WO2016084668A1

WO2016084668A1 - Heat exchanger

Info

Publication number: WO2016084668A1
Application number: PCT/JP2015/082354
Authority: WO
Inventors: 浩隆門; 金子　智; 祐介飯野
Original assignee: サンデンホールディングス株式会社
Priority date: 2014-11-26
Filing date: 2015-11-18
Publication date: 2016-06-02
Also published as: CN107003088A; JP2016099096A; DE112015005288T5

Abstract

[Problem] To provide a heat exchanger that can increase the drainage performance in a header tank and improve durability and heat efficiency. [Solution] Provided is a heat exchanger (1) that is formed by stacking three or more heat exchange modules (2), through which a refrigerant flows, in a ventilation direction (X). Each heat exchange module is provided with: a pair of upper and lower header tanks (4, 6) that are arranged so as to be vertically separated from each other; and a plurality of tubes (8) that extend parallel to one another between the upper and lower header tanks, each tube having two ends respectively communicated to the inside of the upper and lower header tanks. The upper header tank and the lower header tank have an upper header tank connection body (4U) and a lower header tank connection body (6L), respectively, formed by front-back header tanks (4A, 4B, 4C or 6A, 6B, 6C, respectively) which are arrayed in the ventilation direction. At least the lower header tank connection body, from among the upper and lower header tank connection bodies, has first waste water channels (26, 40) that separate the front-back header tanks from each other in the longitudinal direction thereof by a first interval (26, 30).

Description

Heat exchanger

The present invention relates to a heat exchanger, and more particularly to a heat exchanger suitable as an evaporator used in a refrigerant circuit of a vehicle air conditioner.

Patent Document 1 discloses a heat exchanger formed by overlapping three heat exchange modules in which a refrigerant flows in the ventilation direction. Each heat exchange module includes a pair of upper and lower header tanks that are spaced apart from each other, and a plurality of tubes that extend in parallel between the upper and lower header tanks and that both ends communicate with each other inside the upper and lower header tanks. Yes.

JP 2001-141379 A

Conventionally, heat exchangers used especially for vehicle air conditioners are often formed by stacking two heat exchange modules. Compared to the outside of the front and rear header tanks adjacent to each other in the ventilation direction of the two heat exchange modules. Draining is easy. However, in the heat exchanger of Patent Document 1, three front and rear header tanks adjacent to each other in the ventilation direction of the three heat exchange modules are in contact with each other, and two depressions are formed between the header tanks.

For this reason, condensed water condensed in the two recesses formed between the header tanks may accumulate, and the drainage performance in the header tanks may deteriorate. In particular, in the case of a heat exchanger in which a header tank is formed in a round pipe shape and three or more heat exchange modules are provided as in the conventional heat exchanger, a plurality of deep recesses are formed between the header tanks. Therefore, the deterioration of drainage in the header tank becomes even more remarkable.

If the drainage of the header tank deteriorates, the accumulated water will cause corrosion of the header tank, reducing the durability of the heat exchanger, and frosting on the header tank, which may significantly reduce the heat efficiency of the heat exchanger. There is also.
This invention is made | formed in view of such a subject, The place made into the objective is to improve the drainage property in a header tank, and to provide the heat exchanger which can improve durability and thermal efficiency. is there.

In order to achieve the above object, the heat exchanger of the present invention is a heat exchanger formed by stacking three or more heat exchange modules through which a refrigerant flows in the ventilation direction, and each heat exchange module is spaced apart in the vertical direction. A pair of upper and lower header tanks and a plurality of tubes extending in parallel between the upper and lower header tanks and having both ends communicated with each other inside the upper and lower header tanks. An upper header tank coupling body and a lower header tank coupling body are formed by the front and rear header tanks, and at least the lower header tank coupling body of the upper and lower header tank coupling bodies has the front and rear header tanks along the longitudinal direction thereof. There is a first drainage channel that is spaced apart with a gap.

Preferably, each header tank is formed in a cylindrical shape.
Preferably, at least one of the upper and lower header tank connections having the first gap includes a communication portion that occupies at least a part of the first gap, and the communication portion communicates with the inside of the front and rear header tanks, and between the heat exchange modules. The first drainage channel is positioned at a portion other than the communication portion of the first gap.
Preferably, the communication portion has a plurality of communication pipes forming a flow path, and the plurality of communication pipes are second drainage channels along the longitudinal direction of the upper and lower header tank coupling bodies in the first gap. Are spaced apart with a second gap used.

