JP2018096559A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger capable of improving heat exchange performance by equalizing an amount of refrigerant flowing into each of flat tubes.SOLUTION: A heat exchanger 1 includes a plurality of flat tubes 2 in which a refrigerant is circulated, fins 3 respectively disposed between adjacent flat tubes 2 and joined to each flat tube 2, a folded header tube 4 to which one end of each downstream-side flat tube 8 is connected to introduce the refrigerant to each downstream-side flat tube 8, and an inlet/outlet header tube 5 to which the other end of each downstream-side flat tube 8 is connected to discharge the refrigerant from each downstream-side flat tube 8. The folded header tube 4 has a turn tube supply portion 27 for supplying the refrigerant to the folded header tube 4. The plurality of flat tubes 2 have opposed flat tubes 9 opposed to the turn tube supply portion 27. The outlet/inlet header tube 5 has a partitioning plate 16 having a communication hole 17.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a heat exchanger that performs heat exchange between a refrigerant flowing in a flat tube and air.

  As a heat exchanger used for an air conditioner or the like, there is a multiflow heat exchanger in which a plurality of flat tubes and fins through which a refrigerant flows are alternately stacked. Such a multi-flow heat exchanger has a pair of header tubes arranged so as to face each other, and each flat tube is connected so as to connect the pair of header tubes. The refrigerant flowing in each flat tube is distributed inside at least one of the pair of header tubes.

  An inlet pipe for supplying refrigerant to the distribution header pipe is connected to a header pipe (hereinafter referred to as “distribution header pipe”) on the side of distributing the refrigerant. The refrigerant that has flowed into the distribution header pipe from the inflow pipe easily flows into the flat pipe disposed at a position facing the inflow pipe with a small flow path loss (bending loss and friction loss), and into the other flat pipe. Therefore, the refrigerant flow rate in each flat tube is biased. In a state where such a bias has occurred, the heat transfer area of the heat exchanger cannot be fully utilized, and the heat exchange performance decreases. When the heat exchange performance of the heat exchanger is lowered, the cooling capacity and the heating capacity are lowered, and the indoor comfort is impaired.

  For example, Patent Document 1 discloses an attempt to solve such a problem. In Patent Document 1, the interval between two flat tubes adjacent to a portion facing the connecting pipe is made wider than the interval between the other flat tubes so that the connecting pipe and the flat tube do not face each other. An exchanger is described. In this heat exchanger, the height of the fins arranged between the flat tubes arranged widely is higher than that of the fins arranged between the remaining flat tubes.

Japanese Patent No. 5716496

  However, in the configuration disclosed in Patent Document 1, adjustment of the flow path loss of the refrigerant flowing in from the connection pipe is insufficient, and the refrigerant flows into the flat tube disposed at the position closest to the connection pipe. It is easy, and there is a possibility that the difference in inflow amount between this flat tube and other flat tubes cannot be sufficiently reduced. Moreover, since the height of the fin arrange | positioned between the flat pipes arrange | positioned widely is higher than the fin arrange | positioned between the remaining flat pipes, two types of fins from which height differs are attached. Therefore, there is a possibility that the number of parts increases and the assembly process becomes complicated.

  This invention is made | formed in view of such a situation, Comprising: It aims at providing the heat exchanger which can equalize the refrigerant | coolant amount which flows in into each flat tube, and can improve heat exchange performance. .

In order to solve the above problems, the heat exchanger of the present invention employs the following means.
That is, the heat exchanger according to one aspect of the present invention includes a plurality of flat tubes that extend in a predetermined direction and are arranged substantially in parallel at intervals and through which the refrigerant flows, and the adjacent flat tubes. Fins disposed between the tubes and joined to the flat tubes and extending in a direction perpendicular to the flat tubes, one ends of the flat tubes are connected, and the refrigerant is introduced into the flat tubes A first header pipe and a second header pipe extending in a direction orthogonal to the flat pipe, connected to the other end of each flat pipe, and discharging the refrigerant from the flat pipe, The first header pipe has a supply part that supplies the refrigerant to the first header pipe, the plurality of flat pipes have opposed flat pipes that face the supply part, and the second header pipe has A pressure loss increasing means for increasing the pressure loss of the refrigerant flowing inside the opposed flat tube is provided. It has been.

  Since the flat tube arranged so as to face the supply unit has a small bending loss and friction loss of the refrigerant, the refrigerant easily flows in, and the amount of the refrigerant flowing in is larger than that of the other flat tubes. In the above configuration, the pressure loss increasing means is provided in the second header pipe to increase the pressure loss of the refrigerant flowing through the opposed flat tube arranged at a position where the refrigerant easily flows. As a result, the amount of refrigerant flowing into the opposing flat tubes is reduced, and the amount of refrigerant flowing into the other flat tubes is increased by the amount of refrigerant flowing into the opposing flat tubes. Therefore, the difference between the amount of refrigerant flowing into the opposing flat tubes and the amount of refrigerant flowing into other flat tubes can be reduced, and the amount of refrigerant flowing into each flat tube can be equalized. By equalizing the amount of refrigerant flowing in, the heat exchange performance of the heat exchanger can be improved.

