JP2002213840A - Evaporator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make improvement in draining of condensed water and ensurance of heat transfer performance compatible with each other, in an evaporator formed such that a tube part and a tank part are formed of different members and the tank parts are arranged in a plurality of rows at a front and in the rear in an air flow direction. SOLUTION: Tank parts 7-10 for distributing and collecting a refrigerant to and from tubes 2 and 3 are formed differently from the tubes 2 and 3, and are arranged in a plurality of rows in the flow direction A of air. The distance between a plurality of rows of the tank parts 7-10 in the portion, corresponding to tube insertion parts 14 and 16 of the tank parts 7 and 10, is reduced to a value smaller than a distance c between the tank parts in other portion not corresponding to the tube insertion parts 14 and 16. A passage 25 for drainage is formed at a spot, corresponding to at least other portion between the tank parts 7-10 in a plurality of rows.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an evaporator for cooling air by evaporating a refrigerant in a refrigeration cycle, and is suitable for use in, for example, a vehicle air conditioner.

[0002]

2. Description of the Related Art In recent years, as the demand for smaller and lighter air conditioners for vehicles has increased, the demand for smaller and lighter evaporators has been increasing. To meet this demand, it is essential to reduce the thickness of the material of the components of the evaporator.

In an evaporator of a vehicle air conditioner, a tube portion forming a flat refrigerant flow path and a tank portion for distributing the refrigerant flow to the tube portion or collecting the refrigerant flow are formed of a sheet metal material. A laminated evaporator is often used in which the metal sheet material and the corrugated fin are alternately laminated and integrally brazed.

[0004]

This type of laminated evaporator has a high performance by combining a flat refrigerant flow path and a corrugated fin, and a good productivity by integrally forming a tube portion and a tank portion. But also has
Since the adjacent tanks need to be in contact with each other to communicate with each other in the tank portion, the protruding height of the tank portion needs to be significantly larger than that of the tube portion.

Accordingly, when the tube portion and the tank portion are integrally formed by overstretching with a thin metal material such as aluminum, in order to avoid processing defects such as tearing caused by drawing of the tank portion, the thin metal material is formed. There was a limit to thinning.

In Japanese Patent Publication No. Hei 7-121451, the tube portion and the tank portion are formed of different members, and the two tank portions at the front and rear in the air flow direction are integrally formed to form an overall shape. A heat exchanger made compact has been proposed, but with such a heat exchanger configuration, the two tank portions before and after in the air flow direction have a completely integrated structure, so that they have been used for air cooling. In this case, when the condensed water generated on the outer surface of the tube falls to the two tank portions, the condensed water cannot be discharged at an intermediate portion of the tank portion in the air flow direction.

Accordingly, the condensed water is discharged only after moving to the most downstream end in the air flow direction of the tank, which deteriorates the drainage of the condensed water.

[0008] The present invention has been made in view of the above points,
In the evaporator in which the tube part and the tank part are formed of different members, and the tank part is arranged in plural rows before and after in the air flow direction, the improvement of drainage of condensed water and the securing of heat transfer performance are achieved. The purpose is to make them compatible.

Another object of the present invention is to improve the assemblability of a plurality of rows of tank portions.

[0010]

In order to achieve the above object, according to the first aspect of the present invention, there is provided a tube (2, 3) which constitutes a refrigerant passage extending vertically. The tanks (7-10) for distributing and collecting the refrigerant to the tubes (7-10) are formed separately from the tubes (2, 3), and the tanks (7-10) are provided at the upper and lower ends of the tubes (2, 3). A plurality of rows are arranged in the air flow direction (A),
Tube insertion part (14, 1) of tank part (7-10)
6) A plurality of rows of tank portions (7 to
The interval (a) of 10) is changed to the tube insertion portion (14, 16).
The space (c) in the other part (24) that does not correspond to the above, and a drain passage is provided at least in a part corresponding to the other part (24) between the plurality of rows of tank parts (7 to 10). (25) is formed.

