JP2017155993A - Heat exchanger and air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger capable of suppressing performance deterioration.SOLUTION: A heat exchanger includes: a first pipe group 22 in which a plurality of first heat transfer pipes 21 are arrayed; a first header part 52 that extends vertically and is formed into a cylindrical shape, and to which one end of each first heat transfer pipe 21 of the first pipe group 22 is communicatively connected; a plurality of second pipe groups 24 in which a plurality of second heat transfer pipes 23 are arrayed; a plurality of second header parts 53 that correspond to the plurality of second pipe groups 24, extend vertically and are formed into a cylindrical shape, and to which one end of each second heat transfer pipe 23 of the second pipe groups 24 is communicatively connected; and a plurality of communication passages that correspond to the plurality of second header parts 53, and whose one end is connected to a position in the same vertical direction as the first header part 52 and the other end is connected to any of the second header parts 53 so as to communicate between the first header part 52 and the second header parts 53.SELECTED DRAWING: Figure 2

Description

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

  As a heat exchanger for an air conditioner, there is known a heat exchanger tube in which a plurality of heat transfer tubes extending in the horizontal direction are arranged at intervals in the vertical direction and fins are provided on the outer surface of each heat transfer tube. Both ends of the plurality of heat transfer tubes are respectively connected to a pair of headers extending in the vertical direction. In such a heat exchanger, in order to secure the flow path length of the refrigerant, the refrigerant introduced into one header and circulated through the heat transfer tube to the other header is transmitted again by being folded back by the other header. It is configured to return to one header via a heat pipe.

In the folded-back header, a plurality of regions are defined by a partition plate that partitions the header in the vertical direction. As a result, the refrigerant introduced into the one region via the heat transfer tube is introduced into the other region through the connection tube, and then the inlet / outlet side through the plurality of heat transfer tubes connected to the other region. Is returned in one of the headers.
For example, Patent Document 1 discloses a heat exchanger that includes a connecting pipe having one main pipe part and a branch pipe part that branches from the main pipe part into a plurality of branches. In this heat exchanger, the main pipe portion is connected to a region in one header, and the branch pipe portions are respectively connected to any of a plurality of other regions in the header. And when using the said heat exchanger as an evaporator, the refrigerant | coolant introduced into one area | region of the header via the heat exchanger tube is introduce | transduced into several other area | regions through the main pipe part and branch pipe part in a connection pipe. Is done.

Japanese Patent Laying-Open No. 2015-55404

  By the way, in the heat exchanger of patent document 1, when diverting a refrigerant | coolant from the main pipe part of a connection pipe to a branch pipe part, the refrigerant | coolant from which a dryness differs in each branch pipe part may be introduce | transduced. That is, depending on the flow rate of the refrigerant and the direction of branching, a large amount of liquid-phase refrigerant may flow through only a part of the plurality of branch pipes, resulting in a problem that the refrigerant is not evenly divided. In addition, the refrigerant in the connecting pipe may be separated into a gas phase and a liquid phase due to a gas-liquid density difference, and the refrigerant may be divided in a state where the flow rate and the dryness are uneven.

If the flow is not evenly divided in this way, the flow state in each branch pipe varies depending on the flow rate, and the refrigerant distribution ratio at the time of the flow also changes.
For this reason, when the refrigerant is introduced again into the heat transfer tube via the header, a heat transfer tube through which almost no liquid-phase refrigerant passes is generated, and the heat transfer region of the heat exchanger cannot be fully utilized. . As a result, for example, when a heat exchanger is used for an air conditioner, cooling performance and heating performance are lowered, and indoor comfort is impaired.

  This invention is made | formed in view of such a subject, Comprising: It aims at providing the heat exchanger which can suppress a performance fall, and the air conditioner using this heat exchanger.

The present invention employs the following means in order to solve the above problems.
That is, the heat exchanger according to the first aspect of the present invention includes a first tube group that includes a first heat transfer tube that extends in the horizontal direction and in which a refrigerant circulates and a plurality of tubes are arranged at intervals in the vertical direction. A first header portion which is formed in a cylindrical shape extending in the vertical direction and one end of each of the first heat transfer tubes of the first tube group is connected in a communicating state; A plurality of second tube groups having a plurality of second heat transfer tubes arranged at intervals in the direction, and a plurality of second tube groups corresponding to the plurality of second tube groups, and having a cylindrical shape extending in the vertical direction A plurality of second header portions each connected to one end of each of the second heat transfer tubes of the second tube group in communication with each other, and a plurality of the second header portions corresponding to the plurality of second header portions; One end is the same as the first header part so that the second header part communicates with the first part. Comprising a communication passage and the other end is connected to the vertical position is connected to one of each of said second header portion.