  Further, for example, when the pressure loss increasing means is provided in the first header pipe that introduces the refrigerant into the plurality of flat tubes, the member constituting the pressure loss increasing means disturbs the flow of the refrigerant in the first header pipe. , It becomes difficult for the refrigerant to uniformly flow into each flat tube. In the above configuration, since the pressure loss increasing means is provided in the second header pipe, the refrigerant flow is not disturbed due to the pressure loss increasing means in the first header pipe. Therefore, compared with the case where the pressure loss increasing means is provided in the first header pipe, the refrigerant can easily flow into each flat pipe evenly.

  Moreover, in the said structure, the difference of the refrigerant | coolant amount which distribute | circulates the inside of each flat tube can be reduced, without affecting the arrangement | positioning of several flat tubes. Thereby, since all the several flat tubes can be installed at equal intervals, the height of all the fins can be made the same. Therefore, the number of parts can be reduced and the assembling process can be simplified as compared with the case where fins having a plurality of heights are used.

  Further, for example, the first header pipe is provided with a partition that divides the plurality of flat tubes into the upstream side and the downstream side, and the second header pipe is also provided with a partition that divides the plurality of flat tubes into the upstream side and the downstream side. Furthermore, you may provide turn piping so that the partition provided in the 1st header pipe may be straddled. By adopting such a configuration, the length of the refrigerant flow path for heat exchange between the refrigerant and air is increased to improve heat exchange performance, and further, the amount of refrigerant flowing into each flat tube is equalized. Thus, the heat exchange performance of the heat exchanger can be improved.

  Moreover, the heat exchanger which concerns on 1 aspect of this invention WHEREIN: The said 2nd header pipe | tube has the discharge part which discharges | emits the said refrigerant | coolant from this 2nd header pipe | tube, and each said flat tube is a said 2nd header pipe | tube. The second header pipe is provided with a partition plate between the discharge port of the opposed flat tube and the discharge portion as the pressure loss increasing means. A communication hole may be formed in the partition plate, extending in a direction intersecting with a direction in which the refrigerant flows from the discharge port toward the discharge portion.

  In the above configuration, since the partition plate in which the communication hole is formed is provided between the discharge port and the discharge part of the opposed flat tube, the refrigerant discharged from the discharge port to the second header pipe has the communication hole. Passes through to the discharge section. Thereby, a pressure loss due to the communication hole is generated in the refrigerant from the discharge port to the discharge portion. Therefore, it is possible to increase the pressure loss of the refrigerant flowing through the opposed flat tube and reduce the flow rate of the refrigerant flowing into the opposed flat tube.

  Moreover, the pressure loss which generate | occur | produces in an opposing flat tube changes with the opening area of a communicating hole. Therefore, by adjusting the opening area of the communication hole, it is possible to generate a desired pressure loss with respect to the refrigerant flowing through the opposed flat tube, and to set the flow rate of the refrigerant flowing into the opposed flat tube to a desired flow rate.

  Moreover, it is good also as a structure which provides multiple communicating holes. By providing a plurality, the opening area can be adjusted more finely, and a desired pressure loss can be generated with respect to the refrigerant flowing through the opposed flat tube more suitably. Further, the opening area of the communication hole may be equal to or less than half the cross-sectional area of the second header pipe. By setting it as such a structure, the pressure loss of the refrigerant | coolant which distribute | circulates the inside of an opposing flat tube can be increased more suitably.

  In the heat exchanger according to an aspect of the present invention, the opposite flat tube has the other end inserted into the second header tube, and the communication hole extends from the extending direction of the second header tube. You may arrange | position so that it may overlap with the said opposing flat tube when the flat surface of a pipe | tube is seen.

  The refrigerant discharged from the opposed flat tube to the second header tube flows toward the discharge portion. In the above configuration, since the communication hole is disposed so as to overlap the opposing flat tube when the flat surface of the second header tube is viewed, the refrigerant discharged from the opposing flat tube to the second header tube is once discharged in the discharge direction. While meandering in the opposite direction, it passes through the communication hole and faces the discharge part. Thereby, a pressure loss is more preferably generated in the refrigerant from the discharge port to the discharge portion. Therefore, it is possible to increase the pressure loss of the refrigerant flowing through the opposed flat tube and reduce the flow rate of the refrigerant flowing into the opposed flat tube.

  Further, the meandering amount of the discharged refrigerant changes depending on the position where the communication hole is provided. When the meandering amount of the discharged refrigerant changes, the pressure loss generated in the opposed flat tube also changes. Therefore, since the pressure loss generated in the refrigerant flowing through the opposed flat tube can be adjusted also by the position where the communication hole is provided, the flow rate of the refrigerant flowing into the opposed flat tube can be adjusted more finely.

