JP3391339B2 - Refrigerant evaporator - Google Patents

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 a refrigerant of a refrigeration cycle, and is suitable for use in, for example, a vehicle air conditioner.

[0002]

2. Description of the Related Art In Japanese Utility Model Registration No. 2518259, a refrigerant evaporator having a refrigerant flow path structure shown in FIG. 21 is proposed. In this conventional refrigerant evaporator 1, as shown in FIG. 22, a tube 100 having two parallel refrigerant passages 100a and 100b therein, and first and second tanks 10 formed separately from the tube 100.
1 and 102, one of the refrigerant passages 100a in the tube 100 communicates with the first tank 101, and the other refrigerant passage 100b in the tube 100 and the second tank 100b communicate with each other.
It communicates with the tank 102. In addition, in the first tank 101 arranged on the upstream side of the air flow A,
A partition plate (not shown) is provided at an intermediate portion in the longitudinal direction, and the inside of the first tank 101 is an inlet tank portion 1 for distributing the refrigerant.
01a and an outlet tank portion 101b that collects the refrigerant, the inlet tank portion 101a is provided with a refrigerant inlet 103, and the outlet tank portion 101b is provided with a refrigerant outlet 104.

In the evaporator 1 having such a structure, the refrigerant flows through the inside thereof through the following route. That is, in FIG. 21, the refrigerant flows from the refrigerant inlet 103 arranged on the upstream side of the air flow A to the inlet tank portion 101a of the first tank 101.
And goes up the windward refrigerant passage in the tube 100. Next, the refrigerant makes a U-turn at the upper part of the tube 100, and then descends through the leeward side refrigerant passage in the tube 100 to reach the second position.
Enter the tank 102. Next, the refrigerant flows in the second tank 102 to the left side in FIG. 21, and rises up the leeward side refrigerant passage in the tube 100 located on the left side in FIG. 21. Next, the refrigerant makes a U-turn at the upper part of the tube 100, then descends the windward refrigerant passage in the tube 100 to enter the outlet tank portion 101b of the first tank 101, and further the refrigerant outlet arranged on the upstream side of the air flow A. It flows to 104 and flows out of the evaporator.

Of the gas-liquid two-phase refrigerant, the liquid refrigerant mainly contributes to the cooling of air. In the evaporator 1 having such a structure, the gas-liquid two-phase refrigerant flows in the second tank 102 as shown in FIG. When flowing toward the left side, the liquid refrigerant is more likely to flow to the inner side (left side in FIG. 21) due to inertia than the gas refrigerant, so that the refrigerant flowing through the refrigerant passage in the tube 100 has a ratio of the liquid refrigerant to the left side in FIG. Becomes higher and the temperature of air blown from the evaporator becomes non-uniform.

Therefore, in the above-described conventional refrigerant evaporator 1, a throttle is provided in the tank portion for distributing the refrigerant on the left side of the second tank 102 in FIG. By limiting the amount, the distribution of the liquid refrigerant flowing into the refrigerant passage is made uniform, and the temperature of the air blown from the evaporator is made uniform over the entire area of the evaporator 1.

[0006]

However, in the above-described conventional refrigerant evaporator 1, when the refrigerant flow rate is small, the flow rate of FIG.
In Fig. 1, a relatively large amount of liquid refrigerant exists in the right side refrigerant passages and parts, but in Fig. 21, the refrigerant is mostly gasified in the left side refrigerant passages and parts. Therefore, the refrigerant passage, the air passing through the side becomes less likely to be cooled, and when the refrigerant flow rate is small, the refrigerant passage, the air passing through the side and the refrigerant passage,
There is a problem that the temperature difference from the air passing through the side becomes large.

The present invention has been made in view of the above points,
Evaporation is performed in an evaporator in which tanks are arranged at both upper and lower ends of the tube, and the tubes and tanks are arranged in multiple rows in the direction of the flow of the external fluid, and the refrigerant flows while meandering in the tubes and tank. The purpose is to make the temperature distribution of the air blown out of the vessel uniform.

[0008]

In order to achieve the above object, in the invention described in claim 1, the tubes (2 to 5) for flowing the refrigerant are arranged such that the refrigerant flow direction is vertical and the external fluid flow direction is The tubes (2 to 5) are arranged in a plurality of rows in the direction (A) of the external fluid, and the refrigerant is distributed to the tubes (2 to 5) or the tubes (2 to 5). 5 to 5), the tank parts (8 to 13) for collecting the refrigerant are provided at the upper and lower ends of the tubes (2 to 5) at the upper and lower ends of the tubes (2 to 5) corresponding to the flow direction of the external fluid ( A), a plurality of rows are arranged, and a refrigerant inlet (6) is arranged in the tank portion (8 to 10) arranged on either the upstream side or the downstream side in the flow direction (A) of the external fluid,
The refrigerant outlet (7) is arranged in the tank portion (11 to 13) arranged on either the upstream side or the downstream side of the flow direction (A) of the external fluid, and the tubes (2 to 5) and the tank portion (8 to 13) In the refrigerant flow path formed inside, the refrigerant turns in a direction orthogonal to the flow direction (A) of the external fluid, and
A row in which the turn direction is configured so that the refrigerant flow passage on the upstream side and the refrigerant flow passage on the downstream side in the flow direction (A) of the external fluid are opposite to each other, and the refrigerant is provided with the refrigerant inlet (6). after passing all the refrigerant flow path, configured so as to extend to the refrigerant outlet through the refrigerant flow path of the adjacent rows in the flow direction of the external fluid (a) in the order (7), the flow direction of the external fluid (a ) Adjacent to
Partition walls (16, 1) that divide the space between the link parts (8 to 13)
7), a communication hole for communicating this tank part (8 to 13)
(18) in the direction perpendicular to the external fluid flow direction (A).
A few tubes are placed at the lower end of the tube (2-5).
In the link section (9, 12), the collecting section (9a,
12a) and the upflow refrigerant distributor (9b, 12b).
As well as the assembly section (9a, 12a) and the distribution section (9
b, 12b) toward the downstream side of the refrigerant flow from the vicinity of the boundary
And a throttle portion (51a-
56a) are provided, and the lower ends of the tubes (2-5) are provided.
The tank portion (1
2) Opening of the throttle part (54a) arranged on the most upstream side in
The mouth area at the lower end side of the tubes (2-5) and the refrigerant
In the tank part (9) arranged on the upstream side of the flow,
Larger than the opening area of the throttle (53a) arranged on the downstream side.
Characterized by the fact

According to this, the flow direction of the external fluid (A)
The refrigerant flow path on the upstream side and the refrigerant flow path on the downstream side have opposite turn directions, and the refrigerant that has passed through all the refrigerant flow paths in the row in which the refrigerant inlet (6) is arranged is ), The refrigerant flow path on the refrigerant inlet (6) side where a relatively large amount of liquid refrigerant is present, and the gas refrigerant are formed. The refrigerant flow path on the side of the refrigerant outlet (7), which has a large amount of air, is in series in the flow direction (A) of the external fluid. Therefore, even when the flow rate of the refrigerant is small, the temperature distribution of the air blown from the evaporator can be made uniform.