  According to such a heat exchanger, the refrigerant introduced into the first header portion via each first heat transfer tube of the first tube group is connected to the same vertical direction position in the first header portion. To be introduced. Here, in the first header part, due to the gas-liquid density difference in the refrigerant, the liquid phase easily accumulates in the lower part of the first header part, and the gas phase easily accumulates in the upper part. Therefore, a difference occurs in the gas-liquid ratio of the refrigerant in the vertical direction in the first header portion. In the heat exchanger of the present invention, the communication paths connected to the plurality of second header portions are connected to the same vertical position of the first header portion, so that the refrigerant having substantially the same gas phase liquid phase ratio. Is introduced into each communication path. Therefore, equalization of the refrigerant flow rate for each of the plurality of communication paths can be achieved. As a result, the flow rate of the refrigerant introduced into the plurality of second heat transfer tubes can be equalized.

  The heat exchanger has one end connected to the first header portion and a plurality of divided flow paths arranged in parallel in the horizontal direction on the inside, and a plurality from the other end side of the main tube portion. A branch flow path that branches and communicates with the divided flow path is formed on the inside and includes branch connection pipes each having a branch pipe connected to each of the second header parts. It may be a channel formed by each of the divided channels and each of the branch channels.

  Thereby, compared with the case where each communicating path is comprised with the separate connection pipe, in the case of a branch connection pipe, since the construction location to a 1st header part becomes one place, construction becomes easy.

  In the heat exchanger, the number of the second heat transfer tubes of each of the second tube groups is different from each other, and the plurality of communication paths are connected to the second tube group having a large number of the second heat transfer tubes. The communication passage connected to the second header portion may have a larger flow path cross-sectional area.

  Accordingly, a larger amount of refrigerant is introduced into the second header portion where the number of second heat transfer tubes to be connected is relatively large. On the other hand, a smaller amount of refrigerant is introduced into the second header portion where the number of second heat transfer tubes connected is relatively small. As a result, it is possible to equalize the amount of refrigerant introduced by being divided into each second heat transfer tube.

  The heat exchanger includes a blower that blows air to each second tube group, and the speed of the air received by each second tube group by the blower is different for each second tube group, The plurality of communication passages may have a larger flow path cross-sectional area as the communication passage is connected to the second header portion to which the second pipe group is connected, which receives a higher speed of blowing air.

  In such a heat exchanger, the higher the speed of the air received by the second tube group, the more the heat exchange in the second tube group is promoted. Therefore, the heat exchange efficiency as the whole heat exchanger can be improved by introducing more refrigerant into the second header portion connected to the second tube group that receives a large speed of blowing air.

  The heat exchanger has one end at the same height position as the communication path connected to the first header portion so that the first header portion communicates with any of the plurality of second header portions. It may be further connected to the first header part and further includes another communication path whose other end is connected to the second header part at a height position different from the communication path connected to the second header part. Good.

  Thereby, a refrigerant | coolant is introduce | transduced into the 2nd header part from the several location from which an up-down direction differs. Therefore, since the gas-liquid ratio of the refrigerant in the vertical direction in the second header portion can be made uniform, it is possible to equalize the flow rate of the refrigerant divided into each second heat transfer tube.

  The heat exchanger includes a header having a cylindrical header main body extending in the vertical direction and a plurality of main partition plates that divide the header main body into a plurality of regions in the vertical direction, the first header portion being , A portion including a lowermost region among the plurality of regions in the header, wherein each of the second header portions includes any region other than the lowermost region among the plurality of regions in the header. It may be a part.

  By forming the first header part and the plurality of second header parts through the main partition plate in one header part, a heat exchanger having these first header part and the plurality of second header parts is easily configured. be able to.

  An air conditioner according to a second aspect of the present invention includes any one of the above heat exchangers.

  Accordingly, it is possible to provide a highly efficient air conditioner by suppressing a decrease in heat exchange performance due to uneven distribution of the refrigerant.

  According to the heat exchanger and the air conditioner of the present invention, efficiency reduction can be suppressed.

1 is an overall configuration diagram of an air conditioner according to a first embodiment of the present invention. It is a longitudinal cross-sectional view of the heat exchanger which concerns on 1st embodiment of this invention. It is a perspective view of the heat exchanger which concerns on 1st embodiment of this invention. It is a side view of the return side header and branch connection pipe of the heat exchanger which concerns on 2nd embodiment of this invention. It is a figure which shows the flow-path cross-sectional shape of the main pipe part in the branch connection pipe of the heat exchanger which concerns on 2nd embodiment of this invention. It is a perspective view of the heat exchanger which concerns on 3rd embodiment of this invention. It is a side view of the return side header and connecting pipe of the heat exchanger which concerns on 3rd embodiment of this invention. It is a perspective view of the heat exchanger which concerns on 4th embodiment of this invention. It is a side view of the return side header and connecting pipe of the heat exchanger which concerns on 4th embodiment of this invention. It is a perspective view which shows an example of the ventilation part which concerns on 4th embodiment of this invention. It is a perspective view of the heat exchanger which concerns on 5th embodiment of this invention. It is a side view of the return side header and connecting pipe of the heat exchanger which concerns on 5th embodiment of this invention. It is a side view of the return side header and connecting pipe of a heat exchanger concerning a 6th embodiment of the present invention.

