CN114174758B - Heat exchanger and refrigeration cycle device - Google Patents

Abstract

The heat exchanger according to an embodiment of the present invention includes a first header, a second header, a plurality of heat transfer tubes, and connection pipes. The first header and the second header extend in the gravity direction and are juxtaposed with each other at a distance from each other. The heat transfer tubes are connected between the first header and the second header and are arranged at intervals in the gravitational direction. The connection pipe is connected to one of the first header and the second header, and supplies the refrigerant into the one header. The connecting pipe is provided with a separation part and a lead-out part. The partition portion partitions the one header in the gravity direction within the one header. The partition portion has an opening portion formed therein, the opening portion communicating one of the headers with the refrigerant flow passage in a gravitational direction and having the refrigerant flow passage through which the refrigerant flows.

Description

Heat exchanger and refrigeration cycle device

Technical Field

Embodiments of the present invention relate to a heat exchanger and a refrigeration cycle device.

Background Art

A heat exchanger for heat exchange between a refrigerant and heat exchange air is mounted in a refrigeration cycle device. The heat exchanger includes a pair of headers arranged along the gravity direction, a plurality of heat transfer tubes connected in parallel between the headers, and fins connected between adjacent heat transfer tubes. A connecting pipe that connects the inside and outside of the heat exchanger is connected to the header from the side of the header.

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

However, in the above-mentioned heat exchanger, since the connecting pipe is connected to the header from the side, an invalid space where liquid refrigerant is retained may be formed in the portion located below the opening of the connecting pipe in the header. In this case, the amount of refrigerant retained in the heat exchanger increases by the amount of refrigerant retained in the invalid space. In addition, when the invalid space is formed in one header, when the heat exchanger is used as a condenser, it is difficult for the refrigerant to flow through the heat transfer pipe opening to the invalid space. As a result, it becomes a cause of reduced heat exchange performance.

Prior art literature

Patent Literature

Patent Document 1: Japanese Patent Application Publication No. 2019-56542

Summary of the invention

Problems to be solved by the invention

An object of the present invention is to provide a heat exchanger and a refrigeration cycle device that can suppress the formation of dead space in a header and achieve improved heat exchange performance.

Means used to solve problems

The heat exchanger of the embodiment includes a first header and a second header, a plurality of heat transfer tubes and a connecting pipe. The first header and the second header extend in the direction of gravity and are arranged side by side with intervals between them. The heat transfer tubes are connected between the first header and the second header and are arranged with intervals in the direction of gravity. The connecting pipe is connected to one of the first header and the second header to supply refrigerant into the one header. The connecting pipe includes a partition and a lead-out portion. The partition partitions one of the headers in the direction of gravity and has a refrigerant flow path for circulating the refrigerant. An opening is formed in the partition to connect the inside of one of the headers with the refrigerant flow path in the direction of gravity.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic configuration diagram of an air conditioner according to a first embodiment.

FIG2 is a partial cross-sectional view of the outdoor heat exchanger according to the first embodiment.

FIG. 3 is an enlarged perspective view of the outdoor heat exchanger showing the periphery of the first partitioning connecting pipe.

FIG. 4 is an enlarged cross-sectional view of a portion IV of FIG. 2 .

Fig. 5 is a cross-sectional view corresponding to the line V-V in Fig. 3 .

FIG6 is an enlarged cross-sectional view of the portion VI of FIG2.

FIG. 7 is a cross-sectional view corresponding to FIG. 4 of the outdoor heat exchanger according to the second embodiment.

DETAILED DESCRIPTION

Hereinafter, the heat exchanger and the refrigeration cycle device of the embodiment will be described with reference to the accompanying drawings. In addition, in the following description, expressions of relative or absolute configurations such as "parallel" or "orthogonal", "center", "coaxial", etc., not only strictly represent such configurations, but also represent the state of relative displacement at an angle or distance with a tolerance or a degree to which the same function can be obtained.

(First Embodiment)

FIG. 1 is a schematic configuration diagram of an air conditioner 1 .