[0011] According to this, since the tube portion and the tank portion are formed of different members, the tube portion can be reduced in thickness without being restricted by the workability, strength and the like of the tank portion. Therefore, the heat exchange part can be miniaturized to improve the heat exchange performance and reduce the size.

In addition, since the drain passage (25) is formed between the plurality of rows of tanks (7 to 10), the condensed water falling along the tubes (2, 3) is prevented from being condensed. The drainage gap (25) between the two can be easily discharged to the outside of the evaporator, and the drainage of condensed water can be improved.

Further, the interval (a) between the plurality of rows of tank portions (7 to 10) in the portion corresponding to the tube insertion portions (14, 16) of the tank portions (7 to 10) is set to the tube insertion portion (14). , 16) is smaller than the interval (c) in the other portion (24) that does not correspond to the tank portion (7).
10) In the overall width dimension (dimension in the air flow direction),
The maximum length (L) of the tube insertion portions (14, 16) can be ensured, so that the joint length between the tubes (2, 3) and the fins is also the largest among the limited tank widths. And heat transfer performance can be secured.

According to the second aspect of the present invention, the tube insertion portion (14, 1) of the plurality of rows of tank portions (7 to 10) is provided.
The parts (15, 17) forming 6) are integrally formed by one sheet metal part (13), and the sheet metal part (1) is formed.
In 3), the drainage passage (25) is partially opened at a position corresponding to the other portion (24).

Thus, a plurality of rows of tank sections (7-1 to 1)
The sheet metal part (13) of (0) is used as one sheet, thereby reducing costs by reducing the number of parts and simultaneously improving drainage of condensed water by partially forming the drainage gap (25). Also, when assembling the evaporator, a plurality of tank body portions (2
1, 22) are assembled to one sheet metal portion (13), so that the plurality of rows of tank body portions can be easily and reliably positioned relative to each other, and the evaporator can be easily assembled.

According to the third aspect of the present invention, a plurality of rows of tank portions (7 to 10) are brought into contact with portions corresponding to the tube insertion portions (14, 16) to correspond to the other portions (24). A drain passage (25) is partially formed at a location.

As described above, the tube insertion portions (14, 1
In the part corresponding to (6), a plurality of rows of tank parts (7-1)
0) is brought into contact with the tube insertion portion (1).
4, 16) The length (L) can be maximized to ensure the heat transfer performance. At the same time, since the plurality of rows of tank portions (7 to 10) are in contact with each other, the positioning of the plurality of rows of tank portions becomes easy, and the assemblability of the evaporator is good. That is, it is possible to secure the heat transfer performance and achieve good assemblability while improving the drainage of the condensed water.

According to the fourth aspect of the present invention, the tube insertion portions (14, 1) of the plurality of rows of tank portions (7 to 10) are provided.
The parts (15, 17) forming 6) are integrally formed by one sheet metal part (13), and one tank body part (21, 22) of a plurality of rows of tank parts (7 to 10) is provided. Of the sheet metal part (13) and the tank body part (21, 22).
In 9), the drainage passage (25) is partially opened at a position corresponding to the other portion (24).

According to this, in addition to exhibiting the same effect as in the second aspect, the tank main bodies (21, 22) of the plurality of rows of tank parts (7 to 10) can be integrated. Further, the cost can be further reduced by reducing the number of parts.

According to a fifth aspect of the present invention, the communication means (26, 26a, 27, 27a) for directly communicating the flow path is formed integrally with the plurality of rows of tank portions (7 to 10). And

This allows direct communication between the flow passages of the plurality of rows of tank portions without the need for a communication member separate from the tank.

The reference numerals in parentheses of the above-mentioned means indicate the correspondence with the concrete means described in the embodiments described later.

[0023]

(First Embodiment) FIGS. 1 to 3 are a front view, a plan view and a left side view of a first embodiment in which the present invention is applied to an evaporator in a refrigeration cycle of a vehicle air conditioner. is there. FIG. 4 is a cross-sectional view of a main part of the tank, and FIGS.
, FIG. 6 is a cross-sectional view taken along the line CC of FIGS. 1 and 4, and FIG. 7 is a cross-sectional view of a part of the heat exchange section of the evaporator 1.