Hereinafter, an air conditioner including a heat exchanger according to a first embodiment of the present invention will be described with reference to FIGS.
As shown in FIG. 1, the air conditioner 1 includes a compressor 2, an indoor heat exchanger 3 (heat exchanger 10), an expansion valve 4, an outdoor heat exchanger 5 (heat exchanger 10), a four-way valve 6, and The pipe 7 for connecting them is provided, and a refrigerant circuit composed of these is constituted.

The compressor 2 compresses the refrigerant and supplies the compressed refrigerant to the refrigerant circuit.
The indoor heat exchanger 3 performs heat exchange between the refrigerant and the indoor air. The indoor heat exchanger 3 is used as an evaporator during cooling operation and absorbs heat from the room, and is used as a condenser during heating operation and dissipates heat to the room.
The expansion valve 4 reduces the pressure by expanding the high-pressure refrigerant liquefied by exchanging heat with the condenser.
The outdoor heat exchanger 5 exchanges heat between the refrigerant and the outdoor air. During cooling operation, it is used as a condenser and dissipates heat to the outside, and during heating operation, it is used as an evaporator and absorbs heat from the outside.
The four-way valve 6 switches the direction in which the refrigerant flows between the heating operation and the cooling operation. Accordingly, during the cooling operation, the refrigerant circulates in the order of the compressor 2, the outdoor heat exchanger 5, the expansion valve 4, and the indoor heat exchanger 3. On the other hand, during the heating operation, the refrigerant circulates in the order of the compressor 2, the indoor heat exchanger 3, the expansion valve 4, and the outdoor heat exchanger 5.

Next, the heat exchanger 10 used as the indoor heat exchanger 3 and the outdoor heat exchanger 5 will be described with reference to FIGS.
The heat exchanger 10 includes a plurality of heat transfer tubes 20, a plurality of fins 28, a pair of headers 30, a first connection tube 60, and a second connection tube 70.

The heat transfer tube 20 is a tubular member extending linearly in the horizontal direction, and a flow path through which the refrigerant flows is formed. A plurality of such heat transfer tubes 20 are arranged at intervals in the vertical direction, and are arranged in parallel to each other.
In this embodiment, each heat transfer tube 20 has a flat tubular shape, and a plurality of flow paths arranged in parallel in the horizontal direction perpendicular to the extending direction of the heat transfer tube 20 are formed inside the heat transfer tube 20. ing. The plurality of flow paths are arranged in parallel to each other. Thereby, the outer shape of the cross section orthogonal to the extending direction of the heat transfer tube 20 is a flat shape with the horizontal direction orthogonal to the extending direction of the heat transfer tube 20 as the longitudinal direction.

  The fins 28 are respectively arranged between the heat transfer tubes 20 arranged as described above. In the present embodiment, the fins 28 are alternately arranged on the heat transfer tubes 20 adjacent in the vertical direction as they extend in the extending direction of the heat transfer tubes 20. It extends in a so-called corrugated shape extending so as to come into contact. In addition, the shape of the fin 28 is not limited to this, and may be any shape as long as it is provided so as to protrude from the outer peripheral surface of the heat transfer tube 20.

  The pair of headers 30 are provided so as to sandwich the heat transfer tubes 20 at both ends of the plurality of heat transfer tubes 20. One of the pair of headers 30 is an inlet / outlet header 40 that serves as an inlet / outlet of the refrigerant into the heat exchanger 10 from the outside, and the other is a return header 50 for returning the refrigerant in the heat exchanger 10. It is said that.

The entrance-and-exit header 40 is a cylindrical member extending in the vertical direction. The upper and lower ends are closed, and the interior is partitioned into two upper and lower areas by a partition plate 41. The lower area partitioned by the partition plate 41 is a lower entry / exit area 42, and the upper area is an upper entry / exit area 43. The lower entrance / exit area 42 and the upper entrance / exit area 43 are not in communication with each other in the entrance / exit header 40. The lower entry / exit area 42 and the upper entry / exit area 43 are connected to the pipes 7 constituting the refrigerant circuit.
Here, among the plurality of heat transfer tubes 20, the heat transfer tube 20 connected in communication with the lower access region 42 is the first heat transfer tube 21, and is connected in communication with the upper input / output region 43. The heat transfer tube 20 is a second heat transfer tube 23.

The folded-back header 50 includes a header body 51 and a main partition plate 58.
The header main body 51 is a cylindrical member extending in the vertical direction, and the upper end and the lower end are closed. The main partition plate 58 is provided in the header body 51, and divides the space in the header body 51 into upper and lower areas. In the present embodiment, two main partition plates 58 are provided in the header main body 51 so as to be spaced apart in the vertical direction. Thereby, the inside of the header body 51 is divided into three regions arranged vertically.

