JP2000055573A - Refrigerant evaporator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To restrict an increasing of pressure loss at a refrigerant side while an effect of unifying a blowing air temperature of an evaporator is being maintained. SOLUTION: Heat exchanging core sections A to D having refrigerant flow passages by tubes 2 to 5 are divided into an air flowing direction Z and its right angle crossing direction, respectively. The heat exchanging core sections A, C across the air flowing direction Z are directly communicated by a first communicating hole 20, and the heat exchanging core sections B, D at the other side across the air flowing direction Z are directly communicated through the second communication hole 21. Refrigerant flow flowed from the refrigerant inlet 7 is divided into two flows, one of the divided flows is flowed to the heat exchanging core sections A, C through the first communicating hole 20, and the other divided refrigerant flow is flowed to the heat exchanging core sections B, D at the other side through the second communicating hole 21.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

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

[0002]

2. Description of the Related Art The present applicant has previously disclosed in Japanese Patent Laid-Open No. 9-1708.
No. 50 proposes a refrigerant evaporator having a refrigerant flow path configuration shown in FIG. This conventional refrigerant evaporator 1
, The inlet tanks 50, 51
And the outlet tanks 52 and 53 are formed, and the refrigerant inlet side heat exchange section X is provided downstream of the air with respect to the flow direction Z of the blown air.
Further, a refrigerant outlet side heat exchange portion Y is defined on the upstream side of the air.

In this evaporator 1, a thin metal plate is
The tubes (refrigerant passages) are formed by joining them in the middle of the sheets, and the tanks 50 to 53 are integrally formed by bowl-shaped projections at both ends of the thin metal plate. In the evaporator 1 having such a configuration, the refrigerant flows inside the evaporator 1 through the following path. That is, in FIG. 14, the refrigerant is
Refrigerant inlet 54a of pipe joint 54 → side refrigerant passage 55 → first inlet tank 51a of lower inlet tank 51 →
Downstream refrigerant passage in tube → upper inlet tank 50 →
The leeward refrigerant passage in the tube → the second inlet tank portion 51b of the lower inlet tank 51 → the side refrigerant passage 56 → the first outlet tank portion 52a of the upper outlet tank 52 → the leeward refrigerant passage in the tube → the lower outlet tank The refrigerant flows through a path of 53 → windward refrigerant passage in the tube → second outlet tank portion 52b of the upper outlet tank 52 → side refrigerant passage 57 → refrigerant outlet 54b, and flows out of the evaporator.

In the above-described refrigerant path, the partition 5
8 and 59, the refrigerant flow direction of both heat exchange portions X and Y is set to the upper direction, and the left side of partition portions 58 and 59 is set to the refrigerant flow direction of both heat exchange portions X and Y to the lower direction. And the flow direction of the refrigerant to the tank portion in the refrigerant inlet side heat exchange portion X is a direction from right to left, and the refrigerant flow to the tank portion in the refrigerant outlet side heat exchange portion Y. The direction is from left to right, and the flow direction of the refrigerant in the tank section is reversed left and right in both heat exchange sections X and Y.

[0005] In the refrigerant passage in which the refrigerant flows upward from below, a large amount of liquid refrigerant flows into the deep portion of the tank portion due to the inertial force of the flow of the gas-liquid two-phase refrigerant, and the liquid refrigerant at the near side of the tank portion. A region where the refrigerant is insufficient occurs in the region. vice versa,
In the refrigerant passage in which the refrigerant flows from above to below, the gas-liquid two-phase refrigerant is affected by gravity, so that a large amount of liquid refrigerant flows into the near side of the tank part, and there is a shortage of the refrigerant in the area on the back side of the tank part. An area occurs.

As described above, 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 in the tube 2, according to the refrigerant passage configuration, both heat exchange units Since the flow direction of the refrigerant in the tank section is reversed in the left and right directions in X and Y, the uneven distribution of the refrigerant can be offset before and after the air flow direction Z, and the temperature of the air blown out from the evaporator can be reduced over the entire area of the evaporator 1. Instead, it can be made uniform.