The evaporator 1 is installed in an air-conditioning unit case (not shown) of a vehicle air conditioner with the vertical direction of FIGS. Air is blown to the evaporator 1 in the direction of arrow A in FIGS. 2 and 3 by a blower (not shown), and the blown air and the refrigerant exchange heat.

The evaporator 1 has tubes 2 and 3 arranged in two rows before and after in the air flow direction A as shown in FIGS. These tubes 2 and 3 are flat tubes that form a refrigerant passage having a flat cross section and extending in the vertical direction. A large number of tubes 2 and 3 are arranged in parallel in a direction intersecting with the air flow direction A (the left-right direction in FIG. 1).

In this embodiment, one joint block 4 (FIGS. 2 and 3) is arranged on the upper left side of the evaporator 1, and the joint block 4 is provided with a refrigerant inlet 5 and a refrigerant outlet 6. The low-temperature low-pressure gas-liquid two-phase refrigerant that has been decompressed and expanded by a temperature-operated expansion valve (not shown) of the refrigeration cycle flows into the refrigerant inlet 5. The refrigerant outlet 6 is connected to a compressor suction pipe (not shown), and is for returning gas refrigerant evaporated in the evaporator 1 to the compressor suction side.

Next, the tank units 7 to 10 of the evaporator 1 will be described. The tank units 7 to 10 distribute the refrigerant to the tubes 2 to 5 or collect the refrigerant from the tubes 2 and 3, Two rows are arranged before and after in the air flow direction A corresponding to the first tube 2 on the upstream side of the flow and the second tube 3 on the downstream side of the air flow. That is, the upper and lower tank portions 7 and 8 are located on the downstream side of the air flow, and the upper and lower tank portions 9 and 10 are located on the upstream side of the air flow.

In this embodiment, the inner space of the upper tank 7 on the downstream side of the air flow is separated by a partition plate 11 located at the center of the tank in the longitudinal direction of the tank (left and right directions in FIGS. 1 and 2). And is divided into. Similarly, the partition plate 1 in which the internal space of the upper tank 9 on the upstream side of the air flow is located at the center in the longitudinal direction of the tank (the left-right direction in FIGS. 1 and 2).
2 separates a left tank portion 9a and a right tank portion 9b.

On the other hand, since the lower tank portions 8, 10 are not provided with a partition plate, the internal space of the lower tank portions 8, 10 becomes one continuous flow path over the entire length in the tank longitudinal direction. I have.

Here, the specific structure of the upper and lower tank portions 7 to 10 will be described. Since the upper tank portions 7, 9 and the lower tank portions 8, 10 may be basically the same structure, FIGS.
, The upper tank portions 7 and 9 will be described. In the present embodiment, the upper tank portions 7 and 9 use a sheet metal portion 13 that forms a tube insertion portion and an integrally molded product common to both tank portions.

That is, the tube 3 on the upper tank 7 side
Curved surface 15 having an insertion hole 14 formed therein and upper tank portion 9
The curved surface 17 formed with the insertion hole 16 of the tube 2 on the side is integrally formed by one sheet metal portion 13. The insertion holes 14 and 16 have a long hole shape parallel to the air flow direction A.

In the air flow direction A of the single sheet metal portion 13, rising portions 18, 19 are integrally formed at both ends thereof, respectively. A connecting portion 20 is formed in the middle of the sheet metal portion 13 in the air flow direction A by bending the sheet surface of the sheet metal portion 13 into a U shape. The opening-side ends of the tank body portions 21 and 22 having a U-shaped cross section are fitted to the inner surfaces of the rising portions 18 and 19 at both ends and the inner surface of the connecting portion 20 at the intermediate portion, and are integrally joined. .

In the direction where the sheet metal portion 13 intersects with the air flow direction A, the outer surface of the U-shaped bent portion of the connecting portion 20 is crimped at the portion where the tube insertion holes 14 and 16 are formed, as shown in FIG. ing. Thereby, the connecting portion 2
The thickness dimension a of the sheet metal portion 13 as shown in FIG.
As a result, the distance between the two tank bodies 21 and 22 before and after in the air flow direction can be set to the minimum structural value (the dimension a).