  A portion including the lowermost region of the three regions in the header body 51 is a first header portion 52. Of the three regions, the portions including the upper two regions other than the lowermost region are respectively set as second header portions 53. That is, in the present embodiment, the header body 51 is partitioned by the two main partition plates 58, so that the folded header 50 has one first header portion 52 and two second headers each having a space therein. A portion 53 is formed. In other words, the first header section 52 and the two second header sections 53 constitute the folded-back header 50.

  The first heat transfer tubes 21 are connected to the first header portion 52 so as to communicate with the inside of the first header portion 52, respectively. The plurality of first heat transfer tubes 21 constitute a first tube group 22. In other words, the heat transfer tube 20 connected to the first header portion 52 is the first heat transfer tube 21.

The second heat transfer tubes 23 are connected to the second header portions 53 so as to be in communication with the respective second header portions 53. That is, the heat transfer tube 20 connected to the second header portion 53 is the second heat transfer tube 23.
In the second heat transfer tube 23, the second tube group 24 is configured by a plurality of second heat transfer tubes 23 connected to the respective second header portions 53. That is, in this embodiment, since the two second header portions 53 are provided, the two second pipe groups 24 are configured so as to be paired with the two second header portions 53.

In the present embodiment, of the two upper and lower second header portions 53, the second header portion 53 disposed below is hereinafter referred to as a lower second header portion 54, and the second header portion disposed above. 53 is referred to as an upper second header portion 55.
Further, the second tube group 24 composed of the second heat transfer tube 23 connected to the lower second header portion 54 is referred to as a lower second tube group 25 and is connected to the upper second header portion 55. The second tube group 24 composed of the heat transfer tubes 23 is referred to as an upper second tube group 26.

  The first connection pipe 60 is a tubular member having a flow path formed therein, and one end of the first connection pipe 60 is connected to the first header part 52 in communication with the inside of the first header part 52. The other end is connected to the lower second header portion 54 in communication with the inside of the lower second header portion 54. More specifically, one end of the first connection pipe 60 is connected to the upper portion of the first header portion 52. The other end of the first connection pipe 60 is connected to the lower part of the lower second header portion 54. In the present embodiment, the flow path in the first connection pipe 60 is a first series passage 61 (communication passage) that connects the first header portion 52 and the lower second header portion 54.

  The second connection pipe 70 is a tubular member having a flow path formed therein, and, like the first connection pipe 60, one end communicates with the inside of the first header section 52 with respect to the first header section 52. Connected in a state. On the other hand, unlike the first connection pipe 60, the other end of the second connection pipe 70 is connected to the upper second header part 55 in communication with the inside of the upper second header part 55. More specifically, one end of the second connection pipe 70 is connected to the upper portion of the first header portion 52. The other end of the first connection pipe 60 is connected to the lower part of the upper second header portion 55. In the present embodiment, the flow path in the second connection pipe 70 is a second communication path 71 (communication path) that connects the first header portion 52 and the upper second header portion 55.

Here, in this embodiment, the connection location to the 1st header part 52 of the 1st connection pipe 60 and the 2nd connection pipe 70 is made into the mutually same up-down direction position. That is, the connection location of the first connection pipe 60 to the first header portion 52 is arranged adjacent to or spaced apart from the connection location of the second connection pipe 70 to the first header portion 52 in the horizontal direction. The positions are the same.
Note that “the same position in the vertical direction” is not limited to the case where the vertical position of the center of the connection portion of the first connection pipe 60 and the second connection pipe 70 to the first header portion 52 is the same, at least, It suffices that the vertical positions of at least some of the connecting portions of the first connection pipe 60 and the second connection pipe 70 to the first header portion 52 overlap each other in the vertical direction.

Next, operations and effects when the heat exchanger 10 is used as an evaporator will be described.
When the heat exchanger 10 is the indoor heat exchanger 3, it is used as an evaporator during the cooling operation of the air conditioner 1, and when the outdoor heat exchanger 5 is used, it evaporates during the heating operation of the air conditioner 1. It will be used as a container.

  When the heat exchanger 10 is used as an evaporator, a gas-liquid two-phase refrigerant with a large liquid phase is supplied from the pipe 7 to the lower inlet / outlet region 42 of the inlet / outlet header 40 shown in FIG. This refrigerant is distributed and supplied into the plurality of first heat transfer tubes 21 in the lower entrance / exit region 42, and exchanges heat with the external atmosphere of the first heat transfer tubes 21 in the process of flowing through the first heat transfer tubes 21. Evaporation is encouraged. Accordingly, the refrigerant supplied from the first heat transfer tube 21 into the first header portion 52 of the folded-back header 50 is a gas-liquid two-phase in which the liquid phase ratio is reduced due to a partial change from the liquid phase to the gas phase. Becomes a refrigerant.