  Moreover, the heat exchanger which concerns on 1 aspect of this invention WHEREIN: The said 2nd header pipe | tube has the discharge part which discharges | emits the said refrigerant | coolant from this 2nd header pipe | tube, and each said flat tube is a said 2nd header pipe | tube. The second header pipe may be provided with a collision plate as the pressure loss increasing means so as to face the discharge port of the opposed flat tube.

  In the above configuration, since the collision plate is provided so as to face the discharge port of the opposed flat tube, the refrigerant discharged from the discharge port into the second header tube collides with the collision plate, and pressure loss occurs. Therefore, it is possible to increase the pressure loss of the refrigerant flowing through the opposed flat tube and reduce the flow rate of the refrigerant flowing into the opposed flat tube.

  Moreover, the pressure loss at the time of the collision between the discharged refrigerant and the collision plate varies depending on the position where the collision plate is provided. Therefore, by adjusting the position where the collision plate is provided, a desired pressure loss can be generated for the refrigerant flowing through the opposed flat tube, and the flow rate of the refrigerant flowing into the opposed flat tube can be set to a desired flow rate.

  Moreover, in the said structure, the pressure loss of the refrigerant | coolant which distribute | circulates the inside of an opposing flat tube is increased because the discharged refrigerant and the collision plate collide. Therefore, in the pressure loss increasing means of the type passing through the communication hole described above, the inside of the opposed flat tube is not generated without generating abnormal noise such as whistling noise that may have occurred due to the relationship between the flow velocity of the refrigerant and the communication hole diameter. The pressure loss of the circulating refrigerant can be increased.

  Further, in the heat exchanger according to one aspect of the present invention, a flow path through which the refrigerant flows is formed in each flat tube, and the pressure loss increasing means is provided in the second header tube, A sealing member that seals a part of the channel area of the channel formed inside the opposed flat tube is provided.

  In the above configuration, the sealing member seals a part of the channel area of the channel formed in the opposed flat tube. Thereby, the pressure loss of the refrigerant | coolant which distribute | circulates the inside of an opposing flat tube can be increased, and the refrigerant | coolant flow rate which flows in into an opposing flat tube can be reduced.

  Moreover, the pressure loss of the refrigerant | coolant which distribute | circulates the inside of an opposing flat tube changes with the flow-path area which a sealing member seals. Therefore, the flow rate of the refrigerant flowing into the opposed flat tube can be set to a desired flow rate by adjusting the flow path area sealed by the sealing member.

  For example, when a plurality of channels are formed in the opposed flat tube, the sealing member may seal only a part of the plurality of channels. In such a case, since the refrigerant does not flow into the sealed flow path, more preferably, the flow area in the opposed flat tube is reduced and the pressure loss of the refrigerant flowing in the opposed flat tube is increased. be able to. Further, for example, when a heat exchanger is used as an evaporator, the flow path arranged at a position where frost formation is difficult causes the refrigerant to circulate, and the flow path arranged at a position where frost formation tends to occur circulates the refrigerant. The flow path through which the refrigerant circulates can be selected from the plurality of flow paths so as to suppress frost formation on the flat tube.

  Further, in the heat exchanger according to one aspect of the present invention, each flat tube has the one end inserted into the first header tube, and the insertion length of each flat tube inserted into the first header tube is It may be less than half the inner diameter of the first header tube.

  In the above configuration, since the insertion length of the flat tube inserted into the first header pipe is shortened, the flow of the refrigerant supplied from the supply unit into the first header pipe is flattened into the first header pipe. Hard to be disturbed by the tube. Thereby, the flow path loss which arises in a 1st header pipe | tube can be suppressed. Therefore, an equal amount of refrigerant easily flows into the plurality of flat tubes in the first header tube, and the amount of refrigerant flowing through each flat tube can be made uniform.

  According to the present invention, the amount of refrigerant flowing into each flat tube can be equalized and the heat exchange performance can be improved.

It is a front view of the heat exchanger which concerns on 1st Embodiment of this invention. (A) is a schematic top view of the partition plate of the heat exchanger shown in FIG. 1, (b) is a figure which shows the modification. It is a typical front view of the 1st header concerning the present invention. (A) is a figure which shows the modification of the partition plate shown in FIG. 2, (b) is a figure which shows the modification of FIG. 4 (a). It is the figure which showed typically the flow of the refrigerant | coolant at the time of providing the partition plate of Fig.4 (a). It is a front view of the heat exchanger which concerns on 2nd Embodiment of this invention. It is a front view of the heat exchanger which concerns on 3rd Embodiment of this invention. (A) is a principal part enlarged view of the heat exchanger shown in FIG. 7, (b) is a figure which shows the modification.

Embodiments according to the present invention will be described below with reference to the drawings.
[First Embodiment]
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. 1 to 3.
The heat exchanger 1 according to the present embodiment is used as an evaporator (not shown) of an air conditioner. The evaporator evaporates a gas-liquid two-phase or liquid single-phase refrigerant expanded in an expansion valve (not shown) in a refrigerant cycle of the air conditioner into a gas-phase refrigerant.

