JPH10238986A - Laminated heat-exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a laminated heat-exchanger having a fluid path in a tube sectioned into a plurality of subpaths by means of a center rib in which detection of internal leakage is facilitated by specifying the gap between thin metal plates being set by the center rib. SOLUTION: In case of an application to a coolant evaporator for car air- conditioner, a large number of tubes 2 being arranged in the evaporator are made by bonding two thin metal plates 4, 4. A windward coolant path 2a and a leeward coolant path 2b are formed in each tube 2 while being partitioned by a center rib 49. The coolant paths 2a, 2b are arranged with inner fins 53, 54 in order to enhance heat transfer performance on the coolant side. In this regard, the interval between the thin metal plates 4, 4 being set by the center rib 49 is set larger than those being set, respectively, by an outer circumferential rib 55 and the inner fins 53, 54 thus preventing internal leakage.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a laminated heat exchanger in which a tube as a fluid passage is formed by a laminated structure of thin metal plates, and more particularly, to a device in which a fluid passage inside a tube is divided into a plurality of passages. In this case, it is possible to easily find an internal leak in the partition.

[0002]

2. Description of the Related Art As a laminated heat exchanger of this type, the present applicant has previously disclosed in a patent application of Japanese Patent Application No. 8-182307 a refrigerant evaporator having a refrigerant flow path configuration shown in FIG. is suggesting. In the refrigerant evaporator 1 of the prior application, the inlet tanks 43 and 44 and the outlet tank 4
7 and 48, the refrigerant inlet side heat exchange part X is provided downstream of the air and the refrigerant outlet side heat is provided upstream of the air with respect to the flow of the blown air A which is absorbed and cooled by the refrigerant. An exchange part Y is formed as a partition.

In this evaporator 1, a tube through which a refrigerant flows is formed by joining two metal thin plates 4 shown in FIG. FIG. 7 is an exploded perspective view of the tube 2 made of a combination of the two thin metal plates 4. The refrigerant passage inside the tube 2 is divided by a center rib 49 into a refrigerant passage 2a on the windward side and a refrigerant passage 2b on the leeward side.

[0004] In the evaporator 1 having such a configuration, the refrigerant flows inside the evaporator 1 through the following path. That is, in FIG. 6, the refrigerant enters the first inlet tank part a of the lower inlet tank 44 from the refrigerant inlet pipe 8a via the refrigerant passage 15 on the side of the evaporator. Then, from the first inlet tank portion a, the refrigerant rises in the leeward refrigerant passage 2 b in the tube 2 and enters the upper inlet tank 43. Next, the refrigerant is supplied to the upper inlet tank 4.
3 and descends down the leeward refrigerant passage 2b in the tube 2 and enters the second inlet tank portion b of the lower inlet tank 44.

Next, the refrigerant flows from the second inlet tank b through the refrigerant passage 13 on the side of the evaporator to the first outlet tank 47 in the upper outlet tank 47.
It enters the outlet tank section c, from which it descends through the windward refrigerant passage 2a in the tube 2 and enters the lower outlet tank 48. Next, the refrigerant rises from the lower outlet tank 48 to the windward refrigerant passage 2 a in the tube 2 and enters the second outlet tank d of the upper outlet tank 47.

Next, the refrigerant flows from the second outlet tank d through the refrigerant passage 14 on the side of the evaporator to the refrigerant outlet pipe 8b, and flows out of the evaporator. In this way, for the flow of the blown air A, the refrigerant inlet side heat exchange section X is provided on the downstream side of the air,
In addition, a refrigerant outlet side heat exchange part Y is defined and formed on the upstream side of the air, and the flow direction of the refrigerant in the refrigerant inlet side heat exchange part X and the refrigerant outlet side heat exchange part Y is matched. That is, in FIG. 6, on the right side of the partitions 51 and 52, the refrigerant flow direction of the heat exchange sections X and Y is set to the upward direction, and on the left side of the partitions 51 and 52, the heat exchange sections X and
The refrigerant flow direction of Y is set to the downward direction.

With such a refrigerant passage configuration, even if the liquid-phase refrigerant and the gas-phase refrigerant of the gas-liquid two-phase refrigerant are unevenly distributed to the refrigerant passages 2a and 2b in the tube 2,
The temperature of the air discharged from the evaporator in the direction of the arrow A can be made uniform over the entire area of the evaporator 1.