As shown in FIG1 , an air conditioner 1 as a refrigeration cycle device of the present embodiment is configured such that 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 exchanger) 6 are sequentially connected via a refrigerant flow path 7. In addition, in the example shown in FIG1 , a solid arrow indicates a flow direction of the refrigerant during cooling, and a dotted arrow indicates a flow direction of the refrigerant during heating.

The compressor 2 includes a compressor body 11 and an accumulator 12 .

The accumulator 12 is a structure that captures liquid refrigerant in the refrigerant supplied to the compressor main body 11 and supplies gaseous refrigerant to the compressor main body 11 .

The compressor body 11 compresses the gas refrigerant taken into the interior through the accumulator 12 to form a high-temperature and high-pressure gas refrigerant.

In such an air conditioner 1, the cooling operation, heating operation, etc. are switched by changing the flow of the refrigerant using the four-way valve 3. For example, in the cooling operation, the refrigerant flows in the refrigerant flow path 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 functions as a condenser and the indoor heat exchanger 6 functions as an evaporator to cool the room.

On the other hand, in the heating operation, in the refrigerant flow path 7, the refrigerant flows 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 functions as a condenser and the outdoor heat exchanger 4 functions as an evaporator to heat the room.

Next, the outdoor heat exchanger 4 will be described. FIG. 2 is a partial cross-sectional view of the outdoor heat exchanger 4. As shown in 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, a plurality of heat transfer tubes 23 and fins 24. In addition, in the following description, the extension direction of each header unit 21, 22 is referred to as the Z direction, and the two directions orthogonal to the Z direction are referred to as the X direction and the Y direction, respectively. In addition, in the X direction, the Y direction and the Z direction, the arrow direction in the figure is referred to as the positive (+) side, and the direction opposite to the arrow is referred to as the negative (-) side. In the present embodiment, the outdoor heat exchanger 4 is arranged in such a manner that the Z direction is along the gravity direction. In this case, the +Z side is set to the top, and the -Z side is set to the bottom.

The first header unit 21 and the second header unit 22 extend parallel to each other in the Z direction with a gap therebetween. In the following description, an example is given in which the outdoor heat exchanger 4 functions as an evaporator. In this case, the first header unit 21 functions as an inlet-side header for the refrigerant. The second header unit 22 functions as an outlet-side header for the refrigerant.

The first header unit 21 includes a first cylinder portion (first header) 31 , a first cover portion 32 , and first connecting pipes 33 , 34 .

The first cylindrical portion 31 is formed in, for example, a cylindrical shape extending in the Z direction.

The first cover portion 32 closes the upper end opening of the first tube portion 31. In the present embodiment, the outer peripheral edge of the first cover portion 32 is joined to the upper end opening edge of the first tube portion 31 by brazing or the like.

Each of the first connecting pipes 33 and 34 has a function of introducing the refrigerant into the first tube portion 31 and partitioning the first tube portion 31 in the Z direction. In the present embodiment, the first connecting pipes 33 and 34 are, for example, a first partitioning connecting pipe 33 and a first cover connecting pipe 34. Each of the first connecting pipes 33 and 34 distributes the refrigerant via a distributor (not shown) provided on the refrigerant flow path 7. In addition, the detailed structure of each of the first connecting pipes 33 and 34 will be described later.

The second header unit 22 includes a second cylinder portion (second header) 36 , a second cover portion 37 , and second connecting pipes 38 , 39 .

The second tube portion 36 is formed in, for example, a cylindrical shape extending in the Z direction.

The second cover portion 37 closes the lower end opening of the second tube portion 36. In the present embodiment, the outer peripheral edge of the second cover portion 37 is joined to the lower end opening edge of the second tube 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 second cylindrical portion 36 and partitioning the second cylindrical portion 36 in the Z direction. In the present embodiment, the second connecting pipes 38 and 39 are, for example, a second partitioning connecting pipe 38 and a second cover connecting pipe 39 .

Fig. 3 is an enlarged perspective view of the outdoor heat exchanger 4 showing the periphery of the first partitioning connection pipe 33. Fig. 4 is an enlarged cross-sectional view of a portion IV in Fig. 2 .

