inserted into the positioning hole 56 and the partition 51 is inserted to a position where the projecting portion 53 a approaches or abuts the opening end face of the assembly hole 55 . In this state, the first partition connecting pipe 33 is brazed to the inner peripheral surface of the first tubular portion 31 , the inner peripheral surface of the assembly hole 55 , and the inner peripheral surface of the positioning hole 56 . As a result, the assembly hole 55 and the positioning hole 56 are closed, and the outer peripheral edge of the partition portion 51 is in close contact with the inner peripheral surface of the first cylindrical portion 31, and the first partition connecting pipe 33 is connected to the first cylindrical portion. It is attached to the part 31 .

As shown in FIG. 2, the first lid connection pipe 34 has a partition portion 51, a connection portion 52 and a transition portion 53, like the first partition connection pipe 33 described above. The partition portion 51 closes the lower end opening of the first tubular portion 31 . The first lid connecting pipe 34 can be assembled to the first cylindrical portion 31 by the same method as that for the above-described first partitioning connecting pipe 33, for example.

The first cylindrical portion interior 31 of the present embodiment includes a first space S1 partitioned by the first lid connection pipe 34 and the first partition connection pipe 33, and a second space S1 partitioned by the first partition connection pipes 33. It is divided into a space S2 and a third space S3 partitioned by the first partitioning connection pipe 33 and the first lid portion 32 . In this embodiment, the volumes (lengths in the Z direction) of the spaces S1 to S3 are all set to be the same. However, the volume of each space S1 to S3 can be changed as appropriate. Also, each cylindrical portion 31 may be partitioned into two or four or more spaces.

FIG. 6 is an enlarged view of the VI part of FIG.
As shown in FIG. 6, the second partitioning connecting pipe 38 has a partitioning portion 51, a connecting portion 52 and a transition portion 53, like the first partitioning connecting pipe 33 described above. The second partition connecting pipe 38 is similar to the first partition connecting pipe 33 except that a lower opening 59 is formed in the lower wall of the partition 51 instead of the above-described upper opening 51a. Configuration.

As shown in FIG. 2 , the second lid connection pipe 39 has a partition portion 51 , a connection portion 52 and a transition portion 53 in the same manner as the second partition connection pipe 38 described above. A lower opening 59 is formed in the . The partition portion 51 of the second lid connection pipe 39 closes the upper end opening of the second cylindrical portion 36 .

The second cylindrical portion interior 36 of the present embodiment includes a second lid portion 37, a second partitioning connection pipe 38, a fourth space S4, a fifth space S5 partitioned by each of the second partitioning connection pipes 38, and a second It is divided into a sixth space S6 partitioned by the connecting pipe 38 for partition and the connecting pipe 39 for the second lid.

Next, the operation of the outdoor heat exchanger 4 described above will be described.
First, the case where the outdoor heat exchanger 4 functions as an evaporator will be described. The refrigerant decompressed by the expansion valve 5 becomes a liquid refrigerant or a liquid-rich gas-liquid two-phase refrigerant with a small degree of dryness, and flows into the first connecting pipes 33 and 34 . The refrigerant that has flowed into each of the first connection pipes 33 and 34 passes through the connection portion 52, the transition portion 53 and the partition portion 51, and flows upward from the upper opening portion 51a toward the spaces S1 to S3 in the first cylindrical portion 31. Dispensed. The refrigerant that has flowed into each of the spaces S1 to S3 is distributed to each of the heat transfer tubes 23 while circulating upward in each of the spaces S1 to S3. In each heat transfer tube 23, the refrigerant flows through the circulation hole 23a toward the +X side.

The refrigerant that has passed through each heat transfer tube 23 flows into the second cylindrical portion 36 and then flows into the second connecting pipes 38 and 39 through the lower openings 59 of the second connecting pipes 38 and 39 . The refrigerant that has flowed into the second connection pipes 38 and 39 is discharged from the outdoor heat exchanger 4 through the partition portion 51 , the transition portion 53 and the connection portion 52 .