Further, it is possible to arbitrarily set the refrigerant distribution of the tube group in which the refrigerant rises by the throttle portions (51a to 56a). Therefore, for example, when the distribution of the refrigerant is uneven in the tube groups that overlap in the flow direction (A) of the external fluid, the refrigerant distribution in the tube group in which the refrigerant rises is reversed from the refrigerant distribution in the other tube groups, The uneven distribution of the refrigerant can be canceled out, and the temperature distribution of the air blown from the evaporator can be made more uniform. In addition, the turn configuration of the refrigerant flow
A communication hole (18) for obtaining the partition wall (16, 17)
Evaporation as it is extremely simple to configure using itself
There is no need to add a side refrigerant passage to the side of the vessel.
As a result, there is no need for components for the side refrigerant passages.
Therefore, the evaporator configuration can be simplified accordingly.
Manufacturing cost can be reduced. Moreover, a series of multiple
The opening area and arrangement of each through hole (18) should be set appropriately.
By setting the communication hole (18) to the downstream side of the refrigerant flow.
The distribution of refrigerant in a certain tube group can be set arbitrarily
It Therefore, the tubes that overlap in the flow direction (A) of the external fluid are overlapped.
If the distribution of the refrigerant is uneven in the group, the communication hole (18)
The refrigerant distribution of the tubes in the
By reversing the refrigerant distribution of the tube group,
Unevenness is canceled out and the temperature distribution of the air blown from the evaporator is made uniform.
Can be planned. In addition, in the lower tank part (9, 12)
Downflow refrigerant collecting part (9a, 12a) and upflow cooling in
Refrigerant flow from the vicinity of the boundary with the medium distributor (9b, 12b)
Toward the downstream side, a narrowed portion (51a-
By providing a plurality of 53a), the tube (2 to
5) The distribution of the refrigerant inside can be set more finely
It Also, at the lower end side of the tubes (2 to 5) and the refrigerant
In the tank portion (12) arranged on the downstream side of the flow
The opening area of the throttle portion (54a) arranged on the most upstream side is
The tubes (2-5) are arranged at the lower end side and the refrigerant flow upstream side.
It was arranged on the most downstream side in the placed tank part (9).
To make it larger than the opening area of the diaphragm (53a)
To suppress pressure loss and prevent cooling performance deterioration.
You can

According to a second aspect of the invention, the tank portion (1
1 to 13), the refrigerant inlet (6) and the refrigerant outlet (7) are arranged at one end on the one side in the direction orthogonal to the flow direction (A) of the external fluid.

By the way, in the conventional refrigerant evaporator 1, the refrigerant inlet 103 and the refrigerant outlet 104 are arranged in the middle portion of the first tank 101 in the evaporator width direction, and are located in the air passage in the air conditioning case. Therefore, one end of the auxiliary pipe for connection is connected to the refrigerant inlet / outlets 103 and 104,
The other end of the connecting auxiliary pipe is projected outside the air conditioning case (on the end side in the width direction of the evaporator) to connect the connecting auxiliary pipe and the external refrigerant pipe. Therefore, it is necessary to provide the auxiliary pipe for connection, and there is a problem that the cost of the auxiliary pipe for connection increases.

On the other hand, according to the second aspect of the present invention, both the refrigerant inlet (6) and the refrigerant outlet (7) are at one end side (the evaporator width direction) orthogonal to the flow direction (A) of the external fluid. Since it is disposed on the end side), an auxiliary pipe for connection is not required, the evaporator configuration can be simplified, and the manufacturing cost can be reduced.

[0014]

[0015]

[0016]

[0017]

When the tubes (2 to 5) and the tank portion (8 to 13) are separately formed and then integrally joined as in the invention described in claim 5 , the tubes (2 to 5) are It is possible to improve the heat exchange performance and reduce the size by reducing the plate thickness and making the heat exchange portion finer. Moreover, in the tank part (8 to 13) which is not related to the heat exchange performance, the plate thickness can be independently set apart from the tubes (2 to 5) from the viewpoint of ensuring strength. The required strength of) can be easily secured.

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

[0020]

BEST MODE FOR CARRYING OUT THE INVENTION 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 automobile air conditioner, and shows an outline of the entire structure of the evaporator.
The evaporator 1 is installed in an air conditioning unit case of an automobile air conditioner (not shown) with the vertical direction of FIG.
Air is blown to the evaporator 1 in the direction of arrow A by a blower (not shown), and the blown air (external fluid) and the refrigerant exchange heat.

The evaporator 1 has tubes 2, 3, 4, 5 arranged in two rows in the air flow direction A. These tubes 2 to 5 are all flat tubes that form a refrigerant passage having a flat cross section. The tubes 2 to 5 are arranged in parallel in a direction orthogonal to the air flow direction A. Here, the first tubes 2 and 3 on the air downstream side constitute a refrigerant passage of the refrigerant inlet side heat exchange section X, and the second tubes 4 and 5 on the air upstream side include the refrigerant inlet side heat exchange section Y. Of the refrigerant passage.

The low-temperature low-pressure gas-liquid two-phase refrigerant, which has been decompressed and expanded by a temperature-operated expansion valve (pressure reducing means) (not shown) of the refrigeration cycle, flows into the refrigerant inlet 6. Further, the refrigerant outlet 7 is connected to a compressor suction pipe (not shown) and is used to recirculate the gas refrigerant evaporated in the evaporator 1 to the compressor suction side. Further, the refrigerant inlet 6 and the refrigerant outlet 7 are arranged in the upper part on the left side of the evaporator 1 in this example, and the refrigerant inlet 6 communicates with the inlet side tank portion 8 located on the left side of the upper part. The refrigerant outlet 7 communicates with the outlet side tank portion 13 located on the left side of the upper portion.

The tank portions 8 to 13 of the evaporator 1 will be described in detail. Each tank portion distributes the refrigerant to the tubes 2 to 5 or collects the refrigerant from the tubes 2 to 5. Tubes 2, 3 and second tube 4,
5 are arranged in two rows in the air flow direction A. That is, the inlet side tank parts 8 to 10 are located on the downstream side of the air flow, and the outlet side tank parts 11 to 13 are located on the upstream side of the air flow.

A partition plate 14 partitions the upper inlet tank portions 8 and 10 from each other, and a partition plate 15 partitions the upper outlet tank portions 11 and 13 from each other. On the other hand, the lower inlet-side tank portion 9 and the lower outlet-side tank portion 12 communicate with each other as one flow passage over the entire length in the width direction of the evaporator 1 without partitioning.