As shown in Fig. 3 and Fig. 4, each heat transfer tube 23 extends in the X direction and is arranged in parallel with each other at intervals in the Z direction. The heat transfer tube 23 is, for example, a flat tube with the Y direction as the long axis direction. As shown in Fig. 3, a plurality of flow holes 23a penetrating the heat transfer tube 23 in the X direction are formed in the heat transfer tube 23 in the Y direction. In addition, the cross-sectional shape of each heat transfer tube 23 can be appropriately changed.

The -X side end of each heat transfer tube 23 is connected to the first header unit 21 (first barrel 31). Specifically, a pipe insertion port 41 opening toward the +X side is formed in the first barrel 31. A plurality of pipe insertion ports 41 are formed at intervals in the Z direction. The -X side end of each heat transfer tube 23 is connected to the inner circumferential surface of the pipe insertion port 41 by brazing or the like while being 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 barrel 31. In the present embodiment, the -X side end edge of each heat transfer tube 23 is located on the axis O1 of the first barrel 31. The -X side end edge of each heat transfer tube 23 may also be located on the +X side or -X side relative to the axis O1. In addition, the -X side end edge of each heat transfer tube 23 may also be arranged to be flush with the inner circumferential surface of the first barrel 31, for example.

As shown in FIG2 , the +X side end of each heat transfer tube 23 is connected to the second header unit 22 (second tube 36). In addition, 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 inserted into a pipe insertion port (not shown) formed in the second tube 36 and connected to the second tube 36 by brazing or the like. Thus, each heat transfer tube 23 connects the header units 21 and 22 in parallel.

The fins 24 are respectively 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 in a state where the upper and lower ends are 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, the refrigerant flowing in the heat transfer tube 23 and the heat exchange air exchange heat via the heat transfer tube 23 and the fins 24. In addition, corrugated fins, plate fins, etc. can be used as the fins 24.

The first partition connection pipe 33 is connected to the middle portion of the first tube 31 in the Z direction at intervals in the Z direction. That is, the first partition connection pipe 33 partitions the first tube 31 into a plurality of spaces in the Z direction.

The first cover closes the lower end opening of the first tube portion 31 with the connecting pipe 34 , thereby separating the first tube portion 31 into the inside and the outside.

Fig. 5 is a cross-sectional view corresponding to the line V-V in Fig. 3 .

As shown in Fig. 3 and Fig. 5, the first partition connection pipe 33 is formed integrally with a pipe material. Specifically, the first partition connection pipe 33 includes a partition portion 51 located at the +X side end (front end), a connection portion (lead-out portion) 52 located at the -X side end (base end), and a transition portion (lead-out portion) 53 located between the partition portion 51 and the connection portion 52.

The partition 51 is in a flat shape that is flattened in the Z direction. The partition 51 has an upper wall and a lower wall, and a refrigerant flow path 57 for circulating the refrigerant is formed between the upper wall and the lower wall (also refer to Figure 4). The top view shape of the partition 51 is formed into a circular shape that imitates the inner circumferential surface shape of the cylinder 31. The thickness of the partition 51 is thinner than the arrangement pitch of adjacent heat transfer tubes 23. The partition 51 is inserted into the first cylinder 31 through an assembly hole 55 formed in the first cylinder 31. Specifically, the assembly hole 55 is a semicircular slit in the first cylinder 31 that opens to the -X side when viewed from above. The partition 51 is arranged between adjacent heat transfer tubes 23, thereby partitioning the first cylinder 31 in the Z direction.

An upper opening portion 51a is formed on the upper wall of the partition portion 51 and passes through the upper wall in the Z direction. The upper opening portion 51a is located on the -X side relative to the axis O1 of the first cylinder portion 31. When viewed from above, the upper opening portion 51a is formed in a circular shape and is arranged at a position that does not overlap with the above-mentioned heat transfer tube 23. The upper opening portion 51a connects the refrigerant flow path 57 in the first cylinder portion 31 and the first partition connecting tube 33 (partition portion 51). However, the upper opening portion 51a can also be arranged to overlap with a portion of the heat transfer tube 23 when viewed from above. In addition, the top view shape, number, etc. of the upper opening portion 51a can be appropriately changed.