Accordingly, the curved surface 1 of the sheet metal portion 13
By maximizing the length of the tube insertion holes 14 and 16 in the air flow direction at 5 and 17, that is, the length L of the tubes 2 and 3 in the air flow direction, the air between the tubes 2 and 3 and a corrugated fin 23 described later is maximized. By maximizing the joining length in the flow direction, the air-side heat transfer performance can be improved.

On the other hand, in the direction intersecting with the air flow direction A of the sheet metal portion 13, the tube insertion holes 14, 16
In other parts where no tube is formed, that is, at the part corresponding to the intermediate part 24 between the adjacent tube insertion holes 14 and 16 (FIG. 4), as shown in FIG.
A predetermined interval b (b = a) is provided between the plate surfaces of the U-shaped bent portion without pressing the plate surfaces of the bent portion.

This interval b can be formed by making a cut line in the upper surface of the U-shaped bent portion of the intermediate connecting portion 20 to widen the space between the plate surfaces of the U-shaped bent portion. And the drainage passage 25 can be formed by this interval b. Since the drain passage 25 is formed in this manner, the interval between the two tank main bodies 21 and 22 is a dimension c that is larger than the dimension a by a predetermined amount.

By the way, of the upper tank portions 7, 8, the right tank portions 7b, 9b are formed integrally with communicating portions 26, 27 for communicating the passage between the two tanks 7b, 9b. FIG. 8 is an explanatory view of the communication portions 26 and 27. The communication portions 26 and 27 are in contact with each other and joined, and the communication portions 26 and 27 have openings 26a and 2a, respectively.
By opening 7a, the right tank portions 7b, 9b
The mutual flow paths can be directly connected.

Corrugated fins (outer fins) 23 are formed between the tubes 2 and 3 so as to be corrugated. As shown in FIG. 7, the corrugated fins 23 are arranged so as to extend over both of the tubes 2 and 3 before and after the air flow direction A, and are integrally joined to the flat surfaces of the tubes 2 and 3. Also, a corrugated inner fin 28 is disposed inside each of the tubes 2 and 3, and the corrugated top of the inner fin 28 is joined to the inner wall surface of each of the tubes to reinforce each of the tubes 2 and 3. At the same time, the performance is improved by increasing the heat transfer area on the refrigerant side.

The components of the above-described evaporator 1 are formed of a thin aluminum plate material, and a clad material in which a brazing material is clad is applied to a part of the components. By assembling and holding the assembled state with an appropriate jig such as a wire and brazing in a furnace, the entire evaporator 1 can be assembled by integral brazing.

Next, the operation of the evaporator according to the first embodiment in the above configuration will be described. FIG. 9 shows a refrigerant passage of the evaporator 1, and a low-temperature low-pressure gas-liquid reduced by an expansion valve (not shown). The two-phase refrigerant is first supplied from the refrigerant inlet 5 to the left tank 7a of the upper tank 7 on the downstream side of the air as shown by the arrow.
And is distributed to a plurality of tubes 3 here.

Next, the refrigerant flows downward through the tube 3 as shown by the arrow, and reaches the left side portion (collection portion) of the lower tank portion 8. Thereafter, the refrigerant flows through the lower tank portion 8 toward the right side (distribution portion) as shown by the arrow, and is then distributed to the plurality of tubes 3, flows upward through the tubes 3 as shown by the arrow, and It flows into the right side tank part 7b of the part 7.

Next, the refrigerant is supplied to the communicating portions 26, 2 shown in FIG.
7, and directly flows into the right tank portion 9b on the upstream side of the air as shown by the arrow. Next, the refrigerant is distributed to the plurality of tubes 2 from the upper right tank portion 9b, and flows down the tubes 2 as indicated by arrows,
It flows into the right side part (collection part) of the lower tank part 10.