[0007]

According to the above prior art, the total flow rate of the refrigerant to the evaporator flows in series through the four refrigerant passages, so that the passage length is originally long. Therefore, in order to improve the mountability in the air conditioning case and reduce the pressure loss on the air side, if the width dimension in the air flow direction Z is to be reduced (thinned), in addition to the long passage length, The passage cross-sectional area decreases, and the refrigerant side pressure loss in the evaporator increases. In particular, in the tank portion through which the total flow rate of the refrigerant in the evaporator flows and the side refrigerant passages 55 to 57 on the side surface of the evaporator, the increase in the pressure loss due to the decrease in the passage cross-sectional area becomes remarkable.

If the compressor suction capacity is the same, an increase in refrigerant side pressure loss in the entire evaporator causes an increase in refrigerant evaporation pressure and an increase in refrigerant evaporation temperature, which causes a decrease in the cooling performance of the evaporator. Therefore, as the evaporator becomes thinner, the performance drop due to an increase in pressure loss becomes remarkable, and this is a major obstacle to the thinning. The present invention has been made in view of the above point, and an object of the present invention is to suppress an increase in pressure loss on the refrigerant side while maintaining an equalizing effect of the evaporator blown air temperature.

[0009]

In order to achieve the above object, according to the present invention, the tubes (2-5) are provided.
Heat exchange core portions (A, B, C,
D) the air flow direction (Z) and the air flow direction (Z)
And a first communication hole (A, C) which is located on one side in the direction orthogonal to the air flow direction (Z) and directly communicates the heat exchange cores (A, C) in the front and rear directions of the air flow direction (Z). 2
0) and a second communication hole (21) located directly on the other side in the direction perpendicular to the air flow direction (Z) and directly communicating the heat exchange core portions (B, D) in the front and rear directions of the air flow direction (Z). Is provided on the partition wall (23) of the tank portion (9-15), and the refrigerant flow from the refrigerant inlet (7) is divided into two flows in a direction orthogonal to the air flow direction (Z). One,
The first and second heat exchange cores (A, C) located on one side in the direction orthogonal to the air flow direction (Z) flow through the first communication hole (20), and the other of the two refrigerant flows flows in the air flow direction. (Z)
It flows through the second communication hole (21) to the front and rear heat exchange core portions (B, D) located on the other side in the direction perpendicular to the direction.

According to this, as shown in FIGS. 3 and 13, the refrigerant from the refrigerant inlet (7) is divided into two, and two refrigerant flow paths divided in a direction orthogonal to the air flow direction (Z). , The refrigerant flow path length in the evaporator is reduced by half compared to the prior art shown in FIG.
It suffices to flow only 1/2 of the total flow rate of the refrigerant through the parallel flow paths.

In addition, first and second communication holes are provided between the heat exchange core portions (A, C) and the heat exchange core portions (B, D) located before and after in the air flow direction Z, respectively. (20,
21), the refrigerant flow paths before and after in the air flow direction can be directly connected without the need for the side refrigerant passages (55 to 57) as in the prior art shown in FIG. Therefore, the side refrigerant passage (55-55) in the prior art
57) can be abolished.

[0012] In combination with the above, the refrigerant-side pressure loss of the entire evaporator can be greatly reduced. By reducing the pressure loss on the refrigerant side, the refrigerant evaporation pressure can be lowered to lower the refrigerant evaporation temperature, and as a result, the cooling performance of the evaporator can be improved. Further, even in a configuration in which the refrigerant flows in parallel through two flow paths divided in the direction perpendicular to the air flow direction (Z),
Nonuniform distribution of the liquid refrigerant before and after the air flow direction can be canceled out to achieve a uniform evaporator blown air temperature.

Moreover, the elimination of the side refrigerant passage eliminates the necessity of the components of the side refrigerant passage, thereby simplifying the structure of the evaporator and reducing the manufacturing cost. Specifically, in the present invention, the flow of the refrigerant from the refrigerant inlet (7) into the tank portions (9, 11) on the refrigerant inlet side among the tank portions (9 to 15) is described. With the configuration including the dividing means (16, 17) for dividing into two flows in the direction perpendicular to the air flow direction (Z), the division of the refrigerant flow can be achieved.

According to a third aspect of the present invention, of the tank sections (9 to 15), the tank section (9, 1) on the refrigerant inlet side is provided.
1) is divided in a direction orthogonal to the air flow direction (Z), and a refrigerant inlet (7) is disposed at an intermediate position between the tank portions (9, 11) on the refrigerant inlet side. You may make it flow directly into the tank part (9, 11) at the refrigerant | coolant inlet side divided | segmented in the direction orthogonal to the air flow direction (Z).