  Among the gas-liquid two-phase refrigerant supplied into the first header portion 52, a refrigerant having a high liquid phase content and a high density gathers under the first header portion 52 due to gravity, and a refrigerant having a high gas phase content and a low density. It will gather at the top of the first header portion 52. That is, in the first header portion 52, the gas-liquid ratio of the refrigerant, that is, the density varies depending on the vertical position. Here, if the connection positions of the first connection pipe 60 and the second connection pipe 70 to the first header portion 52 are different from each other in the vertical direction, the first connection pipe 60 and the second connection pipe 70 are introduced. The gas-liquid ratio of the refrigerant will be different. As a result, a refrigerant having a high density is introduced into one of the first connecting pipe 60 and the second connecting pipe 70 that is connected to the lower side of the first header portion 52. As a result, the mass flow rate of the refrigerant is large. Become. On the other hand, a refrigerant having a lower density is introduced into the more connected one, resulting in a smaller mass flow rate of the refrigerant.

  On the other hand, in this embodiment, the connection position to the 1st header part 52 of the 1st connection pipe 60 and the 2nd connection pipe 70 is made into the mutually same up-down direction position. Therefore, substantially the same gas-liquid ratio refrigerant is introduced into the first connection pipe 60 and the second connection pipe 70, respectively. As a result, the gas-liquid ratio of the refrigerant introduced into the lower second header portion 54 and the upper second header portion 55 via the first connection pipe 60 and the second connection pipe 70 is substantially the same. That is, the mass flow rate of the refrigerant flowing through the first connection pipe 60 and the second connection pipe 70 is equalized.

  Thereafter, the refrigerant introduced into the lower second header part 54 and the upper second header part 55 via the first connection pipe 60 or the second connection pipe 70 is supplied to the plurality of second heat transfer pipes 23 connected thereto. The flow is divided and flows through the second heat transfer tubes 23. Then, the refrigerant is urged to evaporate again by exchanging heat with the external atmosphere of the second heat transfer tube 23 in the process of flowing through the second heat transfer tube 23. As a result, the liquid phase remaining in the refrigerant changes into a gas phase in the second heat transfer tube 23, and the gas phase refrigerant is supplied to the upper entrance / exit region 43 of the inlet / outlet header 40. Then, the refrigerant is introduced into the pipe 7 from the upper entrance / exit area 43 and circulates in the refrigerant circuit.

  As described above, in the heat exchanger 10 of the present invention, the first series passage 61 of the first connection pipe 60 and the second communication path 71 of the second connection pipe 70 respectively connected to the plurality of second header portions 53 are provided. Since the first header portion 52 is connected to the same vertical position, the refrigerant having substantially the same vapor phase liquid phase ratio is introduced into each communication path. Therefore, equalization of the refrigerant flow rate for each of the plurality of communication paths can be achieved. As a result, for example, when the heat exchanger 10 is used in an air conditioner, the cooling performance and the heating performance are not impaired.

Next, the heat exchanger 80 which concerns on 2nd embodiment of this invention is demonstrated with reference to FIG.4 and FIG.5. In the second embodiment, the same components as those in the first embodiment are denoted by the same reference numerals as those in the first embodiment, and detailed description thereof is omitted.
As shown in FIG. 4, the heat exchanger 80 of the second embodiment is provided with one branch connection pipe 81 instead of the first connection pipe 60 and the second connection pipe 70 of the first embodiment. It is different from the first embodiment.

The branch connection pipe 81 has a main pipe part 82 and a plurality of (two in this embodiment) branch pipe parts 85.
One end of the main pipe part 82 is connected to the first header part 52. In the first header portion 52, as shown in FIGS. 5A and 5B, the first header portion 52 is formed so as to be divided into two regions in the horizontal direction. Two divided flow paths 83 are formed. The divided flow paths 83 extend in parallel in the horizontal direction from one end to the other end in the main pipe portion 82. As shown in FIG. 5A, the main pipe part 82 has a structure in which two divided flow paths 83 are formed by providing a divided wall part 84 at the center in the horizontal direction of the flow path having a circular cross section. Also good. Further, as shown in FIG. 5B, the divided flow passages 83 in which a part of the flow passage having a circular cross section is cut out linearly are arranged in parallel with each other by the divided wall portions 84 constituting the linear portion. The structure provided so that it may be sufficient.

  Two branch pipe portions 85 are provided so as to branch into a plurality from the other end side of the main pipe portion 82. The branch pipe portions 85 are connected to the lower second header portion 54 and the upper second header portion 55, respectively. Moreover, the branch flow path 86 which is a flow path inside each branch pipe section 85 communicates with the divided flow path 83 in the main pipe section 82 in a one-to-one relationship. As a result, of the two divided flow paths 83 of the main pipe portion 82, one divided flow path 83 is in communication with the inside of the lower second header portion 54 via one branch flow path 86. One divided channel 83 and one branch channel 86 form a first series passage 61 that allows the first header portion 52 and the lower second header portion 54 to communicate with each other. In addition, the other divided flow path 83 is in communication with the inside of the upper second header portion 55 via the other branch flow path 86, that is, by the other divided flow path 83 and the other branch flow path 86. A second communication passage 71 is formed to communicate the inside of the first header portion 52 and the upper second header portion 55.

