JPH08136182A - Heat exchanger - Google Patents

Abstract

PURPOSE: To provide a heat exchanger in which efficient heat exchanging is conducted by making uniform the state of refrigerant flowing in a heat exchanging pipe. CONSTITUTION: In a heat exchanger 15, a plurality of heat exchanging pipes 18 are installed at a predetermined interval oppositely between a pair of first and second headers 16 and 17, and a radiating material 19 having pin fins 20 is assembled with the pipes 18. A partition plate 21 for partitioning the header 16 into upper and lower parts 16a, 16b is provided on the way of the header 16 to feed refrigerant in a zigzag manner in the exchanger 15, first to third recesses 25 to 27 recessed in the headers 16, 17 are provided at the headers 16, 17 to mix the refrigerants of various states near the recesses 25 to 27.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger used for, for example, an air conditioner (hereinafter referred to as "air conditioner").

[0002]

2. Description of the Related Art Conventionally, there is a corrugated fin type heat exchanger 1 shown in FIG. 5 as a condenser used in, for example, an air conditioner of an automobile. The heat exchanger 1 is provided with the first and second cylindrical headers 2 and 3 which are erected in a state where the upper end and the lower end are closed, and the first and the second headers which are arranged in parallel in the vertical direction at a predetermined interval. The heat exchange pipes 4 are provided between the second headers and communicate with each other, and the wavy fins 5 (corrugated fins) are interposed between the heat exchange pipes 4 that are vertically adjacent to each other.

At the upper end of the first header 2 is a refrigerant inlet pipe 6
Are connected, and the refrigerant outlet pipe 7 is connected to the lower end. Then, partition plates 9, 10 and 11 are provided at appropriate places in the first header 2 and the second header 3, and the refrigerant meanders as shown by an arrow (a) indicated by a dashed line in the figure. It is configured to flow like a stream.

The refrigerant thus flows through the heat exchange pipes 4 through the first and second headers 2 and 3 so that heat is exchanged between the refrigerant and the outside air that hits the fins 5, and the refrigerant flows. According to this, it is condensed.

[0005]

By the way, the temperature of the above-mentioned refrigerant gradually decreases while flowing through the heat exchange pipe 4, and finally reaches the condensation temperature to become a liquid refrigerant.
However, the state of the refrigerant flowing through the heat exchange pipe 4 is not uniform, and there are gas refrigerant regions and liquid refrigerant regions. If the refrigerant in the two states is not mixed well, the liquid refrigerant flows downward into the headers 2 and 3 and drops downward, and collects at the lower ends of the headers 2 and 3. In this state, only the liquid refrigerant flows and the gas refrigerant no longer flows in the heat exchange pipe located at the lowermost end.

Since the liquid refrigerant is sufficiently low in temperature, the heat exchange pipe located at the lowermost end does not function effectively for heat exchange. Therefore, in such a state, the heat exchange pipe provided at this position is wasted in terms of size.

Further, the heat exchange must be performed by the heat exchange pipes other than the heat exchange pipe located at the lowermost end, which causes a decrease in the performance of the heat exchanger. Therefore, in order to eliminate such a state, it is necessary to mix the liquid refrigerant and the gas refrigerant in the header. Conventionally, there was an idea to perform such mixing, but by inserting a component for mixing the refrigerant in this header and brazing,
It had a complicated structure and was difficult to assemble. Further, there is a possibility that the flow in the header is unnecessarily obstructed and the performance of the heat exchanger is deteriorated.

The present invention has been made in view of the above circumstances, and an object thereof is to provide a heat exchanger that can make the state of the refrigerant flowing in the heat exchange pipe uniform and perform efficient heat exchange. To do.

[0009]

The first means of the present invention comprises a pair of headers in which a refrigerant flows, and a plurality of headers installed between the headers, in which the refrigerant branched from the pair of headers flows. In a heat exchanger having a heat exchange pipe and a radiating fin interposed between the heat exchange pipes, the header has a cylindrical shape, and a peripheral wall thereof has a recessed portion that is recessed inward of the header. Is a heat exchanger.