In the outdoor heat exchanger 4 of this embodiment, the heat exchange air passes in the Y direction through the gaps between the fins 24 between the heat transfer tubes 23 facing each other in the Z direction. When the heat-exchanged air passes through the outdoor heat exchanger 4 , heat is exchanged with the refrigerant flowing through the heat transfer tubes 23 via the heat transfer tubes 23 and the fins 24 . At this time, the refrigerant supplied into the outdoor heat exchanger 4 absorbs heat while flowing through the heat transfer tubes 23, thereby cooling the heat exchange air and becoming a gas-rich gas-liquid two-phase refrigerant. That is, the gas-rich two-phase refrigerant flows into the second tubular portion 36 .

When the outdoor heat exchanger 4 functions as a condenser, the refrigerant flows in a manner opposite to that described above. That is, the refrigerant compressed by the compressor 2 flows into the second connection pipes 38 and 39 as a gas refrigerant or a gas-liquid two-phase refrigerant with a high dryness. Refrigerant that has flowed into each of the second connection pipes 38 and 39 is discharged downward from the lower opening 59 toward each of the spaces S4 to S6 in the second cylindrical portion 36. As shown in FIG. The refrigerant that has flowed into each of the spaces S1 to S3 is distributed to each heat transfer tube 23 while flowing downward in each of the spaces S1 to S3. When the outdoor heat exchanger 4 functions as a condenser, the refrigerant flowing through the heat transfer tubes 23 heats the heat exchange air while flowing through the heat transfer tubes 23, thereby warming the heat exchange air and forming a liquid-rich gas. It becomes a liquid two-phase refrigerant.

After that, the refrigerant that has passed through each heat transfer tube 23 flows into the first cylindrical portion 31 and then flows into the first connection pipes 33 and 34 through the upper openings 51 a of the first connection pipes 33 and 34 . The refrigerant that has flowed into the first connection pipes 33 and 34 is discharged from the outdoor heat exchanger 4 through the partition portion 51 , the transition portion 53 and the connection portion 52 .

Here, in the present embodiment, the first connecting pipes 33 and 34 partition the first tubular portion 31 in the Z direction, and the partition portion 51 of the first connecting pipes 33 and 34 separates the inside of the first tubular portion 31 from the refrigerant flow path. 57 in the Z direction.
According to this configuration, by partitioning the first cylindrical portion 31 by the partitioning portions 51 of the first connecting pipes 33 and 34, compared to the case where the partitioning member and the connecting pipe are provided separately, the lowermost portion of each of the spaces S1 to S3 The upper opening 51a can be arranged at a point. As a result, it is possible to prevent the liquid refrigerant from accumulating in the spaces S1 to S3, and to prevent the formation of an ineffective space (a space in which the liquid refrigerant accumulates) in the first cylindrical portion 31. FIG. As a result, the amount of refrigerant held by the outdoor heat exchanger 4 can be reduced. In addition, since it is possible to suppress the formation of void space, for example, when the outdoor heat exchanger 4 is used as a condenser, the refrigerant flows smoothly between the heat transfer tubes 23 and the inside of the first tubular portion 31 .

In particular, in the present embodiment, the partition portion 51, the connection portion 52, and the transition portion 53 are integrally formed. It is possible to reduce the number of parts. In addition, as the number of parts is reduced, the number of connection points (for example, brazing points) with the first tubular portion 31 can also be reduced, so it is possible to improve manufacturing efficiency.

In this embodiment, the upper opening 51a is formed in the partition 51 at a position that does not overlap the heat transfer tube 23 in plan view.
According to this configuration, it is possible to prevent the refrigerant discharged from the upper opening 51 a from hitting the heat transfer tubes 23 . Therefore, the refrigerant can be efficiently discharged upward in the first tubular portion 31 .