Next, the refrigerant flows through the lower tank section 10 toward the left side (distribution section) as shown by the arrow, and is then distributed to the plurality of tubes 2 and flows upward through the tubes 2 as shown by the arrow. Thereafter, the refrigerant from the tube 2 is gathered in the left tank 9a of the upper tank 9 and moves from the right to the left as shown by the arrow in the upper left tank 9a. Leaks to

On the other hand, the blown air (conditioned air) is blown in the direction of arrow A, and passes through the gap of the heat exchange core portion formed by the tubes 2 and 3 and the corrugated fins 23.
At this time, the refrigerant in the tubes 2 and 3 absorbs heat from the blown air and evaporates, so that the blown air is cooled and becomes cool air, and is blown out into the vehicle compartment to cool the vehicle compartment.

In the evaporator 1, arrows to
The refrigerant inlet side heat exchange part X composed of a meandering flow path on the refrigerant inlet side indicated by the arrow is disposed on the downstream side in the air flow direction A, and the refrigerant outlet side heat formed by the serpentine flow path on the refrigerant outlet side indicated by the arrow- Since the exchange part Y is arranged on the upstream side in the air flow direction A, heat exchange between the refrigerant and the air in the orthogonal counterflow having good heat transfer performance can be performed.

Incidentally, the condensed water generated in the heat exchange core falls down along the surfaces of the tubes 2 and 3. At this time, the condensed water can be drained from the most downstream portion in the air flow direction A in the lower tank portions 8 and 10 as shown by the arrow A, and the upstream tank portion 10 and the downstream tank portion in the air flow direction A are simultaneously discharged. 8, a drain passage 25 is formed, so that condensed water can be drained from an intermediate portion in the air flow direction A through the passage 25 as shown by the arrow B.

As described above, in the lower tank portions 8 and 10, condensed water can be discharged from both the most downstream end portion in the air flow direction A and the passage 25 at the intermediate portion in the air flow direction A. Drainage can be improved.

Further, according to the first embodiment, the following effects can be exerted simultaneously with the improvement of drainage of condensed water.

(1) Even if the drainage passage 25 is formed, as shown in FIGS. 5 and 6, the tank body portions 21 and 22 of a plurality of rows of tank portions located before and after in the air flow direction A are shared by one sheet. Can be easily positioned relative to each other when assembling the evaporator.

(2) In the direction intersecting the air flow direction A of the sheet metal portion 13, the tube insertion holes 14, 16
Is formed, the U-shaped bent portion of the connecting portion 20 is press-bonded, and the thickness dimension a of the connecting portion 20 is set to a plate thickness (minimum value) twice as large as that of the sheet material of the sheet metal portion 13 so as to be before and after the air flow direction. Interval between the two tank main bodies 21 and 22 (above dimension a)
Can be a structural minimum.

Therefore, the curved surface 1 of the sheet metal portion 13
By maximizing the length of the tube insertion holes 14 and 16 in the air flow direction at 5 and 17, that is, the length L of the tubes 2 and 3 in the air flow direction, the air between the tubes 2 and 3 and a corrugated fin 23 described later is maximized. By maximizing the joining length in the flow direction, the air-side heat transfer performance can be improved.

(3) Since the sheet metal portions 13 of the plurality of rows of tank portions are formed as a single integrated product, cost can be reduced by reducing the number of parts.

(4) Tubes 7 to 10 are connected to tubes 2 and 3
After the two parts are integrally formed, the two parts are integrally joined. Therefore, the thickness of the sheet material constituting the tank parts 7 to 10 is set to a required value to secure the strength, and at the same time, the tubes 2 and 3 are formed.
With respect to the thickness, the plate thickness is made sufficiently thinner than the tank portion, so that the tubes 2, 3 and the corrugated fins 23 can be miniaturized, and the size and performance of the refrigerant evaporator can be reduced.

In the first embodiment, as shown in FIG. 2 and FIG. 4, drainage passages 25 are provided every other one of the intermediate portions 24. 25 may be provided. Further, in the first embodiment, the plate surface of the U-shaped bent portion of the connecting portion 20 is crimped. A gap may be provided. It is generally better to provide this minute gap in the connecting portion 20.
The formation of the U-shaped bent portion becomes easy.