[0008]

By the way, when the above-mentioned prior application was put to practical use, the inventors of the present invention actually examined the prototype and found that the following problems occurred in the production thereof. That is, in the above evaporator, the metal sheet 4
Is formed from an aluminum alloy, the metal thin plates 4 are laminated and assembled into a predetermined evaporator shape, and then the entire evaporator is integrally brazed in a furnace to produce the evaporator. At the time of this integral brazing, a center rib 4 that partitions the refrigerant passage inside the tube 2 into a refrigerant passage 2a on the leeward side and a refrigerant passage 2b on the leeward side.
When the brazing failure occurs at the portion 9, a short circuit of the passage occurs at this portion, and the two passages 2 a and 2 b are directly connected. Cannot flow, and the cooling performance of the evaporator is significantly reduced.

However, short-circuiting of the passage due to poor brazing at the portion of the center rib 49 causes the tube 2 to fail.
Since there is a short circuit (internal leakage) between the internal passages 2a and 2b, a leakage inspection for a normal external leakage (a leakage inspection gas is press-fitted into the internal passage of the evaporator, and a junction of the leakage inspection gas Inspection to measure the presence or absence of leakage from water) cannot be found.

[0010] The present invention has been made in view of the above points,
A stacked heat exchanger in which the tubes of the heat exchange section are formed by a laminated structure of thin metal plates, and the fluid passages in the tubes of the heat exchange section are divided into a plurality of passages by a center rib integrally formed with the thin metal plate. In addition to making the center rib part less likely to cause joint failure, even if the center rib part fails to join, internal leakage due to this joint failure can be easily found by ordinary external leakage inspection. The purpose is to do.

[0011]

In order to achieve the above object, according to the first aspect of the present invention, at least one of the two thin metal plates (4) has an outer peripheral edge rib (55) and a center rib (49). Is formed, and two metal thin plates (4) are joined at the portion of the outer peripheral edge rib (55) and the portion of the center rib (49) to form a tube (2). 49), the plurality of fluid passages (2a,
2b) and the plurality of fluid passages (2a,
2b), the inner fins (53, 54) are respectively arranged, a plurality of tubes (2) are stacked, and a center rib is formed in a stacked heat exchanger in which a plurality of fluid passages (2a, 2b) communicate with each other. The interval between the metal sheets set by (49) is made larger than the interval between the metal sheets set by the outer peripheral rib (55) and the interval between the metal sheets set by the inner fins (53, 54). Of the joints of the tube (2), the joint of the center rib (49) is preferentially brought into contact with the joint of the outer peripheral rib (55) and the joint of the inner fins (53, 54). It is characterized by doing.

According to the first aspect of the present invention, by setting the dimensions of each part of the tube (2) in the above relationship, the center rib (49) can be used when brazing after assembling the heat exchanger. , 49), there is no gap between the tops,
Since this portion can always be preferentially brazed, occurrence of the above-mentioned internal leakage can be prevented. If a gap is generated between the tops of the center ribs (49, 49) and a brazing failure occurs, the center ribs (49, 49) are removed.
Since a larger gap is generated in the outer peripheral ribs (55, 55) than in the 9) part, the outer peripheral ribs (55, 55)
5) Leakage from the inside of the tube to the outside, that is, external leakage always occurs due to the gap in the portion. Therefore, by performing a normal external leakage inspection, the outer peripheral rib 5
By measuring the leakage of the inspection gas from the gaps of the five parts, a product defect can be easily found.

According to a first aspect of the present invention, as in the second aspect, two outer peripheral ribs (55) are stamped and formed at the same height from the outer peripheral edges of the two thin metal plates (4, 4). The center rib (49) is composed of two ribs formed by stamping at the same height from the center of the two thin metal plates (4, 4).
9,49) height (H ₁₎ the height of each outer peripheral edge rib (55) as well as higher than (H _2), each center rib (4
This can be suitably performed by setting the height (H ₁ ) of 9) higher than １ ／ of the height (H ₃ ) of the inner fins (53, 54).