  In such a heat exchanger 80 of the second embodiment, the two divided flow paths 83 in the main pipe portion 82 of the branch connection pipe 81 are arranged in parallel in the horizontal direction. Are introduced with refrigerant of almost the same density. The refrigerant is introduced into the lower second header portion 54 and the upper second header portion 55 via the branch flow path 86. Therefore, the mass flow rate of the refrigerant introduced into the lower second header portion 54 and the upper second header portion 55 can be equalized as in the first embodiment.

  Moreover, since the connection place to the 1st header part 52 becomes only one place compared with the case where the 1st connection pipe 60 and the 2nd connection pipe 70 are provided separately like 1st embodiment, construction is carried out. It can be made easier.

Next, the heat exchanger 90 which concerns on 3rd embodiment of this invention is demonstrated with reference to FIG.6 and FIG.7. In the third embodiment, components similar to those in the first embodiment are denoted by the same reference numerals as those in the first embodiment, and detailed description thereof is omitted.
As shown in FIGS. 6 and 7, the heat exchanger 90 of the third embodiment includes the number of the second heat transfer tubes 23 in the lower second tube group 25 and the number of the second heat transfer tubes 23 in the upper second tube group 26. The first embodiment is different from the first embodiment in that the numbers are different from each other and the cross-sectional areas of the first connection pipe 60 and the second connection pipe 70 are different from each other.

  The heat exchanger 90 of the present embodiment is provided with a larger number of second heat transfer tubes 23 in the upper second tube group 26 than the number of second heat transfer tubes 23 in the lower second tube group 25. In addition, since the space | interval of the up-down direction of each 2nd heat exchanger tube 23 is the same, the difference in the number of the 2nd heat exchanger tubes 23 of the lower side 2nd pipe group 25 and the 2nd heat exchanger tubes 23 of the upper side 2nd pipe group 26 is. Accordingly, the upper second header portion 55 has a larger vertical dimension than the lower second header portion 54.

  Furthermore, the flow passage cross-sectional area of the second connection pipe 70 is set larger than the flow passage cross-sectional area of the first connection pipe 60 over the entire extending direction of the first connection pipe 60 and the second connection pipe 70. . The channel cross-sectional area is the area of the channel in the cross section orthogonal to the extending direction of each of the first connecting pipe 60 and the second connecting pipe 70.

  Thus, in this embodiment, the flow path of the 1st connection pipe 60 connected to the lower side 2nd header part 54 corresponding to the lower side 2nd pipe group 25 with relatively few 2nd heat exchanger tubes 23. The cross-sectional area is set relatively small. The flow passage cross-sectional area of the second connection pipe 70 connected to the upper second header portion 55 corresponding to the upper second pipe group 26 having a relatively large number of second heat transfer pipes 23 is set to be relatively large. ing.

  According to the heat exchanger 90 of the third embodiment, a larger amount of refrigerant is introduced into the upper second header portion 55 having a relatively large number of second heat transfer tubes 23 connected thereto. On the other hand, a smaller amount of refrigerant is introduced into the lower second header portion 54 where the number of second heat transfer tubes 23 to be connected is relatively small. The larger the number of connected second heat transfer tubes 23, the more refrigerant can be circulated in the second heat transfer tube 23 and the heat exchange can be promoted, so the mass of the refrigerant that circulates as a whole of the second heat transfer tube 23. The flow rate can be equalized.

Next, the heat exchanger 100 which concerns on 4th embodiment of this invention is demonstrated with reference to FIGS. In the third embodiment, components similar to those in the first embodiment are denoted by the same reference numerals as those in the first embodiment, and detailed description thereof is omitted.
As shown in FIGS. 8 and 9, the heat exchanger 100 according to the fourth embodiment is configured so that the second heat transfer pipe 23 of the lower second pipe group 25 receives the speed of air blow and the second heat transfer of the upper second pipe group 26. It differs from the first embodiment in that the speed of the air blow received by the heat pipe 23 is different and the cross-sectional areas of the first connection pipe 60 and the second connection pipe 70 are different from each other.

In the present embodiment, the speed of the air received by the upper second pipe group 26 is greater than the speed of the air received by the lower second pipe group 25. The difference in the speed of the ventilation which receives is produced by the ventilation part 103 as shown in FIG. 10, for example.
That is, as shown in FIG. 10, the heat exchanger 100 of the present embodiment has a casing 101 that houses the heat exchanger 100.