As shown in Fig. 5, a positioning protrusion 54 protruding in the +X direction is formed on the partition 51. The positioning protrusion 54 may be formed on at least one of the upper wall and the lower wall of the partition 51. The positioning protrusion 54 is inserted into a positioning hole 56 in the first cylinder 31, and the positioning hole 56 is formed at a position opposite to the assembly hole 55 in the X direction.

As shown in FIG3 , the transition portion 53 is connected to the -X side end of the partition portion 51. The transition portion 53 is reduced in the Y direction as it moves toward the -X side, and gradually increases in the Z direction, while being led out from the assembly hole 55. The +X side edge of the transition portion 53 constitutes an extension portion 53a extending from the outer peripheral edge of the partition portion 51 to both sides in the Y direction. The extension portion 53a is close to or abuts against the opening end surface of the assembly hole 55.

The connection portion 52 extends from the transition portion 53 toward the −X side. The connection portion 52 is formed into a circular shape when viewed in a cross section perpendicular to the X direction. The refrigerant flow path 7 is connected to the connection portion 52 .

As shown in FIGS. 3 and 5 , in order to assemble the first partition connection pipe 33 to the first cylinder 31, the partition 51 is first 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 extension 53a is close to or abuts against the open end surface of the assembly hole 55. In this state, the first partition connection pipe 33 is brazed to the inner circumferential surface of the first cylinder 31, the inner circumferential surface of the assembly hole 55, and the inner circumferential surface of the positioning hole 56. Thus, the first partition connection pipe 33 is assembled to the first cylinder 31 in a state where the assembly hole 55 and the positioning hole 56 are closed and the outer circumferential edge of the partition 51 is in close contact with the inner circumferential surface of the first cylinder 31.

As shown in Fig. 2, the first cover connection pipe 34 has a partition portion 51, a connection portion 52, and a transition portion 53, similarly to the first partition connection pipe 33. The partition portion 51 closes the lower end opening of the first cylinder portion 31. The first cover connection pipe 34 can be assembled to the first cylinder portion 31 by, for example, the same method as the first partition connection pipe 33.

The first barrel 31 of the present embodiment is divided into a first space S1 separated by the first cover connecting tube 34 and the first partition connecting tube 33, a second space S2 separated by each first partition connecting tube 33, and a third space S3 separated by the first partition connecting tube 33 and the first cover 32. In the present embodiment, the volume (length in the Z direction) of each space S1 to S3 is set to be equal. However, the volume of each space S1 to S3 can be appropriately changed. In addition, each barrel 31 can also be divided into two or more spaces.

FIG. 6 is an enlarged view of portion VI of FIG. 2 .

As shown in Fig. 6, the second partition connection pipe 38 has a partition portion 51, a connection portion 52, and a transition portion 53, similarly to the first partition connection pipe 33. The second partition connection pipe 38 has the same structure as the first partition connection pipe 33, except that a lower opening portion 59 is formed on the lower wall of the partition portion 51 instead of the upper opening portion 51a.

2, the second cover connection pipe 39 has a partition portion 51, a connection portion 52, and a transition portion 53 similarly to the second partition connection pipe 38, and a lower opening portion 59 is formed on the lower wall of the partition portion 51. The partition portion 51 of the second cover connection pipe 39 closes the upper end opening of the second cylinder portion 36.

The second tube portion 36 of the present embodiment is divided into a fourth space S4 partitioned by the second cover portion 37 and the second partition connection pipe 38 , a fifth space S5 partitioned by each second partition connection pipe 38 , and a sixth space S6 partitioned by the second partition connection pipe 38 and the second cover connection pipe 39 .

Next, the operation of the outdoor heat exchanger 4 will be described.