Preferably, the communication pipe is a burring portion that is projected by burring on the wall of one header tank of the front and rear header tanks, and the burring portion is connected to the wall of the other header tank of the front and rear header tanks. Connection holes are formed.
Preferably, one or a plurality of communication portions are formed in the same first gap, and the communication portions are positioned at positions that are symmetrical with respect to the center in the longitudinal direction of the upper and lower header tank assemblies.

According to the heat exchanger of the present invention, drainage performance in the header tank can be improved, and both the durability and thermal efficiency of the heat exchanger can be improved.

It is a perspective view of the heat exchanger which concerns on one Embodiment of this invention. It is a front view of the heat exchanger shown in FIG. FIG. 3 is an enlarged view of a region S shown in FIG. 2. FIG. 3 is a cross-sectional view of the upper header tank connection body shown in FIG. It is a top view of the upper header tank coupling body shown in FIG. FIG. 6 is a DD sectional view of the lower header tank coupling body shown in FIG. 5. FIG. 3 is a cross-sectional view of the lower header tank connecting body shown in FIG. It is a bottom view of the lower header tank coupling body shown in FIG. It is an enlarged view of the communicating member shown in FIG. FIG. 10 is a side view of the communication member shown in FIG. 9 viewed from the ventilation direction. FIG. 10 is an EE cross-sectional view of the lower header tank coupling body shown in FIG. 9. It is a partial enlarged view of the lower header tank coupling body which concerns on the modification of this invention. FIG. 13 is a cross-sectional view of the lower header tank assembly shown in FIG.

Hereinafter, the heat exchanger 1 which concerns on one Embodiment of this invention is demonstrated with reference to drawings.
FIG. 1 shows a perspective view of the heat exchanger 1, and FIG. 2 shows a front view of the heat exchanger 1. The heat exchanger 1 forms, for example, a refrigeration cycle of a vehicle air conditioner, is incorporated in a refrigerant circuit in which high-pressure carbon dioxide refrigerant circulates, and is used as an evaporator during operation of the vehicle air conditioner.

As shown in FIG. 1 and FIG. 2, the heat exchanger 1 has three heats of an upwind (front side) module 2A, a central module 2B, and a downwind (rear side) module 2C in order from the upwind of the ventilation A indicated by the arrows. The exchange module 2 is formed so as to overlap in the ventilation direction X. Ventilation A is vehicle interior air (inside air) or vehicle interior air (outside air).
FIG. 3 is an enlarged view of the region S in FIG. As shown in FIGS. 2 and 3, each heat exchange module 2 includes a pair of upper header tank 4 and lower header tank 6 that are spaced apart from each other in the vertical direction, and the upper and

lower header tanks

4, 6 are parallel to each other. A plurality of flat tubes 8 that extend and have both ends communicating with the inside of the upper and

lower header tanks

4 and 6 are provided. The upper and

lower header tanks

4 and 6 are formed in a cylindrical shape (round pipe shape) having the same diameter.

Both ends of each tube 8 are joined to the upper and

lower header tanks

4 and 6 by brazing, and corrugated fins 10 are arranged between the tubes 8. Each fin 10 is joined to the flat surface of the tube 8 which opposes by brazing, and the ventilation flow path of the ventilation A in the heat exchange module 2 is formed. In the heat exchange module 2, the tubes 8 and the fins 10 are alternately arranged in the horizontal direction to form a core 12 for heat exchange between the refrigerant and the ventilation A. That is, the windward module 12A, the central module 2B, and the leeward module 2C are formed with the windward core 12A, the central core 12B, and the leeward core 12C, respectively. The left and right side surfaces of these cores 12 are each covered and protected by a single side plate 14.

4 is a cross-sectional view taken along the line BB of the upper header tank coupling body 4U constituted by the upper header tanks 4 of the heat exchanger 1 shown in FIG. 2, and FIG. 5 is an upper surface of the upper header tank coupling body 4U. FIG. As shown in FIGS. 4 and 5, the upside (front side), center, and downside (rear)

upper header tanks

4A, 4B, and 4C adjacent to each other in the ventilation direction X of different heat exchange modules 2 are separated from each other. An upper gap (first gap) 16 is secured between the

upper header tanks

4A, 4B, and 4C along the longitudinal direction Y of the upper header tank coupling body 4U.