In the refrigerant inlet side heat exchange section X, one end portion (upper end portion) of the left tube 2 has an upper inlet side tank section 8
And the other end (lower end) is connected to the lower inlet tank 9
Is in communication with. Similarly, one end portion (upper end portion) of the right tube 3 communicates with the upper inlet tank portion 10, and the other end portion (lower end) communicates with the lower inlet tank portion 9. Further, in the refrigerant outlet side heat exchange section Y, one end portion (upper end portion) of the left tube 4 has an upper outlet side tank portion 13
And the other end (lower end) of the lower outlet side tank part 1
It communicates with 2. Similarly, one end (upper end) of the right tube 5 communicates with the upper outlet side tank part 11, and the other end (lower end) communicates with the lower outlet side tank part 12.

By the way, between the upper tank portions 8 and 13 which are adjacent to each other in the air flow direction A, the upper tank portion 10 is provided.
Partition walls 16 and 17 that extend over the entire length in the width direction of the evaporator 1 are formed between the tanks 9 and 11 and between the lower tanks 9 and 12. This partition wall 1
6 and 17 are formed integrally with the tank portions 8 to 13, as described later.

However, in the upper partition wall 16, the tank portion 1 is provided at the right side partitioning between the tank portions 10 and 11.
A communication hole 18 that connects 0 and 11 is provided. A plurality of the communication holes 18 are provided in a direction orthogonal to the air flow direction A (width direction of the evaporator 1). More specifically, the communication holes 18 correspond to the arrangement of the tubes 3 and 5, respectively. It is preferable to provide the same number as the tubes 3 and 5 in order to improve the distribution of the refrigerant to each tube.

Here, a plurality of communication holes 18 can be punched simultaneously in a thin metal plate (aluminum or the like) forming the partition wall 16 by, for example, press working.
The shape of 8 is, for example, a rectangular shape as shown in FIG. Further, the opening area and arrangement of the communication holes 18 are set so that the refrigerant distribution property to each tube is optimized.

Corrugated fins 19 formed in a corrugated shape are arranged between the tubes 2 to 5, and the corrugated fins 19 are integrally joined to the flat surfaces of the tubes 2 to 5. Further, a corrugated inner fin 20 is arranged inside each tube 2 to 5, and the top of the corrugated inner fin 20 is joined to the inner wall surface of each tube to reinforce each tube 2 to 5. At the same time, the performance is improved by increasing the heat transfer area on the refrigerant side.

FIG. 2 shows the structure of the lower inlet side tank section 9 and the lower outlet side tank section 12, in which the liquid refrigerant is distributed to the tubes 3 and 4 in the lower inlet side tank section 9. In order to arbitrarily set the
First to third diaphragm plates 51 to 53 forming a to 53a are installed. The first throttle plate 51 has a collecting tank portion 9a for collecting the refrigerant in the lower inlet tank portion 9.
And a distribution tank portion 9b that distributes the refrigerant. In addition, the second and third diaphragm plates 52 and 53 are
It is arranged at a predetermined interval in the distribution tank portion 9b of the lower inlet tank portion 9.

Similarly, the fourth to sixth throttle parts 54a to 56a are formed in the lower outlet side tank part 12 as well.
-Sixth diaphragm plates 54-56 are installed. The fourth diaphragm plate 54 is arranged in the lower outlet side tank portion 12 at a boundary portion between a collecting tank portion 12a for collecting the refrigerant and a distribution tank portion 12b for distributing the refrigerant. Further, the fifth and sixth diaphragm plates 55, 56 are arranged in the distribution tank portion 12b of the outlet side tank portion 12 in the lower portion.

Here, the first to sixth throttle holes 51a to 56 are provided.
A can be punched by, for example, press working on a thin metal plate (aluminum or the like) forming the diaphragm plates 51 to 56, and the shape of the diaphragm holes 51a to 56a is, for example, a circular shape as shown in FIG.

The entire evaporator 1 shown in FIGS. 1 and 2 is assembled by being integrally joined by brazing as described later.

Next, the operation of the evaporator according to the first embodiment in the above structure will be described. The low-temperature low-pressure gas-liquid two-phase refrigerant decompressed by the expansion valve (not shown) is first introduced from the refrigerant inlet 6 to the air downstream side. It flows into the upper tank portion 8, where
It is distributed to a plurality of tubes 2 and flows downward in the tubes 2 as indicated by an arrow a to reach the collective tank portion 9a of the lower tank portion 9. After that, the refrigerant flows in the lower tank portion 9 toward the distribution tank portion 9b side as shown by an arrow b, and then is distributed to the plurality of tubes 3, and flows through the tubes 3 upward as shown by an arrow c. It flows into the tank section 10.

Next, the refrigerant passes through the communication hole 18 formed in the partition wall 16 as shown by the arrow d, moves from the air downstream side to the air upstream side, and the upper tank portion 11 on the air upstream side.
Flows in. Next, the refrigerant is distributed from the upper tank portion 11 to the plurality of tubes 5, flows downward in the tubes 5 as indicated by arrow e, and flows into the collecting tank portion 12a of the lower tank portion 12.

Next, the refrigerant flows through the lower tank portion 12 toward the distribution tank portion 12b side as indicated by the arrow f, and then is distributed to the plurality of tubes 4, and the tubes 4 flow upward as indicated by the arrow g. Then, the refrigerant from the tube 4 is collected in the upper tank portion 13, moves from the right side to the left side in the upper tank portion 13 as indicated by an arrow h, and flows out of the evaporator 1 from the refrigerant outlet 7.

On the other hand, the blown air (air-conditioned air) is blown in the direction of arrow A and passes through the void portion 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, whereby the blown air is cooled and becomes cold air, which blows out into the vehicle interior to cool the vehicle interior.

By the way, in the evaporator 1, the refrigerant inlet side heat exchange section X, which is formed by the meandering flow path on the refrigerant inlet side indicated by the arrows a to c, is arranged on the downstream side in the air flow direction A,
Since the refrigerant outlet side heat exchange section Y formed of the meandering flow path on the refrigerant outlet side indicated by the arrows e to h is arranged on the upstream side in the air flow direction A, the heat transfer performance between the refrigerant and the air. It is possible to perform heat exchange in a cross-counterflow having a good temperature.

Moreover, since the tank portions 10 and 11 located at the front and rear in the air flow direction A are directly communicated with each other by the communication hole 18 formed in the partition wall 16, there is no need for the side refrigerant passage. It is possible to connect the refrigerant passages before and after the air flow direction. Therefore, the entire structure of the evaporator can be simplified, and the pressure loss of the refrigerant passage of the entire evaporator can be reduced. By reducing the pressure loss of the refrigerant flow path, the refrigerant evaporation pressure can be decreased to lower the refrigerant evaporation temperature, and as a result, the cooling performance of the evaporator can be improved.