According to the third aspect of the present invention, at least one of the two metal sheets (4) has an outer peripheral edge rib (55),
Center ribs (49) and reinforcing ribs (56, 56a,
57, 57a), and a portion of the outer peripheral edge rib (55);
The center rib (49) and the reinforcing ribs (56, 5
6a, 57, 57a), the two metal sheets (4) are joined to form a tube (2), and the inside of the tube (2) is divided into a plurality of fluid passages (2a, 2a, 2a, 2a, 2a) by a center rib (49).
b) and reinforcing ribs (56, 56a, 5
7, 57a) are arranged so as to protrude into the plurality of fluid passages (2a, 2b), a plurality of tubes (2) are laminated, and the plurality of tubes (2a, 2b) communicate with each other. In the heat exchanger, the interval between the metal sheets set by the center rib (49) is set to the interval between the metal sheets set by the outer peripheral edge rib (55) and the reinforcing ribs (56, 56).
a, 57, 57a), the joint between the center ribs (49) of the joints of the tube (2) is larger than the joint between the outer peripheral ribs (55). And reinforcing ribs (56, 56a, 57, 57a)
It is characterized in that it comes into contact preferentially over the joint portion.

According to a third aspect of the present invention, as described above, instead of the inner fins (53, 54) in the first and second aspects, the reinforcing ribs (5) integrally formed on the thin metal plate (4) are provided.
6, 56a, 57, 57a), and even in the configuration using this reinforcing rib, the inside of the joint portion of the center rib (49) can be formed in the same manner as in claims 1 and 2 by the above-described dimension setting. Leak prevention and easy discovery in the event of an internal leak occurring can be achieved.

According to a third aspect of the present invention, the reinforcing ribs (56, 57) are configured such that the tops are joined to the inner wall surface of the metal thin plate (4) on the other side. can do. According to a third aspect of the present invention, the reinforcing ribs (56a, 57a) are set in the two metal thin plates (4) at positions opposed to each other, as in the fifth aspect.
The tops of the reinforcing ribs (56a, 57a) may be joined to each other.

Further, according to the present invention, the air blown to the outside of the tube (2) and the tube (2) are provided.
Heat exchange with the refrigerant of the refrigeration cycle flowing through the refrigerant passages (2a, 2b) in the inside, and the evaporator evaporates the refrigerant,
It can be suitably implemented. In addition, the code | symbol in parenthesis of the said each means shows the correspondence with the concrete means of embodiment described later.

[0018]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a block diagram showing a first embodiment of the present invention. (First Embodiment) FIGS. 1 to 8 show a first embodiment in which the evaporator of the present invention is applied to a refrigerant evaporator in a refrigeration cycle of an air conditioner for a vehicle.

FIGS. 1 and 2 show the overall structure of the evaporator 1. The evaporator 1 is installed in a cooling unit case (not shown) of a vehicle air conditioner with the vertical direction of FIGS. You. A pipe joint 8 is disposed at one end (right end) in the left-right direction of the evaporator 1, and an outlet pipe of a temperature-operated expansion valve (not shown) is provided at an inlet pipe 8 a of the pipe joint 8. The low-temperature low-pressure gas-liquid two-phase refrigerant, which is connected and decompressed and expanded by the expansion valve, flows in.

The evaporator 1 includes a plurality of tubes 2 arranged in parallel, and a heat exchange unit 3 for exchanging heat between a refrigerant flowing through a refrigerant passage in the tubes 2 and air-conditioning air flowing outside the tubes 2. ing. In the figure, the arrow A indicates the flow direction of the blown air. The tube 2 is formed by a laminated structure of a thin metal plate 4 shown in FIG. 3. Hereinafter, an outline of the laminated structure will be described. In the heat exchange unit 3, as the thin metal plate 4, for example, an aluminum core material (A3000 series) is used. 3) using a double-sided clad material (sheet thickness: about 0.4 to 0.6 mm) in which a brazing material (A4000 series material) is clad on both sides of this material and forming the double-sided clad material into a predetermined shape shown in FIG. A large number of tubes 2 are formed in parallel by laminating a large number of these as one set and joining them by brazing.

Accordingly, as shown in FIG. 7, each of the tubes 2 is formed by joining the thin metal plates 4 as a set and joining them in a middle state. The refrigerant passage 2a on the leeward side and the refrigerant passage 2b on the leeward side are formed in parallel along the longitudinal direction of the metal sheet.
The thin metal plate 4 shown in FIG. 3 is a basic thin plate constituting most of the tubes 2, and has communication holes 41 at upper and lower ends thereof for communicating between the refrigerant passages 2a and between the refrigerant passages 2b. , An inlet tank part 43 with 42
4, and an outlet tank part 4 having communication holes 45 and 46
7, 48 are formed side by side. These tank portions 43, 44, 47, 48 are each formed by an elliptic cylindrical projection projecting outward from the metal thin plate 4.