The reference numerals in parentheses of the above means indicate the correspondence with the specific means described in the embodiment described later.

[0016]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to the drawings. (First Embodiment) FIG. 1 shows a first embodiment in which the present invention is applied to a refrigerant evaporator in a refrigeration cycle of an automotive air conditioner, and shows an outline of the entire configuration of the evaporator.
The evaporator 1 is installed in an air conditioning unit case (not shown) of a vehicle air conditioner with the vertical direction of FIG.
Air is blown to the evaporator 1 in the direction of arrow Z by a blower (not shown), and the blown air (external fluid) exchanges heat with the refrigerant.

The evaporator 1 has tubes 2, 3, 4, and 5 arranged in two rows in the air flow direction Z. Here, A to D in parentheses attached to reference numerals 2 to 5 of the tubes correspond to heat exchange core parts A to D shown in FIG. Each of these tubes 2 to 5 is a flat tube constituting a refrigerant passage having a flat cross section, and has an inner fin 6 inserted therein. A large number of tubes 2 to 5 are arranged in parallel in the direction perpendicular to the air flow direction Z.
Here, the first tubes 2 and 3 on the downstream side of the air constitute a refrigerant passage of the refrigerant inlet side heat exchange section X, and the second tubes 4 and 5 on the upstream side of the air constitute the refrigerant outlet side heat exchange section Y. Of the refrigerant passage.

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 7. The refrigerant outlet 8 is connected to a compressor suction pipe (not shown), and is for returning the gas refrigerant evaporated in the evaporator 1 to the compressor suction side. In this example, the refrigerant inlet 7 and the refrigerant outlet 8 are arranged adjacent to the upper left portion of the evaporator 1, and the refrigerant inlet 7 communicates with the inlet-side tank portion 9 located on the upper left side. Also,
The refrigerant outlet 8 communicates with an upper outlet side tank portion 15.

Here, the tank sections 9 to 15 of the evaporator 1 will be specifically described.
For distributing the refrigerant to the tubes or collecting the refrigerant from the tubes 2 to 5, and arranged in two rows in the air flow direction Z corresponding to the first tubes 2, 3 and the second tubes 4, 5. Have been. That is, as shown in FIG. 2, the inlet-side tank portions 9 to 12 are located on the downstream side of the air flow, and the outlet-side tank portions 13 to 15 are located on the upstream side of the air flow.

A flow path dividing partition plate 16 is disposed between the upper inlet side tank portions 9 and 11. As shown in FIG. 8 described later, the partition plate 16 has a triangular opening 1 opening half the cross-sectional area of the inlet-side tanks 9 and 11.
The triangular opening 16a allows the left and right inlet side tanks 9 and 11 to communicate with each other with a half sectional area.

A partition plate 17 for dividing the inside of the tank flow path into two sections is disposed in the upper left inlet side tank portion 9 through the center of the circular opening of the refrigerant inlet 7. As shown in FIG. 9 described later, the partition plate 17 is arranged diagonally with respect to the rectangular flow path cross section in the inlet-side tank portion 9, and the upper space in the inlet-side tank portion 9 is a partition plate. It communicates with the inside of the right inlet side tank portion 11 through the 16 triangular openings 16a. Therefore, in the present embodiment, the dividing means for dividing the refrigerant flow from the refrigerant inlet 7 into the flows to the two inlet-side tank portions 9 and 11 (that is, the two flows in the direction perpendicular to the air flow direction Z) is described above. Two types of partition plates 1
6 and 17.

Partition plates 18 and 19 having no openings are arranged between the lower inlet side tank portions 10 and 12 and between the lower outlet side tank portions 13 and 14, respectively. By the partition plates 18 and 19, the space between the lower inlet tank portions 10 and 12 and the lower outlet tank portion 13 are formed.
And 14 are completely separated from each other. On the other hand, the upper outlet-side tank portion 15 forms one flow path over the entire width of the evaporator 1 without a partition.