A second means is the heat exchanger of the first means, characterized in that the header is bent at a portion where the recess is formed. A third means is the heat exchanger of the second means, wherein the concave portion is formed so as to close the inside of the header when the header is bent at the portion where the concave portion is formed. It is a heat exchanger characterized by including. A fourth means is the heat exchanger according to the first means, characterized in that the concave portion includes one formed so as to close the inside of the header.

[0011]

According to this structure, the flow of the refrigerant in the header is disturbed by the recesses, and the refrigerant in various states can be mixed. Further, the header can be bent at the portion where the recess is formed. Further, the inside of the header can be partitioned by forming the recess so as to close the header.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. First, a first embodiment will be described. The heat exchanger 15 of this embodiment is a pin fin type heat exchanger.

That is, as shown in FIG. 1, the heat exchanger 15 includes first and second headers 16 and 17 which are provided upright.
And a plurality of heat exchange pipes 18 laid between the first and second headers 16 and 17, and the heat exchange pipes 18 stacked at a predetermined interval and having the longitudinal direction orthogonal to the heat exchange pipes 18. A plurality of heat dissipating members 19 combined with the exchange pipe 18 are provided, and the heat dissipating member 19 is punched out at predetermined intervals to form a large number of pin-shaped fins 2.
It is a heat exchanger formed with 0 (pin fins).

The pin fin 20 has a cross sectional shape of 0.
The pin fins 20 are formed so as to have a minute shape of 2 mm × 0.2 mm, and the adjacent pin fins 20 have an interval of about 0.2 mm. When the cross section of this heat exchanger is taken, the pin fins 20 are arranged in a matrix.

According to the heat exchanger having the pin fins 20 as described above, the heat exchange efficiency is very high as compared with the conventional plate fin type heat exchanger and the corrugated fin type heat exchanger described in the section of the conventional example. It is generally known to be expensive.

On the other hand, the inside of the first header 16 is partitioned by a partition plate shown in FIG. 21 to be divided into two regions, an upper part 16a and a lower part 16b. The refrigerant inlet pipe 22 is connected to the upper portion 16a of the first header 16 and the refrigerant outlet pipe 23 is connected to the lower portion 16b.

Therefore, as shown in FIG. 2, the refrigerant flowing through the heat exchanger 15 flows from the refrigerant inlet pipe 22 into the upper portion 16a of the first header 16 as shown in FIG. The heat is divided into the heat exchange pipes 18 (three heat exchange pipes 18 in this embodiment) connected to the upper portion 16a.

The refrigerant having passed through the heat exchange pipes 18 flows into the second header 17 and splits into the heat exchange pipes 18 located below the second header 17. The refrigerant that has passed through the heat exchange pipe 18 is the first header 16 described above.
Flowing into the lower portion 16a, becomes a liquid refrigerant, and is discharged to the outside (for example, the fluid compressor side) from the refrigerant outlet pipe 23.

By flowing in the heat exchanger 15 in a meandering manner, the refrigerant exchanges heat with the outside air that collides with the pin fins 20 attached to the heat exchange pipe 18, and flows. As the temperature rises, the temperature lowers and gradually condenses, and the state changes from a gas refrigerant to a liquid refrigerant.

Further, the first and second headers 16 and 17 are also provided.
In addition, as shown in FIGS. 1 and 2, the first to third recesses (recesses) inwardly of the headers 16 and 17 are formed on the peripheral wall thereof.
The recesses 25 to 27 are formed. The first to third recesses 25 to 27 have a function of narrowing the flow passages of the headers 16 and 17 and restricting the flow of the refrigerant.

The recesses 25 to 27 are formed by pressing. For example, it may be formed by pressing a V-shaped or semicircular convex mold against the side surface of a cylindrical header material made of aluminum.

Further, a rod-shaped lower mold having a concave cavity is inserted into the header material, and then a convex upper mold is formed on a portion of the peripheral wall of the header material corresponding to the lower mold cavity. Press. As a result, the recesses 25 to 27 may be formed on the peripheral wall of the header material.