  As shown in FIG. 1, the heat exchanger 1 according to this embodiment is provided adjacent to a plurality of flat tubes 2 (9 in this embodiment) extending in the horizontal direction and adjacent flat tubes 2. Fins 3 that connect the flat tubes 2 to each other, an entrance / exit header tube 5 that is erected in the vertical direction and connected to one end of each flat tube 2, and the other end of each of the flat tubes 2 that is erected in the vertical direction The folded header pipe 4 and the turn pipe 6 provided outside the folded header pipe 4 are provided.

  Each flat tube 2 has a pair of upper and lower flat surfaces 2a and a pair of left and right curved surfaces 2b connecting the pair of upper and lower flat surfaces 2a, and has an oblong shape with a flat cross-sectional shape (FIG. 8 ( a) (b)). A plurality of flow paths 10 (six in this embodiment) having a rectangular cross-sectional shape are formed inside each flat tube 2. Each flow path 10 extends in the extending direction of the flat tube 2 and is arranged in a line in a direction orthogonal to the extending direction of the flat tube 2 (see FIGS. 8A and 8B).

  As shown in FIG. 1, the plurality of flat tubes 2 are arranged at substantially equal intervals so that the flat surfaces 2 a face each other. One end portion and the other end portion of each flat tube 2 are connected to be inserted into the entrance / exit header tube 5 and the folded header tube 4, respectively.

The plurality of flat tubes 2 are divided into an upstream flat tube 7 and a downstream flat tube 8.
The upstream flat tube 7 is a flat tube 2 positioned below a first partition wall 15 and a second partition wall 23 to be described later, and in the present embodiment, is located third from the bottom of the flat tube 2 positioned at the bottom. These are three flat tubes up to the flat tube 2. Each of the six flow paths 10 formed inside each of the upstream flat tubes 7 has an inlet 7 a that communicates with the inlet / outlet header tube 5 and an outlet 7 b that communicates with the folded header tube 4.

  The downstream flat tube 8 is a flat tube 2 located above a first partition wall 15 and a second partition wall 23 to be described later, and in the present embodiment, it is positioned sixth from the top of the flat tube 2 positioned at the top. There are six flat tubes up to the flat tube 2. Each of the six flow paths 10 formed inside each of the downstream flat tubes 8 has an inlet 8 a that communicates with the folded header tube 4 and a discharge port 8 b that communicates with the inlet / outlet header tube 5.

  The fin 3 is a plate-like member formed of metal, extends in the vertical direction, and has an upper end and a lower end fixed to the flat surface 2a of the flat tube 2 by brazing.

  The entrance / exit header pipe 5 has a supply pipe (supply part) 11 for supplying the refrigerant from the refrigerant cycle to the entrance / exit header pipe 5 and an exhaust pipe (discharge part) 12 for discharging the refrigerant from the entrance / exit header pipe 5 to the refrigerant cycle. , Formed into a cylindrical shape having a space inside. The supply pipe 11 communicates with the lower part of the entrance / exit header pipe 5, and the discharge pipe 12 communicates with the upper part of the entrance / exit header pipe 5. Inside the inlet / outlet header pipe 5, a first partition wall 15 is provided to separate an inlet space 13 that communicates with the supply pipe 11 and an outlet space 14 that communicates with the discharge pipe 12. The first partition wall 15 is a circular plate-like member having substantially the same cross-sectional shape in the longitudinal direction of the entrance / exit header tube 5, and an outer peripheral portion thereof is fixed to an inner peripheral portion of the entrance / exit header tube 5 by brazing.

  Further, in the outlet space 14, there is a space between the flat tube 2 (opposite flat tube 9 described later) disposed immediately above the first partition 15 and the flat tube 2 positioned one above the counter flat tube 9. In addition, a partition plate 16 is provided. The partition plate 16 is a circular plate member having substantially the same cross-sectional shape in the longitudinal direction of the entrance / exit header tube 5, and an outer peripheral portion thereof is fixed to an inner peripheral portion of the entrance / exit header tube 5 by brazing. A communication hole 17 is formed in the partition plate 16. As shown in FIG. 2A, the communication hole 17 is disposed at a position that does not overlap the flat tube 2 inserted into the entrance / exit header tube 5 when the entrance / exit header tube 5 is viewed in plan. The opening area of the communication hole 17 is formed to be less than half of the area of the longitudinal sectional shape of the entrance / exit header pipe 5. A plurality of communication holes may be formed as shown in FIG. The plurality of communication holes 18 are all arranged at positions that do not overlap the flat tube 2 inserted into the entrance / exit header tube 5 when the entrance / exit header tube 5 is viewed in plan. The total opening area of the plurality of communication holes 18 is less than half of the area of the longitudinal sectional shape of the entrance / exit header pipe 5.