On the other hand, a partition wall 2 between the lower tank section 10 and the lower tank section 13 is provided between the two tank sections.
3 through a communication hole 20 penetrating therethrough. In addition, between the lower inlet side tank portion 12 and the outlet side tank portion 14,
Communication hole 2 penetrating partition wall 23 between the two tank portions
1 communicates. Here, the communication hole 20 is located at the left end of the tank portions 10 and 13 that is closest to the refrigerant ports 7 and 8. The communication hole 21 is located at the left end of the tank portions 12 and 14 that is closest to the partition plates 18 and 19.

In the air flow direction Z, between the upper inlet tanks 9 and 11 and the outlet tank 15 adjacent to each other, and between the lower inlet tanks 10 and 12 and the outlet tanks 13 and 14 adjacent to each other. Are divided by partition walls 22 and 23 extending over the entire length of the evaporator 1 in the width direction. These partition walls 22, 23 are formed integrally with the tank portions 9 to 15, as described later.

In the refrigerant inlet side heat exchange section X, one end (upper end) of the left tube 2 is connected to the upper inlet side tank section 9.
And the other end (lower end) is the lower inlet side tank 1
It communicates with 0. Similarly, one end (upper end) of the right tube 3 communicates with the upper inlet-side tank 11, and the other end (lower end) communicates with the lower inlet-side tank 12.

In the refrigerant outlet heat exchange section Y, one end (upper end) of the left tube 4 communicates with the upper outlet tank 15 and the other end (lower end) connects with the lower outlet tank. It communicates with the part 13. Similarly, the right tube 5
Has one end (upper end) communicating with the upper outlet side tank portion 15, and the other end (lower end portion) communicating with the lower outlet side tank portion 14.

Corrugated fins (outer fins) 24 each having a corrugated shape are arranged between the tubes 2 to 5.
And is integrally joined to the flat surface. In addition, each tube 2-5
The inner fin 6 inserted into the inside is formed into a corrugated shape (see FIG. 5 described later), and the top of the corrugated shape of the inner fin 6 is joined to the inner wall surface of each tube to reinforce each of the tubes 2 to 5. In addition, the heat transfer area on the refrigerant side is increased. Note that the entire evaporator 1 shown in FIG. 1 is integrally joined and assembled by brazing as described later.

Next, the operation of the first embodiment in the above configuration will be described. First, a low-temperature low-pressure gas-liquid two-phase refrigerant decompressed by an expansion valve (not shown) is first supplied from the refrigerant inlet 7 to the upper tank section on the downstream side of the air. 9 flows into. At this time, the refrigerant inlet 7
The cross section of the circular flow path and the cross section of the rectangular flow path in the inlet-side tank portion 9 are divided into two by the partition plate 17 arranged obliquely. The upper space is divided into two.

The refrigerant that has flowed into the lower space of the partition plate 17 as shown by an arrow a in FIG. 1 is then distributed to a plurality of tubes 2 and flows down the tubes 2 as shown by an arrow b. Thereafter, the refrigerant flows leftward in the lower tank portion 10 toward the communication hole 20 as shown by an arrow c, and then flows into the communication hole 2.
0 flows as shown by an arrow d, moves from the downstream side of the air to the upstream side of the air, and flows into the lower tank portion 13.

Next, an arrow e indicates the inside of the lower tank portion 13.
Flows to the right like, and is distributed to a plurality of tubes 4,
The tube 4 flows upward as indicated by an arrow f. Then, the refrigerant flows into the upper tank portion 15, flows leftward in the tank portion 15 as shown by an arrow g, and flows out of the evaporator 1 from the refrigerant outlet 8. On the other hand, the refrigerant flowing from the refrigerant inlet 7 into the space above the partition plate 17 flows into the right inlet side tank portion 11 through the triangular opening 16a of the partition plate 16 as shown by an arrow h. Next, the tank 11
Is distributed to a plurality of tubes 3 from the
Flows downward as indicated by the arrow i, and flows into the lower tank portion 12. Next, the refrigerant flows to the left side in the tank portion 12 toward the communication hole 21 as shown by an arrow j.

Then, the air passes through the communication hole 21 as shown by an arrow k, moves from the downstream side of the air to the upstream side of the air, and flows into the lower tank portion 14 on the upstream side of the air. Next, the refrigerant flows in the lower tank portion 14 to the right as shown by an arrow m,
It is distributed to a plurality of tubes 5 and flows upward through the tubes 5 as indicated by an arrow n. The refrigerant flows into the right side portion of the upper tank portion 15 and collects. Next, the refrigerant flows from the right side to the left side in the upper tank portion 15 as shown by the arrow p, merges with the refrigerant from the tube 4 described above, and flows out of the evaporator 1 from the refrigerant outlet 8.