In this embodiment, the cross-sectional areas of the inlet tanks 43 and 44 are set smaller than the cross-sectional areas of the outlet tanks 47 and 48. Reference numeral 49 denotes a center rib that separates the refrigerant passage 2a on the windward side from the refrigerant passage 2b on the leeward side. In this example, the center rib partitions the refrigerant passage 2a and the refrigerant passage 2b to have the same width. Further, in the heat exchange section 3, a corrugated fin (fin means) 7 is joined to a gap between the outer surfaces of the adjacent tubes 2 to increase the heat transfer area on the air side. The corrugated fin 7 is formed into a corrugated aluminum bare material such as A3003 which is not clad with a brazing material.

A side plate 9 made of a thin metal plate located at one end (left end in FIG. 1, right end in FIG. 2) of the heat exchanging section 3 in the laminating direction of the thin metal plates, an end plate 10 joined to the side plate 9, and a metal In the present example, the side plate 11 made of a metal thin plate and the end plate 12 joined thereto at the other end (the right end in FIG. 1, the left end in FIG. 2) in the lamination direction are also the same as the metal thin plate 4 in this example. Similarly, it is formed from a double-sided clad material. However, these plate members 9, 10, 11, and 12 are made thicker than the metal thin plate 4, for example, a plate thickness of about 1.0 to 1.6 mm in order to secure strength.

As shown in FIGS. 4 and 5, the end plates 10, 12 have a plurality of overhangs 10a, 1
2a. The overhang portions 10a and 12a are shown in FIG.
Are formed in a rectangular cross section, and are formed in parallel along the longitudinal direction of the end plates 10 and 12.
Refrigerant passages (fluid passages) 13 and 15 are formed by spaces formed between the overhang portions 10a and 12a and the flat surfaces of the side plates 9 and 11. The specific role of the refrigerant passages (fluid passages) 13 and 15 will be described later with reference to FIG.

On the other hand, connecting portions 10b and 12b extending in a band shape are formed between the plurality of overhanging portions 10a and 12a, and the connecting portions 10b and 12b abut against the flat surfaces of the side plates 9 and 11, and It is joined to plates 9 and 11.
A tank portion 11a and a tank portion 11b are formed at upper and lower ends of the side plate 11 at the left end portion in FIG. 2, respectively.
1 is formed from a single elongated bowl-shaped part extending along the width direction of the first part, and a communication hole 11c is formed in the tank part 11a.
However, a communication hole 11d is formed in the tank portion 11b.

Refrigerant passage 1 formed by overhang 12a
The lower end of 3 is the tank 1 at the lower end of the side plate 11
It communicates with the communication hole 42 of the inlet tank 44 at the lower end of the thin metal plate 4 in FIG. 3 through the communication hole 11d of 1b. Also,
The upper end of the refrigerant passage 13 communicates with the communication hole 45 of the outlet tank 47 at the upper end of the thin metal plate 4 in FIG. 3 through the communication hole 11c of the tank 11a at the upper end of the side plate 11.

The side plate 9 at the left end of FIG.
Since it has substantially the same shape as the side plate 11 at the left end,
Detailed description is omitted. As shown in FIG. 1, the end plate 10 at the left end in FIG. 1 has the overhang 10a formed below the pipe joint 8 and another overhang 10c above the pipe joint 8. Are formed.
This another overhang 10c is different from the overhang 10a,
It is formed from one bowl-shaped part.

The portion between the overhanging portion 10c and the overhanging portion 10a is divided as a refrigerant passage. The space formed between the inside of the overhang portion 10c and the side plate 9 at the left end in FIG. 1 forms the refrigerant passage 14 (see FIG. 6). The refrigerant passage 14 communicates with the communication hole 45 of the upper outlet tank portion 47 of the thin metal plate 4 via the communication hole (not shown) of the outlet tank portion 9a of the side plate 9,
It communicates with the refrigerant outlet pipe 8b of the piping joint 8. The upper end of the refrigerant passage 15 constituted by the lower projecting portion 10a communicates with the refrigerant inlet pipe 8a of the pipe joint 8, and the lower end of the refrigerant passage 15 communicates with the communication hole of the inlet tank 9b of the side plate 9. (Not shown) through metal sheet 4
Communicates with the communication hole 42 of the lower inlet tank 44.