The folded header pipe 4 is formed in a cylindrical shape having a space inside. Inside the folded header pipe 4, a second partition wall 23 is provided that separates a lower space 21 to which the upstream flat tube 7 is connected and an upper space 22 to which the downstream flat tube 8 is connected. The second partition wall 23 is a circular plate-like member having substantially the same cross-sectional shape in the longitudinal direction of the folded header tube 4, and the outer peripheral portion thereof is fixed to the inner peripheral portion of the folded header tube 4 by brazing. Further, as shown in FIG. 3, the insertion length of each flat tube 2 inserted into the folded header tube 4 is not more than half of the inner diameter of the sectional shape in the longitudinal direction of the folded header tube 4.
The turn pipe 6 has a turn pipe introduction port 26 that communicates with the lower space 21 and a turn pipe supply port 27 that communicates with the upper space 22, and is provided so as to straddle the second partition wall 23 outside the folded header pipe 4. Piping. The turn pipe supply port 27 communicates with the lower part of the upper space 22 and is disposed on the flat wall 2 (ie, the lowermost of the downstream flat pipes 8) immediately above the first partition wall 15 and the second partition wall 23. It opposes the opposing flat tube 9 which is the flat tube 2) located in this.

Next, the flow of the refrigerant in the heat exchanger 1 in the present embodiment will be described.
As indicated by the arrows in FIG. 1, the heat exchanger 1 is supplied with a refrigerant via a supply pipe 11. The refrigerant supplied from the supply pipe 11 first flows into the inlet space 13 in the inlet / outlet header pipe 5. The refrigerant that has flowed into the inlet space 13 passes through each upstream flat tube 7 (that is, passes through the six flow paths 10 in each upstream flat tube 7), and the lower space 21 in the folded header tube 4. Flow into. The refrigerant that has flowed into the lower space 21 then flows into the turn pipe 6. The refrigerant flowing through the turn pipe 6 from the turn pipe introduction port 26 is supplied to the upper space 22 from the turn pipe supply port 27. The refrigerant supplied to the upper space 22 is distributed to each downstream flat tube 8 in the upper space 22. The distributed refrigerant passes through the downstream flat tubes 8 as they are (that is, passes through the six flow paths 10 in the downstream flat tubes 8), and is discharged into the outlet space 14. The refrigerant discharged to the outlet space 14 is directed to the discharge pipe 12 and discharged from the discharge pipe 12 to the outside of the heat exchanger 1. At this time, among the downstream flat tubes 8, the refrigerant that has passed through the opposed flat tubes 9 (that is, passed through the six flow paths 10 in the opposed flat tubes 9) and discharged into the outlet space 14 is partitioned. It passes through the communication hole 17 provided in the plate 16 and faces the discharge pipe 12.
The case where the heat exchanger 1 is used as an evaporator has been described above. However, when the heat exchanger 1 is used as a condenser, the flow is opposite to the flow described above.

According to this embodiment, there exist the following effects.
Since the partition plate 16 in which the communication hole 17 is formed is provided between the discharge port 9b of the opposed flat tube 9 and the discharge tube 12, the refrigerant discharged from the discharge port 9b to the inlet / outlet header tube 5 is communicated. It flows through the hole 17 to the discharge pipe 12. Thereby, a pressure loss due to the communication hole 17 occurs in the refrigerant from the discharge port 9b to the discharge pipe 12. Therefore, the pressure loss of the refrigerant flowing through the opposed flat tube 9 can be increased, and the flow rate of the refrigerant flowing into the opposed flat tube 9 in the folded header pipe 4 can be reduced. The amount of refrigerant flowing into the other downstream flat tube 8 increases as the amount of refrigerant flowing into the opposed flat tube 9 decreases. Therefore, the difference between the amount of refrigerant flowing into the opposed flat tube 9 and the amount of refrigerant flowing into the other downstream flat tubes 8 can be reduced, and the amount of refrigerant flowing into each downstream flat tube 8 can be equalized. . By equalizing the amount of refrigerant flowing in, the heat exchange performance of the heat exchanger 1 can be improved.

  Further, the pressure loss generated in the opposed flat tube 9 varies depending on the opening area of the communication hole 17. Therefore, by adjusting the opening area of the communication hole 17, a desired pressure loss is generated for the refrigerant flowing in the opposed flat tube 9, and the flow rate of the refrigerant flowing into the opposed flat tube 9 is set to a desired flow rate. be able to. Specifically, by forming the opening area of the communication hole 17 large, the pressure loss of the refrigerant flowing through the opposed flat tube 9 is reduced, and the flow rate of the refrigerant flowing into the opposed flat tube 9 is set to be relatively large. By forming the opening area of the communication hole 17 small, the pressure loss of the refrigerant flowing through the opposed flat tube 9 increases, and the flow rate of the refrigerant flowing into the opposed flat tube 9 is set to be relatively small. Can do. In addition, as shown in FIG. 2 (b), when a plurality of communication holes 18 are provided, the opening area can be adjusted more finely, and it is more desirable for the refrigerant circulating in the opposed flat tube 9 to be more desirable. The pressure loss can be generated.

  Moreover, in this embodiment, since the opening area of the communicating hole 17 is formed to be half or less of the area of the longitudinal sectional shape of the entrance / exit header pipe 5, the pressure loss of the refrigerant that preferably circulates in the opposed flat pipe 9 Can be increased.