Further, in the evaporator 1, the refrigerant flowing from the refrigerant inlet 6 passes through the refrigerant inlet side heat exchanging section X and then passes through the refrigerant outlet side heat exchanging section Y to reach the refrigerant outlet 7. In addition, since the refrigerant flow path is configured, the refrigerant inlet 6 and the refrigerant outlet 7 can be arranged centrally on one end side (the upper left portion in FIG. 1) in the direction orthogonal to the air flow direction A. Therefore, by providing an opening in the air conditioning case (not shown) corresponding to the positions of the refrigerant inlets and outlets 6 and 7, it is possible to connect the external refrigerant pipes outside the air conditioning case and the refrigerant inlets and outlets 6 and 7, and thus the auxiliary connection. No need for piping.

In the evaporator 1, the distribution of the refrigerant flowing into the evaporator 1 in each of the tubes 2 to 5 is set as follows in order to make the temperature distribution of the air blown from the evaporator uniform. ing.

First, the distribution of the refrigerant in the tubes 2 and 4 located before and after the air flow direction A will be described. First, when the refrigerant is distributed from the upper tank portion 8 to the tube 2, the liquid refrigerant is generally gravitationally generated, and thus the upper tank portion 8 is generally used.
A large amount of the liquid refrigerant flows into the tube 2 at a portion close to the refrigerant inlet portion side (left side in FIG. 1), while the liquid refrigerant tends to hardly flow into the tube 2 at a portion far from the refrigerant inlet portion (right side in FIG. 1).
However, the refrigerant at the time of flowing into the upper tank portion 8 has a high proportion of the liquid refrigerant since it has not undergone heat exchange with air, and therefore the liquid refrigerant also flows into the tube 2 at a portion far from the refrigerant inlet portion (right side in FIG. 1). Sufficiently flows in, and the distribution of the liquid refrigerant in the tube 2 is relatively uniform.

Therefore, in the tube 4 located on the upstream side of the air flow of the tube 2, as will be described in detail below, the fourth to sixth throttle holes 5 arranged in the distribution tank portion 12b.
The liquid refrigerant distribution in the tube 4 is adjusted to be substantially uniform by 4a to 56a.

First, the fourth to sixth throttle holes 54a to 56a.
When there is no liquid refrigerant, a large amount of liquid refrigerant flows into the back side (left side in FIG. 1) due to inertia, so that the liquid refrigerant mainly flows through the tube 4 on the back side and the gas refrigerant mainly flows through the tube 4 on the front side. The refrigerant distribution becomes non-uniform. However, the evaporator 1
In the above, the flow rate of the refrigerant flowing through the lower tank portion 12 as indicated by the arrow f is first increased when passing through the fourth throttle hole 54a, and immediately after passing through the fourth throttle hole 54a, the gas refrigerant and the liquid refrigerant are Are agitated to mix the two, so that the refrigerant in which the gas refrigerant and the liquid refrigerant are mixed flows into the tube 4 immediately after the fourth throttle hole 54a. The refrigerant that has proceeded further toward the inner side (the left side in FIG. 1) is blocked by the fifth diaphragm plate 55, so that the tube 4 in the portion immediately before the fifth diaphragm plate 55 is blocked. , A large amount of liquid refrigerant flows in.

Further, at the position immediately after passing through the fifth throttle hole 55a, the gas refrigerant and the liquid refrigerant are agitated and mixed with each other, so that the tube 4 at the portion immediately after the fifth throttle hole 55a is gas-liquid. Two-phase refrigerant flows in. Similarly, a large amount of the liquid refrigerant flows into the tube 4 immediately before the sixth throttle plate 56 by the damming action, and at the position immediately after passing through the sixth throttle hole 56a, the gas-liquid two-phase refrigerant is stirred by the stirring action. Flows in.

Then, the fourth to sixth throttle holes 54a to 56 are formed.
By appropriately setting the opening area of a and the arrangement of the fourth to sixth diaphragm plates 54 to 56, it is possible to make the liquid refrigerant distribution in the tube 4 substantially uniform, and thus the air flow direction A It is possible to make the temperature distribution of the air passing through the tubes 2 and 4 located before and after the temperature distribution uniform.

In FIG. 3, only the refrigerant outlet side heat exchange section Y is taken out, and the blown air of the tube 4 when air of 27 ° C. is blown without the presence of the fourth to sixth throttle holes 54a to 56a. The temperature is compared. The solid line shows the result with a throttle hole, and the broken line shows the result without a throttle hole. As is clear from FIG. 3, the uniform distribution of the liquid refrigerant through the throttle holes 54a to 56a significantly improves the temperature distribution of the blown air (uniformization).
Is possible.

Further, by homogenizing the distribution of the liquid refrigerant in each of the tubes 2 to 5, the entire area of the heat exchange sections X and Y is effectively used for heat exchange, and the heat exchange efficiency can be improved. Further, the uniform distribution of the liquid refrigerant in the tubes 4 makes it easy to just complete the gasification of the refrigerant when the refrigerant flows from the tubes 4 into the tank 13.

Next, the distribution of the refrigerant in the tubes 3 and 5 located before and after the air flow direction A will be described. First, the first to third throttle holes 51a to 53a arranged in the distribution tank portion 9b function similarly to the fourth to sixth throttle holes 54a to 56a arranged in the distribution tank portion 12b. The liquid refrigerant distribution in the tube 3 is adjusted to be substantially uniform. Then, in response to the liquid refrigerant distribution in the tube 3 being adjusted to be substantially uniform, the plurality of communication holes 18 are formed so that the refrigerant distribution in the tube 5 is also uniform.
The openings have the same area and are arranged at equal intervals in the direction orthogonal to the air flow direction A. Therefore, it is possible to make the temperature distribution of the air passing through the tubes 3 and 5 located before and after the air flow direction A uniform.

When the distribution of the liquid refrigerant in the tube 2 is large, the opening areas of the fourth to sixth throttle holes 54a to 56a arranged in the distribution tank portion 12b and the fourth to sixth throttle holes 54a to 56a. By appropriately setting the arrangement of the diaphragm plates 54 to 56 of No. 6, the distribution of the liquid refrigerant in the tube 4 can be reversed to the distribution of the refrigerant in the tube 2, whereby the positions of the liquid refrigerant in the front and rear of the air flow direction A can be set. The temperature distribution of the air passing through the tubes 2 and 4 can be made uniform.

When the liquid refrigerant distribution in the tube 3 remains uneven, the refrigerant distribution in the tube 5 is adjusted by appropriately setting the opening areas and the arrangement of the plurality of communication holes 18. It is possible to make the temperature distribution of the air passing through the tubes 3 and 5 located before and after the air flow direction A uniform.

Next, the first to sixth throttle holes 51a to 56a.
The desirable opening area ratio will be described with reference to FIG. Here, the opening area ratio is a value obtained by dividing the opening areas of the throttle holes 51a to 56a by the cross-sectional areas of the flow paths of the tank portions 9 and 12. The cooling performance ratio is the same for all the throttle holes 51a to 56a.
The cooling performance (the cooling performance of the blown air by the evaporator 1) when the opening area ratio of 1 is optimally set is 100%.
Then, FIG. 4 shows the cooling performance ratio when the opening area ratio of any one of the throttle holes is changed and the opening area ratios of the other throttle holes are set to optimum values.