It should be noted that such processing may be performed by air pressure instead of the die. Further, the recesses 25 to 27 may be formed by bending the header material once and returning it to the original state.

Next, the effect of the first to third recesses 25 to 27 will be described. As shown in FIG. 2, the recesses 25 to 27 serve as a flow resistance in the headers 16 and 17 to regulate the flow of the refrigerant, thereby causing the headers 16 and 17 to flow.
It has a role of mixing the refrigerants in various states that flow in or out to make the state of the refrigerant uniform.

That is, when the second and third recesses 26 and 27 are not formed in the second header 27, various states of refrigerant (gas refrigerant) flowing into the second header 17 are obtained. , Liquid refrigerant) flows straight in the lower direction of the second header 17 without being mixed with each other.

In the second header 17, the liquid refrigerant and the gas refrigerant may be separated, and the liquid refrigerant may be accumulated in the lower portion of the second header 17. When such a phenomenon occurs, the heat exchange pipe 1 located at the bottom end
Only the liquid refrigerant flows through 8, and the heat exchange pipe 18 does not function for heat exchange.

On the other hand, when the first and second recesses 25 and 26 are provided in the second header 17 as in the present invention, the flow of the refrigerant in the second header 17 is restricted. To be done. As a result, the flow of the refrigerant flowing in from each heat exchange pipe 18 is disturbed, and the refrigerant in various states is mixed in the vicinity of the recesses 25 and 26.

As a result, it is less likely that the gas refrigerant and the liquid refrigerant are separated and accumulated at the bottom of the header 17, so that all the heat exchange pipes 18 can be effectively used.

In other words, all heat exchange pipes 18
Can be effectively contributed to the heat exchange, so that the heat exchange performance of the heat exchanger 15 is improved. Also,
As described above, since the recesses 25 to 27 can be formed by press working, for example, a component such as the partition plate 21 is inserted into the heat exchanger 15 for brazing, or the header 16 is used. , 17 are provided outside the slits, and there is an effect that the manufacture thereof can be easily performed as compared with the case where parts for mixing are inserted into the headers 16 and 17 through the slits.

Further, there is an effect that the design can be easily changed. For example, in the first embodiment, the recesses 25-2
Although 7 has a conical shape that is pointed toward the inside of the headers 16 and 17, it may be a hemispherical shape or a cubic shape, and the mixing of the refrigerant is best depending on the size of the heat exchanger 15. It may be formed into a shape that can be performed.

Further, the number and arrangement of the recesses 25 to 27 may be determined by selecting a combination of the number and arrangement in which the refrigerant can be mixed efficiently and reliably.

Further, in the case of press working, welding is unnecessary, and since it is not necessary to provide a cut or the like in the headers 16 and 17, there is no fear of leakage of the refrigerant.

Next, a second embodiment of the present invention will be described. The same components as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted. The heat exchanger of the second embodiment is the above-described pin fin type heat exchanger, and as shown in FIG. 3, the first and second headers 16 'and 17' are A, B, and The heat exchanger 15 'is bent at three points, and the entire heat exchanger 15' is bent at these three points.

Next, a method of manufacturing this heat exchanger will be described. First, the first header 16 'is molded. As shown in FIG. 4 (a), the first header 16 'is formed by forming V-shaped valley-shaped first to third concave portions on the bent portions A to C of the header 16' by pressing. 30a, 31
a and 32a are provided. At this time, as for the second concave portion 30b provided in the part B, as shown in FIG. 4A, the projecting end portion of the concave portion 30b which protrudes into the header 16 'is formed on the inner wall surface of the header 16' which faces. Mold so that they abut. As for the other portions A and C, as shown in the drawing, the depths of the recesses 31a and 32c are set so as not to be too large.

Then, the first header 16 'is replaced by A to C.
When bent at each part of the above, the first to third recesses 30a,
Side walls 31a and 32a are joined to each other to form plate-shaped first to third projecting portions 34a, 35a and 36a which project into the first header 16 'as shown in FIG. In addition, the protruding portion 35a provided in the part B is the header 1
Completely occlude 6.