Here, the shapes of the outlet tank portion 9a and the inlet tank portion 9b of the side plate 9 are not clearly shown in FIG.
a, 11b. The pipe joint 8 is formed by integrally forming a refrigerant inlet pipe 8a and a refrigerant outlet pipe 8b with an aluminum bear material of A6000 series, for example. (Not shown) and brazed. Refrigerant inlet pipe 8a of this piping joint 8
As described above, the outlet side refrigerant pipe of the expansion valve (not shown) is connected to the refrigerant outlet pipe 8b.
Is connected to a compressor suction pipe for sucking the gas refrigerant evaporated in the above into a compressor (not shown).

FIG. 6 is a schematic diagram showing the configuration of the refrigerant passage in the evaporator 1 and is prepared corresponding to the state shown in FIG. In the middle of the lower inlet tank part 44 and the middle of the upper outlet tank part 47 of the metal sheet 4,
1, 52 are provided. The one partition part 51 is a thin metal plate, and the communication hole 4 of the lower inlet tank part 44 shown in FIG.
It can be formed by using a material in which 2 is closed. In addition, the other partition part 52 can be formed by using a metal sheet having a closed communication hole 45 of the upper outlet tank part 47 shown in FIG.

Due to the arrangement of the partitions 51 and 52, the lower inlet tank 44 of the thin metal plate 4 is connected to the first inlet tank a.
And the second inlet tank b, and the metal sheet 4
Can be partitioned into a first outlet tank portion c and a second outlet tank portion d. As described above, the refrigerant flows through the evaporator 1 from the refrigerant inlet pipe 8 a to the refrigerant passage 15.
→ The first inlet tank part a of the lower inlet tank part 44 → the refrigerant passage 2b of the tube 2 → the upper inlet tank part 43 → the refrigerant passage 2b of the tube 2 → the second inlet tank part b of the lower inlet tank part 44 → the refrigerant Passage 13 → First of upper outlet tank part 47
The outlet tank c → the refrigerant passage 2a of the tube 2 → the lower outlet tank 48 → the refrigerant passage 2a of the tube 2 → the second outlet tank d of the upper outlet tank 47 → the refrigerant passage 14 → the refrigerant outlet pipe 8b. Flows.

As described above, by forming the refrigerant path, the temperature of the air flowing out in the direction of arrow A and blown out from the evaporator can be made uniform over the entire area of the heat exchange section 3. The manufacturing method of the refrigerant evaporator according to the present embodiment will be briefly described. First, the thin metal plate 4, the corrugated fin 7, the side plates 9, 1
1, and the end plates 10 and 12 are laminated, and further, the piping joint 8 is assembled to the end plate 10 and assembled to a predetermined heat exchanger structure shown in FIGS.

Next, the assembled body of the heat exchanger structure is tightened from the outside of the end plates 10 and 12 by the wires 60 and 61 extending in the laminating direction of the thin metal plates 4 to maintain the assembled posture of the assembled body. . Next, in a state where the assembly posture is maintained, the assembly is carried into the brazing furnace, and the assembly is heated to the melting point of the brazing material of the aluminum double-sided clad material in the brazing furnace. Then, the joint of each part of the assembly is brazed together. Thereby, the assembly of the entire evaporator 1 is completed.

By the way, in the present embodiment, it is possible to find an internal leak caused by poor brazing at the center rib 49 that partitions the refrigerant passage inside the tube 2 into the refrigerant passage 2a on the upstream side and the refrigerant passage 2b on the leeward side. In order to do so, the following ideas have been devised. FIG. 8 is a cross-sectional view of the tube 2 in the air flow direction A (a direction perpendicular to the tube longitudinal direction). In the example of FIG. 8, the windward-side refrigerant passage 2 a and the leeward-side refrigerant passage 2 b in the tube 2 have corrugated shapes. The inner fins 53 and 54 are formed to improve the heat transfer performance on the refrigerant side, and the inner fins 53 and 54 extend in the thickness direction of the passage of the tube 2 (the left-right direction in FIG. 8).
Reinforced by 54. Here, the inner fin 5
3 and 54 are also formed of an aluminum alloy, for example, an aluminum bare material such as A3003 which is not clad with a brazing material, and is joined to the inner wall surface of the thin metal plate 4 constituting the tube 2.