On the other hand, the blown air (conditioned air) is blown in the direction of the arrow Z and passes through the gap of the heat exchange core portion constituted by the tubes 2 to 5 and the corrugated fins 19.
At this time, the refrigerant in the tubes 2 to 5 absorbs heat from the blown air and evaporates, so that the blown air is cooled and becomes cool air, and the cool air is blown into the vehicle interior to cool the vehicle interior.

In the evaporator 1, the refrigerant from the refrigerant inlet 7 is divided into two by the partition plates 16 and 17, and the refrigerant flows of arrows a to g and the refrigerant flows of arrows h to p are formed in parallel. Therefore, the length of the refrigerant flow path in the evaporator 1 is reduced by half as compared with the prior art shown in FIG. 14, and it is only necessary to flow the refrigerant by half of the total flow through this parallel flow path.

In addition, between the tanks 10 and 13 located before and after in the air flow direction Z and between the tanks 12 and 14
Are directly communicated by the communication holes 20 and 21 formed in the partition wall 23, so that the side refrigerant passages 55 to 57 are not required as in the prior art shown in FIG. Refrigerant channels can be connected. Therefore, the side refrigerant passages 55 to 57 in the related art can be eliminated.

In combination with the above, the refrigerant-side pressure loss of the entire evaporator can be greatly reduced. Therefore, the elimination of the side refrigerant passages 55 to 57 makes it possible to simplify the overall configuration of the evaporator, and to reduce the pressure loss of the refrigerant flow path of the entire evaporator. By reducing the pressure loss in the refrigerant channel, the refrigerant evaporation pressure can be reduced to lower the refrigerant evaporation temperature, and as a result, the cooling performance of the evaporator can be improved.

Next, the temperature distribution of the temperature of the air blown out from the evaporator will be described. FIG. 3 shows a heat exchange core portion composed of the tubes 2 to 5 and the corrugated fins 24, a first core portion A composed of the tube 2, The four cores are divided into a second core B formed by the tube 3, a third core C formed by the tube 4, and a fourth core D formed by the tube 5, and the distribution state of the refrigerant in each core is schematically shown. .

In each of the first core portion A and the second core portion B in which the refrigerant from the refrigerant inlet 7 flows from the upper side to the lower side, the liquid refrigerant is affected by gravity, so that the front side near the refrigerant inlet 7 (see FIG. Since the distribution of the liquid refrigerant is increased in the part on the left side, the distribution of the liquid refrigerant is reduced in the part on the far side (the right side in FIG. 3) away from the refrigerant inlet 7. As a result, in the first and second core portions A and B, a refrigerant shortage region E is generated in a lower portion on the right side in FIG.

On the other hand, in the third core portion C and the fourth core portion D, the refrigerant from the communication holes 20 and 21 flows upward from below, so that the gravity does not affect the refrigerant distribution state. When the refrigerant flows into the lower tanks 13 and 14 from the communication holes 20 and 21, the refrigerant flows from the portion immediately after the communication holes 20 and 21 because the tank space volume is much larger than the tube flow volume. Lower tanks 13, 14
Inside the tank in the longitudinal direction of the tank (to the right in FIG. 3), and the inertia of this flow causes the third core portion C and the fourth core portion D to move away from the communication holes 20 and 21 (see FIG. 3, the distribution of the liquid refrigerant is increased in the portion (right side of FIG. 3), and conversely, the distribution of the liquid refrigerant is reduced in the portion on the front side (left side in FIG. 3) close to the communication holes 20 and 21.

As a result, in the third and fourth core portions C and D,
A refrigerant shortage region F occurs in the upper portion on the left side of FIG. However, before and after the air flow direction Z, the refrigerant deficient regions E of the first and second core portions A and B overlap with regions of the third and fourth core portions C and D where the liquid refrigerant distribution is large, and Third, the refrigerant shortage region F of the fourth core portions C and D overlaps with the regions of the first and second core portions A and B where the liquid refrigerant distribution is large. Therefore, the region in which the liquid refrigerant distribution is high and the region in which the liquid refrigerant distribution is low are divided into the air flow direction Z.
, And the temperature distribution of the conditioned air can be made uniform to the same degree as in the prior art.