First, the case where the outdoor heat exchanger 4 functions as an evaporator is described. The refrigerant decompressed by the expansion valve 5 becomes a liquid refrigerant or a gas-liquid two-phase refrigerant rich in liquid with a low dryness and flows into each of the first connecting pipes 33 and 34. The refrigerant flowing into each of the first connecting pipes 33 and 34 is discharged upward from the upper opening 51a toward each of the spaces S1 to S3 in the first cylinder 31 through the connecting portion 52, the transition portion 53, and the partition portion 51. The refrigerant flowing 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. The refrigerant flows toward the +X side in the flow hole 23a in the heat transfer tube 23.

The refrigerant passing through each heat transfer tube 23 flows into the second cylinder portion 36, and then flows into the second connecting pipes 38 and 39 through the lower opening 59 of the second connecting pipes 38 and 39. The refrigerant flowing into the second connecting pipes 38 and 39 is discharged from the outdoor heat exchanger 4 via the partition portion 51, the transition portion 53, and the connecting portion 52.

In the outdoor heat exchanger 4 of the present embodiment, the heat exchange air passes through the gaps between the fins 24 along the Y direction between the heat transfer tubes 23 that are opposed to each other in the Z direction. Moreover, when the heat exchange air passes through the outdoor heat exchanger 4, it exchanges heat with the refrigerant flowing in the heat transfer tubes 23 through the heat transfer tubes 23 and the fins 24. At this time, the refrigerant supplied to the outdoor heat exchanger 4 absorbs heat while flowing in 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 gas-liquid two-phase refrigerant flows into the second cylinder 36.

In addition, when the outdoor heat exchanger 4 is made to function as a condenser, the refrigerant flows in a flow opposite to the above-mentioned action. That is, the refrigerant compressed by the compressor 2 becomes a gas refrigerant or a gas-liquid two-phase refrigerant rich in gas with a high degree of dryness and flows into each second connecting pipe 38, 39. The refrigerant flowing into each second connecting pipe 38, 39 is discharged downward from the lower opening 59 toward each space S4 to S6 in the second cylinder 36. The refrigerant flowing into each space S1 to S3 is distributed to each heat transfer tube 23 while flowing downward in each space S1 to S3. When the outdoor heat exchanger 4 is made to function as a condenser, the refrigerant flowing in the heat transfer tube 23 dissipates heat during the process of flowing in the heat transfer tube 23, thereby heating the heat exchange air and becoming a gas-liquid two-phase refrigerant rich in liquid.

After that, the refrigerant passing through each heat transfer tube 23 flows into the first cylinder portion 31, and then flows into the first connecting pipes 33 and 34 through the upper opening 51a of the first connecting pipes 33 and 34. The refrigerant flowing into the first connecting pipes 33 and 34 is discharged from the outdoor heat exchanger 4 via the partition portion 51, the transition portion 53, and the connecting portion 52.

Here, in this embodiment, the following structure is adopted: the first tube portion 31 is divided in the Z direction by the first connecting pipes 33 and 34, and an upper opening portion 51a is formed in the dividing portion 51 of the first connecting pipes 33 and 34 to connect the inside of the first tube portion 31 with the refrigerant flow path 57 in the Z direction.

According to this configuration, by dividing the first cylinder 31 by the partition 51 of the first connecting pipes 33 and 34, the upper opening 51a can be arranged at the lowest point of each space S1 to S3, compared with the case where the partition member and the connecting pipe are separately provided. As a result, the liquid refrigerant can be prevented from being retained in each space S1 to S3, and the formation of an invalid space (a space where the liquid refrigerant is retained) in the first cylinder 31 can be prevented. As a result, the amount of refrigerant retained by the outdoor heat exchanger 4 can be reduced. In addition, since the formation of an invalid space can be prevented, for example, when the outdoor heat exchanger 4 is used as a condenser, the flow of the refrigerant in each heat transfer tube 23 and the first cylinder 31 becomes smooth.

In particular, in this embodiment, since the partition 51, the connection portion 52 and the transition portion 53 are formed integrally, the number of parts can be reduced compared to, for example, the case where the partition 51 is formed separately from the connection portion 52 and the transition portion 53. In addition, as the number of parts is reduced, the connection portion (for example, the brazing portion) with the first cylinder portion 31 can also be reduced, so that the manufacturing efficiency can also be improved.