The outer peripheral ribs 55 are formed on the outer peripheral portions of the two metal thin plates 4 constituting the tube 2 at the same height over the entire outer periphery thereof. And
The launch height of the center rib 49 is H ₁ , and the outer peripheral rib 5
Assuming that the launch height of No. 5 is H ₂ and the height of the inner fins 53 and 54 is H ₃ , the dimensions of each part of the tube 2 are set as follows.

The interval (2 × H ₁ ) between the metal sheets 4, 4 set by the center ribs 49, 49
The interval between the metal sheets 4, 4 set by 5, 55 (2
× H ₂ ) and the distance (H ₃ ) between the metal sheets 4, 4 set by the inner fins 53, 54. That is, the tube 2 is set so as to satisfy the relations of (2 × H ₁ )> (2 × H ₂ ) and (2 × H ₁ )> H _3.
The dimensions of each part are set.

Here, as a specific design example of each of the above dimensions, H ₁ = 0.92 mm, H ₂ = 0.87 mm, H ₃
= 1.76 mm. Therefore, in the case of this design example,
(2 × H ₁ )> H ₃ > (2 × H ₂ ). As described above, (2 × H ₁ )> (2 × H ₂ ) and (2 × H ₁ )
By setting the dimensions of each part of the tube 2 in a relationship of H ₁ )> H ₃ , when the assembly of the evaporator is completed, the tube 2
Of the two thin metal plates 4, 4, the top of the inner fins 53, 54 and the inner wall surfaces of the thin metal plates 4, 4, and the top of the outer peripheral ribs 55, 55 are joined to each other On the other hand, the joints between the tops of the center ribs 49 always contact with priority.

Accordingly, when the evaporator is assembled and carried into the brazing furnace for brazing, no gap is formed between the tops of the center ribs 49, 49, and this part must be given priority. Therefore, the occurrence of the above-described internal leakage can be prevented. If a gap is generated between the tops of the center ribs 49, 49 and brazing failure occurs,
Outer edge ribs 55, 55 than center ribs 49, 49
Since a larger gap is generated at the portion, leakage from the inside of the tube to the outside, that is, external leakage always occurs due to the gap between the outer peripheral edge ribs 55, 55. Therefore, by performing a normal external leakage inspection, the leakage of the inspection gas from the gap of the outer peripheral rib 55 is measured.
Product defects can be easily found. Therefore, it is possible to reliably prevent a product having a fatal defect such as an internal leak from being supplied to the market in advance.

(Second Embodiment) FIG. 9 shows a second embodiment. In the first embodiment, the tube 2 is used.
Although the case where the inner fins 53 and 54 formed in a wavy shape are arranged in the windward-side refrigerant passage 2a and the leeward-side refrigerant passage 2b in the inside has been described, the inner fins 53 and 54 are eliminated, and instead, As shown in FIG. 9, reinforcing ribs 56 and 57 projecting into the leeward side refrigerant passage 2a and the leeward side refrigerant passage 2b are integrally formed on the two thin metal plates 4 and 4 constituting the tube 2, respectively.

In the present embodiment, the reinforcing ribs 56 and 57 are formed of small projections each having a U-shaped cross section, and are provided in a large number in the refrigerant flow direction of the upstream-side refrigerant passage 2a and the leeward-side refrigerant passage 2b. Flows between the reinforcing ribs 56 and 57 to improve the heat transfer performance on the refrigerant side. In the state after the heat exchanger brazing, the reinforcing ribs 56, 5
The tube 2 is reinforced by joining the tops of the tubes 7 to the inner wall surfaces of the metal sheets 4, 4 on the other side.

Also in the second embodiment, the reinforcing ribs 56,
When the height of 57 is H ₄ , the center ribs 49, 49
(2 × H ₁ )
The metal sheet 4, which is set by the outer peripheral ribs 55, 55,
The distance (2 × H ₂ ) between the metal sheets 4 and the distance (H ₄ ) set by the reinforcing ribs 56 and 57 are larger than the distance between the metal sheets 4 and 4 (H ₄ ).