Next, a specific configuration example of the present embodiment will be described. FIG. 4 illustrates the tank sections 9 to 15, and the upper tank sections 9 and 11 are formed by bending a single aluminum sheet material. , 15 are formed.
And the partition wall 22 is comprised by the center bending part. Similarly, the lower tank portions 10, 12, 13,
The partition 14 and the partition wall 23 are also formed by bending a single aluminum sheet.

Next, FIG. 5 shows the cross-sectional shape of the tubes 2 to 5, and the tubes 2 to 5 are made of one aluminum thin plate material 2.
5 is bent and joined (brazed) to form a passage having a flat cross section. Here, tube 2
The internal refrigerant passage 26 in the inside 5 is divided into a number of small passages by joining the corrugated tops of the inner fins 6. Reference numeral 27 denotes an enlarged portion of the joint at the bent end portion of the aluminum thin plate material 25.

Next, FIG. 6 shows an example of a joint portion between the tank portions 9 to 15 and both ends of the tubes 2 to 5.
The flat surface 15 has a tube insertion hole 29 into which both ends 28 of the tubes 2 to 5 are inserted. Here, in order to facilitate the insertion of both ends 28 of the tubes 2 to 5 into the holes 29, the both ends 28 are formed in a shape shown in FIG.

That is, as shown in FIG. 7, the enlarged portion 27 of the tube joint portion is deleted at both end portions 28 of the tube to form a cutout portion 27a, so that both end portions 28 of the tube are substantially oval. It is formed into a shape. This notch 2
7a plays a role of a positioning stopper when inserting both ends 28 of the tubes 2 to 5 into the tube insertion holes 29 of the tanks 9 to 15 as shown in FIG. In addition,
FIG. 7E schematically shows only one of the tank sections 9 to 15 in the air flow direction Z.

The insertion holes 29 are oblong corresponding to both ends 28 of the tubes 2 to 5, and have a burring shape in which an oblong embossed portion 29a is embossed outward of the tank. . Thereby, the tank portions 9 to 15 and the tubes 2 to 5 can be joined using the brazing material on the inner surfaces of the tank portions 9 to 15. FIG. 8 shows an assembling structure of the flow path dividing partition plate 16 disposed between the tank portion 9 and the tank portion 11, and the partition plate 16 can be inserted between the tank portion 9 and the tank portion 11. The slits 30 are formed, the partition plate 16 is inserted into the slits 30, and the partition plates 16 are joined (brazed) to the peripheral portions of the slits 30 of the tank portions 9 and 11.

The partition plates 18, 19 disposed between the lower inlet tank portions 10 and 12 and between the lower outlet tank portions 13 and 14 are flat plates having no openings. Although it is different from the flow path dividing partition plate 16, its assembling structure is the same as that of the flow path dividing partition plate 16. FIG. 9 shows an assembling structure of a partition plate 17 for dividing the cross-section of the flow path in the tank into two sections. The partition plate 17 is disposed diagonally to the cross-section of the rectangular flow path in the inlet-side tank section 9. And is joined (brazed) to the inner wall surface of the inlet-side tank portion 9. 9, the arrow a indicates the flow of the refrigerant flowing from the refrigerant inlet 7 through the lower space of the partition plate 17 into the upper end of the tube 2, and the arrow h indicates the flow of the refrigerant from the refrigerant inlet 7 to the partition plate 1.
7, a triangular opening 16a of the partition plate 16
2 shows the flow of the refrigerant flowing into the right inlet-side tank portion 11 through the inlet.

Next, FIG. 10 shows the communication holes 20 and 2 described above.
FIG. 10 (a) illustrates a specific method of forming the first embodiment.
First, as shown in FIG.
A burring hole 31a and a punched hole 31b having a size that allows a punched portion of the burring hole 31a to be fitted therein are formed in the aluminum thin plate material 31 constituting the parts 3 and 14 by press working.

Next, as shown in FIG. 10B, the portion where the burring hole 31a and the punched hole 31b are formed is
Fold it into a letter shape. Next, as shown in FIG.
The punched portion of the burring hole 31a is fitted into the punched hole 31b. Next, as shown in FIG. 10 (d), the tip of the embossed portion of the burring hole 31a is swaged to the outer peripheral side.
As a result, it is possible to prevent the burring hole 31a from returning to the fitted state of the embossed portion, and the formation of the communication holes 20, 21 can be completed. The partition wall 23 is formed by the U-shaped bent portion.