In the present embodiment, the inside of the first cylindrical portion 31 is partitioned into a plurality of spaces S1 to S3 by the first partitioning connecting pipe 33 .
According to this configuration, since the refrigerant is discharged upward into each of the spaces S1 to S3, the refrigerant can be easily distributed to the uppermost portion of each of the spaces S1 to S3. Therefore, especially when the outdoor heat exchanger 4 functions as an evaporator, the amount of liquid refrigerant supplied to each heat transfer tube 23 can be made uniform. As a result, it is possible to prevent the evaporation of the liquid refrigerant from being completed in the middle of the heat transfer tube (so-called dryout), thereby improving the heat exchange performance.

In this embodiment, the first lid connection pipe 34 is configured to block the lower end opening of the first tubular portion 31 .
According to this configuration, the refrigerant can be discharged from the lowermost end of the first tubular portion 31, so that the formation of the above-described invalid space can be suppressed more reliably.

In the present embodiment, by flattening the distal end portion of the integrally connected tubular member to form the partition portion 51, even when the diameter of the first cylindrical portion 31 is larger than the diameter of the connecting portion 52, the first cylindrical portion 31 The inside of the cylindrical portion 31 can be partitioned. In this case, it is possible to adjust, for example, the amount of flattening of the partition portion 51 (the amount of crushing in the Z direction) according to the outer shape of the first cylindrical portion 31 in a plan view.

In addition, in the present embodiment, by including the outdoor heat exchanger 4 described above, it is possible to provide a high-quality air conditioner 1 that is low in cost and excellent in heat exchange performance.

(Second embodiment)
FIG. 7 is a sectional view corresponding to FIG. 4 in the outdoor heat exchanger 4 according to the second embodiment. In the following description, the same reference numerals are given to the same configurations as in the above-described first embodiment, and the description thereof is omitted. This embodiment differs from the above-described embodiment in that openings are formed on both upper and lower sides of the partition 51 .

In the first partition connecting pipe 33 shown in FIG. 7, the lower wall of the partition portion 51 is formed with a lower opening portion 51b. The lower opening 51b penetrates the lower wall in the Z direction. The lower opening 51b overlaps the upper opening 51a in plan view. The equivalent diameter of the lower opening 51b is smaller than the equivalent diameter of the upper opening 51a. In this embodiment, the equivalent diameter of the lower opening 51b is set to about 1/2 of the equivalent diameter of the upper opening 51a. The equivalent diameter is the diameter of a perfect circle having an outer circumference equivalent to the outer circumference of each of the openings 51a and 51b. Therefore, when the openings 51a and 51b are perfectly circular, the diameters of the openings 51a and 51b are equal to the equivalent diameters. Note that the openings 51a and 51b may be arranged at positions that do not overlap each other in plan view. Also, the equivalent diameter of the lower opening 51b may be greater than or equal to the equivalent diameter of the upper opening 51a.

In this embodiment, the partition portion 51 is formed with an upper opening portion 51a and a lower opening portion 51b. Therefore, it becomes possible to supply the coolant to the upper space (for example, space S3) positioned above the partition portion 51 and the lower space (for example, space S2) positioned below the partition portion 51, respectively. Therefore, the refrigerant can be more uniformly supplied to the spaces S1 to S3, and the refrigerant can be evenly supplied to the heat transfer tubes 23 arranged in the Z direction.

Moreover, in this embodiment, the equivalent diameter of the upper opening 51a is larger than the equivalent diameter of the lower opening 51b.
According to this configuration, the coolant can be positively supplied to the upper space of the partition portion 51 . On the other hand, by supplying the refrigerant to the space above the spaces S1 and S2 through the lower opening 51b, the refrigerant can be supplied to the heat transfer tubes 23 connected above the spaces S1 and S2.

In the above-described embodiment, the case where the Z direction of the outdoor heat exchanger 4 matches the direction of gravity has been described. good too.
Although the outdoor heat exchanger 4 has been described as an example in the above-described embodiment, the configuration of the above-described embodiment may be adopted for the indoor heat exchanger 6 .