In addition, a large number of connection holes 18 for inserting the tubes 8 and brazing and joining them are opened on the bottom surface of each upper header tank 4. Further, both open ends of each upper header tank 4 are closed by integral lid members 20, and these lid members 20 connect each upper header tank 4, each core 12, and thus each heat exchange module 2. Done. A refrigerant inlet pipe 22 and an outlet pipe 24 are connected to one of the lid members 20. The inlet pipe 22 communicates with the leeward upper header tank 4C, and the outlet pipe 24 communicates with the leeward upper header tank 4A.

FIG. 6 is a DD sectional view of the upper header tank assembly shown in FIG. As shown in FIG. 6, in the present embodiment, each upper gap 16 is used as an upper drainage channel (first drainage channel) 26 over the entire area in the longitudinal direction Y of the upper header tank coupling body 4U. Yes. In the upper header tank coupling body 4U, due to the formation of the upper drainage channel 26, the water dripped onto the upper surface of the upper header tank coupling body 4U passes through the upper drainage channel 26 and is drained downward by its own weight. Each upper header tank 4 is formed in a cylindrical shape, and the upper surface of each upper header tank 4 has a curved surface. For this reason, the water dripped onto the upper surface of the upper header tank coupling body 4U is guided to the upper drainage channel 26 along this curved surface and smoothly drained downward.

FIG. 7 is a cross-sectional view taken along the line CC of the lower header tank coupling body 6L constituted by the lower header tanks 6 of the heat exchanger 1 shown in FIG. 2, and FIG. 8 is a bottom view of the lower header tank coupling body 6L. FIG. 9 is an enlarged view of the communication member (communication portion) 28 shown in FIG.
As shown in FIGS. 7 to 9, each of the

upper header tanks

6A, 6B, and 6C on the windward (front side), center, and leeward (rear side) adjacent to the ventilation direction X of different heat exchange modules is the upper header tank. As in the case of 4A, 4B, 4C, they are spaced apart from each other, and the lower gaps (the first gaps) are arranged between the

lower header tanks

6A, 6B, 6C along the longitudinal direction Y of the lower header 6L. 30) is secured.

A large number of connection holes 32 are opened on the bottom surface of each lower header tank 6 for inserting each tube 8 and joining them by brazing. Further, both open ends of each upper header tank 4 are closed by integral lid members 34, and these lid members 34 connect each lower header tank 6, each core 12, and eventually each heat exchange module 2. Done.

In the case of this embodiment, communication members 28 A are arranged on the left and right ends of the lower gap 30 in the lower gap 30 on the leeward (rear side) of each lower gap 30. These communication members 28A are communication members 28 that respectively communicate with the lower header tanks (front and rear header tanks) 6 before and after the communication member 28A, that is, inside the leeward (rear side) and center

lower header tanks

6C and 6B. Thus, a refrigerant flow path in the direction Z1 from the leeward core 12C toward the central core 12B is formed.

On the other hand, in the lower gap 30 on the windward (front side) of each lower gap 30, a communication member 28B similar to that described above is disposed at the center of the lower gap 30. The communication member 28B is a communication member 28 that communicates with the lower header tanks (front and rear header tanks) 6 before and after the communication member 28B, that is, the center and the upwind (front side)

lower header tanks

6B and 6A. The refrigerant flow path in the direction Z2 from the central core 12B toward the upwind core 12A is formed.

Further, in the case of the present embodiment, each communication member 28 is disposed at a symmetrical position with respect to the center in the longitudinal direction Y of the lower header tank coupling body 6L. Further, as shown in FIG. 7, the lower header tank 6B in the center has a communication member 28A disposed on each of the left and right ends of the leeward lower gap 30 in the longitudinal direction Y, and the leeward lower gap 30. The partition plates 36 are respectively provided at positions that are boundaries with the communication member 28 B disposed in the center. Each partition plate 36 is inserted into an insertion hole (not shown) formed on the bottom surface of the lower header tank 6B in the center, and joined to the lower header tank 6B by brazing from the outside of the lower header tank 6B.

As described above, the communication member 28 and the partition plate 36 are appropriately disposed in the lower header tank coupling body 6L, so that the counter flow type refrigerant longitudinal flow in which the respective cores 12 are divided and the refrigerant is sequentially flowed is converted into the heat exchanger 1. Can be realized. Thus, efficient heat exchange can be performed between the ventilation A that is passed through each core 12 and the refrigerant that flows through each of the cores 12 that are divided by pass.