If the opening area ratio of each throttle hole 51a to 56a is larger than the optimum value, the cooling performance is deteriorated without obtaining the optimum refrigerant distribution, while the opening area ratio of each throttle hole 51a to 56a is optimum. If it is smaller than the value, the pressure loss increases and the cooling performance decreases.

According to FIG. 4, the optimum value of the opening area ratio of the respective diaphragm holes 51a to 56a is about 46 for the first diaphragm hole 51a.
%, The second throttle hole 52a is about 35%, the third throttle hole 53
a is approximately 20%, the fourth aperture 54a is approximately 80%, the fifth aperture 55a is approximately 65%, and the sixth aperture 56a is approximately 46%.
%.

Of the lower two tank parts 9 and 12, the first to the first tank parts provided on the inlet side tank part 9 on the upstream side of the refrigerant flow.
The optimum opening area ratio of the third throttle portions 51a to 53a and the fourth to sixth throttle portions 54a to 5 provided in the outlet side tank portion 12 on the refrigerant flow downstream side of the lower two tank portions 9 and 12.
Comparing with the optimum opening area ratio of 6a, the optimum opening area ratio of the first to third diaphragm portions 51a to 53a is smaller than the optimum opening area ratio of the fourth to sixth diaphragm portions 54a to 56a. Become.

The first tank in the inlet side tank section 9 on the upstream side
-Comparing the optimal opening area ratios of the third throttle parts 51a to 53a, the smaller the downstream side of the refrigerant flow, the smaller. Further, the fourth to sixth throttle parts 54a in the outlet side tank part 12 on the downstream side.
Comparing the optimum opening area ratios of .about.56a, the smaller the opening area, the smaller the downstream side of the refrigerant flow.

The first diaphragm plate 51 and the fourth diaphragm plate 5
4 is arranged at the boundary between the collecting tank parts 9a, 12a for collecting the refrigerant and the distribution tank parts 9b, 12b for distributing the refrigerant, the first diaphragm plate 51 and the fourth diaphragm plate 54
Is a collection tank portion 9a, 12a and a distribution tank portion 9
In the vicinity of the boundary between b and 12b, the same effect can be obtained even if the position is slightly shifted.

In the conventional refrigerant evaporator 1 shown in FIGS. 21 and 22, when the flow rate of the refrigerant is small, the temperature difference between the air passing through the refrigerant passage and the refrigerant passage and the air passing through the side becomes large. However, in the present embodiment, the refrigerant flow path on the refrigerant inlet 6 side where a relatively large amount of liquid refrigerant exists and the refrigerant flow path on the refrigerant outlet 7 side where the amount of gas refrigerant is large are:
Since it is in series in the flow direction A of the external fluid, the temperature distribution of the air blown from the evaporator can be made uniform even when the refrigerant flow rate is small.

Further, in the conventional refrigerant evaporator 1 shown in FIGS. 21 and 22, the refrigerant that has risen in the leeward refrigerant passage is U in the upper portion.
Since it turns and flows into the windward refrigerant passage in the same refrigerant distribution state as the refrigerant passage, if the distribution of the liquid refrigerant flowing into the leeward refrigerant passage is not sufficiently uniform, the liquid in the windward refrigerant passage The distribution of the refrigerant becomes non-uniform, and the variation in the temperature of air blown from the evaporator becomes extremely large.
Therefore, in order to make the distribution of the liquid refrigerant flowing into the leeward side refrigerant passage more uniform, it is necessary to provide a large number of throttles in the refrigerant distribution portion of the refrigerant passage to make fine adjustments. There is a problem that the pressure loss becomes large.

On the other hand, in this embodiment, the distribution of the liquid refrigerant in each of the tubes 2 to 5 is changed to the throttle holes 51a to 56.
Since it can be individually adjusted by a and the communication hole 18, it is not necessary to provide a large number of throttles at a specific portion to perform fine adjustment as in the conventional evaporator, and therefore an increase in pressure loss of the refrigerant flow path is increased. Can be reduced.

Next, the specific structure and manufacturing method of the evaporator 1 according to the first embodiment will be described. FIG. 5 exemplifies the tank parts 8 to 13. By bending one thin aluminum plate material, the upper tank parts 8, 10,
11 and 13 are formed. The partition wall 16 is formed by the central bent portion. Similarly, the lower tank portions 9 and 12 and the partition wall 17 are also formed by bending one thin aluminum plate. The plate thickness of the aluminum thin plate material is, for example, about 0.6 mm to secure the strength of the tank portion to which a large stress due to the refrigerant pressure acts compared to the tube.

As a specific material example of the aluminum thin plate material, a single-sided clad material in which a brazing material (A4000 series) is clad on the inner surface and a core material (A3000 series) is arranged on the outer surface is used. In this case, the corrosion resistance may be improved as a sandwich structure in which a sacrificial corrosion material (for example, Al-1.5 wt% Zn) is provided on the outer surface of the core material.

Next, FIG. 6 (a) shows the cross-sectional shape of the tubes 2 to 5, and the tubes 2 to 5 form a passage shape having a flat cross-section by bending one aluminum thin plate material. Here, the internal refrigerant passages 21 in the tubes 2 to 5 are divided into a large number of small passages by joining the corrugated tops of the inner fins 20.

As a concrete material example of the aluminum thin plate material of the tube, as shown in FIG.
The sacrificial corrosive material (for example, Al-
An aluminum bare material provided with 1.5 wt% Zn) 23 can be used. The plate thickness t of the aluminum thin plate material of the tube can be reduced to about 0.25 to 0.4 mm by the reinforcing action of the inner fin 20. The tube height h is 1.75 mm due to the thinned tube plate thickness t.
Can be as low as a degree. Inner fin 20
Is made of A3000 series aluminum bare material.

In order to join the tubes 2 to 5 and the inner fin 20, the brazing material (A40
No. 00 system) is applied as shown in FIG. That is, the aluminum thin plate material 2 that constitutes the tubes 2 to 5
Before the bending process of No. 4, the paste-like brazing material (A4000 series) 2 is applied to the inner side surfaces of both ends of the tube thin plate material 24.
4a and 24a are applied. Similarly, the inner fin 20
Before incorporating into the tube, the brazing filler metal (A4000 series) 20a on the corrugated top of the inner fin 20.
Apply.

By applying this brazing material, the tube thin plate material 2
It is possible to join the both end portions of 4 and the inner wall surface of the tube thin plate member 24 and the corrugated top portions of the inner fins 20 when integrally brazing the entire evaporator. If a single-sided clad material having an inner side surface clad with a brazing material is used as the material of the tube thin plate material 24, the above brazing material application becomes unnecessary. Alternatively, a double-sided clad material in which a brazing material is clad on both sides is used as the material of the inner fin 20, and it is not necessary to apply the brazing material to the corrugated top of the inner fin 20.