In the embodiment described above, the configuration in which the connection pipes 33, 34, 38, and 39 are connected to the first tubular portion 31 and the second tubular portion 36 has been described, but the configuration is not limited to this. For example, only the connecting pipe for the partition may be used, or only the connecting pipe for the lid may be used. Alternatively, a connection pipe may be used only for either the first header unit 21 or the second header unit 22 .
In the above-described embodiment, the configuration in which the tubular portions 31 and 36 are divided into a plurality of spaces by the connecting pipes has been described, but the configuration is not limited to this. The inside of each cylindrical portion 31, 36 may be defined as one space by a connecting pipe for lid or a lid portion.

According to at least one embodiment described above, the connection pipe includes a partition portion that partitions the one header in the direction of gravity, and a drawer that is integrally connected to the partition portion and is pulled out from the one header. , and the partition has an opening that communicates the inside of one of the headers with the refrigerant flow path in the direction of gravity.
According to this configuration, it is possible to suppress the formation of void spaces in the header and improve the heat exchange performance.

While several embodiments of the invention have been described, these embodiments have been presented by way of example and are not intended to limit the scope of the invention. These embodiments can be implemented in various other forms, and various omissions, replacements, and modifications can be made without departing from the scope of the invention. These embodiments and their modifications are included in the scope and spirit of the invention, as well as the scope of the invention described in the claims and equivalents thereof.

DESCRIPTION OF SYMBOLS 1... Air conditioner, 4... Outdoor heat exchanger (heat exchanger), 6... Indoor heat exchanger (heat exchanger), 6... Indoor heat exchanger (heat exchanger), 23... Heat transfer tube, 31... No. 1 cylindrical part (first header), 33... first partition connecting pipe (connecting pipe), 34... first lid connecting pipe (connecting pipe), 36... second cylindrical part (second header), 38... second 2 partition connection pipe (connection pipe), 39 second lid connection pipe (connection pipe), 51 partition, 51a upper opening (opening), 51b lower opening (opening), 52 ... connection portion (drawer portion), 53 ... transition portion (drawer portion), 57 ... refrigerant flow path, 59 ... lower opening (connection pipe), S1 ... first space (lower space), S2 ... second space ( upper space, lower space), S3 ... third space (upper space)

Claims (5)

a first header and a second header extending along the direction of gravity and arranged side by side with a gap therebetween;
a plurality of heat transfer tubes connecting between the first header and the second header and arranged at intervals in the direction of gravity;
a connecting pipe connected to one of the first header and the second header and supplying a refrigerant into the one header;
The connection pipe is
a partitioning portion in the one header that partitions the one header in the direction of gravity and has a refrigerant flow passage through which the refrigerant flows;
a pull-out portion integrally connected to the partition portion and pulled out from the one header;
The partition is formed with an opening that communicates the inside of the one header with the refrigerant flow passage in the direction of gravity ,
The lead-out portion is integrally formed with the partition portion, and gradually increases in the direction of gravity as it separates from the partition portion, and extends in a direction intersecting the extending direction of the one header when viewed from the direction of gravity. containing a tapering transition ,
Heat exchanger.




the ends of the heat transfer tubes are inserted into the one header,
The opening is formed in the partition at a position that does not overlap the end of the heat transfer tube in a plan view viewed from the direction of gravity.
A heat exchanger according to claim 1. the partition part partitions the inside of the one header into an upper space and a lower space at an intermediate portion in the gravity direction of the one header;
The opening is
an upper opening that opens toward the upper space;
a lower opening that opens toward the lower space;
A heat exchanger according to claim 1 or claim 2. the equivalent diameter of the upper opening is greater than the equivalent diameter of the lower opening;
A heat exchanger according to claim 3. Functioning the heat exchanger according to any one of claims 1 to 4 as an evaporator,
Refrigeration cycle equipment.

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