In the present embodiment, a configuration is adopted in which the upper opening 51 a is formed at a position in the partition 51 that does not overlap with the heat transfer tube 23 in a plan view.

According to this configuration, it is possible to suppress the refrigerant discharged from the upper opening 51a from coming into contact with the heat transfer tube 23. Therefore, the refrigerant can be efficiently discharged upward in the first cylindrical portion 31.

In the present embodiment, a configuration is adopted in which the interior of the first tube portion 31 is partitioned into a plurality of spaces S1 to S3 by the first partition connection pipe 33 .

According to this configuration, the refrigerant is discharged upwards into each space S1 to S3, so that the refrigerant is easily distributed in the uppermost part of each space S1 to S3. Therefore, in particular, 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, the evaporation of the liquid refrigerant can be suppressed from being completed in the middle of the heat transfer tube (so-called drying up), thereby improving the heat exchange performance.

In the present embodiment, a configuration is adopted in which the lower end opening of the first tube portion 31 is closed with the first cover connection pipe 34 .

According to this configuration, the refrigerant can be discharged from the lowermost end of the first cylindrical portion 31 , and thus the formation of the above-mentioned ineffective space can be more reliably suppressed.

In this embodiment, the partition 51 is formed by flattening the front end of the integrally connected pipe into a flat shape, so that the first cylinder 31 can be partitioned even when the diameter of the first cylinder 31 is larger than the diameter of the connecting portion 52. In this case, for example, the flattening amount (the amount of crushing in the Z direction) of the partition 51 can be adjusted according to the top view shape of the first cylinder 31.

Furthermore, in the present embodiment, by providing the outdoor heat exchanger 4 described above, it is possible to provide a high-quality air conditioner 1 having excellent heat exchange performance at low cost.

(Second Embodiment)

Fig. 7 is a cross-sectional view corresponding to Fig. 4 of the outdoor heat exchanger 4 of the second embodiment. In the following description, the same reference numerals are given to the same components as those of the first embodiment and the description thereof is omitted. In the present embodiment, openings are formed on both upper and lower sides of the partition 51, which is different from the above embodiment.

In the first partition connection pipe 33 shown in FIG. 7 , a lower opening portion 51b is formed on the lower wall of the partition portion 51. The lower opening portion 51b penetrates the lower wall in the Z direction. The lower opening portion 51b overlaps with the upper opening portion 51a when viewed from above. The equivalent diameter of the lower opening portion 51b is smaller than the equivalent diameter of the upper opening portion 51a. In the present embodiment, the equivalent diameter of the lower opening portion 51b is set to about 1/2 of the equivalent diameter of the upper opening portion 51a. The so-called equivalent diameter refers to the diameter of a perfect circle having an outer circumference equal to the outer circumference of each opening portion 51a, 51b. Therefore, when each opening portion 51a, 51b is a perfect circle, the diameter of each opening portion 51a, 51b is equal to the equivalent diameter. In addition, each opening portion 51a, 51b can also be arranged at a position that does not overlap when viewed from above. In addition, the equivalent diameter of the lower opening 51 b may be equal to or larger than the equivalent diameter of the upper opening 51 a .

In this embodiment, an upper opening 51a and a lower opening 51b are formed in the partition 51. Therefore, the refrigerant can be supplied to the upper space (for example, the space S3) located above the partition 51 and the lower space (for example, the space S2) located below the partition 51. Thus, the refrigerant can be supplied more evenly to each space S1 to S3, and the refrigerant can be evenly supplied to each heat transfer tube 23 arranged in the Z direction.

Furthermore, in the present embodiment, the equivalent diameter of the upper opening 51 a is larger than the equivalent diameter of the lower opening 51 b .

According to this configuration, refrigerant can be actively supplied to the space above the partition 51. Meanwhile, by supplying refrigerant to the space above the spaces S1 and S2 through the lower opening 51b, refrigerant can be supplied to the heat transfer tubes 23 connected to the spaces S1 and S2.