FIG. 11 shows the lid member 32 of the tanks 9 to 15. The other end of the tank in the longitudinal direction (horizontal direction in FIG. 1) other than the portion where the refrigerant inlet 7 and the refrigerant outlet 8 are provided. The lid member 32 is disposed at the location. The lid member 32 is formed into a bowl-like shape by press-forming a single-sided clad material in which only the inner surface is clad with a brazing material. Then, the lid member 32 is fitted to the outer surface side of the longitudinal end of the tank, and the brazing material on the inner surface of the lid member 32 is used.
Is brazed to the tank longitudinal end to close the opening at the tank longitudinal end.

Next, FIG. 12 shows an example of the structure of a pipe joint block.
It has a three-layer laminated structure of a lid member 33, an intermediate plate member 34, and a joint cover member 35 brazed to the longitudinal end of the tank. The first connection port 35 through which the refrigerant decompressed by the expansion valve (not shown) flows into the joint cover member 35.
a, and a cylindrical second connection port 35b connected to the inlet of the gas refrigerant temperature sensing portion of the expansion valve. The first connection port 35a communicates with the refrigerant inlet 7 opened in the lid member 33, and the second connection port 35b communicates with the refrigerant outlet 8 opened in the lid member 33.

(Second Embodiment) FIG. 13 shows a second embodiment. In the first embodiment, a refrigerant inlet 7 and a refrigerant outlet 8 are provided.
Are communicated with the upper side tank portion 9 and the side surface portion of the outlet side tank portion 15, respectively. The partition plate 17 for dividing the inside of the tank into two sections in the inlet side tank portion 9, and a triangular opening With the flow path dividing partition plate 16 having 16a,
The refrigerant flow from the refrigerant inlet 7 is divided into two at the left and right sides of the evaporator 1.

On the other hand, in the second embodiment, the refrigerant inlet 7 is connected to the upper left and right inlet side tank portions 9 as shown in FIG.
The partition plate 160 disposed at an intermediate position between the inlet side tank portions 9 and 11 has a shape having no opening 16a. As a result, the refrigerant flow from the refrigerant inlet 7 is directly
It can be divided and allowed to flow into the left and right inlet side tank portions 9 and 11.

Then, the lower left and right inlet side tank sections 1
At positions 0 and 12, the positions close to the partition plate 18 (ie, intermediate positions between the left and right inlet side tank portions 10 and 12)
The communication holes 20 and 21 are arranged. Therefore, the communication hole 20 in the first embodiment is replaced with the partition plate 18 in the second embodiment.
Will be arranged at a position close to. Further, in the second embodiment, the refrigerant outlet 8 is connected to the upper outlet side tank portion 15.
It is located in the middle position.

Thus, in the second embodiment, a refrigerant path indicated by an arrow in FIG. 13 is formed, and substantially the same operation and effect as in the first embodiment can be exerted. (Other Embodiments) In the first embodiment, as shown in FIG. 3, a direction perpendicular to the air flow direction Z (lateral direction).
The case where the size of the left core portions A and C and the size of the right core portions B and D are made equal has been described, but the size of the left core portions A and C and the size of the right core portions B and D are described. May be different from each other, and the flow rates of the refrigerant flowing through the left and right core portions may be different in accordance with the difference in the core size.

That is, the size of the core portion divided in the left-right direction and the distribution amount of the refrigerant can be arbitrarily changed.

[Brief description of the drawings]

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

FIG. 2 is a schematic perspective view illustrating a configuration of a tank portion of the refrigerant evaporator of FIG.

FIG. 3 is an operation explanatory view of the refrigerant evaporator of FIG. 1;

FIG. 4 is a side view showing an end face shape of the tank unit of FIG. 1;

FIG. 5 is a sectional view showing a sectional shape of the tube of FIG. 1;

FIG. 6 is a sectional view of a fitting portion between the tank unit and the tube in FIG. 1;

FIG. 7A is a plan view of the end of the tube of FIG. 1, and FIG.
Is a front view of the tube end, (c) is a partially enlarged view of (b), (d) is an enlarged perspective view of (a), and (e) is an assembled state in which the tube end is inserted into the tank. FIG.