The protruding portion 35a provided at this portion B is
The inside of the first header 16 'is divided into an upper portion 16a and a lower portion 16b. Therefore, since it plays the same role as the partition plate 21 provided in the first header 16 of the first embodiment, it will be referred to as "partition plate 35a" hereinafter.

Next, the second header 17 'is molded. This second header 17 'is formed by molding the first header 16 described above.
The procedure is almost the same as that for ´. That is, as shown in FIG. 4B, the first to third recesses 30b, 31b, 32 are provided at the positions corresponding to the portions A to C on the side surface of the second header 17 '.
b is provided, and the header 17 'is bent at the concave portions 30b, 31b, 32b. As a result, each of the recesses 30b, 31b, 32b is, as shown in FIG.
Similar to the first header 16 ', the first to third protrusions 34b, 35b, 36b are formed.

However, the recesses 30b, 31b, 32b provided in the second header 17 'are the same as those in the first header 16 described above.
4 ', the second recesses 3 of the first header 16' are all provided at substantially the same depth as shown in FIG. 4B.
It is ensured that the inwardly protruding end portion does not come into contact with the inner wall surface of the header 17 'as in 1a.

Therefore, the first to third protrusions 34b, 35b and 36 formed on the second header 17 'are formed.
None of these b blocks the header 17 '. Next, a plurality of heat exchange pipes 18 are installed between the first and second headers 16 'and 17'. Then, the heat radiating material 19 formed with the pin fins 20 is attached to the heat exchange pipe 18. The heat dissipating member 19 is not a long member as in the first embodiment, but is a bent portion AC.
It is cut and divided into strips at the portion corresponding to.

According to such a heat exchanger 15 ', the first
The header 16 'is divided into an upper portion 16a and a lower portion 16b by the partition plate 35a, as in the first embodiment. In addition, the first and second headers 16 'and 17'
Inside is a protrusion 34a, 36a, 34b, 35b, 36b which has the same function as the recesses 25 to 27 of the first embodiment.
Is provided.

Therefore, the refrigerant supplied into the first header 16 'through the refrigerant inlet pipe 22 is transferred from the upper portion 16a of the first header 16' to the heat exchange pipe 1 '.
8 into the second header 17 ', then from the second header 17' through the heat exchange pipe 18 into the lower portion 16b of the first header 16 ', It is designed to be discharged from the outlet pipe 23 to the outside.

Then, the first and second headers 16 ',
Since the protrusions 34a to 36b are provided inside 17 ', the refrigerants (gas refrigerant, liquid refrigerant) in various states are mixed in the vicinity of the protrusions 34a to 36b, and the inside of the heat exchange pipe 18 is provided. Therefore, the refrigerant in a uniform state is split.

Therefore, according to the second embodiment, the same effect as that of the first embodiment can be obtained. Further, in the first embodiment, the partition plate 21 is formed by inserting a disc-shaped component into the first header and brazing it, but in the second embodiment, the partition plate 21 is formed by brazing. The partition plate 35a can be formed only by providing the header 16 'with the concave portion 31a and bending at this portion. Therefore, there is an effect that the partition plate 35a can be easily formed.

Since the recesses 30a to 32a are present, the headers 16 'and 17' can be easily bent, and the heat exchanger 15 'is manufactured by bending the headers 16' and 17 'in this manner. There is an effect that can be easily performed. Further, each of the projecting portions 34a to 36b formed in a plate shape by bending is the header 16 ', 17'.
Since it serves as a reinforcing member, the strength of the headers 16 'and 17' is also improved.

The present invention is not limited to the above-mentioned embodiment, but can be variously modified without changing the gist of the invention. In the first and second embodiments, the case where the heat exchangers 15 and 15 'are used as condensers has been described, but they may be used as evaporators. Even in this case, since the liquid refrigerant and the gas refrigerant can be mixed, there is an effect that the heat exchange efficiency is improved.