  Further, for example, when the communication hole 17 is provided in the upper space 22 of the folded header pipe 4, the flow of the refrigerant in the folded header pipe 4 is disturbed by the partition plate 16 in which the communication hole 17 is formed, and each downstream flat tube There is a possibility that the refrigerant is difficult to uniformly flow into 8. In the present embodiment, since the partition plate 16 in which the communication hole 17 is formed is provided in the outlet space 14 of the inlet / outlet header pipe 5, the refrigerant flow is not disturbed due to the partition plate 16 in the upper space 22. Therefore, compared with the case where the partition plate 16 in which the communication hole 17 is formed is provided in the upper space 22, the refrigerant can easily flow into each downstream flat tube 8.

  Moreover, in this embodiment, since all the several flat tubes 2 are installed at equal intervals, the height of all the fins 3 can be made the same. Therefore, the number of parts can be reduced and the assembling process can be simplified as compared with the case where fins having a plurality of heights are used.

  In the present embodiment, the plurality of flat tubes 2 are divided into the upstream flat tube 7 and the downstream flat tube 8, and the upstream flat tube 7 and the downstream flat tube 8 are connected by the turn pipe 6. Further, the heat exchange performance of the heat exchanger 1 is improved by increasing the length of the refrigerant flow path for heat exchange between the refrigerant and air to improve the heat exchange performance, and further equalizing the amount of refrigerant flowing into each flat tube 2. Can be improved.

  In the above configuration, the insertion length of the downstream flat tube 8 inserted into the folded header tube 4 is less than half the inner diameter of the sectional shape in the longitudinal direction of the folded header tube 4. The flow of the refrigerant supplied from the opening 27 into the folded header pipe 4 is hardly disturbed by the downstream flat tube 8 inserted into the folded header pipe 4. Thereby, the flow path loss which arises in the return header pipe | tube 4 can be suppressed. Accordingly, an equal amount of refrigerant easily flows into the plurality of downstream flat tubes 8 in the folded header tube 4, and the amount of refrigerant flowing in the downstream flat tubes 8 can be made uniform.

Next, a modification of the partition plate 16 in the present embodiment will be described with reference to FIGS.
The partition plate 28 according to this modification is different from the partition plate 16 according to the first embodiment in the formation positions of the communication holes. Other configurations are denoted by the same reference numerals as those of the heat exchanger 1 according to the first embodiment, and description thereof is omitted.

  As shown in FIG. 4A, the communication hole 29 according to this modification is formed so as to overlap with the flat tube 2 inserted into the entrance / exit header tube 5 when the entrance / exit header tube 5 is viewed in plan. Has been. In this way, by forming the communication hole 29, as indicated by the arrow in FIG. 5, the refrigerant discharged from the opposed flat tube 9 to the entrance / exit header tube 5 once meanders in the direction opposite to the discharge direction, It passes through the communication hole 29 and faces the discharge pipe 12. Thereby, a pressure loss is more preferably generated in the refrigerant from the discharge port 9b toward the discharge pipe 12. Therefore, the pressure loss of the refrigerant flowing through the opposed flat tube 9 can be increased, and the flow rate of the refrigerant flowing into the opposed flat tube 9 can be reduced.

  In the present modification, the case where the entire communication hole 29 is disposed at a position overlapping the flat tube 2 inserted into the entrance / exit header pipe 5 has been described. However, the communication hole is illustrated in FIG. Like the hole 30, you may arrange | position so that a part may overlap with the flat tube 2 inserted in the entrance / exit header tube 5. As shown in FIG. When a plurality of communication holes are formed, all the communication holes may be formed so as to overlap the flat tube 2 inserted into the entrance / exit header pipe 5 or inserted into the entrance / exit header pipe 5. You may form both the communicating hole which overlaps with the flat tube 2, and the communicating hole which does not overlap with the flat tube 2 inserted in the entrance / exit header tube 5. FIG.

  The meandering amount of the discharged refrigerant changes depending on the position where the communication hole is provided. When the meandering amount of the discharged refrigerant changes, the pressure loss generated in the opposed flat tube 9 also changes. Therefore, in addition to adjusting the pressure loss generated in the refrigerant flowing through the opposed flat tube 9 by changing the opening area of the communication hole, it is generated in the refrigerant flowing through the opposed flat tube 9 depending on the position where the communication hole is provided. The pressure loss can be adjusted. Specifically, when the refrigerant meandering distance is shortened, the pressure loss of the refrigerant flowing through the opposed flat tube 9 is reduced, and when the refrigerant meandering distance is increased, the pressure of the refrigerant flowing through the opposed flat tube 9 is reduced. Loss increases.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIG.
This embodiment is different from the first embodiment described above in that a collision plate 32 is provided instead of the partition plate 16. About another point, it attaches | subjects the same code | symbol similarly to 1st Embodiment, and the description is abbreviate | omitted.