  The casing 101 includes a casing main body 102, a ventilation part 104, and the air blowing part 103. The casing main body 102 is a substantially rectangular parallelepiped box extending in the vertical direction. For example, the casing main body 102 has a ventilation portion 104 through which air can flow inside and outside the casing main body 102 on two side surfaces adjacent to each other among four side surfaces. Yes. In addition, the top surface of the casing main body 102 is provided with a blower unit 103 including a fan that can rotate around a vertical axis. When the fan of the ventilation section 104 is operated, the air in the casing body 102 is sent to the outside of the casing 101, that is, from below to above. Accordingly, air is sent into the casing body 102 from the outside of the casing body 102 through the ventilation portion 104. Thus, if the ventilation part 104 is operated so that air may be discharged from the upper part of the casing 101, the heat exchanger 100 arrange | positioned in the casing main body 102 will receive ventilation with a different wind speed in the up-down direction. Thereby, in this embodiment, the speed of the ventilation which the upper side 2nd pipe group 26 receives becomes larger than the speed of the ventilation which the lower side 2nd pipe group 25 receives.

  In this embodiment, as in the third embodiment, the flow passage cross-sectional area of the second connection pipe 70 is greater than the flow passage cross-sectional area of the first connection pipe 60. Is set to be large over the entire extending direction.

  Thus, in this embodiment, the flow path cross-sectional area of the 1st connection pipe 60 connected to the lower side 2nd header part 54 corresponding to the lower side 2nd pipe group 25 with the small speed of the ventilation received is relatively It is set small. Moreover, the flow path cross-sectional area of the second connection pipe 70 connected to the upper second header portion 55 corresponding to the upper second pipe group 26 having a relatively large number of second heat transfer pipes 23 that receive a large speed of blowing air is: It is set relatively large.

  In such a heat exchanger 100, the higher the speed of the air received by the second tube group 24, the more the heat exchange in the second tube group 24 is promoted. Therefore, the heat exchange efficiency of the heat exchanger 100 as a whole can be improved by introducing more refrigerant into the second header portion 53 connected to the upper second pipe group 26 that receives a large speed of blowing.

Next, a heat exchanger 110 according to a fifth embodiment of the present invention will be described with reference to FIGS. In the fifth embodiment, the same components as those in the first embodiment are denoted by the same reference numerals as those in the first embodiment, and detailed description thereof is omitted.
As shown in FIGS. 11 and 12, the heat exchanger 110 according to the present embodiment is provided with three partition plates 58 in the folded header 50. That is, these partition plates 58 are installed at intervals in the vertical direction, thereby dividing the partition plate 58 into four areas in the vertical direction in the area within the header 30. The portion including the lowermost region of the four regions is the first header portion 52 as in the first embodiment. In addition, the portions including the upper three regions excluding the lowermost region among the four regions are set as second header portions 53, respectively. In the present embodiment, one first header portion 52 and three second header portions 53 are provided.

Furthermore, in this embodiment, the connecting pipe 120 that connects the first header portion 52 and the lowermost second header portion 53 of the three second header portions 53, the first header portion 52 and the three second headers. The connecting pipe 120 that connects the second header section 53 at the center of the sections 53, and the connecting pipe 120 that connects the uppermost second header section 53 of the first header section 52 and the three second header sections 53. A total of three connecting pipes 120 are provided. In each connecting pipe 120, a communication path 121 that connects the first header portion 52 and any one of the second header portions 53 is formed.
Moreover, the connection location with the 1st header part 52 in each connection pipe 120 is made into the mutually same up-down direction position similarly to 1st embodiment.

In such a heat exchanger 110 as well, as in the first embodiment, it is possible to equalize the mass flow rate of the refrigerant introduced from the first header portion 52 to each second header portion 53.
In the present embodiment, an example in which three second header portions 53 are provided has been described, but there may be four or more second header portions 53. In that case, the number of connecting pipes 120 increases in accordance with the number of second header portions 53.

Next, a heat exchanger 130 according to a sixth embodiment of the present invention will be described with reference to FIG. In the sixth embodiment, components similar to those in the first embodiment are denoted by the same reference numerals as those in the first embodiment, and detailed description thereof is omitted.
The sixth embodiment is different from the first embodiment in that a plurality of first connecting pipes 60 and a plurality of second connecting pipes 70 are provided.

  That is, in the sixth embodiment, a plurality (three in this embodiment) of the first connection pipes 60 are provided. In each first connection pipe 60, the connection location with the first header portion 52 is the same vertical position, while the connection location to the lower second header portion 54 is a different vertical position. ing. In the present embodiment, the first first connecting pipe 60 among the three first connecting pipes 60 is connected to the lower part of the lower second header portion 54, and the second second connecting pipe 70 is connected to the lower second connecting pipe 70. The third first connection pipe 60 is connected to the upper part of the lower second header part 54 and is connected to the central part of the second side header part 54.

  In the sixth embodiment, a plurality (three in this embodiment) of second connection pipes 70 are also provided. The connection locations with the first header portion 52 in each second connection pipe 70 are the same vertical position, whereas the connection locations with the upper second header portion 55 are different positions in the vertical direction. Yes. In the present embodiment, the first first connecting pipe 60 among the three first connecting pipes 60 is connected to the lower part of the upper second header portion 55, and the second second connecting pipe 70 is connected to the upper first The third first connection pipe 60 is connected to the upper part of the upper second header part 55.