Further, in the second embodiment, the recesses 30a, 31a, 32a and 30b, 31b, 32b are provided on the side surfaces of the headers 16 ', 17', and the portions are bent. It is not limited to this,
Since the amount of protrusion into the header may be small except for the portion to be the partition plate 35a, the headers 16 'and 17' may be bent without providing the above-described recess.

Further, in the above-mentioned one embodiment, the heat exchanger 1
Although 5 and 15 'were pin fin type heat exchangers, the present invention is not limited to this and may be a plate fin type heat exchanger or a corrugated fin type heat exchanger as long as it uses a header. Can be applied.

[0048]

As described above, according to the first structure of the present invention, a pair of headers in which a refrigerant flows, and a plurality of headers installed between the headers, in which the refrigerant branched from the pair of headers flow, are provided. In a heat exchanger having a book heat exchange pipe and a radiation fin interposed between the heat exchange pipes,
The header has a cylindrical shape, and a peripheral wall thereof is provided with a recessed portion which is recessed inward of the header.

According to this structure, since the refrigerants in various states flowing in the header can be mixed in the vicinity of the recess, it is possible to prevent only the liquid refrigerant from separating, and the entire heat exchanger can be prevented. It can function effectively. Therefore, there is an effect that a heat exchanger with high heat exchange performance can be obtained.

The recess can be formed by, for example, press working, and operations such as forming a hole in the header and welding are unnecessary. Therefore, there is an effect that the header having the above effect can be easily formed.

Further, there is an effect that the design can be easily changed. A second means is the heat exchanger of the first means, characterized in that the header is bent at a portion where the recess is formed.

By using the recesses, it is possible to mix the refrigerants, and it is possible to easily bend the header due to the presence of the recesses. The third means is
In the heat exchanger of the second means, the concave portion includes one formed so as to close the header when the header is bent at the portion where the concave portion is formed. It is a heat exchanger.

In order to cause the refrigerant to meander in the heat exchanger, the inside of the header is divided by a partition plate. According to the third means, the work of bending the partition plate into the header is performed. Only by doing so, there is an effect that it can be easily formed without performing work such as welding.

A fourth means is a heat exchanger according to the first means, characterized in that the concave portion includes one formed so as to close the inside of the header. According to such a configuration, since the inside of the header can be partitioned by the recess without performing a work such as inserting a disk into the header and welding, there is an effect that the header can be easily molded. is there.

[Brief description of drawings]

FIG. 1 is an overall perspective view showing a first embodiment of the present invention.

FIG. 2 is a schematic vertical sectional view showing the same in a simplified manner.

FIG. 3 is a front view and a vertical sectional view showing a second embodiment.

FIG. 4 is a vertical sectional view showing molding of the header.

FIG. 5 is a front view showing a general corrugated heat exchanger.

[Explanation of symbols]

15 ... Heat exchanger (first embodiment), 16 ... First header, 17 ... Second header, 18 ... Heat exchange pipe, 19 ...
Heat dissipation material, 20 ... Pin fins, 25 ... First recesses, 26 ...
2nd recessed part, 27 ... 3rd recessed part, 15 '... Heat exchanger (2nd Example), 16' ... 1st header, 17 '... 2nd header, 31a (35a) ... 2nd Recessed part (protruding part, partition plate).

Claims (4)

[Claims] 1. A pair of headers, through which a refrigerant flows, and a plurality of heat exchange pipes, which are installed between the headers and through which the refrigerant branched from the pair of headers flows, and are interposed between the heat exchange pipes. A heat exchanger having a heat radiating fin, wherein the header has a cylindrical shape, and a peripheral wall of the header has a recessed portion that is recessed inward of the header. 2. The heat exchanger according to claim 1, wherein the header is bent at a portion where the recess is formed. 3. The heat exchanger according to claim 2, wherein the recess is formed so as to close the inside of the header when the header is bent at a portion where the recess is formed. A heat exchanger characterized by including. 4. The heat exchanger according to claim 1, wherein the recess includes one formed so as to close the inside of the header.