FIG. 8 is an exploded perspective view showing an assembling structure of the tank part and the flow path dividing partition plate of FIG.

9 is a perspective view showing an assembling structure of the tank portion of FIG. 1 and a partition plate for dividing the inside of the tank passage into two sections;

FIG. 10 is a sectional view for explaining a method of forming the communication hole in FIG. 1;

FIG. 11 is a perspective view of a lid member of the tank unit of FIG. 1;

FIG. 12 is a perspective view of a pipe joint portion connected to the refrigerant inlet and the refrigerant outlet of FIG. 1;

FIG. 13 is a schematic perspective view of a refrigerant evaporator according to a second embodiment of the present invention.

FIG. 14 is a schematic perspective view showing a refrigerant passage configuration of a conventional evaporator.

[Explanation of symbols]

2-5: tube, 7: refrigerant inlet, 8: refrigerant outlet, 9-
Reference numeral 15: tank part, 16: flow path dividing partition plate, 17: partition plate for dividing the flow path inside the tank into two, 20, 21: first and second communication holes, 22, 23: partition walls, A, B, C , D: heat exchange core part.

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Toshio Ohara 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture Inside Denso Corporation (72) Inventor Sadayuki Kamiya 1-1-1, Showa-cho, Kariya-shi, Aichi Co., Ltd. F term in DENSO (reference) 3L103 AA09 AA17 BB38 CC18 CC22 DD15 DD18 DD54 DD55

Claims (3)

[Claims] A plurality of tubes (2 to 5) for flowing a refrigerant are arranged in a plurality of rows in an air flow direction (Z), and the tubes (2 to 5) are arranged in a horizontal direction orthogonal to the air flow direction (Z). A large number of the tubes (2 to 5) are arranged at both ends of the tubes (2 to 5).
-5) for distributing the refrigerant to the tubes or collecting the refrigerant from the tubes (2-5). The tanks (9-15) are provided with the plurality of rows of tubes (2-5).
5), a plurality of rows are arranged in the air flow direction (Z), and the refrigerant flowing from the refrigerant inlet (7) is supplied to the tank portion (9 to 9).
15) a refrigerant evaporator that is turned multiple times in a flow path passing through the tubes (2 to 5) and then flows out from a refrigerant outlet (8); Replace the exchange cores (A, B, C, D) with the air flow direction (Z).
And divided in the direction perpendicular to the air flow direction (Z), and located on one side in the direction perpendicular to the air flow direction (Z).
Heat exchange cores (A, C) before and after the air flow direction (Z)
A first communication hole (20) for directly communicating with the air flow direction, and a heat exchange core portion (B, D) located on the other side in the direction orthogonal to the air flow direction (Z), in the front and rear directions of the air flow direction (Z). The second communication hole (21) for directly communicating with the tank portion (9 to 9)
15), a refrigerant flow from the refrigerant inlet (7) is divided into two flows in a direction orthogonal to the air flow direction (Z), and one of the two refrigerant flows is It flows through the first communication hole (20) to the front and rear heat exchange cores (A, C) located on one side in the direction perpendicular to the air flow direction (Z), and the other of the two refrigerant flows is Air flow direction (Z)
The refrigerant evaporator is characterized in that the refrigerant evaporator is arranged to flow through the second communication hole (21) to the front and rear heat exchange core portions (B, D) located on the other side in the direction orthogonal to the first direction. 2. A refrigerant flow from said refrigerant inlet (7) in said tank part (9, 11) of said tank part (9-15) is defined by said air flow direction (Z). The refrigerant evaporator according to claim 1, further comprising a dividing means (16, 17) for dividing the flow into two flows in an orthogonal direction. 3. A refrigerant inlet-side tank part (9, 11) of the tank parts (9 to 15) is divided in a direction orthogonal to the air flow direction (Z), and the refrigerant inlet-side tank part is divided. The refrigerant inlet (7) is disposed at an intermediate position of (9, 11), and a refrigerant flow from the refrigerant inlet (7) is divided in a direction orthogonal to the air flow direction (Z). The refrigerant evaporator according to claim 1, wherein the refrigerant evaporator flows directly into the sections (9, 11).