According to such a heat exchanger 130, the mass flow rate of the refrigerant introduced into the lower second header portion 54 and the upper second header portion 55 can be equalized as in the first embodiment.
Further, particularly in the present embodiment, the refrigerant is introduced into the first header portion 52 and the second header portion 53 from a plurality of locations having different height positions. Therefore, the refrigerant is mixed in the first header part 52 and the second header part 53 in the vertical direction, thereby promoting the uniformization of the refrigerant in the first header part 52 and the second header part 53. Can do. Thereby, equalization of the mass flow rate of the refrigerant introduced into each second heat transfer tube 23 can be achieved.

  The embodiment of the present invention has been described above, but the present invention is not limited to this, and can be appropriately changed without departing from the technical idea of the present invention.

For example, the branch connection pipe 81 of the second embodiment may be applied to the third to fifth embodiments.
Further, the third embodiment and the fourth embodiment are combined with each other, and according to the number of the second heat transfer tubes 23 constituting the second tube group 24 and the air volume of the air received by each second heat transfer tube 23, the first The cross-sectional areas of the connecting pipe 60 and the second connecting pipe 70 may be adjusted.

DESCRIPTION OF SYMBOLS 1 Air conditioner 2 Compressor 3 Indoor heat exchanger 4 Expansion valve 5 Outdoor heat exchanger 6 Four-way valve 7 Pipe 10 Heat exchanger 20 Heat transfer tube 21 First heat transfer tube 22 First tube group 23 Second heat transfer tube 24 Second Pipe group 25 Lower second pipe group 26 Upper second pipe group 28 Fin 30 Header 40 Entrance / exit side header 41 Partition plate 42 Lower entrance / exit area 43 Upper entrance / exit area 50 Return side header 51 Header body 52 First header part 53 Second header Part 54 lower second header part 55 upper second header part 58 main partition plate 60 first connection pipe 61 first series passage 70 second connection pipe 71 second communication path 80 heat exchanger 81 branch connection pipe 82 main pipe part 83 Divided flow channel 84 Divided wall portion 85 Branch pipe portion 86 Branch flow channel 90 Heat exchanger 100 Heat exchanger 101 Casing 102 Casing body 103 Blower portion 104 Ventilation portion 110 Heat exchanger 120 Connecting pipe 121 Road 130 heat exchanger

Claims (7)

A first tube group having a first heat transfer tube extending in the horizontal direction and having a plurality of refrigerants arranged in the vertical direction with the refrigerant flowing therethrough;
A first header portion that is connected in a communicating state with one end of each of the first heat transfer tubes of the first tube group in a vertically extending cylindrical shape;
A plurality of second tube groups having a second heat transfer tube that extends in the horizontal direction and in which the refrigerant circulates and is arranged at intervals in the vertical direction,
A plurality of second tube groups are provided corresponding to the plurality of second tube groups, and each of the second heat transfer tubes of the second tube group is connected in a communicating state to each other in a cylindrical shape extending in the vertical direction. A header section;
A plurality of second header portions are provided corresponding to the plurality of second header portions, and one end of each of the first header portions is the same as that of the first header portion so that the first header portions and the second header portions communicate with each other. A communication path connected to the directional position and each other end connected to one of the second header parts;
A heat exchanger. One end is connected to the first header portion, and a plurality of divided flow paths arranged in parallel in the horizontal direction are formed on the inner side, and a plurality of branched from the other end side of the main pipe portion to the inner side A branch connection pipe having a branch pipe connected to any one of the second header parts and having a branch flow path communicating with the split flow path;
2. The heat exchanger according to claim 1, wherein each of the communication paths is a flow path formed by each of the divided flow paths and each of the branch flow paths. The number of the second heat transfer tubes in each of the second tube groups is different from each other,
The flow path cross-sectional area of the said communicating path is large as the said communicating path connected to the said 2nd header part to which the said 2nd pipe group with many said 2nd heat exchanger tubes was connected. Heat exchanger. A blower for blowing air to each of the second tube groups,
The speed of the air received by each of the second tube groups by the air blowing unit is different from each other for each of the second tube groups,
4. The flow path cross-sectional area of the communication path is larger as the communication path is connected to the second header portion to which the second pipe group is connected. The heat exchanger as described in.   One end is at the same height position as the communication path connected to the first header part so that the first header part communicates with any of the plurality of second header parts. The other end of the communication passage further connected to the second header portion at a height position different from that of the communication passage connected to the second header portion. The heat exchanger as described in any one. A header having a cylindrical main body extending in the vertical direction, and a plurality of main partition plates that vertically divide the header main body into a plurality of regions,
The first header portion is a portion including a lowermost region among the plurality of regions in the header,
6. The heat exchanger according to claim 1, wherein each of the second header portions is a portion including any region other than a lowermost region among the plurality of regions in the header.   An air conditioner comprising the heat exchanger according to any one of claims 1 to 6.

Images