FIG. 10 is a side view of the communication member 28 shown in FIG. As shown in FIGS. 9 and 10, the communication member 28 includes a long plate portion 28a extending in the longitudinal direction Y, and a communication tube 28b protruding in pairs from both side surfaces of the long plate portion 28a with the long plate portion 28a interposed therebetween. And. A plurality of communication pipes 28b are arranged along the longitudinal direction Y.

FIG. 11 is an EE cross-sectional view of the lower header tank coupling body 6L shown in FIG. As shown in FIG. 11, also in the lower header tank coupling body 6 L, a lower drainage channel (first drainage channel) 40 similar to the upper drainage channel 26 is provided in a portion other than the communication member 28 of the lower gap 30. It is secured. Each communication pipe 28b has a cylindrical shape, and the inside of each pair of communication pipes 28b penetrates the long plate portion 28a and communicates with each other.

Further, connecting holes 38 are opened at positions corresponding to the respective communication pipes 28b in the facing

walls

6c and 6b of the

lower header tanks

6C and 6B at the leeward (rear side) and the center. The communication member 28 is disposed between the leeward (rear side) and the central

lower header tanks

6C and 6B, and the communication pipes 28b are inserted into the corresponding connection holes 38 and connected by brazing, so that the leeward The refrigerant flow path in the direction Z1 is formed from the core 12C toward the central core 12B.

The pair of communication pipes 28b sandwiching the long plate portion 28a is formed by, for example, a so-called burring process in which a member of the long plate portion 28a is squeezed out so as to protrude into a cylindrical shape while making a hole in the long plate portion 28a. In addition, two constituent members having communication pipes 28b formed by burring are prepared on one side surface of the long plate portion 28a, and these constituent members are joined to the other side surface of the long plate portion 28a by brazing. It may be formed.

Here, as shown in FIG. 11, in the communication member 28, the thickness t of the long plate portion 28 a is set smaller than the width W 1 of the lower gap 30. The long plate portion 28a and the walls of the front and rear lower header tanks (front and rear header tanks) 6, that is, the leeward (rear side) and the

walls

6c and 6b of the

lower header tanks

6C and 6B at the center, On both sides, a communication portion gap (second gap) 42 having a width W2 is provided and separated. The communication portion gap 42 is used as a communication portion drainage channel (second drainage channel) 44. The width W2 secured on both sides of the long plate portion 28a may be different, or the width W2 may be secured only on one side of the long plate portion 28a.

In the lower header tank coupling body 6L, the condensed water adhered and dropped on the upper surface of the lower header tank coupling body 6L is formed by the formation of the lower drainage channel 40 and the communication part drainage channel 44. The water is drained downward by its own weight through not only the lower drainage channel 40 but also the communication part drainage channel 44. Similarly to the upper header tank 4, the lower header tank 6 is also formed in a cylindrical shape, and the upper surface of each lower header tank 6 has a curved surface. Therefore, the condensed water adhering to the upper surface of the lower header tank coupling body 6 L. Is guided to the lower drainage channel 40 and the communication part drainage channel 44 through this curved surface, and is smoothly drained downward.

As described above, in the heat exchanger 1 of the present embodiment, the upper and

lower header tanks

4 and 6 of each heat exchange module 2 are respectively separated by the upper header tank 4 and the lower header tank 6 before and after being arranged in the ventilation direction X. An upper header tank coupling body 4U and a lower header tank coupling body 6L are formed. In the upper and lower header

tank coupling bodies

4U and 6L, the upper and lower upper header tanks 4 and the lower header tanks 6 along the longitudinal direction Y thereof have the upper gap 16 and the lower gap 30, respectively. The upper drainage channel 26 and the lower drainage channel 40 are formed.

Thereby, even if it is the heat exchanger 1 formed by overlapping the heat exchange module 2 in the ventilation direction X as in the present embodiment, the core 12 condenses and flows down, and the lower header tank coupling body 6L Condensed water that drops and adheres to the upper surface can be drained downward by its own weight via the lower drainage channel 40. Therefore, since the drainage property in the lower header tank coupling body 6L can be enhanced, it is possible to suppress a decrease in durability of the heat exchanger 1 due to the corrosion of the lower header tank coupling body 6L due to the adhesion of condensed water. .

Moreover, the fall of the thermal efficiency of the heat exchanger 1 accompanying the frost formation to the lower header tank coupling body 6L can be suppressed, and both durability and thermal efficiency of the heat exchanger 1 can be improved.
In addition, each upper gap 16 is used as an upper drainage channel 26 over the entire area in the longitudinal direction Y. Thereby, since the water dripped on the upper surface of the upper header tank coupling body 4U is drained downward by its own weight through the upper drainage channel 26, not only the lower header tank coupling body 6L but also the upper header tank coupling body 4U can be drained. Thus, the durability and thermal efficiency of the heat exchanger 1 can be further improved.