Next, FIG. 7 shows an example of a joint portion between the tank portions 8 to 13 and both ends of the tubes 2 to 5.
The flat surface of 13 is provided with tube insertion holes 26 into which both ends 25 of the tubes 2 to 5 are inserted. Here, in order to facilitate the insertion of the both end portions 25 of the tubes 2 to 5 into the hole 26, the both end portions 25 are formed in the shape shown in FIG.

That is, the enlarged end portion 27 of the tube joint portion shown in FIG. 6 (a) is deleted at both end portions 25 of the tube to form notches 27a so that both end portions 25 of the tube have a substantially oval shape. It is formed in a shape. This notch 27a
Serves as a positioning stopper when inserting both ends 25 of the tubes 2 to 5 into the tube insertion holes 26 of the tanks 8 to 13 as shown in FIG. Will be easier. Note that FIG.
In (e), of the tank portions 8 to 13, only a tank portion on one side before and after the air flow direction A is schematically illustrated.

Here, the insertion hole 26 has an elliptical shape corresponding to both end portions 25 of the tubes 2 to 5, and the burring has an elliptical ejection portion 26a (see FIG. 7) ejected to the outside of the tank. It has a shape. Thereby, the tank parts 8 to 1
The tank portions 8 to 13 and the tubes 2 to 5 can be joined by using the brazing material on the inner surface of No. 3.

As shown in FIG. 9, when the ejection portion 26a of the tube insertion hole 26 of the tank portion 8 to 13 is ejected to the inside of the tank, only the both ends 25 of the tubes 2 to 5 are brazed in the state of the tube alone. Is applied, and the tank portions 8 to 13 and the tubes 2 to 5 may be joined using this brazing material.

FIG. 10 shows a corrugated fin (outer fin) 19 joined to the outer surface of the tube, and a known louver 19a is cut and raised diagonally. The corrugated fins 19 are formed of A3000 series aluminum bare material, and after applying the brazing material 19b only to the corrugated tops which are the joining (brazing) points with the tubes, the corrugated fins 19 and the tubes 2 to 5 are formed. Assemble.

FIG. 11 exemplifies the assembling structure of the partition plates 14 and 15. In this example, in order to simplify the assembling, 2
The two partition plates 14 and 15 are integrally formed by a single plate material 27. As an example of the material of the plate material 27 (partition plates 14 and 15), a double-sided clad material in which a brazing material (A4000 series) is clad on both surfaces of a core material (A3000 series) is used.

The plate member 27 has a slit groove 27a which fits into the partition wall 16 between the tanks 11 and 13 and the tanks 8 and 10.
Is formed. On the other hand, partition plates 14 and 1 are provided between the tanks 11 and 13 and between the tanks 8 and 10, respectively.
5, slit grooves 28 and 29 for insertion are formed. By inserting the partition plates 14 and 15 into the slit grooves 28 and 29 while fitting the slit groove 27a into the partition wall 16, the partition plate 14 is formed by using the brazing material on both sides of the plate material 27 and the brazing material inside the tank. , 15 are brazed to the tanks 10 to 13 to partition the space between the tanks 11 and 13 and the space between the tanks 8 and 10, respectively. In addition, the partition plate 14,
It goes without saying that the assembly and brazing described above may be performed by completely dividing 15 into two members.

FIG. 12 shows a lid member 30 for the tanks 8 to 13, and it shows three parts of the end portion in the tank longitudinal direction (left and right direction in FIG. 1) other than the portion where the refrigerant inlet 6 and the refrigerant outlet 7 are provided. The lid member 30 is arranged at the location. The lid member 30 is formed into a bowl shape by press-molding a single-sided clad material in which a brazing material is clad only on its inner surface. Then, the lid member 30 is fitted to the outer surface side of the tank longitudinal direction end, and the brazing material on the inner surface of the lid member 30 is used to cover the lid member 30.
Is brazed to the longitudinal end of the tank to close the opening at the longitudinal end of the tank.

Next, FIGS. 13 to 15 show an example of the structure of the pipe joint block portion. The lid member 31 of FIG.
Is joined to the end portion in the tank longitudinal direction similarly to the lid member 30 described above, and is formed by press molding a double-sided clad material in which a brazing material is clad on both sides. This lid member 31
As shown in FIG. 14, there is provided a refrigerant inlet 6 communicating with the tank portion 8 and a refrigerant outlet 7 communicating with the tank portion 13.

The intermediate plate member 32 is made of A3000 series bare material with no brazing material clad, and as shown in FIG. 15, an inlet side opening 32a communicating with the refrigerant inlet 6 and an outlet side communicating with the refrigerant outlet 7. Through the opening 32b,
In addition, the protruding portion 32c is slanted from the portion of the inlet side opening 32a
Is formed by extrusion.

The intermediate plate member 32 includes the joint body member 3
3 are joined. The joint main body member 33 is a single-sided clad material in which a brazing material is clad only on its inner surface. The joint body member 33 is provided with a semi-cylindrical passage forming portion 33a that covers the joint plate member 33 from the inlet side opening 32a of the intermediate plate member 32 to the tip of the protrusion 32c in a bowl shape. The tip of the passage forming portion 33a is formed. A connection port 33b is opened in the portion. Further, the joint cover member 33 has a cylindrical portion 33 communicating with the outlet side opening 32 b of the intermediate plate member 32.
c is formed so as to project from the plate surface.

The connection port 33b is connected to the outlet of the refrigerant whose pressure is reduced by the expansion valve, and the cylindrical portion 33c is connected to the inlet of the gas refrigerant temperature sensing portion of the expansion valve.

With the above configuration, the lid member 31, the intermediate plate portion
Brazing of material 32 and joint body member 33
And the tank parts 8 and 13 side
Piping pitch P between the refrigerant inlet 6 and the refrigerant outlet 7 of₁Compared to
The piping pitch P on the expansion valve side ₂If the
Pipe pitch P₁, P₂The structure that can absorb the deviation
You can

Next, FIGS. 16 (a), 16 (b) and 16 (c)
It illustrates three specific forms of the communication hole 18 described above. 16 (a), (b), (c) communication hole 18
Is a burring hole (hole shape with a punched-out portion) formed in the central partition portion (folded portion) 16 of the upper tank portions 10 and 11 formed by bending one thin aluminum plate material. Has been done.

FIG. 17 exemplifies a specific method of forming the communication hole 18. As shown in FIG. 17A, first, a thin aluminum plate forming the upper tank portions 8, 10, 11, 13 is formed. A burring hole 34a and a punching hole 34b having a size into which the punched-out portion of the burring hole 34a can be fitted are formed in the plate member 34 by press working.