That is, (2 × H ₁ )> (2 × H ₂ ),
The dimensions of each part of the tube 2 are set so as to satisfy the relationship of (2 × H ₁ )> H ₄ . As a result, of the joint portions of the two metal sheets 4 forming the tube 2,
The joint between the tops of the center ribs 49, 49 is always the same as the joint between the tops of the reinforcing ribs 56, 57 and the inner wall surfaces of the thin metal plates 4, 4, and the joint between the tops of the outer peripheral ribs 55, 55. The contact comes preferentially, and the same operation and effect as in the first embodiment can be exhibited.

As a specific design example of each of the above dimensions, H ₁ = 0.92 mm, H ₂ = 0.87 mm, and H ₄ =
1.76 mm. Therefore, in the case of this design example,
(2 × H ₁ )> H ₄ > (2 × H ₂ ). (Third Embodiment) FIG. 10 shows a third embodiment. In the above-described second embodiment, two metal sheets 4 constituting a tube 2 are provided on the inner wall surfaces of the other metal sheet, respectively. reinforcing ribs 5 having only the height H ₄ may bonded to
In the third embodiment, the reinforcing ribs 56a and 57a are set at opposing portions of the two thin metal plates 4 and 4, respectively.
The top portions 7a are joined to each other.

Also in the third embodiment, the reinforcing ribs 56
a, when the height of 57a was H _5, the center rib 4
The distance between the metal sheets 4 and 4 (2
× H ₁₎ distance between the metal sheet 4, 4 which are set by the outer peripheral edge rib 55 a ₍₂ × H 2) and the reinforcing ribs 56
The distance between the metal thin plates 4 and 4 (2 × H ₅ ), which is set by a and 57a, is larger than that.

That is, (2 × H ₁ )> (2 × H ₂ ),
The dimensions of each part of the tube 2 are set so as to satisfy the relationship of (2 × H ₁ )> (2 × H ₅ ). Thereby, of the joining portions of the two thin metal plates 4 constituting the tube 2, the joining portions between the top portions of the reinforcing ribs 56a and 57a and the joining portions between the top portions of the outer peripheral ribs 55 and 55 are formed. The center ribs 49, 49 are always brought into close contact with each other at the tops, and the same operation and effect as in the first embodiment can be exhibited.

As a specific design example of each of the above dimensions, H ₁ = 0.92 mm, H ₂ = 0.87 mm, and H ₅ =
0.88 mm. Therefore, in the case of this design example,
(2 × H ₁ )> (2 × H ₅ )> (2 × H ₂ ). (Other Embodiments) The essential part of the present invention lies in the prevention of internal leakage at the partitioning portion and the easy detection of the internal leakage by the center ribs 49, 49. Various modifications are possible without being limited to the example shown in FIG.

In the metal sheet 4 of FIG. 3, the center rib 49 is set at the center of the metal sheet in the width direction, and
Although the widths of a and 2b are set to be the same, the center rib 49 may be set at a position shifted left and right from the center in the width direction of the metal sheet. In the first to third embodiments described above, the center ribs 49, 49 and the outer peripheral edge ribs 55, 5
5 are formed on the two metal sheets 4, 4, respectively, and the tops of the center ribs 49, 49 and the outer peripheral edge ribs 55, 55 are formed.
Of the reinforcing ribs 56, 5 in FIG.
7, a center rib 49 and an outer peripheral rib 55 are formed on only one of the two thin metal plates 4 and 4 so that the center rib 49 and the outer peripheral rib 55 are respectively formed in the metal thin plate 4 on the other side. The present invention can be implemented even if it is joined to a wall surface.

The present invention is not limited to a refrigerant evaporator, but can be widely applied to heat exchangers for performing heat exchange of various fluids.

[Brief description of the drawings]

FIG. 1 is a perspective view of an evaporator to which the present invention is applied.

FIG. 2 is a perspective view of the evaporator of FIG. 1 as viewed from a side opposite to an air flow direction A.

FIG. 3 is a front view of a thin metal plate for a tube used in the evaporator of FIG. 1;

FIG. 4 is an enlarged view of a portion B in FIGS.

FIG. 5 is a sectional view taken along the line CC of FIGS. 1 and 2;

FIG. 6 is a schematic perspective view showing a refrigerant passage configuration in the evaporator of FIG. 1;

FIG. 7 is an exploded perspective view of a tube portion in the evaporator of FIG.