Further, since each

header tank

4, 6 is formed in a cylindrical shape, that is, a round pipe shape, the water dropped on the upper and lower header

tank coupling bodies

4 U, 6 L travels along the curved surface of the wall and is connected to the upper drainage channel 26 and the lower side. It becomes possible to guide efficiently to the drainage channel 40, and the drainage performance of the upper and lower header

tank coupling bodies

4U, 6L can be further improved.
In addition, since the upper and

lower header tanks

4 and 6 are formed into a round pipe shape, the walls of the upper and

lower header tanks

4 and 6 can be formed into a continuous shape having no joint portion.

Further, the tube 8 is inserted into the connection holes 18 and 32 formed in the walls, and the partition plate 36 is inserted into the insertion hole (not shown) formed in the wall, and brazed from the outside of the upper and

lower header tanks

4 and 6. Thus, each core 12 can be manufactured by a simple operation of simply joining. Thereby, in the upper and

lower header tanks

4 and 6, since there is no joint portion that cannot be visually observed from the appearance, the joint portion can be inspected only by the appearance inspection, and the nondestructive inspection can be eliminated. Therefore, the productivity of the heat exchanger 1 can be further improved.

Further, in the lower header tank coupling body 6L, although the communication member 28 is disposed in the lower gap 30, a lower drainage channel 40 is secured in a portion other than the communication member 28 of the lower gap 30. Further, the plurality of communication pipes 28b have a communication part gap 42 used as the communication part drainage channel 44 along the longitudinal direction Y of the lower header tank coupling body 4U in the lower gap 30 and are separated from each other. Yes. As a result, even in the region where the communication member 28 of the lower gap 30 is disposed, drainage from the communication part drainage channel 44 is possible, so that the drainage of the lower header tank coupling body 6L can be further improved, and as a result Further durability and heat efficiency of the exchanger 1 can be improved.

Further, one or a plurality of communication members 28 are disposed in the same lower gap 30. Specifically, in the leeward (rear) lower gap 30, communication members 28 A are disposed on the left and right ends of the lower gap 30, respectively. Further, a communication member 28 B is disposed at the center of the lower gap 30 in the lower gap 30 on the windward (front side). Both of the

communication members

28A and 28B are positioned at positions that are symmetrical with respect to the center in the longitudinal direction Y of the lower header tank coupling body 6L.

Thus, by providing the

communication members

28A and 28B at positions that are bilaterally symmetrical with respect to the center in the longitudinal direction Y of the lower header tank coupling body 6L, the condensed water is biased to either the left or right side of the lower header tank coupling body 6L. The imbalance of drainage in the lower header tank coupling body 6L due to accumulation can be corrected, and the drainage can be made uniform. Thereby, the drainage property of 6 L of lower header tank coupling bodies can further be improved, and the further durability and thermal efficiency of the heat exchanger 1 can be aimed at by extension.

Although the description of the embodiment of the present invention has been completed above, the present invention is not limited to the above embodiment, and various modifications can be made without departing from the spirit of the present invention.
For example, as shown in FIGS. 12 and 13, instead of the communication member 28, the wall 6 c of the lower header tank 6 C itself is subjected to burring processing, and a large number of cylindrical burring portions are formed to project as the communication pipe 46. good. These communication pipes 46 are connected by brazing to connection holes 48 opened in the wall 6b of the lower header tank 6B facing the lower header tank 6C, thereby forming a communication portion 50 in the lower header tank coupling body 6L. .

In this case, in a region where the communication portion 50 of the lower gap 30 is formed, a communication portion gap (second gap) 52 having the same width as that of the lower drainage channel 40 is intermittently formed. Can be easily secured. Accordingly, it is possible to further improve the drainage performance of the lower header tank coupling body 6L, and further improve the durability and thermal efficiency of the heat exchanger 1. Moreover, since the communication member 28 is not necessary, the number of parts and the manufacturing cost of the heat exchanger 1 can be reduced, and the productivity of the heat exchanger 1 can be further improved.