Next, as shown in FIG. 17B, the portion where the burring hole 34a and the punching hole 34b are formed is U-shaped.
Fold it in a letter shape. Next, as shown in FIG.
The punched-out portion of the burring hole 34a is fitted into the punched hole 34b. Next, as shown in FIG. 17D, the tip of the punched-out portion of the burring hole 34a is caulked to the outer peripheral side.
As a result, it is possible to prevent the punched-out portion of the burring hole 34a from returning to the fitted state, and complete the formation of the communication hole 18.

FIG. 18 exemplifies the assembly structure of the first to sixth diaphragm plates 51 to 56. The lower tank portions 9 and 12 are provided with slit grooves 36 for inserting the diaphragm plates 51 to 56. It is formed at an arbitrary position. As an example of the material of each diaphragm plate 51 to 56, a brazing material (A4
A double-sided clad material clad with No. 000 series is used.
Then, by inserting the diaphragm plates 51 to 56 into the slit grooves 36 at predetermined positions, the brazing materials on both sides of the diaphragm plates 51 to 56 and the brazing material inside the tank are used to remove the diaphragm plates 51 to 56. The lower tank parts 9 and 12 are brazed.

The advantages of the above-described manufacturing method will be described below. Since the tank portions 8 to 13 are formed separately from the tubes 2 to 5 and then integrally joined, the thin plate member 34 constituting the tank portions 8 to 13 is formed. At the same time as increasing the plate thickness to increase the strength, for tubes 2-5, the plate thickness is made sufficiently thin, and the tubes 2-5 and corrugated fins 19 are miniaturized to reduce the size of the refrigerant evaporator. And higher performance can be achieved.

Since the tank parts 8 to 13 can be constructed by bending one thin aluminum plate 34, it is not necessary to attach a brazing material to the outer surface of the thin plate 34, and the corrosion resistance of the tank is improved. it can.

Also in the tubes 2 to 5, it is not necessary to attach a brazing material to the outer surface side, so that the corrosion resistance can be improved. Also, since no brazing material is attached to the outer surface of the tubes 2 to 5,
Formation of the surface treatment layer becomes good, and drainage is improved. Further, as the drainage property is improved, the effect of suppressing the generation of odor in the refrigerant evaporator is enhanced.

Since the brazing material is not attached to the corrugated fin portion 19 as well, the surface treatment layer can be formed well. As a result, similar to the above, the drainage property and the effect of suppressing the generation of odor can be improved.

(Second Embodiment) In the first embodiment, an example is shown in which the evaporator 1 is installed substantially vertically in the air conditioning unit case, but the evaporator 1 is tilted as in the second embodiment shown in FIG. (The tilt angle θ with respect to the horizontal line C is about 1
The present invention can be applied to 0 degree or more), and the same effect as that of the first embodiment can be obtained. The specific configuration of the evaporator 1 is the same as that of the first embodiment.

(Third Embodiment) FIG. 20 shows a third embodiment. In the first embodiment, the refrigerant inlet 6 and the refrigerant outlet 7 are shown.
Is arranged on the upper left side of the evaporator 1, whereas in the present embodiment, the refrigerant inlet 6 and the refrigerant outlet 7 are arranged on the lower left side. Specifically, the refrigerant inlet 6 is the lower inlet side tank. The left side of the portion 9 communicates with the refrigerant outlet 7, and the refrigerant outlet 7 communicates with the left side of the lower outlet side tank portion 12.

Due to the change in the arrangement of the refrigerant inlet 6 and the refrigerant outlet 7, the partition plates 14 and 15 are arranged in the lower tank portions 9 and 12, and the communication hole 18 is also formed in the lower partition wall 17. Further, in the present example, a diaphragm plate 51 is provided between the refrigerant inlet 6 and the partition plate 14 in the lower inlet tank portion 9.
One is installed.

According to the configuration of this embodiment, the refrigerant flowing from the refrigerant inlet 6 first flows into the lower tank portion 9 and is distributed to the tube 2, and flows upward in the tube 2 as indicated by an arrow m. It flows into the upper tank portion 8 and further reaches the tank portion 10. After that, the refrigerant is distributed to the tubes 3,
The tube 3 flows downward as shown by an arrow n and flows into the lower tank portion 9. Then, the refrigerant passes through the communication hole 18, moves from the refrigerant inlet side heat exchanger X to the refrigerant outlet side heat exchanger Y, and flows into the lower tank portion 12 on the air upstream side.

Next, the refrigerant from the lower tank portion 12 is distributed to the tube 5, flows upward in the tube 5 as indicated by an arrow o, flows into the upper tank portion 11, and further the tank portion 1
Up to 3. Next, the refrigerant is distributed to the tube 4, and the tube 4 flows downward as indicated by an arrow p. After a while,
The refrigerant from the tube 4 is collected in the lower tank portion 12 and flows out of the evaporator 1 from the refrigerant outlet 7.

Here, when the refrigerant is distributed to the tubes 4, a large amount of the liquid refrigerant flows into the tubes 4 on the right side of FIG. 20 due to gravity, and the distribution of the liquid refrigerant becomes uneven. Therefore, the liquid refrigerant distribution in the tube 2 is adjusted by the throttle holes 51a so that the liquid refrigerant distribution in the tube 2 located on the downstream side of the air flow of the tube 4 is opposite to the liquid refrigerant distribution in the tube 4. As a result, the temperature distribution of the air passing through the tubes 2 and 4 located before and after the air flow direction A can be made uniform.

On the other hand, when the refrigerant is distributed to the tubes 3, a large amount of the liquid refrigerant flows into the tubes 3 on the left side of FIG. 20 due to gravity, and the distribution of the liquid refrigerant becomes uneven. Therefore, by appropriately setting the opening area and the arrangement of the plurality of communication holes 18, the refrigerant distribution in the tube 5 is adjusted, and the tubes 3 located before and after the air flow direction A and the air passing through the tube 5 are adjusted. The temperature distribution can be made uniform.

(Other Embodiments) In the first embodiment,
The inlet side tank portion 9 and the outlet side tank portion 12 are each provided with three throttle holes 51a to 56a, but one throttle hole may be provided depending on the required refrigerant distribution characteristics.
There may be two or more. Further, the shapes of the aperture holes 51a to 56a can be set variously such as an ellipse and a rectangle.

In the first embodiment, the partition wall 1
The two tank portions 10 and 11 were communicated with each other through the communication hole 18 provided in No. 6, but instead of the communication hole 18, a member having a side refrigerant passage was added to the side surface of the evaporator (right side surface in FIG. 1). It is also possible to connect the two tank portions 10 and 11 with each other by the side refrigerant passage.

In the above embodiment, the refrigerant inlet side heat exchange section X may be arranged upstream of the air flow and the refrigerant outlet side heat exchange section Y may be arranged downstream of the air flow.

In the above embodiment, the heat exchange parts X and Y are used.
Are arranged in two rows in the air flow direction A, but the present invention is also applicable to a refrigerant evaporator in which the heat exchange sections X and Y are arranged in three or more rows in the air flow direction A.