  In the present embodiment, as shown in FIG. 6, a collision plate 32 is provided in the outlet space 14 of the inlet / outlet header pipe 5. The collision plate 32 is brazed and fixed to the upper surface of the first partition 15 and extends upward from the upper surface of the first partition 15 so as to face the discharge port 9b of the flow path 10 formed in the opposed flat tube 9. Yes. The collision plate 32 and one end of the opposed flat tube 9 are disposed so as to be separated from each other. The height in the vertical direction of the collision plate 32 is set higher than the upper end of the opposed flat tube 9 and lower than the lower end of the flat tube 2 disposed on one of the opposed flat tubes 9. In the present embodiment, the distance at which the collision plate 32 and the discharge port 9b are separated is set short, and the refrigerant collides with the collision plate 32 immediately after being discharged from the discharge port 9b.

According to this embodiment, there exist the following effects.
In the above configuration, since the collision plate 32 is provided so as to face the discharge port 9b of the flow path 10 formed in the opposed flat tube 9, the refrigerant discharged from the discharge port 9b into the inlet / outlet header tube 5 Colliding with the collision plate 32, a pressure loss occurs. Therefore, the pressure loss of the refrigerant flowing through the opposed flat tube 9 can be increased, and the flow rate of the refrigerant flowing into the opposed flat tube 9 can be reduced.

  The pressure loss at the time of collision between the discharged refrigerant and the collision plate 32 varies depending on the position where the collision plate 32 is provided. Therefore, by adjusting the position where the collision plate 32 is provided, a desired pressure loss is generated for the refrigerant flowing in the opposed flat tube 9, and the flow rate of the refrigerant flowing into the opposed flat tube 9 is set to a desired flow rate. be able to. Specifically, when the distance between the collision plate 32 and the discharge port 9b is increased, the pressure loss of the refrigerant flowing through the opposed flat tube 9 is decreased, and when the distance between the collision plate 32 and the discharge port 9b is decreased, The pressure loss of the refrigerant flowing through the flat tube 9 increases.

  Moreover, in this embodiment, the pressure loss of the refrigerant | coolant which distribute | circulates the inside of the opposing flat tube 9 is increased because the discharged refrigerant and the collision board 32 collide. Therefore, without causing the generation of abnormal noise such as whistling noise that may have occurred due to the relationship between the flow rate of the refrigerant and the diameter of the communication hole 17 in the form of passing through the communication hole 17 described in the first embodiment, The pressure loss of the refrigerant flowing through the opposed flat tube 9 can be increased.

  In the present embodiment, the collision plate 32 is brazed and fixed to the first partition 15, and then the first partition 15 is fixed to the inner peripheral surface of the entrance / exit header pipe 5 by brazing. Therefore, it is possible to reduce the amount of refrigerant flowing into the opposed flat tube 9 while reducing the number of parts and reducing the brazed locations in the entrance / exit header tube 5.

[Third Embodiment]
Next, a third embodiment of the present invention will be described with reference to FIGS.
This embodiment is different from the above-described first embodiment in that a sealing member 35 is provided instead of the partition plate 16. About another point, it attaches | subjects the same code | symbol similarly to 1st Embodiment, and the description is abbreviate | omitted.

  In the present embodiment, as shown in FIG. 7, a sealing member 35 is provided in the outlet space 14 of the inlet / outlet header pipe 5. The sealing member 35 is brazed and fixed to the upper surface of the first partition wall 15 and extends upward from the upper surface of the first partition wall 15 so as to face the discharge port 9b of the flow path 10 formed in the opposed flat tube 9. It is an existing plate-like member. The sealing member 35 and one end of the opposed flat tube 9 are disposed so as to contact each other. The height in the vertical direction of the sealing member 35 is set higher than the upper end of the opposed flat tube 9 and lower than the lower end of the flat tube 2 disposed on one of the opposed flat tubes 9.

  As shown in FIG. 8A, the sealing member 35 has one rectangular communication opening 36 at the approximate center of the side surface. The communication opening 36 is disposed so as to communicate with the discharge ports 9 b of the two central flow paths 10 among the six flow paths 10 formed in the opposed flat tube 9. That is, the sealing member 35 seals the discharge port 9 b of the flow channel 10 other than the two central flow channels 10 among the six flow channels 10 formed in the opposed flat tube 9.

  In the present embodiment, the case where one communication opening 36 is formed at substantially the center of the sealing member 35 has been described. However, there are a plurality of communication openings such as the communication opening 37 shown in FIG. It may be formed.

According to this embodiment, there exist the following effects.
In the above configuration, the sealing member 35 seals some of the channels 10 among the plurality of channels 10 formed in the opposed flat tube 9. Since the refrigerant hardly flows into the sealed flow path 10, the pressure loss of the refrigerant flowing in the opposed flat tube 9 can be increased more preferably. Therefore, the flow rate of the refrigerant flowing into the opposed flat tube 9 can be preferably reduced.