(Second Embodiment) In the first embodiment described above, as shown in FIGS. 4 and 5, tube insertion of the two tank portions 7, 9 or the tank portions 8, 10 before and after in the air flow direction A. Although the sheet metal portion 13 forming the holes 14 and 16 is formed of an integral molded product common to both, in the second embodiment, the sheet metal portion is formed by two tanks before and after in the air flow direction A as shown in FIG. The sheet metal portions 130 and 131 are independent of each other.

In the second embodiment, rising portions 18 and 1 are provided at both ends of the two independent sheet metal portions 130 and 131 in the air flow direction A before and after the air flow direction A, respectively.
8a19 and 19a are integrally formed by bending.

In the air flow direction A, the rising portions 18a and 19a located in the middle of the entire tank portion correspond to the connecting portions 20 of the first embodiment, and intersect with the air flow direction A. At tube insertion hole 1
In the locations corresponding to 4 and 16, the start-up section 18 in the middle section
a, 19a are brought into direct contact and joined together (brazing)
It is supposed to. Therefore, also in the second embodiment, at locations corresponding to the tube insertion holes 14 and 16, the distance between the tank main bodies 21 and 22 has the dimension a as in FIG. 5.

On the other hand, the intermediate portion 24 of the tube insertion holes 14 and 16 in the direction intersecting with the air flow direction A
In the locations corresponding to, the start-up portions 18a, 19
The drainage passage 25 is formed between the a and the a by a distance b (b = a) in FIG. Thereby, in the intermediate portion 24, the interval between the tank main bodies 21 and 22 becomes the c dimension as in FIG. In the second embodiment, a drain passage 25 is formed for each intermediate portion 24.

The second embodiment has the same configuration as that of the first embodiment except that two independent sheet metal portions 130 and 131 are disposed before and after in the air flow direction A, and exhibits the same operation and effect. it can.

(Third Embodiment) In the above-described second embodiment, the drainage passage 25 is formed for each intermediate portion 24. In the third embodiment, as shown in FIG. Are formed alternately with respect to the intermediate portion 24.

(Fourth Embodiment) In the above-described second and third embodiments, the rising portions 18a, 19a of the intermediate portions are formed at positions corresponding to the tube insertion holes 14, 16 in a direction intersecting with the air flow direction A. Direct contact, but the fourth
In the embodiment, as shown in FIG.
Also at the locations corresponding to 4 and 16, the rising portions 18a and 19a in the middle are separated by a predetermined amount.

Therefore, according to the fourth embodiment, between the two tank portions 7 and 9 or the tank portions 8 and 10 before and after in the air flow direction A, the drain passage 25 extends in the direction crossing the air flow direction A. It is formed over the entire length. Therefore, the drainage of the condensed water can be improved although the width dimension of the entire tank portion is slightly increased.

(Fifth Embodiment) FIG. 13 shows a fifth embodiment in which the inner fins 28 are not provided in the tubes 2 and 3 as can be seen from comparison with FIG.

(Sixth Embodiment) In each of the above embodiments,
In the two tank portions 7, 9 or the tank portions 8, 10 before and after in the air flow direction A, the tank body portions 21, 22 are formed separately, but in the sixth embodiment, FIGS.
As shown in (2), the two tank main bodies 21 and 22 in the front and rear in the air flow direction A are integrally formed of one plate.

A connecting portion 29 is formed between the two tank body portions 21 and 22 by bending a plate material into a U shape. Here, the U-shaped bent shape of the connecting portion 20 in the middle portion of the sheet metal portion 13 in the air flow direction A and the U-shaped bent portion of the connecting portion 29 in the middle portion of the tank body portions 21 and 22 in the air flow direction A are used.
The bent shapes are oriented in opposite directions, and the tops of the U-shaped bent shapes of the two 20 and 29 are brought into contact with each other and joined.

Further, in the direction intersecting with the air flow direction A, the tube insertion holes 14, 16
1, that is, an intermediate portion 24 between the adjacent tube insertion holes 14 and 16 (FIG. 1).
At a location corresponding to 4), through holes (FIG. 16) are opened at the tops of the U-shaped bent shapes of the two 20 and 29 so as to communicate with each other to form a drainage passage 25.