Moreover, although the heat exchanger 1 of the said embodiment and the modification is formed by overlapping three heat exchange modules 2 in the ventilation direction X, it is also applicable to a heat exchanger in which four or more heat exchange modules 2 are stacked. Is possible.
Further, the communication member 28 or the communication portion 50 may be provided not only in the lower header tank connection body 6L but also in the upper header tank connection body 4U. By forming all the communication members 28 or communication portions 50 in the upper header tank coupling body 4U, all the lower gaps 30 are inevitably all lower drainage over the entire area in the longitudinal direction Y of the lower header tank coupling body 6L. It can be used as the path 40.

Therefore, the drainage performance of the lower header tank coupling body 6L can be further improved, and further the durability and thermal efficiency of the heat exchanger 1 can be further improved. However, when the communication member 28 is provided in the lower header tank coupling body 6L, it has been experimentally found that the heat efficiency of the heat exchanger 1 is higher than that when the communication member 28 is provided in the upper header tank coupling body 4U. Therefore, the configuration in which the communication member 28 is provided in the lower header tank coupling body 6 L contributes to improving the thermal efficiency of the heat exchanger 1.

In the heat exchanger 1 of the above embodiment and the modified example, the upper gap 16 is formed in the upper header tank coupling body 4U, and the upper drainage channel 26 is secured. However, even if the upper gap 16 and the upper drainage channel 26 are not formed, it is sufficient if the heat exchanger has at least the lower gap 30 formed in the lower header tank connector 6L and the lower drainage channel 40 is secured. In this case, it is possible to at least enhance the drainage of the condensed water that has condensed and flowed down at each core 12 and dropped onto and adhered to the upper surface of the lower header tank coupling body 6L. Thermal efficiency can be improved.

Further, the refrigerant used in the heat exchanger 1 of the above embodiment and the modification is a carbon dioxide refrigerant, but other refrigerants may be used. However, as in the present embodiment, the heat exchanger 1 having a configuration in which three or more heat exchange modules 2 are stacked using the

header tanks

4 and 6 made of relatively small-diameter round pipes is excellent in pressure resistance performance. Therefore, the use of a carbon dioxide refrigerant is preferable.

1 Heat exchanger 2 Heat exchange module 4

Upper header tank

4A, 4B, 4C Upper header tank (front and rear header tanks)
4U Upper header tank assembly 6

Lower header tank

6b,

6c Wall

6A, 6B, 6C Lower header tank (front and rear header tanks)
6L Lower header tank assembly 8 Tube 16 Upper gap (first gap)
26 Upper drainage channel (first drainage channel)
28 Communication member (communication part)
28b Communication pipe 30 Lower gap (first gap)
40 Lower drainage channel (first drainage channel)
42,52 Communication portion gap (second gap)
44, 54 Drainage channel (second drainage channel)
46 Communication pipe (burring part)
48 Connection hole 50 Communication part

Claims

A heat exchanger formed by stacking three or more heat exchange modules in which the refrigerant flows in the direction of ventilation,
Each of the heat exchange modules includes a pair of upper and lower header tanks that are spaced apart from each other, and a plurality of tubes that extend in parallel between the upper and lower header tanks and that have both ends communicating with the inside of the upper and lower header tanks. With
The upper and lower header tanks form an upper header tank connection body and a lower header tank connection body by front and rear header tanks arranged in the ventilation direction,
At least the lower header tank coupling body of the upper and lower header tank coupling bodies has a first drainage path that separates the front and rear header tanks with a first gap along their longitudinal direction. Exchanger.
The heat exchanger according to claim 1, wherein each header tank is formed in a cylindrical shape.
At least one of the upper and lower header tank connections having the first gap includes a communication portion that occupies at least a part of the first gap;
The communication portion communicates the inside of the front and rear header tanks to form a refrigerant flow path between the heat exchange modules,
The heat exchanger according to claim 2, wherein the first drainage channel is positioned in a portion other than the communication portion of the first gap.
The communication part has a plurality of communication pipes forming the flow path,
The plurality of communication pipes are spaced apart from each other with a second gap used as a second drainage channel along the longitudinal direction of the upper and lower header tank coupling bodies in the first gap. The heat exchanger according to claim 3.
The communication pipe is a burring portion that is projected by burring on the wall of one of the front and rear header tanks,
The heat exchanger according to claim 4, wherein a connection hole for connecting the burring portion is formed in a wall of the other header tank of the front and rear header tanks.
One or a plurality of the communication portions are formed in the same first gap, and the communication portions are positioned at positions that are symmetrical with respect to the center in the longitudinal direction of the upper and lower header tank coupling bodies. Item 6. The heat exchanger according to any one of Items 2 to 5.