  Further, the pressure loss of the refrigerant flowing through the opposed flat tube 9 varies depending on the number of the flow paths 10 sealed by the sealing member 35. Therefore, by adjusting the number of the flow paths 10 sealed by the sealing member 35, the flow rate of the refrigerant flowing into the opposed flat tube 9 can be set to a desired flow rate. Specifically, when the number of the flow paths 10 to be sealed is set to be small, the pressure loss of the refrigerant flowing in the counter flat tube 9 is reduced, and when the number of the flow paths 10 to be sealed is set to be large, the counter flat tube is set. The pressure loss of the refrigerant flowing through 9 increases.

  Further, in the present embodiment, among the plurality of flow paths 10, the refrigerant is circulated through the flow path 10 disposed in the central portion, which is a position where frost formation is difficult, and is disposed outside the position where frost formation is easy. Since the refrigerant is not allowed to flow through the flow path 10, frost formation on the opposed flat tube 9 can be suppressed.

  In the present embodiment, a part of the flow path 10 is sealed by the plate-shaped sealing member 35, but the mode of sealing the flow path 10 is not limited to this. For example, only the flow path 10 to be sealed may be crushed and closed.

  Note that the present invention is not limited to the invention according to each of the above embodiments, and can be appropriately modified without departing from the gist thereof. For example, in each of the above embodiments, means for increasing the pressure loss is provided in the outlet space 14 of the inlet / outlet header pipe 5 in order to make the flow rate of the refrigerant flowing into each downstream side flat pipe 8 uniform. In order to make the flow rate of the refrigerant flowing into the pipe 7 uniform, means for increasing the pressure loss may be provided in the lower space 21 of the folded header pipe 4.

  Moreover, in each said embodiment, although the case where the heat exchanger 1 was used as an evaporator was demonstrated, the heat exchanger 1 of this invention is effective also when used as a condenser. When used as a condenser, the refrigerant flow is reversed, and means for increasing the pressure loss is provided in the upper space 22 of the folded header pipe 4 or the inlet space 13 of the inlet / outlet header pipe 5.

  Moreover, in each said embodiment, although the 1st partition 15 grade | etc., Is fixed by brazing, a fixing aspect is not limited to this, For example, you may fix by welding. Moreover, in each said embodiment, although the several flow path 10 is formed in the flat tube 2, the flow path 10 in a flat tube may be one.

DESCRIPTION OF SYMBOLS 1 Heat exchanger 2 Flat tube 3 Fin 4 Folded header pipe 5 Entrance / exit header pipe 6 Turn pipe 7 Upstream flat pipe 8 Downstream flat pipe 9 Opposed flat pipe 10 Flow path 11 Supply pipe (supply part)
12 Discharge pipe (discharge section)
13 Inlet space 14 Outlet space 15 First partition 16 Partition plate (pressure loss increasing means)
17 communication hole 21 lower space 22 upper space 23 second partition wall 32 collision plate (pressure loss increasing means)
35 Sealing member (pressure loss increasing means)
36 Communication opening

Claims (6)

A plurality of flat tubes that extend in a predetermined direction and are arranged substantially in parallel at intervals, and through which the refrigerant flows;
A fin disposed between the adjacent flat tubes and joined to each flat tube;
A first header pipe extending in a direction perpendicular to the flat pipe, one end of each flat pipe being connected, and introducing the refrigerant into each flat pipe;
A second header pipe extending in a direction orthogonal to the flat pipe, connected to the other end of each flat pipe, and discharging the refrigerant from the flat pipe,
The first header pipe has a supply section for supplying the refrigerant to the first header pipe,
The plurality of flat tubes have opposed flat tubes facing the supply unit,
A heat exchanger in which the second header pipe is provided with pressure loss increasing means for increasing the pressure loss of the refrigerant flowing through the inside of the opposed flat pipe. The second header pipe has a discharge portion for discharging the refrigerant from the second header pipe,
Each of the flat tubes has a discharge port communicating with the second header tube,
In the second header pipe, as the pressure loss increasing means, a partition plate is provided between the discharge port and the discharge portion of the opposed flat pipe,
The partition plate extends in a direction intersecting a direction in which the refrigerant flows from the discharge port toward the discharge portion,
The heat exchanger according to claim 1, wherein a communication hole is formed in the partition plate. The opposite flat tube has the other end inserted into the second header tube,
3. The heat exchanger according to claim 2, wherein the communication hole is disposed so as to overlap with the opposed flat tube when the flat surface of the flat tube is viewed from an extending direction of the second header tube. The second header pipe has a discharge portion for discharging the refrigerant from the second header pipe,
Each of the flat tubes has a discharge port communicating with the second header tube,
The heat exchanger according to claim 1, wherein the second header pipe is provided with a collision plate as the pressure loss increasing means so as to face the discharge port of the opposed flat pipe. Inside each of the flat tubes, a flow path through which the refrigerant flows is formed,
The sealing member which seals a part of channel area of the channel formed in the counter flat tube as the pressure loss increasing means is provided in the second header tube. The heat exchanger as described in. Each of the flat tubes has the one end inserted into the first header tube,
The heat exchanger according to any one of claims 1 to 5, wherein an insertion length of each of the flat tubes inserted into the first header tube is not more than half of an inner diameter of the first header tube.

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