[Brief description of drawings]

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

FIG. 2 is a schematic perspective view showing a lower tank portion of FIG.

FIG. 3 is a characteristic diagram comparing the outlet air temperatures of the tubes 4 of FIG.

4 is a diagram showing the relationship between the opening area ratio of the throttle holes in FIG. 1 and the cooling performance.

5 is a side view showing an end surface shape of the tank portion in FIG. 1. FIG.

6A is a cross-sectional view showing a cross-sectional shape of the tube of FIG. 1, FIG. 6B is an explanatory view of an example of a material of the tube, and FIG. 6C is an explanatory view of applying a brazing material to a tube constituent member.

7 is a cross-sectional view of a fitting portion between the tank portion and the tube in FIG.

8A is a plan view of the tube end portion of FIG. 1, FIG.
Is a front view of the tube end portion, (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 portion is inserted into the tank portion. It is a schematic explanatory drawing.

9 is a cross-sectional view showing another example of the fitting portion between the tank portion and the tube in FIG.

FIG. 10 is an explanatory diagram of applying a brazing material to the corrugated fins of FIG. 1.

11 is an enlarged perspective view of the partition plate portion of FIG. 1 in an exploded state.

FIG. 12 is a perspective view of a lid member of the tank portion of FIG.

13 is a perspective view of the pipe joint portion of FIG. 1. FIG.

FIG. 14 is a perspective view of a lid member in the pipe joint portion of FIG.

15A is a front view of the pipe joint portion of FIG. 13, FIG. 15B is a sectional view taken along line BB of FIG. 15A, and FIG. 15C is a front view of an intermediate plate member.

16 is a cross-sectional view of the communication hole portion of FIG.

FIG. 17 is a sectional view for explaining the method of forming the communication hole portion of FIG.

FIG. 18 is an exploded perspective view showing an assembly structure of the diaphragm plate of FIG. 2.

FIG. 19 is a perspective view showing an installed state of a refrigerant evaporator according to a second embodiment of the present invention.

FIG. 20 is a schematic perspective view showing a refrigerant passage structure of a refrigerant evaporator according to a third embodiment of the present invention.

FIG. 21 is a schematic perspective view showing a refrigerant passage structure of a conventional evaporator.

22 is a cross-sectional view of the evaporator of FIG. 21.

[Explanation of symbols]

2 to 5 ... Tube, 6 ... Refrigerant inlet, 7 ... Refrigerant outlet, 8 ...
13 ... Tank part, 9b, 12b ... Distribution tank part, 51
a to 56a ... A diaphragm hole.

Continuation of the front page (56) Reference JP-A-5-346297 (JP, A) JP-A-7-305990 (JP, A) JP-A-5-223490 (JP, A) JP-A-3-247993 (JP , A) JP-A-10-170098 (JP, A) JP-A-11-287587 (JP, A) JP-A-63-3153 (JP, A) Fukukaihei 4-3274 (JP, U) Utility model registration 2518259 (JP, Y2) (58) Fields surveyed (Int.Cl. ⁷ , DB name) B60H 1/32 613 F28F 9/02 301 F28F 9/00 F25B 39/02 F28D 1/00 F28F 9/02

Claims (5)

(57) [Claims] 1. Tubes (2-5) for flowing a refrigerant
Are arranged in parallel in a direction orthogonal to the flow direction (A) of the external fluid with the refrigerant flow direction being up and down, and the tubes (2 to 5) are arranged in a plurality of rows in the flow direction (A) of the external fluid, A tank part (8) for distributing the refrigerant to the tubes (2-5) or collecting the refrigerant from the tubes (2-5).
To 13) on both upper and lower ends of the tube (2 to 5),
Corresponding to the plurality of rows of tubes (2-5), a plurality of rows are arranged in the flow direction (A) of the external fluid, and are arranged on either the upstream side or the downstream side of the flow direction (A) of the external fluid. The refrigerant inlet (6) is arranged in the tank portion (8 to 10), and the tank portion (11 to 13) is arranged on either the upstream side or the downstream side in the flow direction (A) of the external fluid. A refrigerant outlet (7) is arranged, the tubes (2-5) and the tank part (8-1).
3) In the refrigerant channel formed inside, the refrigerant turns in a direction orthogonal to the flow direction (A) of the external fluid, and this turn direction is on the upstream side of the flow direction (A) of the external fluid. The refrigerant flow path and the downstream refrigerant flow path are arranged in opposite directions, and after the refrigerant has passed through all the refrigerant flow paths of the row in which the refrigerant inlet (6) is arranged, the flow of the external fluid A tank section (8) configured to sequentially pass through the refrigerant passages in a row adjacent to the direction (A) to reach the refrigerant outlet (7) and is adjacent to the external fluid flow direction (A).
The partition walls (16, 17) that divide the space between
The communication hole (18) that connects the tank parts (8 to 13) is
Plural units are arranged in the direction orthogonal to the flow direction (A) of the external fluid.
And the tank arranged on the lower end side of the tubes (2 to 5)
In the portion (9, 12), the collecting portion (9a, 12) of the downflow refrigerant is
a) and the distribution part (9b, 12b) of the upflow refrigerant are formed.
And the collecting part (9a, 12a) and the distributing part.
From the vicinity of the boundary with (9b, 12b) to the refrigerant flow downstream side
Toward the throttle passage for narrowing the refrigerant flow passage at a predetermined interval.
A plurality of (51a to 56a) are provided, and are on the lower end side of the tubes (2 to 5) and on the refrigerant flow downstream side.
In the tank part (12) arranged in
Arranged and throttle unit opening area of (54a), said tubing
Before the lower end of (2-5) and the upstream side of the refrigerant flow
The throttle section arranged on the most downstream side in the tank section (9)
A refrigerant evaporator having a larger opening area than (53a) . 2. In the tank section (11-13),
The refrigerant evaporator according to claim 1, wherein the refrigerant inlet (6) and the refrigerant outlet (7) are arranged at one end on the one side in the direction orthogonal to the flow direction (A) of the external fluid. 3. A refrigerant evaporator according to claim 1 or 2, wherein the tank portion of the refrigerant flow upstream of the tank portion disposed at the lower end side (9, 12) of the tube (2-5) (9 )
The opening area of the narrowed portions (51a to 53a) provided in
Of the tank parts (9, 12) arranged on the lower end side of the tubes (2 to 5), the tank part (1
The refrigerant evaporator is characterized in that the opening area of the throttle portions (54a to 56a) provided in 2) is made smaller. 4. The refrigerant evaporator according to claim 1 , wherein the plurality of throttle portions (51a to 53a, 54a to 56).
A refrigerant evaporator characterized in that the opening area of a) is made smaller toward the downstream side of the refrigerant flow. Wherein said tank portions and tube (2-5) and (8-13), in any one of the four claims 1, characterized in that joining together after separately formed Refrigerant evaporator described.