FIG. 8 is a sectional view of a tube portion showing the first embodiment of the present invention.

FIG. 9 is a sectional view of a tube portion showing a second embodiment of the present invention.

FIG. 10 is a sectional view of a tube part showing a third embodiment of the present invention.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Evaporator, 2 ... Tube, 2a ... Upwind side refrigerant passage, 2
b ... leeward side refrigerant passage, 4 ... thin metal plate, 49 ... center rib, 53, 54 ... inner fin, 55 ... outer peripheral edge rib,
56, 56a, 57, 57a ... reinforcing ribs.

Claims (6)

[Claims] An outer peripheral rib (55) and a center rib (49) are formed on at least one of two metal thin plates (4), and a portion of the outer peripheral rib (55) and the center rib (49) are formed. ), The two metal sheets (4) are joined to form a tube (2), and the inside of the tube (2) is partitioned into a plurality of fluid passages (2a, 2b) by the center rib (49). With
Inner fins (53, 54) are respectively arranged in the plurality of fluid passages (2a, 2b), a large number of the tubes (2) are stacked, and communication is established between the plurality of fluid passages (2a, 2b). A distance between the metal sheets set by the center rib (49), a distance between the metal sheets set by the outer peripheral edge rib (55), and the inner fins (53, 54). )
The joint between the center rib (49) and the joint between the outer peripheral rib (55) and the inner A stacked heat exchanger characterized in that the fins (53, 54) abut preferentially at the joints. 2. The outer peripheral edge rib (55) is composed of two ribs stamped and formed at the same height from the outer peripheral edges of the two thin metal plates (4). Two metal sheets (4)
2 stamped and formed at the same height from the center of
A height (H ₁ ) of each of the center ribs (49) is higher than a height (H ₂ ) of each of the outer peripheral edge ribs (55); and a height of each of the center ribs (49). 2. The stacked heat exchanger according to claim 1, wherein the height (H ₁ ) is higher than １ ／ of the height (H ₃ ) of the inner fins (53, 54). 3. An outer peripheral rib (55), a center rib (49) and a reinforcing rib (56, 56a, 57, 57a) are formed on at least one of the two thin metal plates (4). 55), the center rib (4
9) and the reinforcing ribs (56, 56a, 57,
At the portion 57a), the two metal sheets (4) are joined to form a tube (2), and the inside of the tube (2) is partitioned into a plurality of fluid passages (2a, 2b) by the center rib (49). With
The reinforcing ribs (56, 56a, 57, 57a) are disposed so as to protrude into the plurality of fluid passages (2a, 2b), and a plurality of the tubes (2) are stacked, and the plurality of fluid passages (2a 2b) a laminated heat exchanger for communicating with each other, wherein a distance between metal sheets set by the center rib (49) is set to a distance between metal sheets set by the outer peripheral edge rib (55). And the reinforcing ribs (56, 56a, 5
7, 57a), the distance between the metal sheets is larger than the distance between the metal sheets, and among the joints of the tube (2), the joint of the center rib (49) is closer to the outer peripheral edge rib (5).
5) and the reinforcing ribs (56, 56a, 5
7. A stacked heat exchanger characterized in that it comes into contact with a junction portion of (7, 57a) preferentially. 4. The laminated mold according to claim 3, wherein the reinforcing ribs (56, 57) are configured such that the tops thereof are joined to the inner wall surface of the counterpart thin metal plate (4). Heat exchanger. 5. The reinforcing ribs (56a, 57a) are set at portions of the two thin metal plates (4) facing each other, and the tops of the reinforcing ribs (56a, 57a) are joined to each other. The stacked heat exchanger according to claim 3, wherein: 6. A laminated heat exchanger according to claim 1, which exchanges heat between air blown out of said tube (2) and a refrigerant of a refrigeration cycle. An evaporator for evaporating the refrigerant, wherein the plurality of fluid passages (2a, 2a,
One of b) is a leeward refrigerant passage (2a), the other is a leeward refrigerant passage (2b), and the longitudinally opposite ends of the tube (2) are provided with the leeward refrigerant passage (2a). 2a) tank portions (43, 44, 44) for communicating between each other and between the leeward side refrigerant passages (2b).
47, 48) are formed.