In the above embodiment, the case where the Z direction of the outdoor heat exchanger 4 coincides with the gravity direction is described. However, the Z direction does not necessarily coincide with the gravity direction, and the Z direction may intersect with the gravity direction.

In the above embodiment, the outdoor heat exchanger 4 is described as an example, but the structure of the above embodiment can also be adopted in the indoor heat exchanger 6.

In the above embodiment, the configuration in which the connecting pipes 33, 34, 38, and 39 are connected to the first tube portion 31 and the second tube portion 36 is described, but the present invention is not limited to this configuration. For example, only the partition connecting pipes may be used, or only the cover connecting pipes may be used. In addition, the connecting pipes may be used only in one of the first header unit 21 and the second header unit 22.

In the above embodiment, the configuration in which each of the cylinders 31 and 36 is partitioned into a plurality of spaces by the connection pipe is described, but the present invention is not limited to this configuration. The inside of each of the cylinders 31 and 36 may be partitioned into a single space by the cover connection pipe and the cover.

According to at least one embodiment described above, the following structure is adopted, that is, the connecting pipe comprises: a partition portion, which divides one collecting pipe along the gravity direction inside one collecting pipe; and a lead-out portion, which is integrally connected to the partition portion and leads out from one collecting pipe to the outside, and an opening portion is formed in the partition portion to connect the inside of one collecting pipe with the refrigerant flow path in the gravity direction.

According to this configuration, it is possible to suppress the formation of dead space in the header, thereby improving the heat exchange performance.

Several embodiments of the present invention have been described, but these embodiments are presented as examples and are not intended to limit the scope of the invention. These embodiments can be implemented in various other ways, and various omissions, substitutions, and changes can be made without departing from the scope of the subject matter of the invention. These embodiments and their variations are included in the scope and subject matter of the invention, and are also included in the invention described in the claims and the scope of their equivalents.

Description of Reference Numerals

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…first cylinder (first header), 33…first partition connecting tube (connecting tube), 34…first cover connecting tube (connecting tube), 36…second cylinder (second header), 38…second partition connecting tube (connecting tube), 39…second cover connecting tube (connecting tube), 51…partition, 51a…upper opening (opening), 51b…lower opening (opening), 52…connecting section (lead-out section), 53…transition section (lead-out section), 57…refrigerant flow path, 59…lower opening (connecting tube), S1…first space (lower space), S2…second space (upper space, lower space), S3…third space (upper space)

Claims (5)

1. A heat exchanger comprising: The first header and the second header extend along the gravity direction and are arranged in parallel with each other at intervals; a plurality of heat transfer tubes connected between the first header and the second header and arranged at intervals in the gravity direction; and a connecting pipe connected to one of the first header and the second header to supply refrigerant to the one header, The connecting pipe has: a partition portion that partitions the one header in the gravity direction within the one header and has a refrigerant flow path through which the refrigerant flows; and The lead-out portion is integrally connected to the partition portion and is led out from the one header to the outside. An opening is formed in the partition portion, the opening communicating the inside of the one header with the refrigerant flow path in the gravity direction; The lead-out portion includes a transition portion that is formed integrally with the partition portion and gradually increases in the gravity direction as it moves away from the partition portion and gradually decreases in a direction intersecting the extension direction of the one header when viewed from the gravity direction. 2. The heat exchanger according to claim 1, wherein: The end of the heat transfer tube is inserted into the one header. The opening is formed at a position in the partition that does not overlap with an end portion of the heat transfer tube in a plan view as seen from the gravity direction. 3. The heat exchanger according to claim 1 or 2, wherein: The partition is located in the middle of the one header in the gravity direction, and divides the inside of the one header into an upper space and a lower space. The opening portion comprises: an upper opening portion, opening toward the upper space; and The lower opening portion opens toward the lower space. 4. The heat exchanger according to claim 3, wherein: The equivalent diameter of the upper opening is larger than the equivalent diameter of the lower opening. 5. A refrigeration cycle device, characterized in that: The heat exchanger according to any one of claims 1 to 4 is made to function as an evaporator.