With such a configuration, the same operation and effect as those of the above embodiments can be exhibited. Moreover, in the sixth embodiment, the two tank body portions 21 before and after in the air flow direction,
22 can be integrally formed with one sheet material, and the manufacturing cost can be reduced.

(Other Embodiments) Since only the lower tanks 8, 10 of the upper and lower tanks require the drain passage 25, the lower tanks 8, 10 1
The drain passage 25 may be formed only at zero.

[Brief description of the drawings]

FIG. 1 is a front view of a refrigerant evaporator according to a first embodiment of the present invention.

FIG. 2 is a plan view of FIG.

FIG. 3 is a left side view of FIG.

FIG. 4 is a sectional view of a main part of a tank unit according to the first embodiment.

FIG. 5 is a sectional view taken along the line BB of FIGS. 1 and 4;

FIG. 6 is a sectional view taken along the line CC of FIGS. 1 and 4;

FIG. 7 is a partial plan view of the heat exchange unit of the first embodiment.

FIG. 8 is a schematic explanatory view of a communicating portion between the tank portions of the first embodiment.

FIG. 9 is a schematic perspective view illustrating a refrigerant passage configuration according to the first embodiment.

FIG. 10 is a cross-sectional view of a main part of a tank unit according to a second embodiment.

FIG. 11 is a sectional view of a main part of a tank section according to a third embodiment.

FIG. 12 is a sectional view of a main part of a tank unit according to a fourth embodiment.

FIG. 13 is a partial plan view of a heat exchange unit according to a fifth embodiment.

FIG. 14 is a sectional view of a main part of a tank unit according to a sixth embodiment.

FIG. 15 is a sectional view taken along the line DD of FIG. 14;

FIG. 16 is a sectional view taken along line EE of FIG. 14;

[Explanation of symbols]

2, 3, tube, 5 refrigerant inlet, 6 refrigerant outlet, 7 ~
10: tank part, 25: passage for drainage.

Claims (5)

[Claims] A tube (2, 3) forming a refrigerant passage extending in a vertical direction, and a tank (7-10) for distributing and collecting refrigerant to the tubes (2, 3) is provided in the tubes (7-10). 2, 3), and a plurality of rows of the tank portions (7 to 10) are arranged at both upper and lower ends of the tubes (2, 3) in the air flow direction (A). Tube insertion portion (1
The interval (a) between the plurality of rows of tank portions (7 to 10) in the portion corresponding to (4, 16) is changed to the interval (c) in another portion (24) not corresponding to the tube insertion portion (14, 16). ), And between the plurality of rows of tank portions (7 to 10),
A cooling heat exchanger, wherein a drain passage (25) is formed at least in a portion corresponding to the other portion (24). 2. A part (15, 17) of said plurality of rows of tank parts (7-10) forming said tube insertion part (14, 16) is integrally formed by one sheet metal part (13). And the other portion (2) in the sheet metal portion (13).
The cooling heat exchanger according to claim 1, wherein the drain passage (25) is partially opened at a location corresponding to (4). 3. A part corresponding to the tube insertion part (14, 16) is brought into contact with the plurality of rows of tank parts (7 to 10), and a part corresponding to the other part (24) is provided with the drainage part. 2. The cooling heat exchanger according to claim 1, wherein the passage is partially formed. 4. A portion (15, 17) of said plurality of rows of tank portions (7-10) forming said tube insertion portions (14, 16) is integrally formed by one sheet metal portion (13). In addition, the tank body portions (21, 22) of the plurality of rows of tank portions (7 to 10) are integrally formed of one plate material, and the sheet metal portion (13) and the tank body portions (21, 22) In the intermediate connecting portion (20, 29),
The cooling heat exchanger according to claim 1, wherein the drainage passage (25) is partially opened at a location corresponding to the other portion (24). 5. The multi-row tank section (7-10)
Communication means (26, 26a, 2
The evaporator according to any one of claims 1 to 4, wherein 7, 27a) are formed integrally.